JP6612838B2 - Screw type tensioner lifter for internal combustion engine - Google Patents

Screw type tensioner lifter for internal combustion engine Download PDF

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JP6612838B2
JP6612838B2 JP2017244739A JP2017244739A JP6612838B2 JP 6612838 B2 JP6612838 B2 JP 6612838B2 JP 2017244739 A JP2017244739 A JP 2017244739A JP 2017244739 A JP2017244739 A JP 2017244739A JP 6612838 B2 JP6612838 B2 JP 6612838B2
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shaft
screw
support
outer diameter
supported
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JP2019112962A (en
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治臣 杉田
勝弘 中道
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

本発明は、内周に雌ねじが刻設されるようにして少なくとも一部が円筒状に形成されるとともに機関本体内で走行する伝動帯に押圧力を付与することを可能とした押圧体と、前記雌ねじに螺合するシャフトと、前記機関本体に固定されるケーシングと、前記シャフトを前記押圧体と反対側から回動可能にスラスト支持して前記シャフトおよび前記ケーシング間に介装されるシャフト受け部材と、前記押圧体が前記伝動帯側に向けて進行する方向に前記シャフトを回動付勢しつつ前記ケーシングおよび前記シャフト間に設けられる弾性部材とを備える内燃機関のねじ式テンショナリフターに関する。   The present invention comprises a pressing body that is capable of applying a pressing force to a transmission band that is formed at least partially in a cylindrical shape so that a female screw is engraved on the inner periphery and travels within the engine body, A shaft that is screwed into the female screw, a casing that is fixed to the engine body, and a shaft receiver that is interposed between the shaft and the casing by thrust-supporting the shaft from the side opposite to the pressing body. The present invention relates to a screw type tensioner lifter for an internal combustion engine, comprising: a member; and an elastic member provided between the casing and the shaft while urging the shaft in a direction in which the pressing body advances toward the transmission band side.

伝動帯であるカムチェーンに押圧力を付与するための押圧体に螺合するシャフトが、機関本体に取り付けられるケーシングに、シャフト受け部材を介してスラスト支持されるようにした内燃機関のねじ式テンショナリフターが、たとえば特許文献１によって既に知られている。   A screw type tensioner for an internal combustion engine in which a shaft screwed to a pressing body for applying a pressing force to a cam chain which is a transmission band is thrust supported by a casing attached to the engine body via a shaft receiving member. A lifter is already known, for example from US Pat.

特開２００１−５００５６号公報JP 2001-50056 A

上記特許文献１で開示されたものでは、押圧体に螺合するようにしてシャフトが有するねじ部の外径よりも、シャフト受け部材へのシャフトの当接面の外径が小さく設定されており、カムチェーンからの反力によって雌ねじのねじ径にてシャフトに回転力が作用したときに、シャフト受け部材へのシャフトの当接部で前記回転力に打ち勝つだけの有効摩擦面積を確保できないことがある。その場合、カムチェーンに摺接しているカムチェーンテンショナーが本来収監されるべき位置に留まらず、最終的に異音が発生してしまう可能性がある。   In the one disclosed in Patent Document 1, the outer diameter of the contact surface of the shaft to the shaft receiving member is set to be smaller than the outer diameter of the screw portion of the shaft so as to be screwed into the pressing body. When the rotational force acts on the shaft with the thread diameter of the female thread due to the reaction force from the cam chain, it is not possible to secure an effective friction area sufficient to overcome the rotational force at the contact portion of the shaft with the shaft receiving member. is there. In this case, the cam chain tensioner that is in sliding contact with the cam chain does not stay at the position where it should be originally confined, and an abnormal noise may eventually occur.

ところで内燃機関の機関本体内部で発生するカムチェーンの乗り越え反力によって生成される反力は、一方向に押す一定の力ではなく、吸気弁および排気弁の開閉に伴って生じる交番荷重である。この交番荷重によるカムチェーン反力によって押されるシャフトは、そのシャフト受け部材との間での静摩擦係数による摩擦力で釣り合いをとることで適正なカムチェーン張力をカムチェーンに付与するのであるが、交番荷重が作用したときに、押圧体およびシャフトの螺合部での慣性力により、あたかも前記静摩擦係数に瞬間的な浮き上がりが生じて、静摩擦係数が見かけ上小さくなるという物理現象が知られている。このため内燃機関の運転中でのねじ式テンショナリフターの内部の静摩擦係数は、静的に計測された静摩擦係数よりも小さくなり、カムチェーン反力に負けて押圧体が戻ってしまい、上述のように異音の発生を招いていたという事実がある。   By the way, the reaction force generated by the overcoming reaction force of the cam chain that occurs inside the engine body of the internal combustion engine is not a constant force that pushes in one direction, but an alternating load that occurs as the intake and exhaust valves are opened and closed. The shaft pushed by the cam chain reaction force due to this alternating load gives the cam chain the proper cam chain tension by balancing with the frictional force due to the static friction coefficient with the shaft receiving member. A physical phenomenon is known in which when a load is applied, momentary lifting occurs in the static friction coefficient due to an inertial force at the threaded portion of the pressing body and the shaft, and the static friction coefficient is apparently reduced. For this reason, the static friction coefficient inside the screw tensioner lifter during operation of the internal combustion engine becomes smaller than the static friction coefficient measured statically, and the pressing body returns due to the cam chain reaction force, as described above. There is a fact that it was causing an abnormal sound.

本発明は、かかる事情に鑑みてなされたものであり、伝動帯からの反力による交番荷重が作用しても押圧体の戻りを回避して異音の発生を抑制し得るようにした内燃機関のねじ式テンショナリフターを提供することを目的とする。   The present invention has been made in view of such circumstances, and an internal combustion engine capable of suppressing the occurrence of abnormal noise by avoiding the return of the pressing body even when an alternating load due to a reaction force from the transmission band acts. An object of the present invention is to provide a screw type tensioner lifter.

上記目的を達成するために、本発明は、内周に雌ねじが刻設されるようにして少なくとも一部が円筒状に形成されるとともに機関本体内で走行する伝動帯に押圧力を付与することを可能とした押圧体と、前記雌ねじに螺合するシャフトと、前記機関本体に固定されるケーシングと、前記シャフトを前記押圧体と反対側から回動可能にスラスト支持して前記シャフトおよび前記ケーシング間に介装されるシャフト受け部材と、前記押圧体が前記伝動帯側に向けて進行する方向に前記シャフトを回動付勢しつつ前記ケーシングおよび前記シャフト間に設けられる弾性部材とを備える内燃機関のねじ式テンショナリフターにおいて、前記シャフトは、前記雌ねじに螺合する雄ねじが外周に刻設されるねじ部と、当該シャフトの軸線に沿う方向で前記シャフト受け部材に当接する当接面を有して前記ねじ部よりも大径に形成される被支持部と、前記ねじ部および前記被支持部間を同軸に結ぶ連結軸部とを一体に有し、前記被支持部の前記連結軸部とは反対の端面には、前記当接面の内周縁を規定しつつ該内周縁から径方向内向きに前記シャフト受け部材の内周縁を超えて伸びる凹部が、軸方向内向きに窪むようにして形成され、該凹部により、前記当接面の最小内径が、前記ねじ部の外径よりも大きく設定されることを第１の特徴とする。 In order to achieve the above-described object, the present invention provides a pressing force to a transmission band that is formed at least partially in a cylindrical shape so that a female screw is engraved on the inner periphery and travels within the engine body. A pressing body capable of rotating, a shaft screwed into the female screw, a casing fixed to the engine body, and a shaft that supports the shaft so that the shaft can be rotated from the side opposite to the pressing body. An internal combustion engine comprising: a shaft receiving member interposed therebetween; and an elastic member provided between the casing and the shaft while urging the shaft in a direction in which the pressing body advances toward the transmission band. In the threaded tensioner lifter for an engine, the shaft includes a threaded portion in which an external thread that engages with the internal thread is engraved on an outer periphery, and a direction along an axis of the shaft. A supported portion that has a contact surface that contacts the shaft receiving member and has a diameter larger than that of the threaded portion, and a connecting shaft portion that coaxially connects the threaded portion and the supported portion. An end surface of the supported portion opposite to the connection shaft portion defines an inner peripheral edge of the contact surface and extends radially inward from the inner peripheral edge of the shaft receiving member. The first feature is that the recess is formed so as to be recessed inward in the axial direction, and the minimum inner diameter of the contact surface is set larger than the outer diameter of the screw portion by the recess .

