JP6061578B2 - Friction drive device and geared motor - Google Patents

Friction drive device and geared motor Download PDF

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JP6061578B2
JP6061578B2 JP2012202918A JP2012202918A JP6061578B2 JP 6061578 B2 JP6061578 B2 JP 6061578B2 JP 2012202918 A JP2012202918 A JP 2012202918A JP 2012202918 A JP2012202918 A JP 2012202918A JP 6061578 B2 JP6061578 B2 JP 6061578B2
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plate
drive device
friction drive
hole
inner peripheral
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JP2014058993A5 (en
JP2014058993A (en
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五明 正人
五明  正人
健太郎 奥原
健太郎 奥原
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Nidec Sankyo Corp
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Priority to CN201310360115.7A priority patent/CN103671781B/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02KDYNAMO-ELECTRIC MACHINES
    • H02K7/00Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/02Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02KDYNAMO-ELECTRIC MACHINES
    • H02K15/00Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines
    • H02K15/14Casings; Enclosures; Supports
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02KDYNAMO-ELECTRIC MACHINES
    • H02K7/00Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/108Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Transmission Devices (AREA)
  • Mechanical Operated Clutches (AREA)

Description

本発明は、フリクション機構を備えたフリクションドライブ装置、および当該フリクションドライブ装置を備えたギヤードモータに関するものである。   The present invention relates to a friction drive device including a friction mechanism, and a geared motor including the friction drive device.

モータの回転を歯車を介して伝達する際、従動側に過大な負荷が加わると、歯車が損傷する等の問題が発生する。そこで、2つの回転部材の間に摩擦により動力を伝達するフリクション機構を設けておき、過大な負荷が加わった際、2つの回転部材が空回りをする構成が提案されている(特許文献1参照)。   When transmitting the rotation of the motor via the gear, if an excessive load is applied to the driven side, problems such as damage to the gear occur. Therefore, a configuration has been proposed in which a friction mechanism for transmitting power by friction is provided between the two rotating members, and when the excessive load is applied, the two rotating members are idle (see Patent Document 1). .

例えば、図9(a)に示す参考例に係るフリクションドライブ装置1xは、軸線方向Lの途中部分に止められた環状部材3xによって軸線方向Lの一方側L1に向く支持面31xが設けられた回転軸2xと、支持面31xより一方側L1で回転軸2xに回転可能に嵌められて支持面31xに接する筒状回転部材4xと、回転軸2xにおいて筒状回転部材4xより一方側L1に位置する連結軸部23xに嵌められた環状の板状付勢部材5xとを備えている。筒状回転部材4xにおいて、外周面には歯車45xが形成され、一方側L1の面には板状付勢部材5xに接する一方側凸部47xが形成され、他方側L2の面には環状部材3xに接する他方側凸部49xが形成されている。連結軸部23xの外周面は、周方向の一部に平坦面23yが形成されており、図9(c)、(d)に示すように、連結軸部23xの外周形状、および板状付勢部材5xにおいて連結軸部23xが嵌る穴50xはいずれもD字形状を有している。このため、板状付勢部材5xは、回転軸2xに対して回り止めされており、回転軸2xと一体に回転する。また、板状付勢部材5xを回転軸2xに対して固定するには、図9(b)に示すように、回転軸2xに環状部材3x、筒状回転部材4xおよび板状付勢部材5xを嵌めた後、プレスによる加締めを行って、連結軸部23xにおいて板状付勢部材5xより一方側L1に位置する部分を他方側L2に向けて塑性変形させる。その結果、図9(a)に示すように、板状付勢部材5xは、連結軸部23xの変形部分23zにより内周部分が他方側L2に押圧される結果、径方向外側に位置する部分が筒状回転部材4xの一方側凸部47xに弾性をもって接することになる。従って、回転軸2xが回転した際、かかる回転は、板状付勢部材5xと筒状回転部材4xとの間の摩擦力、および環状部材3xと筒状回転部材4xとの間の摩擦力によって、筒状回転部材4xに伝達されるので、筒状回転部材4xが回転する。これに対して、筒状回転部材4xの側に過大な負荷が加わった際には、板状付勢部材5xと筒状回転部材4xとの間、および環状部材3xと筒状回転部材4xとの間に空回りが発生するので、動力の伝達が遮断される。このため、筒状回転部材4xの側に過大な負荷が加わったときでも、歯車の損傷を防止することができる。   For example, in the friction drive device 1x according to the reference example shown in FIG. 9A, the rotation surface provided with the support surface 31x facing the one side L1 in the axial direction L is provided by the annular member 3x stopped in the middle portion in the axial direction L. The shaft 2x, a cylindrical rotating member 4x that is rotatably fitted to the rotating shaft 2x on one side L1 from the support surface 31x and is in contact with the supporting surface 31x, and the rotating shaft 2x is positioned on one side L1 from the cylindrical rotating member 4x. And an annular plate-like biasing member 5x fitted to the connecting shaft portion 23x. In the cylindrical rotating member 4x, a gear 45x is formed on the outer peripheral surface, a one-side convex portion 47x in contact with the plate-like urging member 5x is formed on the surface of the one side L1, and an annular member is formed on the surface of the other side L2. The other side convex part 49x which touches 3x is formed. The outer peripheral surface of the connecting shaft portion 23x is formed with a flat surface 23y in a part of the circumferential direction. As shown in FIGS. 9C and 9D, the outer peripheral shape of the connecting shaft portion 23x and the plate shape are attached. Each of the holes 50x into which the connecting shaft portion 23x fits in the force member 5x has a D shape. For this reason, the plate-like urging member 5x is prevented from rotating with respect to the rotating shaft 2x and rotates integrally with the rotating shaft 2x. Further, in order to fix the plate-like urging member 5x to the rotating shaft 2x, as shown in FIG. 9B, the annular member 3x, the cylindrical rotating member 4x, and the plate-like urging member 5x are attached to the rotating shaft 2x. After fitting, crimping by pressing is performed to plastically deform a portion of the connecting shaft portion 23x located on the one side L1 from the plate-like urging member 5x toward the other side L2. As a result, as shown in FIG. 9 (a), the plate-like urging member 5x is a portion located on the radially outer side as a result of the inner peripheral portion being pressed against the other side L2 by the deformed portion 23z of the connecting shaft portion 23x. Will be elastically in contact with the one-side convex portion 47x of the cylindrical rotating member 4x. Therefore, when the rotating shaft 2x rotates, the rotation is caused by the frictional force between the plate-like biasing member 5x and the cylindrical rotating member 4x and the frictional force between the annular member 3x and the cylindrical rotating member 4x. Since this is transmitted to the cylindrical rotating member 4x, the cylindrical rotating member 4x rotates. On the other hand, when an excessive load is applied to the cylindrical rotating member 4x side, between the plate-like biasing member 5x and the cylindrical rotating member 4x, and between the annular member 3x and the cylindrical rotating member 4x, Since idling occurs during this period, power transmission is interrupted. For this reason, even when an excessive load is applied to the cylindrical rotating member 4x side, damage to the gears can be prevented.

特開平9−107658号公報の図8FIG. 8 of JP-A-9-107658.

しかしながら、連結軸部23xの外周形状、および板状付勢部材5xの穴50xをD字形状として、連結軸部23xにおいて板状付勢部材5xより一方側L1に位置する部分をプレスして塑性変形させる加締めでは、フリクショントルクのばらつきが大きいといった問題点、異音が発生しやすいといった問題点、歯車が損傷しやすいといった問題点がある。本願発明者による上記の問題点の検討の結果、連結軸部23xでは、平坦面23yが形成されている側にプレスの力が加わらないため、回転軸2xが、平坦面23yが形成されている側とは反対側に曲がってしまい、回転軸2xや筒状回転部材4xにブレや摺動圧のばらつきが発生してしまうという新たな知見を得た。また、かかるブレは、異音の発生や歯車の損傷の原因となるので、好ましくないことが判明した。なお、図9に示す構成は、本発明に対する参考例であり、従来例ではない。   However, the outer peripheral shape of the connecting shaft portion 23x and the hole 50x of the plate-like biasing member 5x are D-shaped, and a portion of the connecting shaft portion 23x located on one side L1 from the plate-like biasing member 5x is pressed to be plastic. In the caulking to be deformed, there are a problem that the variation of the friction torque is large, a problem that abnormal noise is likely to occur, and a problem that the gear is easily damaged. As a result of the examination of the above problems by the inventor of the present application, in the connecting shaft portion 23x, no pressing force is applied to the side on which the flat surface 23y is formed, so that the rotating shaft 2x is formed with the flat surface 23y. It was bent to the opposite side to the side, and a new finding was obtained that the rotation shaft 2x and the cylindrical rotation member 4x cause fluctuations and variations in sliding pressure. Further, it has been found that such blurring is undesirable because it causes abnormal noise and damages to gears. The configuration shown in FIG. 9 is a reference example for the present invention and is not a conventional example.

以上の問題点に鑑みて、本発明の課題は、回転軸の連結軸部に嵌めた板状付勢部材を、連結軸部を塑性変形させることにより固定した場合でも、回転軸に曲がりが発生しにくいフリクションドライブ装置、および当該フリクションドライブ装置を備えたギヤードモータを提供することにある。   In view of the above problems, the problem of the present invention is that even when the plate-like biasing member fitted to the connecting shaft portion of the rotating shaft is fixed by plastically deforming the connecting shaft portion, the rotating shaft is bent. It is an object of the present invention to provide a friction drive device that is difficult to perform, and a geared motor including the friction drive device.

上記課題を解決するために、本発明に係るフリクションドライブ装置は、軸線方向の途中部分で当該軸線方向の一方側に向く支持面が設けられた回転軸と、前記支持面より前記一方側で前記回転軸に回転可能に嵌められて前記支持面に接する筒状回転部材と、前記回転軸において前記筒状回転部材より前記一方側に位置する連結軸部に嵌められた環状の板状付勢部材と、を有し、前記連結軸部は、外側面が円形の丸棒状であり、前記板状付勢部材において前記連結軸部が嵌る穴の内周縁は、前記軸線に対して回転対称であり、当該穴の内周縁には、前記連結軸部の外周面からみて径方向外側に向けて凹んだ回り止め用の係合凹部が形成されており、前記筒状回転部材の前記一方側の面には、前記穴より径方向外側に前記板状付勢部材に接する一方側凸部が形成されており、前記連結軸部において前記板状付勢部材より前記一方側に位置する丸棒部分の外周面の全周を前記軸線方向の他方側に向けて塑性変形させた変形部分により、前記板状付勢部材の内周部分が前記他方側に押圧されて当該内周部分より径方向外側に位置する部分が前記筒状回転部材の前記一方側凸部に弾性をもって接しているとともに、前記変形部分のうち、前記係合凹部の内側に入り込んだ部分は、前記板状付勢部材の前記回転軸に対する回り止めとして機能していることを特徴とする。 In order to solve the above-described problem, a friction drive device according to the present invention includes a rotating shaft provided with a support surface facing in the axial direction at an intermediate portion in the axial direction, and the rotating shaft provided on the one side with respect to the support surface. A cylindrical rotating member that is rotatably fitted to a rotating shaft and is in contact with the support surface, and an annular plate-shaped biasing member that is fitted to a connecting shaft portion that is located on the one side of the rotating shaft with respect to the cylindrical rotating member. The connecting shaft portion has a round bar shape whose outer surface is circular, and the inner peripheral edge of the hole into which the connecting shaft portion fits in the plate-like biasing member is rotationally symmetric with respect to the axis. The inner peripheral edge of the hole is formed with a locking recess for rotation that is recessed radially outward as viewed from the outer peripheral surface of the connecting shaft portion, and the one surface of the cylindrical rotating member Is in contact with the plate-like biasing member radially outward from the hole. Square-side protrusion is formed, by plastically deforming the entire circumference of the outer circumferential surface of the round bar portion located on the one side than the plate-like urging member toward the other side of the axial direction in the connection shaft section Due to the deformed portion, the inner peripheral portion of the plate-like biasing member is pressed to the other side, and the portion positioned radially outward from the inner peripheral portion has elasticity on the one convex portion of the cylindrical rotating member. A portion of the deformed portion that enters the inside of the engagement recess functions as a detent for the rotation of the plate-like biasing member with respect to the rotation shaft .

本発明では、回転軸および筒状回転部材のうちの一方(駆動側部材)が回転した際、かかる回転は、板状付勢部材と筒状回転部材との間の摩擦力、および支持面と筒状回転部材との間の摩擦力によって、他方(従動側部材)に伝達されるので、他方が回転する。これに対して、従動側部材の側に過大な負荷が加わった際には、板状付勢部材と筒状回転部材との間、および支持面と筒状回転部材との間に空回りが発生するので、動力の伝達が遮断される。このため、従動側部材の側に過大な負荷が加わったときでも、駆動側部材や駆動側部材より駆動側に設けられた歯車等の損傷を防止することができる。また、板状付勢部材は、連結軸部において板状付勢部材より一方側に位置する部分の全周を他方側に向けて塑性変形させた変形部分により内周部分が他方側に押圧され、その結果、径方向外側に位置する部分が筒状回転部材に弾性をもって接している。かかる構造を実現するにあたって、連結軸部は、外側面が軸線に対して回転対称であるため、塑性変形させる際の力が周方向で偏って印加されることを防止することができる。従って、塑性変形させる際の力によって回転軸に曲がることを防止することができるので、回転軸や筒状回転部材にブレが発生しにくい。また、板状付勢部材において連結軸部が嵌る穴の内周縁は、回り止め用の係合部が形成されているが、穴の内周縁は軸線に回転対称の形状を有している。このため、連結軸部の塑性変形による変形部分によって板状付勢部材の内周縁を押圧した際、周方向で均等な力が確実に加わるので、板状付勢部材が傾きにくい。また、筒状回転部材の一方側の面には、穴より径方向外側に板状付勢部材に接する一方側凸部が形成されているため、筒状回転部材と板状付勢部材との接触面積や接触状態を安定した状態に設定することができる。従って、板状付勢部材と筒状回転部材との間の摩擦力を適正なレベルに安定させることができる。 In the present invention, when one of the rotating shaft and the cylindrical rotating member (drive-side member) rotates, the rotation is caused by the frictional force between the plate-like biasing member and the cylindrical rotating member, and the support surface . Since the frictional force between the cylindrical rotating member and the cylindrical rotating member is transmitted to the other (driven member), the other rotates. On the other hand, when an excessive load is applied to the driven side member, idle rotation occurs between the plate-like urging member and the cylindrical rotating member and between the support surface and the cylindrical rotating member. As a result, power transmission is interrupted. For this reason, even when an excessive load is applied to the driven side member, it is possible to prevent damage to the driving side member and the gear provided on the driving side from the driving side member. The plate-like urging member has its inner peripheral portion pressed to the other side by a deformed portion obtained by plastic deformation of the entire circumference of the portion located on one side of the plate-like urging member in the connecting shaft portion toward the other side. As a result, the portion located on the outer side in the radial direction is in elastic contact with the cylindrical rotating member. In realizing such a structure, since the outer surface of the connecting shaft portion is rotationally symmetric with respect to the axis, it is possible to prevent a force applied during plastic deformation from being biased in the circumferential direction. Accordingly, it is possible to prevent the rotating shaft from being bent by the force of plastic deformation, so that the rotating shaft and the cylindrical rotating member are less likely to be blurred. Further, the inner peripheral edge of the hole into which the connecting shaft portion fits in the plate-like urging member is formed with an engagement portion for preventing rotation, but the inner peripheral edge of the hole has a rotationally symmetric shape with respect to the axis. For this reason, when the inner peripheral edge of the plate-like urging member is pressed by a deformed portion due to plastic deformation of the connecting shaft portion, a uniform force is reliably applied in the circumferential direction, so that the plate-like urging member is not easily tilted. Moreover, since the one side convex part which contact | connects a plate-shaped biasing member in the radial direction outer side from a hole is formed in the surface of one side of a cylindrical rotating member, between a cylindrical rotating member and a plate-shaped biasing member The contact area and the contact state can be set to a stable state. Therefore, the frictional force between the plate-like urging member and the cylindrical rotating member can be stabilized at an appropriate level.

この場合、前記板状付勢部材の前記穴は、丸穴であって、内周縁に前記係合凹部が形成されていることが好ましい。かかる構成によれば、連結軸部の塑性変形による変形部分によって板状付勢部材の内周縁を押圧した際、周方向で均等な力が加わるので、板状付勢部材が傾きにくい。それ故、板状付勢部材と筒状回転部材との間の摩擦力を適正なレベルに安定させることができる。この場合、前記係合凹部は、周方向の複数個所に等角度間隔に形成されている構成を採用することができる。 In this case, it is preferable that the hole of the plate-like urging member is a round hole, and the engagement recess is formed on the inner peripheral edge. According to such a configuration, when the inner peripheral edge of the plate-like urging member is pressed by the deformed portion of the connecting shaft portion due to plastic deformation, a uniform force is applied in the circumferential direction, so that the plate-like urging member is not easily tilted. Therefore, the frictional force between the plate-like urging member and the cylindrical rotating member can be stabilized at an appropriate level. In this case, it is possible to adopt a configuration in which the engaging recesses are formed at equiangular intervals at a plurality of locations in the circumferential direction.

本発明において、前記係合凹部は、半円形状をもって前記穴の内周縁から径方向外側に凹んでいる態様を採用することができる。
この場合、前記係合凹部は、全体として、前記穴の内周縁の1/3に相当する角度範囲を占めるように複数形成されている態様を採用してもよい。
本発明において、前記係合凹部は、三角形状をもって前記穴の内周縁から径方向外側に凹んでいる態様を採用してもよい。
本発明において、前記穴および前記係合凹部は、多角形の穴を構成し、前記多角形の角によって前記係合凹部が形成されている態様を採用してもよい。この場合、前記多角形は正多角形であることが好ましい。
In the present invention, it is possible to adopt a mode in which the engaging concave portion has a semicircular shape and is recessed radially outward from the inner peripheral edge of the hole.
In this case, a mode may be adopted in which a plurality of engaging recesses are formed so as to occupy an angle range corresponding to 1/3 of the inner peripheral edge of the hole as a whole.
In the present invention, the engaging recess may have a triangular shape and is recessed radially outward from the inner periphery of the hole.
In this invention, the said hole and the said engagement recessed part may comprise a polygonal hole, and the aspect by which the said engagement recessed part is formed by the corner | angular of the said polygon may be employ | adopted. In this case, arbitrary preferred that the polygon is a regular polygon.

本発明において、前記筒状回転部材には、前記他方側に向けて突出して前記支持面に接する他方側凸部が前記回転軸の周りに形成されていることが好ましい。かかる構成によれば、筒状回転部材と環状部材との接触面積や接触状態を安定した状態に設定することができるので、筒状回転部材と環状部材との間の摩擦力を適正なレベルに安定させることができる。   In this invention, it is preferable that the other side convex part which protrudes toward the said other side and contacts the said support surface is formed in the said cylindrical rotation member around the said rotating shaft. According to such a configuration, the contact area and contact state between the cylindrical rotating member and the annular member can be set in a stable state, so that the frictional force between the cylindrical rotating member and the annular member is set to an appropriate level. It can be stabilized.

本発明において、前記支持面は、前記回転軸に嵌められた環状部材の前記一方側に向く面からなることが好ましい。かかる構成によれば、環状部材の表面を適正な状態にすれば、回転軸の表面粗さ等にかかわらず、筒状回転部材と環状部材との間の摩擦力を適正なレベルに安定させることができる。   In this invention, it is preferable that the said support surface consists of a surface which faces the said one side of the cyclic | annular member fitted by the said rotating shaft. According to this configuration, if the surface of the annular member is in an appropriate state, the frictional force between the cylindrical rotating member and the annular member can be stabilized at an appropriate level regardless of the surface roughness of the rotating shaft. Can do.

本発明に係るフリクションドライブ装置は、モータ部、および歯車列を備えたギヤードモータに用いられ、この場合、前記回転軸は、前記モータ部のモータ軸、または前記歯車列において前記モータ軸の回転が伝達される歯車と一体に回転する回転軸のうちの何れかである。   The friction drive device according to the present invention is used in a geared motor including a motor unit and a gear train. In this case, the rotation shaft is a motor shaft of the motor unit or the motor shaft rotates in the gear train. One of the rotating shafts that rotates integrally with the transmitted gear.