なお、実施の形態の環状凹部５３は上記凹部に対応する。The annular recess 53 in the embodiment corresponds to the recess.

また本発明は、内周に雌ねじが刻設されるようにして少なくとも一部が円筒状に形成されるとともに機関本体内で走行する伝動帯に押圧力を付与することを可能とした押圧体と、前記雌ねじに螺合するシャフトと、前記機関本体に固定されるケーシングと、前記シャフトを前記押圧体と反対側から回動可能にスラスト支持して前記シャフトおよび前記ケーシング間に介装されるシャフト受け部材と、前記押圧体が前記伝動帯側に向けて進行する方向に前記シャフトを回動付勢しつつ前記ケーシングおよび前記シャフト間に設けられる弾性部材とを備える内燃機関のねじ式テンショナリフターにおいて、前記シャフトは、前記雌ねじに螺合する雄ねじが外周に刻設されるねじ部と、当該シャフトの軸線に沿う方向で前記シャフト受け部材に当接する当接面を有して前記ねじ部よりも大径に形成される被支持部と、前記ねじ部および前記被支持部間を同軸に結ぶ連結軸部とを一体に有し、前記当接面の最小内径が、前記ねじ部の外径よりも大きく設定され、前記シャフト受け部材に、前記被支持部の外周の少なくとも一部を囲繞する円筒状の側壁部と、前記ケーシングに形成される支持孔に嵌入される円筒状の支持筒部とが一体に設けられ、前記ねじ部の外径よりも小径にして前記被支持部から同軸に突出するとともに前記支持筒部に挿入される支持軸部が前記シャフトに設けられ、前記支持軸部の外周および前記支持筒部の内周間の間隙が、前記側壁部の内周および前記被支持部の外周間の間隙よりも小さく設定されることを第２の特徴とする。 Also, the present invention provides a pressing body that is capable of applying a pressing force to a transmission band that is formed at least partially in a cylindrical shape so that a female screw is engraved on the inner periphery and that travels within the engine body. A shaft screwed into the female screw, a casing fixed to the engine body, and a shaft interposed between the shaft and the casing by thrust-supporting the shaft from the opposite side to the pressing body. In a screw-type tensioner lifter for an internal combustion engine, comprising: a receiving member; and an elastic member provided between the casing and the shaft while urging the shaft in a direction in which the pressing body advances toward the transmission band. The shaft is in contact with the shaft receiving member in a direction along the axis of the shaft, and a threaded portion in which an external thread that engages with the internal thread is engraved. A supported portion that has a contact surface that is larger in diameter than the screw portion, and a connecting shaft portion that coaxially connects the screw portion and the supported portion. A minimum inner diameter of the surface is set to be larger than an outer diameter of the screw portion, and the shaft receiving member is formed in the cylindrical side wall portion that surrounds at least a part of the outer periphery of the supported portion, and the casing. A support shaft that is integrally provided with a cylindrical support tube portion that is fitted into the support hole, has a smaller diameter than the outer diameter of the screw portion, protrudes coaxially from the supported portion, and is inserted into the support tube portion A portion is provided on the shaft, and a gap between the outer periphery of the support shaft portion and the inner periphery of the support cylinder portion is set smaller than a gap between the inner periphery of the side wall portion and the outer periphery of the supported portion. Is the second feature.

本発明は、第２の特徴の構成に加えて、前記被支持部の前記連結軸部とは反対の端面に、前記当接面が形成されるとともに、前記ねじ部の外径よりも大きな内径を有する環状凹部が前記当接面の内周縁を規定しつつ前記支持軸部を囲むようにして形成されることを第３の特徴とする。   In the present invention, in addition to the configuration of the second feature, the contact surface is formed on the end surface of the supported portion opposite to the connection shaft portion, and the inner diameter is larger than the outer diameter of the screw portion. A third feature is that an annular recess having a shape is formed so as to surround the support shaft portion while defining an inner peripheral edge of the contact surface.

本発明は、第２または第３の特徴の構成に加えて、前記支持軸部の前記支持筒部内での軸方向長さが、当該支持軸部の外径よりも大きく設定されることを第４の特徴とする。   According to the present invention, in addition to the configuration of the second or third feature, the axial length of the support shaft portion in the support cylinder portion is set to be larger than the outer diameter of the support shaft portion. 4 features.

本発明は、第２〜第４の特徴の構成のいずれかに加えて、前記被支持部の最大外径が、前記ねじ部の外径よりも大きく、かつ前記ねじ部の外径の３倍以下に設定されることを第５の特徴とする。   According to the present invention, in addition to any of the configurations of the second to fourth features, the maximum outer diameter of the supported portion is larger than the outer diameter of the screw portion and is three times the outer diameter of the screw portion. The fifth feature is to be set as follows.

さらに本発明は、第２〜第５の特徴の構成のいずれかに加えて、前記シャフトのうち少なくとも前記支持軸部と、前記シャフト受け部材の前記支持筒部とに、すり割りが形成されることを第６の特徴とする。   Further, according to the present invention, in addition to any of the configurations of the second to fifth features, a slit is formed in at least the support shaft portion of the shaft and the support tube portion of the shaft receiving member. This is the sixth feature.

本発明の第１の特徴によれば、シャフトの被支持部に形成されてシャフト受け部材に当接する当接面の最小内径が、押圧体の雌ねじに螺合する雄ねじが外周に刻設されたねじ部の外径よりも大きいので、押圧体およびシャフトの螺合部の径よりも大きい径でシャフトにかかる荷重をシャフト受け部材で受けるようにしつつ、シャフト受け部材でシャフトを受ける面積を充分に大きくすることで、伝動帯からの交番荷重が作用する状態にあってもシャフト受け部材へのシャフトの当接部で前記交番荷重による回転力に打ち勝つだけの有効摩擦面積を確保して、異音の発生を抑制することができる。しかも、当接面の内周縁を規定する凹部が、被支持部の連結軸部とは反対の端面に形成され、この凹部により当接面の最小内径がねじ部の外径よりも大きく設定されるので、当接面の最小内径がねじ部の外径よりも大きい構造を簡単に構成しつつ当接面の面積を大きくし、異音発生を効果的に抑制することができる。 According to the first feature of the present invention, the minimum inner diameter of the abutting surface formed on the supported portion of the shaft and abutting on the shaft receiving member is engraved on the outer periphery of the male screw that engages with the female screw of the pressing body. Since it is larger than the outer diameter of the threaded portion, the shaft receiving member receives the load applied to the shaft with a diameter larger than the diameter of the pressing body and the screwed portion of the shaft, and the shaft receiving member has a sufficient area for receiving the shaft. By enlarging, an effective friction area that can overcome the rotational force due to the alternating load is secured at the abutting portion of the shaft against the shaft receiving member even in a state where an alternating load from the transmission band acts, Can be suppressed. In addition, a recess that defines the inner peripheral edge of the contact surface is formed on the end surface opposite to the connecting shaft portion of the supported portion, and the minimum inner diameter of the contact surface is set larger than the outer diameter of the threaded portion by this recess. Therefore, it is possible to increase the area of the abutment surface while effectively configuring a structure in which the minimum inner diameter of the abutment surface is larger than the outer diameter of the threaded portion, and to effectively suppress the generation of noise.

また本発明の第２の特徴によれば、シャフト受け部材に、円筒状の側壁部と、ケーシングの支持孔に嵌入される円筒状の支持筒部とが一体に設けられ、ねじ部の外径よりも小径に形成されてシャフトの被支持部から同軸に突出しつつ支持筒部に挿入される支持軸部の外周および支持筒部の内周間の間隙が、側壁部の内周および被支持部の外周間の間隙よりも小さいので、ねじ部の外径よりも小径の支持軸部がシャフト受け部材で支持されるようにすることで、機関回転数によるあらゆる周波数の交番荷重下でも、シャフトが慣性力で傾いたりするような不安定な姿勢になることを回避しつつ、小さな摩擦力で挙動の安定化を保持することができる。   According to the second feature of the present invention, the shaft receiving member is integrally provided with a cylindrical side wall portion and a cylindrical support cylinder portion fitted into the support hole of the casing, and the outer diameter of the screw portion. The gap between the outer periphery of the support shaft portion and the inner periphery of the support tube portion inserted into the support tube portion while being coaxially projected from the supported portion of the shaft is smaller than the inner periphery of the side wall portion and the supported portion. Since the support shaft portion smaller in diameter than the outer diameter of the screw portion is supported by the shaft receiving member, the shaft can be operated under alternating loads of all frequencies depending on the engine speed. Stabilization of behavior can be maintained with a small frictional force while avoiding an unstable posture such as tilting due to inertial force.