本発明では、回転軸および筒状回転部材のうちの一方(駆動側部材)が回転した際、かかる回転は、板状付勢部材と筒状回転部材との間の摩擦力、および支持面と筒状回転部材との間の摩擦力によって、他方(従動側部材)に伝達されるので、他方が回転する。これに対して、従動側部材の側に過大な負荷が加わった際には、板状付勢部材と筒状回転部材との間、および支持面と筒状回転部材との間に空回りが発生するので、動力の伝達が遮断される。このため、従動側部材の側に過大な負荷が加わったときでも、駆動側部材や駆動側部材より駆動側に設けられた歯車等の損傷を防止することができる。また、板状付勢部材は、連結軸部において板状付勢部材より一方側に位置する部分の全周を他方側に向けて塑性変形させた変形部分により内周部分が他方側に押圧され、その結果、径方向外側に位置する部分が筒状回転部材に弾性をもって接している。かかる構造を実現するにあたって、連結軸部は、外側面が軸線に対して回転対称であるため、塑性変形させる際の力が周方向で偏って印加されることを防止することができる。従って、塑性変形させる際の力によって回転軸に曲がることを防止することができるので、回転軸や筒状回転部材にブレが発生しにくい。また、板状付勢部材において連結軸部が嵌る穴の内周縁は、回り止め用の係合部が形成されているが、穴の内周縁は軸線に回転対称の形状を有している。このため、連結軸部の塑性変形による変形部分によって板状付勢部材の内周縁を押圧した際、周方向で均等な力が確実に加わるので、板状付勢部材が傾きにくい。 In the present invention, when one of the rotating shaft and the cylindrical rotating member (drive-side member) rotates, the rotation is caused by the frictional force between the plate-like biasing member and the cylindrical rotating member, and the support surface . Since the frictional force between the cylindrical rotating member and the cylindrical rotating member is transmitted to the other (driven member), the other rotates. On the other hand, when an excessive load is applied to the driven side member, idle rotation occurs between the plate-like urging member and the cylindrical rotating member and between the support surface and the cylindrical rotating member. As a result, power transmission is interrupted. For this reason, even when an excessive load is applied to the driven side member, it is possible to prevent damage to the driving side member and the gear provided on the driving side from the driving side member. The plate-like urging member has its inner peripheral portion pressed to the other side by a deformed portion obtained by plastic deformation of the entire circumference of the portion located on one side of the plate-like urging member in the connecting shaft portion toward the other side. As a result, the portion located on the outer side in the radial direction is in elastic contact with the cylindrical rotating member. In realizing such a structure, since the outer surface of the connecting shaft portion is rotationally symmetric with respect to the axis, it is possible to prevent a force applied during plastic deformation from being biased in the circumferential direction. Accordingly, it is possible to prevent the rotating shaft from being bent by the force of plastic deformation, so that the rotating shaft and the cylindrical rotating member are less likely to be blurred. Further, the inner peripheral edge of the hole into which the connecting shaft portion fits in the plate-like urging member is formed with an engagement portion for preventing rotation, but the inner peripheral edge of the hole has a rotationally symmetric shape with respect to the axis. For this reason, when the inner peripheral edge of the plate-like urging member is pressed by a deformed portion due to plastic deformation of the connecting shaft portion, a uniform force is reliably applied in the circumferential direction, so that the plate-like urging member is not easily tilted.

本発明を適用したフリクションドライブ装置の説明図である。It is explanatory drawing of the friction drive apparatus to which this invention is applied. 本発明を適用したフリクションドライブ装置に用いた各部材の説明図である。It is explanatory drawing of each member used for the friction drive apparatus to which this invention is applied. 本発明を適用したフリクションドライブ装置に用いられる各種板状付勢部材の平面図である。It is a top view of the various plate-shaped urging members used for the friction drive device to which the present invention is applied. 本発明を適用したフリクションドライブ装置における板状付勢部材の反り量と回転軸の先端の振れ量との関係を評価した結果のグラフである。It is a graph of the result of having evaluated the relationship between the curvature amount of the plate-shaped biasing member in the friction drive device to which this invention is applied, and the deflection amount of the front-end | tip of a rotating shaft. 本発明を適用したフリクションドライブ装置における板状付勢部材の反り量と静フリクショントルクとを評価した結果のグラフである。It is a graph of the result of having evaluated the curvature amount and static friction torque of the plate-shaped urging member in the friction drive device to which the present invention is applied. 本発明を適用したフリクションドライブ装置における板状付勢部材の反り量と動フリクショントルクとを評価した結果のグラフである。It is a graph of the result of having evaluated the curvature amount and dynamic friction torque of the plate-shaped urging member in the friction drive device to which the present invention is applied. 本発明を適用したフリクションドライブ装置の信頼性を評価した結果のグラフである。It is a graph of the result of having evaluated the reliability of the friction drive device to which the present invention is applied. 本発明を適用したフリクションドライブ装置が搭載されるギヤードモータの説明図である。It is explanatory drawing of the geared motor by which the friction drive device to which this invention is applied is mounted. 本発明の参考例に係るフリクションドライブ装置の説明図である。It is explanatory drawing of the friction drive apparatus which concerns on the reference example of this invention.

図面を参照して、本発明を適用したフリクションドライブ装置を説明する。本発明を適用したフリクションドライブ装置では、回転軸と筒状回転部材との間で動力の伝達を行なう際、回転軸および筒状回転部材のうちの一方が駆動側部材とされ、他方が従動側部材となる。従って、以下の説明では、回転軸が駆動側部材とされ、筒状回転部材が従動側部材として構成されている例を説明するが、回転軸が従動側部材とされ、筒状回転部材が駆動側部材として構成されている場合に本発明を適用してもよい。   A friction drive device to which the present invention is applied will be described with reference to the drawings. In the friction drive device to which the present invention is applied, when power is transmitted between the rotating shaft and the cylindrical rotating member, one of the rotating shaft and the cylindrical rotating member is a drive side member, and the other is a driven side. It becomes a member. Therefore, in the following description, an example in which the rotation shaft is a drive side member and the cylindrical rotation member is configured as a driven side member will be described. However, the rotation shaft is a driven side member and the cylindrical rotation member is driven. You may apply this invention, when comprised as a side member.

(フリクションドライブ装置の構成)
図1は、本発明を適用したフリクションドライブ装置の説明図であり、図1(a)、(b)は各々、フリクションドライブ装置の部分断面図、および回転軸に板状付勢部材を固定する様子を示す説明図である。なお、図1では、フリクションドライブ装置のうち、環状部材、筒状回転部材および板状付勢部材については断面で表してある。図2は、本発明を適用したフリクションドライブ装置に用いた各部材の説明図であり、図2(a)、(b)、(c)、(d)、(e)は各々、回転軸の側面図、回転軸を軸線方向の一方側(先端側)からみた平面図、環状部材の平面図、筒状回転部材の断面図、および板状付勢部材の平面図である。図3は、本発明を適用したフリクションドライブ装置に用いられる各種板状付勢部材の平面図であり、図3(a)、(b)、(c)、(d)は各々、第1例に係る板状付勢部材の平面図、第2例に係る板状付勢部材の平面図、第3例に係る板状付勢部材の平面図、および第4例に係る板状付勢部材の平面図である。
(Configuration of friction drive device)
FIG. 1 is an explanatory view of a friction drive device to which the present invention is applied. FIGS. 1A and 1B are a partial sectional view of the friction drive device and a plate-like urging member fixed to a rotating shaft, respectively. It is explanatory drawing which shows a mode. In FIG. 1, in the friction drive device, the annular member, the cylindrical rotating member, and the plate-like urging member are shown in cross section. FIG. 2 is an explanatory view of each member used in the friction drive device to which the present invention is applied, and FIGS. 2 (a), (b), (c), (d), and (e) are respectively the rotation shafts. FIG. 4 is a side view, a plan view of the rotating shaft viewed from one side (tip side) in the axial direction, a plan view of an annular member, a sectional view of a cylindrical rotating member, and a plan view of a plate-like biasing member. FIG. 3 is a plan view of various plate-like urging members used in the friction drive device to which the present invention is applied. FIGS. 3A, 3B, 3C, and 3D are respectively a first example. The plan view of the plate-like urging member according to the above, the plan view of the plate-like urging member according to the second example, the plan view of the plate-like urging member according to the third example, and the plate-like urging member according to the fourth example FIG.

図1(a)に示すフリクションドライブ装置1は、概ね、回転軸2、環状部材3、筒状回転部材4および板状付勢部材5により構成されている。図1(a)、(b)および図2(a)、(b)に示すように、回転軸2では、軸線方向Lに沿って大径部21と、大径部21に対して軸線方向Lの一方側L1で大径部21より小さな径を有する中径部22と、中径部22に対して軸線方向Lの一方側L1で中径部22より小さな径を有する連結軸部23と、連結軸部23に対して軸線方向Lの一方側L1で連結軸部23より小さな径を有する小径部24と、小径部24に対して軸線方向Lの一方側L1で小径部24より小さな径を有する軸端部25とがこの順に設けられた構造を有している。大径部21において、他方側L2の端部では周方向の一部が平坦面211になっており、かかる端部を利用して駆動源側(動力伝達経路の上流側)に連結される。また、中径部22の外周面は、周方向の一部が平坦面221になっている。これに対して、連結軸部23、小径部24、および軸端部25は丸棒状になっており、外周面は軸線を中心に回転対称になっている。   A friction drive device 1 shown in FIG. 1A is generally composed of a rotating shaft 2, an annular member 3, a cylindrical rotating member 4, and a plate-like biasing member 5. As shown in FIGS. 1A and 1B and FIGS. 2A and 2B, the rotary shaft 2 has a large diameter portion 21 along the axial direction L and an axial direction with respect to the large diameter portion 21. A medium diameter portion 22 having a diameter smaller than the large diameter portion 21 on one side L1 of L, and a connecting shaft portion 23 having a diameter smaller than the medium diameter portion 22 on one side L1 in the axial direction L with respect to the medium diameter portion 22; A small diameter portion 24 having a smaller diameter than the connecting shaft portion 23 on one side L1 in the axial direction L with respect to the connecting shaft portion 23, and a smaller diameter than the small diameter portion 24 on one side L1 in the axial direction L with respect to the small diameter portion 24. And a shaft end portion 25 having a structure provided in this order. In the large diameter portion 21, a part in the circumferential direction is a flat surface 211 at the end portion on the other side L <b> 2, and is connected to the drive source side (upstream side of the power transmission path) using this end portion. Further, a part of the outer circumferential surface of the medium diameter portion 22 in the circumferential direction is a flat surface 221. On the other hand, the connecting shaft portion 23, the small diameter portion 24, and the shaft end portion 25 have a round bar shape, and the outer peripheral surface is rotationally symmetric about the axis.