本発明の第３の特徴によれば、当接面の内周縁を規定する環状凹部が、被支持部の連結軸部とは反対の端面に形成され、環状凹部の内径がねじ部の外径よりも大きいので、当接面の最小内径がねじ部の外径よりも大きい構造を簡単に構成しつつ当接面の面積を大きくし、異音発生を効果的に抑制することができる。   According to the third feature of the present invention, the annular recess defining the inner peripheral edge of the contact surface is formed on the end surface opposite to the connecting shaft portion of the supported portion, and the inner diameter of the annular recess is the outer diameter of the screw portion. Therefore, it is possible to increase the area of the abutting surface while easily constructing a structure in which the minimum inner diameter of the abutting surface is larger than the outer diameter of the threaded portion, thereby effectively suppressing the generation of noise.

本発明の第４の特徴によれば、支持軸部の支持筒部内での軸方向長さが当該支持軸部の外径よりも大きいので、支持筒部による支持軸部ひいてはシャフトの支持を安定化することができる。   According to the fourth feature of the present invention, since the axial length of the support shaft portion in the support tube portion is larger than the outer diameter of the support shaft portion, the support shaft portion by the support tube portion, and thus the shaft is stably supported. Can be

本発明の第５の特徴によれば、被支持部の最大外径がねじ部の外径よりも大きく、かつねじ部の外径の３倍以下であるので、被支持部が径方向で過度に大きくなることを回避しつつ当接面の面積を充分に確保することができる。   According to the fifth feature of the present invention, since the maximum outer diameter of the supported portion is larger than the outer diameter of the screw portion and not more than three times the outer diameter of the screw portion, the supported portion is excessive in the radial direction. It is possible to ensure a sufficient area of the contact surface while avoiding the increase in size.

さらに本発明の第６の特徴によれば、シャフトのうち少なくとも前記支持軸部と、シャフト受け部材の支持筒部とにすり割りがあることで、それらのすり割りを利用してシャフトおよびシャフト受け部材間への給油を容易とすることができる。   Furthermore, according to the sixth aspect of the present invention, there is a slit in at least the support shaft portion of the shaft and the support tube portion of the shaft receiving member, and the shaft and the shaft receiver are utilized using these slits. Oil supply between members can be facilitated.

実施の形態の機関本体の縦断側面図である。It is a vertical sectional side view of an engine body of implementation forms. ねじ式テンショナリフターの拡大断面図であるIt is an expanded sectional view of a screw type tensioner lifter. 参考形態のねじ式テンショナリフターの断面図である。It is sectional drawing of the screw type tensioner lifter of a reference form.

以下、本発明の実施の形態および参考形態を、添付の図面を参照しながら説明する。 Embodiments and reference embodiments of the present invention will be described below with reference to the accompanying drawings.

本発明の第１の実施の形態について図１および図２を参照しながら説明すると、先ず図１において、たとえば自動二輪車に搭載される内燃機関Ｅの機関本体１１は、クランクシャフト１６を回転自在に支持するクランクケース１２と、該クランクケース１２に結合されるシリンダボディ１３と、該シリンダボディ１３に結合されるシリンダヘッド１４と、該シリンダヘッド１４に結合されるヘッドカバー１５とを備えるものであり、クランクシャフト１６の軸線と平行な軸線を有するカムシャフト１７が、前記シリンダヘッド１４に設けられるホルダ１８と、該ホルダ１８に締結されるホルダキャップ１９とで回転自在に支持される。   A first embodiment of the present invention will be described with reference to FIGS. 1 and 2. First, in FIG. 1, for example, an engine body 11 of an internal combustion engine E mounted on a motorcycle can rotate a crankshaft 16. A crankcase 12 to be supported, a cylinder body 13 coupled to the crankcase 12, a cylinder head 14 coupled to the cylinder body 13, and a head cover 15 coupled to the cylinder head 14. A camshaft 17 having an axis parallel to the axis of the crankshaft 16 is rotatably supported by a holder 18 provided on the cylinder head 14 and a holder cap 19 fastened to the holder 18.

前記カムシャフト１７にはクランクシャフト１６からの回転動力が調時伝動機構２０により１／２に減速されて伝達されるものであり、この調時伝動機構２０は、クランクシャフト１６に固設される駆動スプロケット２１と、前記カムシャフト１７の一端部に固設される従動スプロケット２２と、駆動スプロケット２１および従動スプロケット２２に巻き掛けられる無端状の伝動帯としてのカムチェーン２３とから成る。   Rotational power from the crankshaft 16 is transmitted to the camshaft 17 by being reduced by a half by a timing transmission mechanism 20, and the timing transmission mechanism 20 is fixed to the crankshaft 16. The driving sprocket 21, a driven sprocket 22 fixed to one end of the camshaft 17, and a cam chain 23 as an endless transmission band wound around the driving sprocket 21 and the driven sprocket 22.

ところで、駆動スプロケット２１は矢印２４で示す方向に回転するものであり、駆動スプロケット２１および従動スプロケット２２間のカムチェーン２３のうち駆動スプロケット２１から送り出される側である弛緩側外周にはチェーンテンショナー２５が当接しており、このチェーンテンショナー２５にカムチェーン２３と反対側から当接するねじ式テンショナリフター２６が機関本体１１の前記シリンダボディ１３に取付けられる。また駆動スプロケット２１および従動スプロケット２２間のカムチェーン２３のうち駆動スプロケット２１で牽引される側である緊張側外周にはカムチェーンガイド２７が当接される。   Incidentally, the drive sprocket 21 rotates in the direction indicated by the arrow 24, and a chain tensioner 25 is provided on the outer periphery of the loose side, which is the side fed from the drive sprocket 21, of the cam chain 23 between the drive sprocket 21 and the driven sprocket 22. A threaded tensioner lifter 26 that is in contact with the chain tensioner 25 from the side opposite to the cam chain 23 is attached to the cylinder body 13 of the engine body 11. A cam chain guide 27 is brought into contact with the outer periphery of the tension side, which is the side pulled by the drive sprocket 21, of the cam chain 23 between the drive sprocket 21 and the driven sprocket 22.

カムチェーンガイド２７は適度な剛性および弾性を有する合成樹脂によってカムチェーン２３側に向けて反った略弓形をなすように形成される。カムチェーンガイド２７のクランクシャフト１６側端部である一端部２７ａは、上方に開いてクランクケース１２に設けられる支持凹部２８に嵌合、支持される。またカムチェーンガイド２７のカムシャフト１７側である他端側には前記カムチェーン２３とは反対側に臨む支持面２７ｂが形成されており、該支持面２７ｂに当接する当接支持軸部２９がシリンダヘッド１４に突設される。またカムチェーンガイド２７の前記支持面２７ｂ寄り中間部両側には、横断面円形の突起３０が一体に突設され、その突起３０は、シリンダボディ１３のシリンダヘッド１４への結合面に設けられた凹部３１に嵌合されてシリンダボディ１３およびシリンダヘッド１４間に挟まれる。 Cam chain guide 27 is formed so as to form a substantially arcuate were anti Tsu toward the side cam chain 23 of a synthetic resin having appropriate stiffness and elasticity. One end portion 27a which is the end portion of the cam chain guide 27 on the crankshaft 16 side is fitted upward and supported by a support recess 28 provided in the crankcase 12. Further, a support surface 27b facing the opposite side of the cam chain 23 is formed on the other end side of the cam chain guide 27 on the camshaft 17 side, and a contact support shaft portion 29 that contacts the support surface 27b is formed. The cylinder head 14 is projected. Further, on both sides of the intermediate portion of the cam chain guide 27 near the support surface 27b, a protrusion 30 having a circular cross section is integrally provided, and the protrusion 30 is provided on a connecting surface of the cylinder body 13 to the cylinder head 14. It fits into the recess 31 and is sandwiched between the cylinder body 13 and the cylinder head 14.

また前記チェーンテンショナー２５は、カムチェーン２３の弛緩側外周に凸曲面を摺接させるようにして弓形に形成され、該チェーンテンショナー２５の前記クランクシャフト１６側の一端部は、枢軸３２を介してクランクケース１２に回動可能に支持される。   The chain tensioner 25 is formed in an arch shape so that a convex curved surface is slidably contacted with the outer periphery of the cam chain 23, and one end portion of the chain tensioner 25 on the crankshaft 16 side is cranked via a pivot 32. The case 12 is rotatably supported.