本形態では、中径部22に環状部材3が嵌められており、かかる環状部材3の一方側L1の面によって支持面31が形成されている。本形態において、環状部材3の軸線方向Lの他方側L2への移動は、中径部22と大径部21との間に位置する段面に環状部材3の他方側L2の面32が当接することによって規制されている。本形態において、中径部22の外周面は、周方向の一部が平坦面になっており、環状部材3において中径部22が嵌る穴30は、中径部22の断面形状と同一の形状を有している。より具体的には、中径部22は、丸棒部分の外周面のうち、互いに反対側に位置する2個所に平坦面221が形成され、その他の部分は円弧状になっている。このため、環状部材3は、外周形状は円形であるが、穴30の内縁は、互いに平行に延在する2つの直線部分30aの両端が円弧部分30bの端部に繋がった形状になっている。このため、環状部材3は、中径部22に嵌めるだけで空回りしないようになっている。   In this embodiment, the annular member 3 is fitted to the medium diameter portion 22, and the support surface 31 is formed by the surface of the one side L <b> 1 of the annular member 3. In this embodiment, the movement of the annular member 3 toward the other side L2 in the axial direction L is such that the surface 32 on the other side L2 of the annular member 3 is in contact with the step surface located between the medium diameter portion 22 and the large diameter portion 21. It is regulated by touching. In this embodiment, the outer peripheral surface of the medium diameter portion 22 is a flat surface in the circumferential direction, and the hole 30 in which the medium diameter portion 22 fits in the annular member 3 has the same cross-sectional shape as the medium diameter portion 22. It has a shape. More specifically, the intermediate diameter portion 22 has a flat surface 221 formed at two locations on the opposite sides of the outer peripheral surface of the round bar portion, and the other portion has an arc shape. For this reason, the annular member 3 has a circular outer peripheral shape, but the inner edge of the hole 30 has a shape in which both ends of two linear portions 30a extending in parallel to each other are connected to end portions of the arc portion 30b. . For this reason, the annular member 3 is prevented from idling only by being fitted to the medium diameter portion 22.

筒状回転部材4は、中径部22のうち、環状部材3から軸線方向Lの一方側L1に突き出た部分が嵌る穴40が中央に形成された円盤部41と、円盤部41の外周縁から軸線方向Lの両側に突き出た円筒部42とを有しており、円筒部42の外周面には、外歯45が形成されている。円盤部41の両面のうち、軸線方向Lの一方側L1に向く一方面46には、穴の周りで一方側L1に断面半円形状に突出した一方側凸部47が形成されている。本形態において、一方側凸部47は、円筒部42と同心状に環状に形成されている。また、円盤部41において、軸線方向Lの他方側に向く他方面48には、穴40の周りで他方側L2に断面半円形状に突出した他方側凸部49が形成されている。本形態において、他方側凸部49は、一方側凸部47と同様、円筒部42と同心状に環状に形成されており、他方側凸部49と一方側凸部47とは、円盤部41の両面で互いに重なるように形成されている。本形態では、筒状回転部材4の穴40は、環状部材3の穴30と違って、軸線方向Lからみたとき、円形である。このため、筒状回転部材4は、中径部22に嵌めた状態で周方向に回転可能である。円盤部41は、一方側凸部47および他方側凸部49より内側に位置する部分は、外側に位置する部分よりわずかに薄くなっている。すなわち、円盤部41において、一方側凸部47および他方側凸部49の内側は、以下に説明する板状付勢部材5が押し込まれてくるため、その分の余裕を取る目的で薄くしてあるのに対して、一方側凸部47および他方側凸部49より外側は、強度確保のため厚くしてある。   The cylindrical rotating member 4 includes a disk part 41 in which a hole 40 into which the part protruding from the annular member 3 to the one side L1 in the axial direction L is formed in the middle diameter part 22 is formed in the center, and the outer peripheral edge of the disk part 41 The cylindrical portion 42 protrudes on both sides in the axial direction L, and external teeth 45 are formed on the outer peripheral surface of the cylindrical portion 42. Of the both surfaces of the disk portion 41, one surface 46 facing the one side L1 in the axial direction L is formed with a one-side convex portion 47 projecting in a semicircular cross section around the hole on the one side L1. In this embodiment, the one-side convex portion 47 is formed concentrically with the cylindrical portion 42 in an annular shape. Further, in the disk portion 41, the other side surface 48 facing the other side in the axial direction L is formed with the other side convex portion 49 that protrudes in a semicircular cross section around the hole 40 on the other side L2. In the present embodiment, the other-side convex portion 49 is formed concentrically with the cylindrical portion 42 in the same manner as the one-side convex portion 47, and the other-side convex portion 49 and the one-side convex portion 47 are the disc portion 41. Are formed so as to overlap each other. In this embodiment, the hole 40 of the cylindrical rotating member 4 is circular when viewed from the axial direction L, unlike the hole 30 of the annular member 3. For this reason, the cylindrical rotating member 4 is rotatable in the circumferential direction while being fitted to the medium diameter portion 22. In the disc part 41, the part located inside the one side convex part 47 and the other side convex part 49 is slightly thinner than the part located outside. That is, in the disc part 41, the inside of the one side convex part 47 and the other side convex part 49 is pushed into the plate-like urging member 5 described below, so that it is made thin for the purpose of taking a margin. On the other hand, the outer side from the one-side convex portion 47 and the other-side convex portion 49 is thickened to ensure strength.

本形態では、連結軸部23に、ワッシャ状の板状付勢部材5が嵌められており、かかる板状付勢部材5の他方側L2の面によって摺動面52が形成されている。また、板状付勢部材5において連結軸部23が嵌る穴50の内周縁には、回り止め用の係合部として、連結軸部23の外周面からみて径方向外側に向けて凹んだ係合凹部50aが形成されている。より具体的には、板状付勢部材5は、外周形状は円形であるが、穴50の内縁は、連結軸部23の外周形状に対応する円形になっているとともに、周方向の一部に径方向外側に凹む係合凹部50aが形成されている。本形態において、穴50は、周方向に複数個所に係合凹部50aが等角度間隔に形成された形状になっており、穴50は軸線を中心に回転対称の形状を有している。より具体的には、穴50は、周方向に3個所に係合凹部50aが等角度間隔に形成された形状になっている。ここで、板状付勢部材5は、連結軸部23に嵌めるだけでは、空回りする状態にある。また、板状付勢部材5は、連結軸部23に嵌めるだけでは、軸線方向Lの一方側L1に移動可能であり、摺動面52と筒状回転部材4の一方側凸部47との間には十分な摩擦力が発生しない。また、板状付勢部材5を連結軸部23に嵌めるだけでは、筒状回転部材4の他方側凸部49と環状部材3の支持面31との間に十分な摩擦力が発生しない。   In this embodiment, the washer-like plate-like urging member 5 is fitted to the connecting shaft portion 23, and the sliding surface 52 is formed by the surface of the other side L <b> 2 of the plate-like urging member 5. Further, in the plate-like urging member 5, the inner peripheral edge of the hole 50 in which the connecting shaft portion 23 fits is a recess that is recessed toward the outside in the radial direction as viewed from the outer peripheral surface of the connecting shaft portion 23. A joint recess 50a is formed. More specifically, the plate-like biasing member 5 has a circular outer peripheral shape, but the inner edge of the hole 50 has a circular shape corresponding to the outer peripheral shape of the connecting shaft portion 23 and a part of the circumferential direction. An engaging recess 50a that is recessed radially outward is formed. In the present embodiment, the hole 50 has a shape in which engaging recesses 50a are formed at equiangular intervals at a plurality of locations in the circumferential direction, and the hole 50 has a rotationally symmetric shape about the axis. More specifically, the hole 50 has a shape in which engagement recesses 50a are formed at equal angular intervals at three locations in the circumferential direction. Here, the plate-like urging member 5 is in an idle state only by being fitted to the connecting shaft portion 23. Further, the plate-like urging member 5 can be moved to the one side L1 in the axial direction L simply by being fitted to the connecting shaft portion 23, and the sliding surface 52 and the one-side convex portion 47 of the cylindrical rotating member 4 can be moved. There is not enough friction between them. Further, only by fitting the plate-like urging member 5 to the connecting shaft portion 23, sufficient frictional force is not generated between the other side convex portion 49 of the cylindrical rotating member 4 and the support surface 31 of the annular member 3.

そこで、本形態では、連結軸部23において板状付勢部材5より一方側L1に位置する部分の全周をプレス加工により他方側L2に向けて塑性変形させ、かかる塑性変形によって生じた変形部分23aによって、板状付勢部材5の内周部分56を他方側L2に押圧した状態にしてある。このため、板状付勢部材5では、内周部分56が外周側に位置する部分より軸線方向Lの他方側L2に変位している。従って、板状付勢部材5は、内周部分56より径方向外側に位置する部分57が筒状回転部材4の一方側凸部47に弾性をもって接するように変形している。また、筒状回転部材4は、軸線方向Lの他方側L2に押圧されるので、筒状回転部材4の他方側凸部49は、弾性をもって環状部材3の支持面31に接している状態となる。従って、摺動面52と筒状回転部材4の一方側凸部47との間には十分な摩擦力が発生し、筒状回転部材4の他方側凸部49と環状部材3の支持面31との間に十分な摩擦力が発生する。   Therefore, in this embodiment, the entire circumference of the portion located on the one side L1 from the plate-like biasing member 5 in the connecting shaft portion 23 is plastically deformed toward the other side L2 by pressing, and a deformed portion generated by the plastic deformation. By 23a, the inner peripheral part 56 of the plate-shaped urging member 5 is pressed against the other side L2. For this reason, in the plate-like urging member 5, the inner peripheral portion 56 is displaced to the other side L2 in the axial direction L from the portion located on the outer peripheral side. Accordingly, the plate-like urging member 5 is deformed so that the portion 57 positioned radially outward from the inner peripheral portion 56 is in elastic contact with the one-side convex portion 47 of the cylindrical rotating member 4. Moreover, since the cylindrical rotating member 4 is pressed to the other side L2 of the axial direction L, the other side convex part 49 of the cylindrical rotating member 4 is in contact with the support surface 31 of the annular member 3 with elasticity. Become. Accordingly, a sufficient frictional force is generated between the sliding surface 52 and the one side convex portion 47 of the cylindrical rotating member 4, and the other side convex portion 49 of the cylindrical rotating member 4 and the support surface 31 of the annular member 3. Sufficient friction force is generated between

また、本形態では、板状付勢部材5の穴50の内周縁には、径方向外側に凹む係合凹部50aが形成されており、連結軸部23において塑性変形によって生じた変形部分23aは、係合凹部50aの内側に入り込んで板状付勢部材5の回り止め機能を発揮している。   In this embodiment, an engagement recess 50a that is recessed radially outward is formed on the inner peripheral edge of the hole 50 of the plate-like biasing member 5, and the deformed portion 23a generated by plastic deformation in the connecting shaft portion 23 is Then, it enters the inside of the engaging recess 50a and exhibits the function of preventing the plate-like urging member 5 from rotating.

本形態では、図2(e)および図3(b)に示すように、係合凹部50aが略半円形状をもって径方向外側に凹んでいるが、図3(a)に示すように、図3(b)に示す係合凹部50aより大の曲率半径をもつ円の約1/3に相当する円弧を有するように径方向外側に凹んだ係合凹部50aを採用してもよい。すなわち、径方向外側に凹んだ複数の係合凹部50aが全体として、丸穴からなる穴50の内周縁の1/3に相当する角度範囲を占めるように形成してもよい。また、図3(c)に示すように、略三角形をもって径方向外側に凹んだ係合凹部50aを採用してもよい。 In this embodiment, as shown in FIG. 2 (e) and FIG. 3 (b), the engaging recess 50a has a substantially semicircular shape and is recessed radially outward, but as shown in FIG. An engagement recess 50a that is recessed outward in the radial direction so as to have an arc corresponding to about 1/3 of a circle having a larger radius of curvature than the engagement recess 50a shown in 3 (b) may be employed. That is, you may form so that the several engagement recessed part 50a dented in the radial direction outer side may occupy the angle range equivalent to 1/3 of the inner periphery of the hole 50 consisting of a round hole. Moreover, as shown in FIG.3 (c), you may employ | adopt the engagement recessed part 50a dented in the radial direction outer side with a substantially triangular shape.

また、板状付勢部材5において連結軸部23が嵌る穴50の内周縁に、連結軸部23の外周面からみて径方向外側に向けて凹んだ係合凹部50aを形成するという観点からすれば、図3(d)に示すように、穴50を多角形としてもよい。かかる形状の穴50によれば、角50cを、連結軸部23の外周面からみて径方向外側に向けて凹んだ係合凹部50aとして機能させることができる。また、穴50が正多角形であれば、複数の係合凹部50aを等角度間隔に設けることもできる。   Further, from the viewpoint of forming an engagement recess 50a that is recessed radially outward when viewed from the outer peripheral surface of the connection shaft 23 on the inner peripheral edge of the hole 50 into which the connection shaft 23 is fitted in the plate-like biasing member 5. For example, as shown in FIG. 3D, the hole 50 may be a polygon. According to the hole 50 having such a shape, the corner 50 c can function as an engagement recess 50 a that is recessed outward in the radial direction when viewed from the outer peripheral surface of the connecting shaft portion 23. Moreover, if the hole 50 is a regular polygon, the some engagement recessed part 50a can also be provided in an equiangular space | interval.

(作用および本形態の主な効果)
このように構成したフリクションドライブ装置1において、回転軸2が軸線周りに回転した際、かかる回転は、板状付勢部材5と筒状回転部材4の一方側凸部47との間の摩擦力、および筒状回転部材4の他方側凸部49と環状部材3の支持面31との間の摩擦力によって、筒状回転部材4に伝達されるので、筒状回転部材4が軸線周りに回転する。これに対して、筒状回転部材4の側に過大な負荷が加わった際には、板状付勢部材5と筒状回転部材4との間、および環状部材3と筒状回転部材4との間に空回りが発生するので、動力の伝達が遮断される。このため、筒状回転部材4の側に過大な負荷が加わったときでも、回転軸2や回転軸2より駆動側に設けられた歯車等の損傷を防止することができる。
(Operation and main effects of this form)
In the friction drive device 1 configured as described above, when the rotary shaft 2 rotates around the axis, the rotation is caused by a frictional force between the plate-like biasing member 5 and the one-side convex portion 47 of the cylindrical rotary member 4. And the frictional force between the convex portion 49 on the other side of the cylindrical rotating member 4 and the support surface 31 of the annular member 3 is transmitted to the cylindrical rotating member 4, so that the cylindrical rotating member 4 rotates around the axis. To do. On the other hand, when an excessive load is applied to the cylindrical rotating member 4 side, between the plate-shaped urging member 5 and the cylindrical rotating member 4, and between the annular member 3 and the cylindrical rotating member 4, Since idling occurs during this period, power transmission is interrupted. For this reason, even when an excessive load is applied to the cylindrical rotating member 4 side, it is possible to prevent damage to the rotating shaft 2 and the gear provided on the driving side from the rotating shaft 2.

ここで、板状付勢部材5は、連結軸部23において板状付勢部材5より一方側L1に位置する部分の全周を他方側L2に向けて塑性変形させた変形部分23aにより内周部分56が他方側L2に押圧されている。ここで、連結軸部23は、外周面が円形の丸棒状であるため、軸線を中心とする回転対称になっている。このため、塑性変形させる際の力が周方向で偏って印加されることを防止することができる。従って、塑性変形させる際の力によって回転軸2に曲がることを防止することができるので、評価結果を後述するように、回転軸2や筒状回転部材4にブレが発生しにくい。また、板状付勢部材5において連結軸部23が嵌る穴50の内周縁には、連結軸部23の外周面からみて径方向外側に向けて凹んだ係合凹部50aが形成されており、塑性変形による変形部分23aは、係合凹部50aの内側に入り込んでいる。このため、連結軸部23が丸棒状であっても、回転軸2に対する板状付勢部材5の空回りを防止することができる。   Here, the plate-like urging member 5 has an inner periphery by a deformed portion 23a obtained by plastically deforming the entire circumference of the portion located on the one side L1 from the plate-like urging member 5 in the connecting shaft portion 23 toward the other side L2. The portion 56 is pressed against the other side L2. Here, since the outer peripheral surface is a round bar shape, the connecting shaft portion 23 is rotationally symmetric about the axis. For this reason, it can prevent that the force at the time of carrying out plastic deformation is biased and applied in the circumferential direction. Therefore, since it can prevent bending to the rotating shaft 2 with the force at the time of plastically deforming, blurring is hard to generate | occur | produce in the rotating shaft 2 or the cylindrical rotating member 4 so that an evaluation result may mention later. In addition, an engagement recess 50a that is recessed outward in the radial direction when viewed from the outer peripheral surface of the connection shaft portion 23 is formed on the inner peripheral edge of the hole 50 in which the connection shaft portion 23 is fitted in the plate-like biasing member 5. The deformed portion 23a due to plastic deformation enters the inside of the engaging recess 50a. For this reason, even if the connecting shaft portion 23 has a round bar shape, it is possible to prevent the plate-like urging member 5 from rotating around the rotating shaft 2.

また、板状付勢部材5の穴50は、丸穴の内周縁に係合凹部50aが形成された形状になっているが、穴50は軸線を中心とする回転対称の形状を有している。このため、連結軸部23の塑性変形による変形部分23aによって板状付勢部材5の内周縁を押圧した際、周方向で均等な力が加わるので、板状付勢部材5が傾きにくい。それ故、板状付勢部材5と筒状回転部材4との間の摩擦力を適正なレベルに安定させることができる。また、係合凹部50aは、周方向の複数箇所に等角度間隔に形成されているため、回転軸2に対する板状付勢部材5の空回りを確実に防止することができるとともに、連結軸部23の塑性変形による変形部分23aによって板状付勢部材5の内周縁を押圧した際、周方向で均等な力が確実に加わるので、板状付勢部材5が傾きにくい。また、筒状回転部材4は、一方側凸部47および他方側凸部49を介して板状付勢部材5の摺動面52および環状部材3の支持面31に接している。このため、筒状回転部材4と板状付勢部材5との接触面積や接触状態を安定した状態に設定することができるので、板状付勢部材5と筒状回転部材4との間の摩擦力を適正なレベルに安定させることができる。さらに、支持面31は、回転軸2に嵌められた環状部材3の一方側L1に向く面からなる。このため、環状部材3の表面を適正な状態にすれば、回転軸2の表面粗さ等にかかわらず、筒状回転部材4と環状部材3との間の摩擦力を適正なレベルに安定させることができる。   Further, the hole 50 of the plate-like urging member 5 has a shape in which an engagement recess 50a is formed on the inner periphery of the round hole. However, the hole 50 has a rotationally symmetric shape about the axis. Yes. For this reason, when the inner peripheral edge of the plate-like urging member 5 is pressed by the deformed portion 23a due to plastic deformation of the connecting shaft portion 23, a uniform force is applied in the circumferential direction, so that the plate-like urging member 5 is not easily tilted. Therefore, the frictional force between the plate-like urging member 5 and the cylindrical rotating member 4 can be stabilized at an appropriate level. In addition, since the engagement recesses 50a are formed at equiangular intervals at a plurality of locations in the circumferential direction, it is possible to reliably prevent the plate-like biasing member 5 from rotating freely with respect to the rotary shaft 2 and to connect the connecting shaft portion 23. When the inner peripheral edge of the plate-like urging member 5 is pressed by the deformed portion 23a due to the plastic deformation, the plate-like urging member 5 is not easily tilted because a uniform force is reliably applied in the circumferential direction. The cylindrical rotating member 4 is in contact with the sliding surface 52 of the plate-like urging member 5 and the support surface 31 of the annular member 3 via the one side convex portion 47 and the other side convex portion 49. For this reason, since the contact area and contact state of the cylindrical rotating member 4 and the plate-like biasing member 5 can be set in a stable state, the gap between the plate-like biasing member 5 and the cylindrical rotating member 4 can be set. The frictional force can be stabilized at an appropriate level. Further, the support surface 31 is a surface facing the one side L <b> 1 of the annular member 3 fitted to the rotating shaft 2. For this reason, if the surface of the annular member 3 is set to an appropriate state, the frictional force between the cylindrical rotating member 4 and the annular member 3 is stabilized at an appropriate level regardless of the surface roughness of the rotating shaft 2. be able to.