前記カムチェーン２３の弛緩側に張りを与えるべく、前記チェーンテンショナー２５には、カムチェーン２３と反対側からねじ式テンショナリフター２６の押圧体３４が当接される。   A pressing body 34 of a screw type tensioner lifter 26 is brought into contact with the chain tensioner 25 from the side opposite to the cam chain 23 in order to give tension to the relaxation side of the cam chain 23.

図２を併せて参照して、前記ねじ式テンショナリフター２６は、内周に雌ねじ４１が刻設されるようにして少なくとも一部が円筒状に形成されるとともに前記カムチェーン２３に押圧力を付与することを可能とした押圧体３４と、前記雌ねじ４１に螺合するシャフト３５と、前記機関本体１１の前記シリンダボディ１３に固定されるケーシング３６と、前記シャフト３５を前記押圧体３４と反対側から回動可能にスラスト支持するようにして前記シャフト３５および前記ケーシング３６間に介装されるシャフト受け部材３７と、前記押圧体３４が前記カムチェーン２３側に向けて進行する方向に前記シャフト３５を回動付勢して前記ケーシング３６および前記シャフト３５間に設けられる弾性部材としてのゼンマイばね３８とを備える。   Referring also to FIG. 2, the threaded tensioner lifter 26 is formed at least partially in a cylindrical shape so that a female screw 41 is engraved on the inner periphery, and applies a pressing force to the cam chain 23. A pressing body 34 that can be engaged, a shaft 35 that is screwed into the female screw 41, a casing 36 that is fixed to the cylinder body 13 of the engine body 11, and the shaft 35 that is opposite to the pressing body 34. A shaft receiving member 37 interposed between the shaft 35 and the casing 36 so as to be thrust-supported so as to be rotatable, and the shaft 35 in a direction in which the pressing body 34 advances toward the cam chain 23 side. And a mainspring spring 38 as an elastic member provided between the casing 36 and the shaft 35.

前記押圧体３４は、この実施の形態では、円筒状の筒部材３９の一端部に、前記チェーンテンショナー２５に当接するキャップ４０が装着されて成るものであり、前記筒部材３９の内周に雌ねじ４１が刻設される。   In this embodiment, the pressing body 34 is configured such that a cap 40 that contacts the chain tensioner 25 is attached to one end of a cylindrical tube member 39. 41 is engraved.

前記ケーシング３６は、前記カムチェーン２３を走行させるべく前記機関本体１１に形成されているカムチェーン通路４２（図１参照）側に一端部（内端部）を開口する円筒部３６ａと、その円筒部３６ａの他端部（外端部）を閉じる端壁部３６ｂと、当該端壁部３６ｂから半径方向外方に張り出すフランジ部３６ｃとを一体に有するように形成される。一方、前記シリンダボディ１３には、前記円筒部３６ａを挿入させる取付け孔４３が設けられ、この取付け孔４３の外端開口部の周囲で前記シリンダボディ１３に設けられている取付け座４４に、前記フランジ部３６ｃが複数のボルト４５によって締結される。また前記ケーシング３６における前記円筒部３６ａの一端部には、前記押圧体３４における前記筒部材３９の軸方向移動をガイドするガイド部材４６がＣ形の止め輪４７で取り付けられる。 The casing 36 includes a cylindrical portion 36a that opens at one end (inner end) on the side of the cam chain passage 42 (see FIG. 1) formed in the engine body 11 so that the cam chain 23 travels, and the cylinder. An end wall portion 36b that closes the other end portion (outer end portion) of the portion 36a and a flange portion 36c that protrudes radially outward from the end wall portion 36b are integrally formed. On the other hand, the cylinder body 13 is provided with a mounting hole 43 into which the cylindrical portion 36a is inserted, and the mounting seat 44 provided in the cylinder body 13 around the outer end opening of the mounting hole 43 is provided with the mounting seat 44. The flange portion 3 6 c is fastened by a plurality of bolts 45. A guide member 46 that guides the axial movement of the cylindrical member 39 in the pressing body 34 is attached to one end portion of the cylindrical portion 36 a in the casing 36 with a C-shaped retaining ring 47.

前記シャフト３５は、前記雌ねじ４１に螺合する雄ねじ４８が外周に刻設されるねじ部３５ａと、当該シャフト３５の軸線に沿う方向で前記シャフト受け部材３７に当接する当接面４９を有して前記ねじ部３５ａよりも大径に形成される被支持部３５ｂと、前記ねじ部３５ａおよび前記被支持部３５ｂ間を同軸に結ぶ連結軸部３５ｃと、前記被支持部３５ｂから同軸に突出する支持軸部３５ｄとを一体に有するように形成される。   The shaft 35 has a threaded portion 35a in which an external thread 48 that engages with the internal thread 41 is engraved on the outer periphery, and a contact surface 49 that contacts the shaft receiving member 37 in a direction along the axis of the shaft 35. A supported portion 35b having a larger diameter than the screw portion 35a, a connecting shaft portion 35c that coaxially connects the screw portion 35a and the supported portion 35b, and a coaxial projection from the supported portion 35b. The support shaft portion 35d is integrally formed.

前記ゼンマイばね３８は、前記押圧体３４における前記筒部材３９の他端に当接するワッシャ５０および前記被支持部３５ｂ間で前記連結軸部３５ｃの一部を囲繞するように配置されるものであり、前記ケーシング３６の前記円筒部３６ａおよび前記連結軸部３５ｃ間に設けられる。   The spring spring 38 is disposed so as to surround a part of the coupling shaft portion 35c between the washer 50 that contacts the other end of the cylindrical member 39 in the pressing body 34 and the supported portion 35b. The casing 36 is provided between the cylindrical portion 36a and the connecting shaft portion 35c.

前記シャフト受け部材３７は、カップワッシャであり、前記当接面４９に一部を当接させるリング板状の受け板部３７ａと、この受け板部３７ａの外周に直角に連なって前記被支持部３５ｂの外周の少なくとも一部（この実施の形態では全外周）を囲繞する円筒状の側壁部３７ｂと、前記受け板部３７ａの内周に直角に連なって前記側壁部３７ｂとは反対側に延びる円筒状の支持筒部３７ｃとを一体に有するように形成される。   The shaft receiving member 37 is a cup washer, and has a ring plate-like receiving plate portion 37a that makes a part of the shaft receiving member 49 contact the contact surface 49, and the supported portion connected to the outer periphery of the receiving plate portion 37a at a right angle. A cylindrical side wall portion 37b that surrounds at least a part of the outer periphery of 35b (the entire outer periphery in this embodiment), and extends in a direction perpendicular to the inner periphery of the receiving plate portion 37a and extends opposite to the side wall portion 37b. It is formed so as to integrally have a cylindrical support cylinder portion 37c.

一方、前記ケーシング３６の前記端壁部３６ｂには、前記シャフト受け部材３７のうち前記受け板部３７ａおよび前記側壁部３７ｂを受け入れる収容凹部５１と、前記支持筒部３７ｃを嵌入させるようにして前記収容凹部５１に同軸に連なる支持孔５２とが設けられる。 On the other hand, the end wall portion 36b of the casing 36 includes a housing recess 5 1 for receiving the receiving plate portion 37a and the side wall portion 37b of the shaft receiving member 37, so as to fit the support tube portion 37c a support hole 5 2 coaxially connected to is provided in the housing recess 5 1.

前記被支持部３５ｂの前記当接面４９は、当該被支持部３５ｂの前記連結軸部３５ｃとは反対の端面に、前記シャフト受け部材３７の前記受け板部３７ａに当接するようにしてリング状の平坦面に形成されるものであり、この当接面４９の最小内径Ｄ１が、前記ねじ部３５ａの外径Ｄ２よりも大きく設定される。 The abutment surface 49 of the supported portion 35b is in a ring so as to abut on the receiving plate portion 37a of the shaft receiving member 37 on the end surface of the supported portion 35b opposite to the connecting shaft portion 35c. The minimum inner diameter D1 of the contact surface 49 is set larger than the outer diameter D2 of the screw portion 35a.

しかも前記被支持部３５ｂの最大外径Ｄ３は、前記ねじ部３５ａの外径Ｄ２よりも大きく、かつ前記ねじ部３５ａの外径Ｄ２の３倍以下に設定される。 Moreover the maximum outer diameter D3 of the supported portion 35b is larger than the outer diameter D2 of the threaded portion 35a, and is set to below 3 times the outer diameter D 2 of the threaded portion 35a.