(評価結果1)
図4は、本発明を適用したフリクションドライブ装置1における板状付勢部材5の反り量P(バネ反り量)と回転軸2の先端の振れ量との関係を評価した結果のグラフであり、図4(a)、(b)、(c)、(d)は各々、図9に示す参考例のフリクションドライブ装置1の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(a)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(b)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、および本発明を適用したフリクションドライブ装置1において図3(c)に示す板状付勢部材5を用いた場合の評価結果を示すグラフである。図5は、本発明を適用したフリクションドライブ装置1における板状付勢部材5の反り量と静フリクショントルクとを評価した結果のグラフであり、図5(a)、(b)、(c)、(d)は各々、図9に示す参考例のフリクションドライブ装置1の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(a)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(b)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、および本発明を適用したフリクションドライブ装置1において図3(c)に示す板状付勢部材5を用いた場合の評価結果を示すグラフである。図6は、本発明を適用したフリクションドライブ装置1における板状付勢部材5の反り量と動フリクショントルクとを評価した結果のグラフであり、図6(a)、(b)、(c)、(d)は各々、図9に示す参考例のフリクションドライブ装置1の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(a)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、本発明を適用したフリクションドライブ装置1において図3(b)に示す板状付勢部材5を用いた場合の評価結果を示すグラフ、および本発明を適用したフリクションドライブ装置1において図3(c)に示す板状付勢部材5を用いた場合の評価結果を示すグラフである。なお、図4、図5、および図6に示す評価結果において、板状付勢部材5の反り量は、図1(a)に示すように、板状付勢部材5の内周側と外周側とにおける軸線方向Lのずれ量である。
(Evaluation result 1)
FIG. 4 is a graph showing a result of evaluating the relationship between the amount of warpage P (spring warpage amount) of the plate-like biasing member 5 and the amount of deflection of the tip of the rotating shaft 2 in the friction drive device 1 to which the present invention is applied. 4 (a), (b), (c), and (d) are graphs showing the evaluation results of the friction drive device 1 of the reference example shown in FIG. 9, respectively. In the friction drive device 1 to which the present invention is applied, FIG. The graph which shows the evaluation result at the time of using the plate-shaped biasing member 5 shown to (a), and the case where the plate-shaped biasing member 5 shown in FIG.3 (b) is used in the friction drive apparatus 1 to which this invention is applied. It is a graph which shows the evaluation result at the time of using the plate-shaped biasing member 5 shown in FIG.3 (c) in the friction drive apparatus 1 to which this invention is applied, and the graph which shows an evaluation result. FIG. 5 is a graph showing a result of evaluating the warpage amount and static friction torque of the plate-like biasing member 5 in the friction drive device 1 to which the present invention is applied. FIGS. 5 (a), 5 (b), and 5 (c). , (D) are graphs showing the evaluation results of the friction drive device 1 of the reference example shown in FIG. 9, and the plate-like urging member 5 shown in FIG. 3 (a) is used in the friction drive device 1 to which the present invention is applied. FIG. 3B is a graph showing an evaluation result in the case of using the plate-like biasing member 5 shown in FIG. 3B in the friction drive device 1 to which the present invention is applied, and a friction in which the present invention is applied. It is a graph which shows the evaluation result at the time of using the plate-shaped biasing member 5 shown in FIG.3 (c) in the drive apparatus 1. FIG. FIG. 6 is a graph showing the results of evaluating the warpage amount and dynamic friction torque of the plate-like urging member 5 in the friction drive device 1 to which the present invention is applied, and FIGS. 6 (a), 6 (b), and 6 (c). , (D) are graphs showing the evaluation results of the friction drive device 1 of the reference example shown in FIG. 9, and the plate-like urging member 5 shown in FIG. 3 (a) is used in the friction drive device 1 to which the present invention is applied. FIG. 3B is a graph showing an evaluation result in the case of using the plate-like biasing member 5 shown in FIG. 3B in the friction drive device 1 to which the present invention is applied, and a friction in which the present invention is applied. It is a graph which shows the evaluation result at the time of using the plate-shaped biasing member 5 shown in FIG.3 (c) in the drive apparatus 1. FIG. In the evaluation results shown in FIGS. 4, 5, and 6, the warping amount of the plate-like biasing member 5 is equal to the inner peripheral side and the outer periphery of the plate-like biasing member 5 as shown in FIG. This is the shift amount in the axial direction L with respect to the side.

図7は、本発明を適用したフリクションドライブ装置1の信頼性を評価した結果のグラフであり、図7(a)、(b)は各々、回転軸2を時計周りの回転、停止、反時計周りの回転、および停止を1サイクルとし、かかるサイクル数と静フリクショントルクとの関係を示すグラフ、および上記のサイクル数と動フリクショントルクとの関係を示すグラフである。なお、図7において、長い破線L10で示すデータは、本発明を適用したフリクションドライブ装置1において図3(a)に示す板状付勢部材5を用いた場合の評価結果であり、実線L20で示すデータは、本発明を適用したフリクションドライブ装置1において図3(b)に示す板状付勢部材5を用いた場合の評価結果であり、短い破線L30で示すデータは、本発明を適用したフリクションドライブ装置1において図3(c)に示す板状付勢部材5を用いた場合の評価結果であり、一点鎖線L40で示すデータは、図9に示す参考例のフリクションドライブ装置1xの評価結果である。   FIG. 7 is a graph showing the result of evaluating the reliability of the friction drive device 1 to which the present invention is applied. FIGS. 7A and 7B respectively rotate the rotating shaft 2 clockwise, stop, and counterclockwise. FIG. 6 is a graph showing the relationship between the number of cycles and static friction torque, and the graph showing the relationship between the number of cycles and dynamic friction torque, with the surrounding rotation and stop taken as one cycle. In FIG. 7, data indicated by a long broken line L10 is an evaluation result when the plate-like biasing member 5 shown in FIG. 3A is used in the friction drive device 1 to which the present invention is applied, and is indicated by a solid line L20. The data shown is an evaluation result when the plate-like urging member 5 shown in FIG. 3B is used in the friction drive device 1 to which the present invention is applied, and the data indicated by a short broken line L30 is applied to the present invention. FIG. 3 is an evaluation result when the plate-like urging member 5 shown in FIG. 3C is used in the friction drive device 1, and the data indicated by the alternate long and short dash line L40 is the evaluation result of the friction drive device 1x of the reference example shown in FIG. It is.

図4(b)〜(d)から分かるように、本発明を適用したフリクションドライブ装置1では、板状付勢部材5の構成を図3(a)〜(c)に示す構造に変更した場合、図9および図10を参照して説明した参考例のフリクションドライブ装置1xに比して、回転軸2の先端の振れ量が小さいとともに、板状付勢部材5の反り量が変化しても、回転軸2の先端の振れ量が大きく変化せず、安定している。 As can be seen from FIGS. 4B to 4D, in the friction drive device 1 to which the present invention is applied , the configuration of the plate-like biasing member 5 is changed to the structure shown in FIGS. 3A to 3C. As compared with the friction drive device 1x of the reference example described with reference to FIGS. 9 and 10, the amount of deflection at the tip of the rotating shaft 2 is small and the amount of warping of the plate-like biasing member 5 changes. The amount of deflection at the tip of the rotating shaft 2 does not change greatly and is stable.

図5(b)〜(d)から分かるように、板状付勢部材5の構成を図3(a)〜(c)に示す構造に変更しても、静フリクショントルクの上限値(例えば、2500gf−cm)を超えないことが確認できた。また、本発明を適用したフリクションドライブ装置1のうち、図3(a)に示す板状付勢部材5を用いた場合には、図3(b)、(c)に示す構成例に比して、板状付勢部材5の反り量が変化したときの静フリクショントルクの変化が小さく、安定していることが確認できた。また、図3(a)〜(c)に示す板状付勢部材5を用いた場合には、板状付勢部材5の反り量が小さい場合でも、1600gf−cm以上の静フリクショントルクを得ることができた。さらに、図3(b)、(c)に示す板状付勢部材5を用いた場合、図3(a)に示す板状付勢部材5に比して、板状付勢部材5の反り量が大きくなるにつれて静フリクショントルクが大きくなることが確認できた。 As can be seen from FIGS. 5B to 5D , even if the configuration of the plate-like biasing member 5 is changed to the structure shown in FIGS. 3A to 3C , the upper limit value of the static friction torque (for example, It was confirmed that it did not exceed 2500 gf-cm). Further, in the friction drive device 1 to which the present invention is applied, when the plate-like urging member 5 shown in FIG. 3A is used, the configuration example shown in FIGS. 3B and 3C is compared. Thus, it was confirmed that the change of the static friction torque when the amount of warping of the plate-like urging member 5 changed was small and stable. Further, when the plate-like urging member 5 shown in FIGS. 3A to 3C is used, a static friction torque of 1600 gf-cm or more is obtained even when the amount of warpage of the plate-like urging member 5 is small. I was able to. Further, when the plate-like urging member 5 shown in FIGS. 3B and 3C is used, the warpage of the plate-like urging member 5 as compared with the plate-like urging member 5 shown in FIG. It was confirmed that the static friction torque increases as the amount increases.