また前記被支持部３５ｂの前記連結軸部３５ｃとは反対の端面には、前記当接面４９の内周縁を規定しつつ該内周縁から径方向内向きに前記シャフト受け部材３７の内周縁を超えて伸び、前記支持軸部３５ｄを囲む環状凹部５３が、前記ねじ部３５ａの外径Ｄ２よりも大きな内径すなわち前記当接面４９の最小内径Ｄ１を有するようにして形成される。 Further, the inner peripheral edge of the shaft receiving member 37 is radially inward from the inner peripheral edge while defining the inner peripheral edge of the contact surface 49 on the end surface of the supported part 35b opposite to the connecting shaft part 35c. An annular recess 53 that extends beyond and surrounds the support shaft portion 35d is formed to have an inner diameter larger than the outer diameter D2 of the screw portion 35a, that is, the minimum inner diameter D1 of the contact surface 49.

前記シャフト３５の前記支持軸部３５ｄは、前記ねじ部３５ａの外径Ｄ２よりも小径にして前記被支持部３５ｂから同軸に突出するとともに、前記シャフト受け部材３７の前記支持筒部３７ｃに挿入されるものであり、前記支持軸部３５ｄの外周および前記支持筒部３７ｃの内周間の間隙ｄ１は、前記シャフト受け部材３７における前記側壁部３７ｂの内周および前記被支持部３５ｂの外周間の間隙ｄ２よりも小さく設定される。また前記支持軸部３５ｄの前記支持筒部３７ｃ内での軸方向長さＬ１は、当該支持軸部３５ｄの外径Ｄ４よりも大きく設定される。 The support shaft portion 35d of the shaft 35 is inserted with and smaller in diameter than the outer diameter D 2 projecting coaxially from the supported portion 35b of the threaded portion 35a, to the support tube portion 37c of the shaft receiving member 37 The gap d1 between the outer periphery of the support shaft portion 35d and the inner periphery of the support cylinder portion 37c is between the inner periphery of the side wall portion 37b and the outer periphery of the supported portion 35b in the shaft receiving member 37. Is set smaller than the gap d2. The axial length L1 of the support shaft portion 35d in the support cylinder portion 37c is set to be larger than the outer diameter D4 of the support shaft portion 35d.

前記シャフト３５のうち少なくとも支持軸部３５ｄ、この実施の形態では前記支持軸部３５ｄから前記被支持部３５ｂを経て前記連結軸部３５ｃの中間部に至るまでの間には、一直径線に沿うすり割り５４が形成される。このすり割り５４には、前記押圧体３４の前記キャップ４０が前記チェーンテンショナー２５に当接する前に平板状のストッパ５５を係合して前記シャフト３５の回転を阻止することが可能であり、前記支持孔５２の外端開口縁には、前記ストッパ５５を係合させる一対ずつ２組の係止凹部５６が、各組の係止凹部５６を前記支持孔５２の直径線上に配置するようにして形成される。   At least the support shaft portion 35d of the shaft 35, and in this embodiment, extends from the support shaft portion 35d through the supported portion 35b to the intermediate portion of the connection shaft portion 35c along a single diameter line. A slot 54 is formed. The slit 54 can engage with a flat stopper 55 before the cap 40 of the pressing body 34 contacts the chain tensioner 25 to prevent the shaft 35 from rotating. Two pairs of locking recesses 56 for engaging the stopper 55 are arranged at the outer edge opening edge of the support hole 52 so that each set of locking recesses 56 is arranged on the diameter line of the support hole 52. It is formed.

前記押圧体３４の前記キャップ４０が前記チェーンテンショナー２５に当接した後に前記ストッパ５５を抜き出した後には、前記支持孔５２の外端部に栓部材５７が螺合される。さらに前記シャフト受け部材３７の前記支持筒部３７ｃにもその全長にわたるすり割り５８が形成される。   After the stopper 55 is extracted after the cap 40 of the pressing body 34 contacts the chain tensioner 25, the plug member 57 is screwed into the outer end portion of the support hole 52. Further, a slit 58 extending over the entire length of the support cylinder portion 37c of the shaft receiving member 37 is also formed.

次にこの実施の形態の作用について説明すると、ねじ式テンショナリフター２６のシャフト３５は、押圧体３４の雌ねじ４１に螺合する雄ねじ４８が外周に刻設されるねじ部３５ａと、当該シャフト３５の軸線に沿う方向でシャフト受け部材３７に当接する当接面４９を有して前記ねじ部３５ａよりも大径に形成される被支持部３５ｂと、前記ねじ部３５ａおよび前記被支持部３５ｂ間を同軸に結ぶ連結軸部３５ｃとを一体に有し、前記当接面４９の最小内径Ｄ１が、前記ねじ部３５ａの外径Ｄ２よりも大きく設定されるので、押圧体３４およびシャフト３５の螺合部の径よりも大きい径でシャフト３５にかかる荷重をシャフト受け部材３７で受けるようにしつつ、シャフト受け部材３７でシャフト３５を受ける面積を充分に大きくすることで、カムチェーン２３からの交番荷重が作用する状態にあってもシャフト受け部材３７へのシャフト３５の当接部で前記交番荷重による回転力に打ち勝つだけの有効摩擦面積を確保して、異音の発生を抑制することができる。 To describe the operation of the implementation in the form of Tsuginiko, shaft 35 of the screw tensioner lifter 26 includes a threaded portion 35a of the male screw 48 screwed into the internal thread 41 of the pressing body 34 is engraved on the outer periphery, the shaft A supported portion 35b having a contact surface 49 that contacts the shaft receiving member 37 in a direction along the axis of 35 and having a diameter larger than that of the screw portion 35a, and the screw portion 35a and the supported portion 35b. And a connecting shaft portion 35c that is coaxially connected to each other, and a minimum inner diameter D1 of the contact surface 49 is set larger than an outer diameter D2 of the screw portion 35a. The shaft receiving member 37 has a sufficiently large area for receiving the shaft 35 while receiving the load applied to the shaft 35 with a diameter larger than the diameter of the threaded portion. Even in a state where an alternating load from the cam chain 23 is applied, an effective friction area sufficient to overcome the rotational force due to the alternating load is secured at the contact portion of the shaft 35 with the shaft receiving member 37, and an abnormal noise can be obtained. Occurrence can be suppressed.

また前記シャフト受け部材３７に、前記被支持部３５ｂの外周の少なくとも一部を囲繞する円筒状の側壁部３７ｂと、ケーシング３６に形成される支持孔５２に嵌入される円筒状の支持筒部３７ｃとが一体に設けられ、前記ねじ部３５ａの外径Ｄ２よりも小径にして前記被支持部３５ｂから同軸に突出するとともに前記支持筒部３７ｃに挿入される支持軸部３５ｄが前記シャフト３５に設けられ、前記支持軸部３５ｄの外周および前記支持筒部３７ｃの内周間の間隙ｄ１が、前記側壁部３７ｂの内周および前記被支持部３５ｂの外周間の間隙ｄ２よりも小さく設定されるので、ねじ部３５ａの外径よりも小径の支持軸部３５ｄがシャフト受け部材３７で支持されるようにすることで、機関回転数によるあらゆる周波数の交番荷重下でも、シャフト３５が慣性力で傾いたりするような不安定な姿勢になることを回避しつつ、小さな摩擦力で挙動の安定化を保持することができる。   The shaft receiving member 37 has a cylindrical side wall portion 37b that surrounds at least a part of the outer periphery of the supported portion 35b, and a cylindrical support cylinder portion 37c that is fitted into a support hole 52 formed in the casing 36. The shaft 35 is provided with a support shaft portion 35d that is smaller than the outer diameter D2 of the screw portion 35a and protrudes coaxially from the supported portion 35b and is inserted into the support cylinder portion 37c. The gap d1 between the outer periphery of the support shaft portion 35d and the inner periphery of the support cylinder portion 37c is set smaller than the gap d2 between the inner periphery of the side wall portion 37b and the outer periphery of the supported portion 35b. By supporting the support shaft portion 35d having a smaller diameter than the outer diameter of the screw portion 35a by the shaft receiving member 37, the shaft can be shut even under alternating loads of all frequencies depending on the engine speed. While avoiding that the bets 35 in an unstable posture such that tilting inertial force, it is possible to retain the stabilization of behavior with a small frictional force.