図6(b)〜(d)から分かるように、板状付勢部材5の構成を図3(a)〜(c)に示す構造に変更すれば、動フリクショントルクが下限値(例えば、1300gf−cm)を下回らないことが確認できた。また、本発明を適用したフリクションドライブ装置1のうち、図3(a)に示す板状付勢部材5を用いた場合には、図3(b)、(c)に示す構成例に比して、板状付勢部材5の反り量が変化したときの動フリクショントルクの変化が小さく、安定していることが確認できた。また、図3(a)〜(c)に示す板状付勢部材5を用いた場合、板状付勢部材5の反り量が小さい場合でも、1600gf−cm以上の動フリクショントルクを確保することができた。特に、図3(b)、(c)に示す板状付勢部材5を用いた場合には、図3(a)に示す板状付勢部材5に比して、板状付勢部材5の反り量が大きくなるにつれて動フリクショントルクが大きくなることが確認できた。 As can be seen from FIGS. 6B to 6D , if the structure of the plate-like urging member 5 is changed to the structure shown in FIGS. 3A to 3C , the dynamic friction torque becomes a lower limit (for example, 1300 gf). -Cm). Further, in the friction drive device 1 to which the present invention is applied, when the plate-like urging member 5 shown in FIG. 3A is used, the configuration example shown in FIGS. 3B and 3C is compared. Thus, it was confirmed that the change of the dynamic friction torque when the warpage amount of the plate-like urging member 5 changed was small and stable. Further, when the plate-like urging member 5 shown in FIGS. 3A to 3C is used, a dynamic friction torque of 1600 gf-cm or more should be ensured even when the amount of warpage of the plate-like urging member 5 is small. I was able to. In particular, when the plate-like biasing member 5 shown in FIGS. 3B and 3C is used, the plate-like biasing member 5 is compared with the plate-like biasing member 5 shown in FIG. It was confirmed that the dynamic friction torque increases as the amount of warpage increases.

図7(a)、(b)から分かるように、板状付勢部材5の構成を図3(a)〜(c)に示す構造に変更しても、静フリクショントルクおよび動フリクショントルクの安定性(耐久性能)は、図9に示す参考例のフリクションドライブ装置1xと同等以上であることが確認できた。また、図3(a)〜(c)に示す構造を比較すると、係合凹部50aが小さい程、静フリクショントルクおよび動フリクショントルクの安定性(耐久性能)に優れている傾向にある。すなわち、図3(b)に示す係合凹部50aは、図3(a)に示す係合凹部50aより小さく、図3(b)に示す板状付勢部材5を用いた場合(実線L20で示す特性)は、図3(a)に示す板状付勢部材5を用いた場合(長い破線L10で示す特性)より、静フリクショントルクおよび動フリクショントルクの変化が小さく、静フリクショントルクおよび動フリクショントルクの安定性(耐久性能)に優れている傾向にある。また、図3(c)に示す係合凹部50aは、図3(a)、(b)に示す係合凹部50aより小さく、図3(c)に示す板状付勢部材5を用いた場合(長い短い破線L30で示す特性)は、図3(a)、(b)に示す板状付勢部材5を用いた場合(長い破線L10で示す特性および実線20で示す特性)より、静フリクショントルクおよび動フリクショントルクの変化が小さく、静フリクショントルクおよび動フリクショントルクの安定性(耐久性能)に優れている傾向にある。 As can be seen from FIGS. 7A and 7B , even if the configuration of the plate-like urging member 5 is changed to the structure shown in FIGS. 3A to 3C , the static friction torque and the dynamic friction torque can be stabilized. It was confirmed that the property (durability) is equal to or higher than that of the friction drive device 1x of the reference example shown in FIG . Further, when the structures shown in FIGS. 3A to 3C are compared, the smaller the engagement recess 50a, the better the stability (endurance performance) of the static friction torque and the dynamic friction torque. That is, the engagement recess 50a shown in FIG. 3B is smaller than the engagement recess 50a shown in FIG. 3A, and the plate-like biasing member 5 shown in FIG. 3B is used (in the solid line L20). The characteristics shown in FIG. 3 are smaller than those in the case where the plate-like biasing member 5 shown in FIG. 3A is used (characteristic shown by the long broken line L10), and the static friction torque and the dynamic friction are smaller. It tends to be excellent in torque stability (endurance performance). Further, the engagement recess 50a shown in FIG. 3C is smaller than the engagement recess 50a shown in FIGS. 3A and 3B, and the plate-like biasing member 5 shown in FIG. 3C is used. (Characteristics indicated by a long short broken line L30) is more static friction than when the plate-like biasing member 5 shown in FIGS. 3A and 3B is used (characteristics indicated by a long broken line L10 and characteristics indicated by a solid line 20). Changes in torque and dynamic friction torque are small, and the stability (endurance performance) of static friction torque and dynamic friction torque tends to be excellent.

(他の実施の形態)
連結軸部23の外周面および板状付勢部材5の穴50を回転対称の形状とし、かつ、板状付勢部材5に回り止め用の係合部を形成した構造としては、図3に示す構成の他、連結軸部23の外周面に凸部を等角度間隔に形成する一方、板状付勢部材5の穴50に凸部が嵌る凹部(回り止め用の係合部)を等角度間隔に形成した構造や、連結軸部23の外周面に凹部を等角度間隔に形成する一方、板状付勢部材5の穴50に凹部に嵌る凸部(回り止め用の係合部)を等角度間隔に形成した構造を採用してもよい。また、連結軸部23の外周面、および板状付勢部材5の穴50を正六角形や正八角形とした構造を採用してもよい。その際、板状付勢部材5の穴50において、複数の辺を1つ置きに径方向外側に凹ませて隙間を形成した構造を採用してもよい。
(Other embodiments)
FIG. 3 shows a structure in which the outer peripheral surface of the connecting shaft portion 23 and the hole 50 of the plate-like urging member 5 have a rotationally symmetric shape, and the plate-like urging member 5 has an anti-rotation engaging portion. In addition to the configuration shown, convex portions are formed at equal angular intervals on the outer peripheral surface of the connecting shaft portion 23, while a concave portion (an engagement portion for rotation prevention) in which the convex portion fits into the hole 50 of the plate-like biasing member 5 is provided. A structure formed at an angular interval, or a concave portion formed on the outer peripheral surface of the connecting shaft portion 23 at an equal angular interval, while a convex portion that fits into the concave portion in the hole 50 of the plate-like biasing member 5 (an engaging portion for rotation prevention) A structure in which is formed at equiangular intervals may be adopted. Moreover, you may employ | adopt the structure which used the outer peripheral surface of the connection shaft part 23, and the hole 50 of the plate-shaped biasing member 5 as a regular hexagon or a regular octagon. In that case, in the hole 50 of the plate-shaped urging member 5, a structure may be adopted in which a plurality of sides are recessed every other side in the radial direction to form a gap.

(ギヤードモータへの搭載例)
図8は、本発明を適用したフリクションドライブ装置1が搭載されるギヤードモータの説明図である。
(Example of mounting on a geared motor)
FIG. 8 is an explanatory diagram of a geared motor on which the friction drive device 1 to which the present invention is applied is mounted.

図8に示すギヤードモータ100は、ステータ部102、ロータ部103、減速輪列となる歯車伝達機構104、出力軸105、および端子部106を備えたステッピングモータであり、ステータ部102と歯車伝達機構104とは隣接して配置されている。ステータ部102は、2つのステータの先端部が交互に入り組むことによって円形状に配置される極歯107と、これらの極歯107と並んで配置される極歯108と、極歯107の外周に巻回されるコイル109と、極歯108の外周に巻回されるコイル110と、ステータを兼ねる円筒状ケース111と、ステータを兼ねる上ケース112とから構成されている。なお、コイル109は、コイルボビン109aを介して、極歯107に巻回され、コイル110は、コイルボビン110aを介して極歯108に巻回されている。ロータ部103は、ロータ軸113と、このロータ軸113に回転可能に支持されマグネット114aを有するロータ114とから構成される。   A geared motor 100 shown in FIG. 8 is a stepping motor including a stator portion 102, a rotor portion 103, a gear transmission mechanism 104 serving as a reduction gear train, an output shaft 105, and a terminal portion 106. The stator portion 102 and the gear transmission mechanism 104 is arranged adjacently. Stator portion 102 has pole teeth 107 arranged in a circular shape by the tip portions of two stators interleaving, pole teeth 108 arranged alongside these pole teeth 107, and outer circumference of pole teeth 107. A coil 109 wound around the outer periphery of the pole teeth 108, a cylindrical case 111 also serving as a stator, and an upper case 112 also serving as a stator. The coil 109 is wound around the pole teeth 107 via the coil bobbin 109a, and the coil 110 is wound around the pole teeth 108 via the coil bobbin 110a. The rotor unit 103 includes a rotor shaft 113 and a rotor 114 that is rotatably supported by the rotor shaft 113 and has a magnet 114a.

歯車伝達機構104は、ロータ軸113に形成されるピニオン114bと、このピニオン114bに噛み合う1番車115と、この1番車115と噛み合う2番車116と、この2番車116と噛み合う3番車117と、この3番車117と噛み合う4番車118と、この4番車118と噛み合うように出力軸105に設けられた歯車105aとからなる。出力軸105は、SUS等の金属より軽いPOM等の樹脂製で、歯車105aが一体成型で形成されており、出力軸105の一端105bは、上ケース112に隣接して配設される中地板119のしぼり加工による円筒部119aに回転可能に支持されている。また、出力軸105の中央は、平板状ケース120のしぼり加工により形成された支持円筒部120aに回転可能に支持されている。出力軸105の他端105cは、エアコンのルーバー駆動機構等に係合している。   The gear transmission mechanism 104 includes a pinion 114 b formed on the rotor shaft 113, a first wheel 115 engaged with the pinion 114 b, a second wheel 116 engaged with the first wheel 115, and a third wheel engaged with the second wheel 116. The vehicle 117 includes a fourth wheel 118 that meshes with the third wheel 117, and a gear 105 a that is provided on the output shaft 105 so as to mesh with the fourth wheel 118. The output shaft 105 is made of a resin such as POM which is lighter than a metal such as SUS, and a gear 105a is formed by integral molding. One end 105b of the output shaft 105 is a center plate disposed adjacent to the upper case 112. It is rotatably supported by the cylindrical portion 119a by the squeezing process 119. In addition, the center of the output shaft 105 is rotatably supported by a support cylindrical portion 120 a formed by squeezing the flat case 120. The other end 105c of the output shaft 105 is engaged with an air conditioner louver drive mechanism or the like.