また前記被支持部３５ｂの前記連結軸部３５ｃとは反対の端面に、前記当接面４９が形成されるとともに、前記ねじ部３５ａの外径よりも大きな内径を有する環状凹部５３が前記当接面４９の内周縁を規定しつつ前記支持軸部３５ｄを囲むようにして形成されるので、当接面４９の最小内径Ｄ１がねじ部３５ａの外径Ｄ２よりも大きい構造を簡単に構成しつつ当接面４９の面積を大きくし、異音発生を効果的に抑制することができる。   Further, the contact surface 49 is formed on the end surface of the supported portion 35b opposite to the connecting shaft portion 35c, and an annular recess 53 having an inner diameter larger than the outer diameter of the screw portion 35a is formed in the contact surface. Since the inner peripheral edge of the surface 49 is defined so as to surround the support shaft portion 35d, the contact surface 49 is in contact with the minimum inner diameter D1 larger than the outer diameter D2 of the screw portion 35a. The area of the surface 49 can be increased, and abnormal noise generation can be effectively suppressed.

また前記支持軸部３５ｄの前記支持筒部３７ｃ内での軸方向長さＬ１が、当該支持軸部３５ｄの外径Ｄ４よりも大きく設定されるので、支持筒部３７ｃによる支持軸部３５ｄひいてはシャフト３５の支持を安定化することができる。   Further, since the axial length L1 of the support shaft portion 35d in the support cylinder portion 37c is set to be larger than the outer diameter D4 of the support shaft portion 35d, the support shaft portion 35d by the support cylinder portion 37c and thus the shaft. The support of 35 can be stabilized.

また被支持部３５ｂの最大外径Ｄ３がねじ部３５ａの外径Ｄ２よりも大きく、かつねじ部３５ａの外径Ｄ２の３倍以下であるので、被支持部３５ｂが径方向で過度に大きくなることを回避しつつ当接面４９の面積を充分に確保することができる。   Further, since the maximum outer diameter D3 of the supported portion 35b is larger than the outer diameter D2 of the screw portion 35a and not more than three times the outer diameter D2 of the screw portion 35a, the supported portion 35b becomes excessively large in the radial direction. The area of the contact surface 49 can be sufficiently secured while avoiding this.

さらに前記シャフト３５のうち少なくとも前記支持軸部３５ｄと、前記シャフト受け部材３７の前記支持筒部３７ｃとに、すり割り５４，５８が形成されるので、それらのすり割り５４，５８を利用してシャフト３５およびシャフト受け部材３７間への給油を容易とすることができる。   Furthermore, since the slits 54 and 58 are formed in at least the support shaft portion 35d of the shaft 35 and the support cylinder portion 37c of the shaft receiving member 37, the slits 54 and 58 are used. Oil supply between the shaft 35 and the shaft receiving member 37 can be facilitated.

本発明の参考形態について図３を参照しながら説明するが、上記実施の形態に対応する部分には同一の参照符号を付して図示するのみとし、詳細な説明は省略する。 Although described with reference to FIG referential embodiment of the present invention, the parts corresponding to the form of the above you facilities and shown only by the same reference numerals, and detailed description thereof will be omitted.

ねじ式テンショナリフター６１は、内周に雌ねじ４１が刻設された円筒状の筒部材３９の一端部にキャップ４０が装着されて成る押圧体３４と、前記雌ねじ４１に螺合するシャフト６５と、機関本体１１のシリンダボディ１３に固定されるケーシング６６と、前記該シャフト６５を前記押圧体３４と反対側から回動可能にスラスト支持するようにして前記シャフト６５および前記ケーシング６６間に介装されるシャフト受け部材６７と、前記押圧体３４が前記カムチェーン２３側に向けて進行する方向に前記シャフト６５を回動付勢して前記ケーシング６６および前記シャフト６５間に設けられる弾性部材としてのゼンマイばね３８とを備える。   The screw type tensioner lifter 61 includes a pressing body 34 in which a cap 40 is attached to one end of a cylindrical tube member 39 in which an internal thread 41 is engraved on the inner periphery, a shaft 65 screwed into the internal thread 41, A casing 66 fixed to the cylinder body 13 of the engine body 11 and the shaft 65 are interposed between the shaft 65 and the casing 66 so as to be thrust-supported so as to be rotatable from the opposite side of the pressing body 34. And a spring as an elastic member provided between the casing 66 and the shaft 65 by rotating and biasing the shaft 65 in a direction in which the pressing body 34 advances toward the cam chain 23 side. And a spring 38.

前記ケーシング６６は、円筒部６６ａと、その円筒部６６ａの外端部を閉じる端壁部６６ｂと、当該端壁部６６ｂから半径方向外方に張り出すフランジ部６６ｃとを一体に有する。また前記シャフト６５は、前記雌ねじ４１に螺合する雄ねじ４８が外周に刻設されるねじ部６５ａと、当該シャフト６５の軸線に沿う方向で前記シャフト受け部材６７に当接する当接面６９を有して前記ねじ部６５ａよりも大径に形成される被支持部６５ｂと、前記ねじ部６５ａおよび前記被支持部６５ｂ間を同軸に結ぶ連結軸部６５ｃと、前記被支持部６５ｂから同軸に突出する支持軸部６５ｄとを一体に有するように形成される。   The casing 66 integrally includes a cylindrical portion 66a, an end wall portion 66b that closes an outer end portion of the cylindrical portion 66a, and a flange portion 66c that protrudes radially outward from the end wall portion 66b. The shaft 65 has a threaded portion 65a in which an external thread 48 that engages with the internal thread 41 is engraved on the outer periphery, and a contact surface 69 that contacts the shaft receiving member 67 in a direction along the axis of the shaft 65. Then, a supported portion 65b formed to have a larger diameter than the screw portion 65a, a connecting shaft portion 65c that coaxially connects the screw portion 65a and the supported portion 65b, and a coaxial projection from the supported portion 65b And a support shaft portion 65d.

前記被支持部６５ｂの前記当接面６９は、当該被支持部６５ｂの外周に形成されるものであり、前記連結軸部６５ｃ側が大径となるようにしたテーパ状に形成され、この当接面６９の最小内径Ｄ５が、前記ねじ部６５ａの外径Ｄ２よりも大きく設定される。また前記被支持部６５ｂの最大外径Ｄ６は、前記ねじ部６５ａの外径Ｄ２よりも大きく、かつ前記ねじ部６５ａの外径Ｄ２の３倍以下に設定される。 The contact surface 69 of the supported portion 65b is formed on the outer periphery of the supported portion 65b, and is formed in a tapered shape so that the connecting shaft portion 65c side has a large diameter. The minimum inner diameter D5 of the surface 69 is set larger than the outer diameter D2 of the screw portion 65a. The maximum outer diameter D6 of the supported portion 65b is larger than the outer diameter D2 of the threaded portion 65a, and is set to below 3 times the outer diameter D 2 of the threaded portion 65a.

前記シャフト受け部材６７は、前記当接面６９に一部を当接させるテーパ状の受け板部６７ａと、この受け板部６７ａの小径端に連なって前記被支持部６５ｂに対向するリング板状の平板部６７ｂと、この平板部６７ｂの内周に直角に連なって前記受け板部６７ａとは反対側に延びる円筒状の支持筒部６７ｃとを一体に有するように形成される。   The shaft receiving member 67 has a tapered receiving plate portion 67a that makes a part of the shaft receiving member abut the abutting surface 69, and a ring plate shape that continues to the small diameter end of the receiving plate portion 67a and faces the supported portion 65b. The flat plate portion 67b and a cylindrical support cylinder portion 67c extending at a right angle to the inner periphery of the flat plate portion 67b and extending to the opposite side of the receiving plate portion 67a are integrally formed.

前記ケーシング６６の前記端壁部６６ｂには、前記シャフト受け部材６７のうち前記受け板部６７ａおよび前記平板部６７ｂを受け入れる収容凹部７１と、前記支持筒部６７ｃを嵌入させるようにして前記収容凹部７１に同軸に連なる支持孔７２とが設けられる。   In the end wall portion 66b of the casing 66, the housing recess portion 71 is fitted so that the receiving recess portion 71 for receiving the receiving plate portion 67a and the flat plate portion 67b of the shaft receiving member 67 and the support cylinder portion 67c are fitted. 71 is provided with a support hole 72 connected coaxially.

また前記シャフト６５の前記支持軸部６５ｄは、前記ねじ部６５ａの外径Ｄ２よりも小径にして前記被支持部６５ｂから同軸に突出するとともに、前記シャフト受け部材６７の前記支持筒部６７ｃに挿入される。しかも前記支持軸部６５ｄの前記支持筒部６７ｃ内での軸方向長さＬ２は、当該支持軸部６５ｄの外径Ｄ７よりも大きく設定される。 Also, the support shaft portion 65d of the shaft 65 is configured to protrude coaxially from the supported portion 65b with diameter smaller than the outer diameter D 2 of the threaded portion 65a, to the support tube portion 67c of the shaft receiving member 67 Inserted. Moreover, the axial length L2 of the support shaft portion 65d in the support cylinder portion 67c is set to be larger than the outer diameter D7 of the support shaft portion 65d.