ここで、外部から出力軸105に強い力が加わった場合、例えばエアコンのルーバーを人が強い力で動作させるような場合、出力軸105の回転は、ロータ114側へ伝えられていく。しかし、ステータ部102とマグネット114aとの間のリラクタンストルクによりロータ114には、その位置を保持しようとする力が働き、ロータ114は余程大きな力でないと回転を開始しない。このため、歯車伝達機構104は、そのいずれかの歯車部分で、歯の折れ等が生じ動作不良となってしまう。   Here, when a strong force is applied to the output shaft 105 from the outside, for example, when a person operates the louver of the air conditioner with a strong force, the rotation of the output shaft 105 is transmitted to the rotor 114 side. However, the reluctance torque between the stator portion 102 and the magnet 114a causes a force to maintain the position of the rotor 114, and the rotor 114 does not start rotating unless the force is too large. For this reason, the gear transmission mechanism 104 may be broken due to tooth breakage or the like at any of the gear portions.

そこで、本形態では、例えば、歯車伝達機構104の回転軸と筒状回転部材との間に、本発明を適用したフリクションドライブ装置1を設けてある。例えば、ロータ軸113とピニオン114bとの間、1番車115の回転軸と歯部との間、2番車116の回転軸と歯部との間、3番車117の回転軸と歯部との間、噛み合う4番車118の回転軸と歯部との間、あるいは出力軸105と歯車105aとの間に本発明を適用したフリクションドライブ装置1を設けてある。   Therefore, in this embodiment, for example, the friction drive device 1 to which the present invention is applied is provided between the rotating shaft of the gear transmission mechanism 104 and the cylindrical rotating member. For example, between the rotor shaft 113 and the pinion 114b, between the rotation shaft and the tooth portion of the first wheel 115, between the rotation shaft and the tooth portion of the second wheel 116, and the rotation shaft and the tooth portion of the third wheel 117 The friction drive device 1 to which the present invention is applied is provided between the rotating shaft and the tooth portion of the fourth wheel 118 engaged with each other, or between the output shaft 105 and the gear 105a.

かかる構成によれば、外部から出力軸105に強い力が加わった場合でも、歯車伝達機構104の歯車部分が損傷する等の不具合を防止することができる。また、出力軸105とエアコンのルーバー駆動機構側の歯車等の筒状回転部材との間に本発明を適用したフリクションドライブ装置1を設けてもよい。   According to this configuration, even when a strong force is applied to the output shaft 105 from the outside, problems such as damage to the gear portion of the gear transmission mechanism 104 can be prevented. Further, the friction drive device 1 to which the present invention is applied may be provided between the output shaft 105 and a cylindrical rotating member such as a gear on the louver drive mechanism side of the air conditioner.

1 フリクションドライブ装置
2 回転軸
3 環状部材
4 筒状回転部材
5 板状付勢部材
23 連結軸部
23a 塑性変形による変形部分
31 支持面
47 一方側凸部
49 他方側凸部
50 穴
50a 係合凹部(係合部)
56 内周部分
L 軸線方向
L1 一方側
L2 他方側
DESCRIPTION OF SYMBOLS 1 Friction drive apparatus 2 Rotating shaft 3 Annular member 4 Cylindrical rotating member 5 Plate-shaped biasing member 23 Connection shaft part 23a Deformation part 31 by plastic deformation Support surface 47 One side convex part 49 The other side convex part 50 Hole 50a Engaging concave part (Engagement part)
56 Inner circumference L Axial direction L1 One side L2 The other side

Claims (11)

軸線方向の途中部分で当該軸線方向の一方側に向く支持面が設けられた回転軸と、
前記支持面より前記一方側で前記回転軸に回転可能に嵌められて前記支持面に接する筒状回転部材と、
前記回転軸において前記筒状回転部材より前記一方側に位置する連結軸部に嵌められた環状の板状付勢部材と、
を有し、
前記連結軸部は、外側面が円形の丸棒状であり
前記板状付勢部材において前記連結軸部が嵌る穴の内周縁は、前記軸線に対して回転対称であり、当該穴の内周縁には、前記連結軸部の外周面からみて径方向外側に向けて凹んだ回り止め用の係合凹部が形成されており、
前記筒状回転部材の前記一方側の面には、前記穴より径方向外側に前記板状付勢部材に接する一方側凸部が形成されており、
前記連結軸部において前記板状付勢部材より前記一方側に位置する丸棒部分の外周面の全周を前記軸線方向の他方側に向けて塑性変形させた変形部分により、前記板状付勢部材の内周部分が前記他方側に押圧されて当該内周部分より径方向外側に位置する部分が前記筒状回転部材の前記一方側凸部に弾性をもって接しているとともに、前記変形部分のうち、前記係合凹部の内側に入り込んだ部分は、前記板状付勢部材の前記回転軸に対する回り止めとして機能していることを特徴とするフリクションドライブ装置。
A rotating shaft provided with a support surface facing toward one side in the axial direction in the middle of the axial direction;
A cylindrical rotating member that is rotatably fitted to the rotation shaft on the one side from the support surface and is in contact with the support surface;
An annular plate-shaped urging member fitted to a connecting shaft portion located on the one side of the cylindrical rotating member in the rotating shaft;
Have
The connecting shaft portion has a round bar shape whose outer surface is circular ,
The inner peripheral edge of the hole into which the connecting shaft portion fits in the plate-like biasing member is rotationally symmetric with respect to the axis, and the inner peripheral edge of the hole is radially outward as viewed from the outer peripheral surface of the connecting shaft portion. Engagement recesses for detents that are recessed toward are formed,
On the one side surface of the cylindrical rotating member, a one-side convex portion that is in contact with the plate-like biasing member is formed on the outer side in the radial direction from the hole,
In the connecting shaft portion , the plate-like urging force is generated by a deformed portion obtained by plastically deforming the entire outer periphery of the round bar portion located on the one side of the plate-like urging member toward the other side in the axial direction . The inner peripheral part of the member is pressed to the other side, and the part located radially outward from the inner peripheral part is in elastic contact with the one-side convex part of the cylindrical rotating member , and among the deformed parts The friction drive device is characterized in that the portion that enters the inside of the engaging recess functions as a detent for the plate-like urging member with respect to the rotating shaft .
前記板状付勢部材の前記穴は、丸穴であって、内周縁に前記係合凹部が形成されていることを特徴とする請求項1に記載のフリクションドライブ装置。 2. The friction drive device according to claim 1, wherein the hole of the plate-shaped biasing member is a round hole, and the engagement recess is formed in an inner peripheral edge . 前記係合凹部は、周方向の複数箇所に等角度間隔に形成されていることを特徴とする請求項2に記載のフリクションドライブ装置。 The friction drive device according to claim 2, wherein the engaging recesses are formed at equiangular intervals at a plurality of locations in the circumferential direction . 前記係合凹部は、半円形状をもって前記穴の内周縁から径方向外側に凹んでいることを特徴とする請求項2または3に記載のフリクションドライブ装置。 4. The friction drive device according to claim 2 , wherein the engaging recess has a semicircular shape and is recessed radially outward from an inner peripheral edge of the hole . 5. 前記係合凹部は、全体として、前記穴の内周縁の1/3に相当する角度範囲を占めるように複数形成されていることを特徴とする請求項4に記載のフリクションドライブ装置。 5. The friction drive device according to claim 4, wherein a plurality of the engaging recesses are formed so as to occupy an angle range corresponding to 1/3 of the inner peripheral edge of the hole as a whole . 前記係合凹部は、三角形状をもって前記穴の内周縁から径方向外側に凹んでいることを特徴とする請求項2または3に記載のフリクションドライブ装置。 4. The friction drive device according to claim 2 , wherein the engaging recess has a triangular shape and is recessed radially outward from an inner peripheral edge of the hole . 5. 前記穴および前記係合凹部は、多角形の穴を構成し、
前記多角形の角によって前記係合凹部が形成されていることを特徴とする請求項1に記載のフリクションドライブ装置。
The hole and the engagement recess constitute a polygonal hole,
The friction drive device according to claim 1, wherein the engagement recess is formed by a corner of the polygon .
前記多角形は正多角形であることを特徴とする請求項7に記載のフリクションドライブ装置。 The friction drive device according to claim 7, wherein the polygon is a regular polygon . 前記筒状回転部材には、前記他方側に向けて突出して前記支持面に接する他方側凸部が前記回転軸の周りに形成されていることを特徴とする請求項1乃至8の何れか一項に記載のフリクションドライブ装置。 The said tubular rotating member, any one of claims 1 to 8, characterized in that the other side protruding portion in contact with the supporting surface protrudes toward the other side is formed around the rotary shaft The friction drive device according to item . 前記支持面は、前記回転軸に嵌められた環状部材の前記一方側に向く面からなることを特徴とする請求項1乃至9の何れか一項に記載のフリクションドライブ装置。 The friction drive device according to any one of claims 1 to 9, wherein the support surface includes a surface facing the one side of the annular member fitted to the rotation shaft . 請求項1乃至10の何れか一項に記載のフリクションドライブ装置、モータ部、および歯車列を備えたギヤードモータであって、
前記回転軸は、前記モータ部のモータ軸、または前記歯車列において前記モータ軸の回転が伝達される歯車と一体に回転する回転軸のうちの何れかであることを特徴とするギヤードモータ
A friction drive device according to any one of claims 1 to 10, a motor unit, and a geared motor including a gear train,
The geared motor, wherein the rotating shaft is either a motor shaft of the motor unit or a rotating shaft that rotates integrally with a gear to which the rotation of the motor shaft is transmitted in the gear train .
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