前記シャフト６５の少なくとも支持軸部６５ｄ、この実施の形態では前記支持軸部６５ｄから前記被支持部６５ｂを経て前記連結軸部６５ｃの中間部に至るまでの間には、一直径線に沿うすり割り７４が形成されており、このすり割り７４には、平板状のストッパ７５を係合して前記シャフト６５の回転を阻止することが可能であり、前記支持孔７２の外端開口縁には、前記ストッパ７５を係合させる一対ずつ２組の係止凹部７６が、各組の係止凹部７６を前記支持孔７２の直径線上に配置するようにして形成される。   At least the support shaft portion 65d of the shaft 65, in this embodiment, from the support shaft portion 65d through the supported portion 65b to the intermediate portion of the connecting shaft portion 65c, a slide along one diameter line. A slit 74 is formed, and a flat stopper 75 can be engaged with the slit 74 to prevent the shaft 65 from rotating. Two pairs of locking recesses 76 for engaging the stopper 75 are formed so that each set of locking recesses 76 is arranged on the diameter line of the support hole 72.

前記ストッパ７５を前記すり割り７４から抜き出した後には、前記支持孔７２の外端部に栓部材７７が螺合される。さらに前記シャフト受け部材６７の前記支持筒部６７ｃにもその全長にわたるすり割り７８が形成される。   After the stopper 75 is extracted from the slit 74, the plug member 77 is screwed into the outer end portion of the support hole 72. Further, a slit 78 extending over the entire length of the support cylinder portion 67c of the shaft receiving member 67 is also formed.

この参考形態によれば、シャフト６５の被支持部６５ｂに形成されつつ当該シャフト６５の軸線に沿う方向でシャフト受け部材６７に当接する当接面６９の最小内径Ｄ５が、シャフト６５のねじ部６５ａの外径Ｄ２よりも大きいので、押圧体３４およびシャフト６５の螺合部の径よりも大きい径でシャフト６５にかかる荷重をシャフト受け部材６７で受けるようにしつつ、シャフト受け部材６７でシャフト６５を受ける面積を充分に大きくすることで、交番荷重の作用状態にあってもシャフト受け部材６７へのシャフト６５の当接部で前記交番荷重による回転力に打ち勝つだけの有効摩擦面積を確保して、異音の発生を抑制することができる。 According to this reference embodiment, the minimum inner diameter D5 of the contact surface 69 that is formed on the supported portion 65b of the shaft 65 and contacts the shaft receiving member 67 in the direction along the axis of the shaft 65 is the threaded portion 65a of the shaft 65. Therefore, the shaft receiving member 67 receives the load applied to the shaft 65 with a diameter larger than the diameter of the threaded portion of the pressing body 34 and the shaft 65, and the shaft receiving member 67 supports the shaft 65. By sufficiently increasing the receiving area, even in an alternating load operating state, an effective friction area that can overcome the rotational force due to the alternating load at the contact portion of the shaft 65 to the shaft receiving member 67 is ensured, Generation of abnormal noise can be suppressed.

また前記ねじ部６５ａの外径Ｄ２よりも小径にしてシャフト６５に設けられる支持軸部６５ｄが、シャフト受け部材６７の支持筒部６７ｃに嵌入され、前記支持軸部６５ｄの前記支持筒部６７ｃ内での軸方向長さＬ２が、当該支持軸部６５ｄの外径Ｄ７よりも大きいので、支持筒部６７ｃによる支持軸部６５ｄひいてはシャフト６５の支持を安定化することができる。   Also, a support shaft portion 65d provided on the shaft 65 with a smaller diameter than the outer diameter D2 of the screw portion 65a is fitted into the support tube portion 67c of the shaft receiving member 67, and the support shaft portion 65d has an inside of the support tube portion 67c. Since the axial length L2 is larger than the outer diameter D7 of the support shaft portion 65d, the support shaft portion 65d by the support cylinder portion 67c and thus the support of the shaft 65 can be stabilized.

また被支持部６５ｂの最大外径Ｄ３がねじ部６５ａの外径Ｄ２よりも大きく、かつねじ部６５ａの外径Ｄ２の３倍以下であるので、被支持部６５ｂが径方向で過度に大きくなることを回避しつつ当接面６９の面積を充分に確保することができる。   Further, since the maximum outer diameter D3 of the supported portion 65b is larger than the outer diameter D2 of the screw portion 65a and not more than three times the outer diameter D2 of the screw portion 65a, the supported portion 65b becomes excessively large in the radial direction. The area of the contact surface 69 can be sufficiently secured while avoiding this.

また前記シャフト６５のうち少なくとも前記支持軸部６５ｄと，前記シャフト受け部材６７の前記支持筒部６７ｃとに、すり割り７４，７８が形成されるので、それらのすり割り７４，７８を利用してシャフト６５およびシャフト受け部材６７間への給油を容易とすることができる。   Moreover, since the slits 74 and 78 are formed in at least the support shaft portion 65d of the shaft 65 and the support cylinder portion 67c of the shaft receiving member 67, the slits 74 and 78 are used. Oil supply between the shaft 65 and the shaft receiving member 67 can be facilitated.

しかもシャフト６５の被支持部６５ｂの外周に形成される当接面６９がテーパ状に形成されるので、被支持部６５ｂの最大外径Ｄ６が大きくなることを回避しながら当接面６９の面積を増大し、シャフト６５をより安定的に支持することができる。 Moreover, since the abutment surface 69 formed on the outer circumference of the supported portion 65b of the shaft 65 is formed in a tapered shape, the abutment surface 69 while avoiding that the maximum outer diameter D6 of the supported portion 65 b is larger The area can be increased and the shaft 65 can be supported more stably.

以上、本発明の実施の形態および参考形態について説明したが、本発明は上記実施の形態に限定されるものではなく、特許請求の範囲に記載された本発明を逸脱することなく種々の設計変更を行うことが可能である。 Although the embodiment and the reference embodiment of the present invention have been described above, the present invention is not limited to the above-described embodiment, and various design changes can be made without departing from the present invention described in the claims. Can be done.

１１・・・機関本体
２３・・・伝動帯であるカムチェーン
２６，６１・・・ねじ式テンショナリフター
３５，６５・・・シャフト
３５ａ，６５ａ・・・ねじ部
３５ｂ，６５ｂ・・・被支持部
３５ｃ，６５ｃ・・・連結軸部
３５ｄ，６５ｄ・・・支持軸部
３６，６６・・・ケーシング
３７，６７・・・シャフト受け部材
３７ｂ・・・側壁部
３７ｃ・・・支持筒部
３８・・・弾性部材であるゼンマイばね
４９，６９・・・当接面
４１・・・雌ねじ
４８・・・雄ねじ
５２・・・支持孔
５３・・・環状凹部
５４，５８・・・すり割り
ｄ１・・・支持軸部の外周および支持筒部の内周間の間隙
ｄ２・・・側壁部の内周および被支持部の外周間の間隙
Ｄ１，Ｄ５・・・当接面の最小内径
Ｄ２・・・ねじ部の外径
Ｄ３・・・被支持部の最大外径
Ｄ４・・・支持軸部の外径
Ｅ・・・内燃機関
Ｌ１・・・支持軸部の支持筒部内での軸方向長さ
DESCRIPTION OF SYMBOLS 11 ... Engine main body 23 ... Cam chain 26, 61 ... Screw type tensioner lifter 35, 65 ... Shaft 35a, 65a ... Screw part 35b, 65b ... Supported part 35c, 65c ... connecting shafts 35d, 65d ... support shafts 36, 66 ... casing 37, 67 ... shaft receiving member 37b ... side wall 37c ... support cylinder 38 ... Spring springs 49, 69, which are elastic members, abutment surface 41, female screw 48, male screw 52, support hole 53, annular recesses 54, 58, slit d1,. Gap d2 between the outer periphery of the support shaft and the inner periphery of the support tube portion. Gap D1, D5 between the inner periphery of the side wall portion and the outer periphery of the supported portion. Outer diameter D3 ... Supported part maximum outer diameter D4 ... Support The axial length of an outer diameter E · · · engine L1 · · · supporting cylindrical portion of the support shaft portion of the shaft portion

Claims (6)

内周に雌ねじ（４１）が刻設されるようにして少なくとも一部が円筒状に形成されるとともに機関本体（１１）内で走行する伝動帯（２３）に押圧力を付与することを可能とした押圧体（３４）と、前記雌ねじ（４１）に螺合するシャフト（３５）と、前記機関本体（１１）に固定されるケーシング（３６）と、前記シャフト（３５）を前記押圧体（３４）と反対側から回動可能にスラスト支持して前記シャフト（３５）および前記ケーシング（３６）間に介装されるシャフト受け部材（３７）と、前記押圧体（３４）が前記伝動帯（２３）側に向けて進行する方向に前記シャフト（３５）を回動付勢しつつ前記ケーシング（３６）および前記シャフト（３５）間に設けられる弾性部材（３８）とを備える内燃機関のねじ式テンショナリフターにおいて、
前記シャフト（３５）は、前記雌ねじ（４１）に螺合する雄ねじ（４８）が外周に刻設されるねじ部（３５ａ）と、当該シャフト（３５）の軸線に沿う方向で前記シャフト受け部（３７）に当接する当接面（４９）を有して前記ねじ部（３５ａ）よりも大径に形成される被支持部（３５ｂ）と、前記ねじ部（３５ａ）および前記被支持部（３５ｂ）間を同軸に結ぶ連結軸部（３５ｃ）とを一体に有し、
前記被支持部（３５ｂ）の前記連結軸部（３５ｃ）とは反対の端面には、前記当接面（４９）の内周縁を規定しつつ該内周縁から径方向内向きに前記シャフト受け部材（３７）の内周縁を超えて伸びる凹部（５３）が、軸方向内向きに窪むようにして形成され、該凹部（５３）により、前記当接面（４９）の最小内径（Ｄ１）が、前記ねじ部（３５ａ）の外径（Ｄ２）よりも大きく設定されることを特徴とする内燃機関のねじ式テンショナリフター。 It is possible to apply a pressing force to the transmission band (23) running in the engine body (11) while at least a part is formed in a cylindrical shape so that a female screw (41) is engraved on the inner periphery. a pressing member was (34), a shaft (35) screwed to the internal thread (41), a casing (3 6) which is fixed to the engine body (11), the pressing the shaft (35) body shaft receiving member (3 7) from the opposite side to be rotatable by thrust support is interposed in said shaft (35) and the casing (3 6) between (34), the pressing member (34) There the transmission belt wherein the traveling direction towards the (23) side shaft (35) wherein while pivotally urged the casing (3 6) and the shaft (35) an elastic member provided between (38) Internal screw engine tensioner In Futa,
The shaft (35) includes a threaded portion (35 a) external threads to be screwed into the internal thread (41) (48) is engraved on the outer periphery, said shaft in a direction along the axis of the shaft (35) receiving part (3 7) in the supported portion which is formed with a larger diameter than the threaded portion has a contact with the abutment surface (4 9) (35 a) and (35 b), the threaded portion (35 a ) and has the connecting shaft portion connecting the supported portion between (35 b) coaxially and (35 c) together,
An end surface of the supported portion (35b) opposite to the connecting shaft portion (35c) defines an inner peripheral edge of the contact surface (49), and the shaft receiving member is radially inward from the inner peripheral edge. A concave portion (53) extending beyond the inner peripheral edge of (37) is formed so as to be recessed inward in the axial direction, and the concave portion (53) allows the minimum inner diameter (D1 ) of the contact surface (49 ) to be A screw type tensioner lifter for an internal combustion engine, wherein the screw type tensioner lifter is set to be larger than an outer diameter (D2 ) of the screw part (35a). 内周に雌ねじ（４１）が刻設されるようにして少なくとも一部が円筒状に形成されるとともに機関本体（１１）内で走行する伝動帯（２３）に押圧力を付与することを可能とした押圧体（３４）と、前記雌ねじ（４１）に螺合するシャフト（３５）と、前記機関本体（１１）に固定されるケーシング（３６）と、前記シャフト（３５）を前記押圧体（３４）と反対側から回動可能にスラスト支持して前記シャフト（３５）および前記ケーシング（３６）間に介装されるシャフト受け部材（３７）と、前記押圧体（３４）が前記伝動帯（２３）側に向けて進行する方向に前記シャフト（３５）を回動付勢しつつ前記ケーシング（３６）および前記シャフト（３５）間に設けられる弾性部材（３８）とを備える内燃機関のねじ式テンショナリフターにおいて、
前記シャフト（３５）は、前記雌ねじ（４１）に螺合する雄ねじ（４８）が外周に刻設されるねじ部（３５ａ）と、当該シャフト（３５）の軸線に沿う方向で前記シャフト受け部材（３７）に当接する当接面（４９）を有して前記ねじ部（３５ａ）よりも大径に形成される被支持部（３５ｂ）と、前記ねじ部（３５ａ）および前記被支持部（３５ｂ）間を同軸に結ぶ連結軸部（３５ｃ）とを一体に有し、前記当接面（４９）の最小内径（Ｄ１）が、前記ねじ部（３５ａ）の外径（Ｄ２）よりも大きく設定され、
前記シャフト受け部材（３７）に、前記被支持部（３５ｂ）の外周の少なくとも一部を囲繞する円筒状の側壁部（３７ｂ）と、前記ケーシング（３６）に形成される支持孔（５２）に嵌入される円筒状の支持筒部（３７ｃ）とが一体に設けられ、前記ねじ部（３５ａ）の外径（Ｄ２）よりも小径にして前記被支持部（３５ｂ）から同軸に突出するとともに前記支持筒部（３７ｃ）に挿入される支持軸部（３５ｄ）が前記シャフト（３５）に設けられ、前記支持軸部（３５ｄ）の外周および前記支持筒部（３７ｃ）の内周間の間隙（ｄ１）が、前記側壁部（３７ｂ）の内周および前記被支持部（３５ｂ）の外周間の間隙（ｄ２）よりも小さく設定されることを特徴とする内燃機関のねじ式テンショナリフター。 It is possible to apply a pressing force to the transmission band (23) running in the engine body (11) while at least a part is formed in a cylindrical shape so that a female screw (41) is engraved on the inner periphery. The pressed body (34), the shaft (35) screwed into the female screw (41), the casing (36) fixed to the engine body (11), and the shaft (35) are connected to the pressed body (34). ) And a shaft receiving member (37) interposed between the shaft (35) and the casing (36) so as to be capable of rotating from the opposite side, and the pressing body (34) are connected to the transmission band (23). ) Screw-type tensioner for an internal combustion engine comprising the casing (36) and an elastic member (38) provided between the shaft (35) while urging and urging the shaft (35) in the direction of traveling toward the side). Lifter In,
The shaft (35) includes a screw portion (35a) in which a male screw (48) screwed to the female screw (41) is engraved on the outer periphery, and the shaft receiving member (in the direction along the axis of the shaft (35)). 37) a supported portion (35b) having a contact surface (49) that is in contact with the screw portion (37) and having a diameter larger than that of the screw portion (35a), the screw portion (35a), and the supported portion (35b). ) And a connecting shaft part (35c) that connects the two parts coaxially, and the minimum inner diameter (D1) of the contact surface (49) is set larger than the outer diameter (D2) of the screw part (35a). And
The shaft receiving member (37) has a cylindrical side wall portion (37b) surrounding at least a part of the outer periphery of the supported portion (35b), and a support hole (52) formed in the casing (36). A cylindrical support tube portion (37c) to be inserted is integrally provided, and the diameter is smaller than the outer diameter (D2) of the screw portion (35a) and protrudes coaxially from the supported portion (35b). A support shaft portion (35d) to be inserted into the support tube portion (37c) is provided on the shaft (35), and a gap between the outer periphery of the support shaft portion (35d) and the inner periphery of the support tube portion (37c) ( d1) is set to be smaller than the gap (d2) between the inner periphery of the side wall portion (37b) and the outer periphery of the supported portion (35b). 前記被支持部（３５ｂ）の前記連結軸部（３５ｃ）とは反対の端面に、前記当接面（４９）が形成されるとともに、前記ねじ部（３５ａ）の外径（Ｄ２）よりも大きな内径を有する環状凹部（５３）が前記当接面（４９）の内周縁を規定しつつ前記支持軸部（３５ｄ）を囲むようにして形成されることを特徴とする請求項２に記載の内燃機関のねじ式テンショナリフター。   The contact surface (49) is formed on the end surface of the supported portion (35b) opposite to the connecting shaft portion (35c) and is larger than the outer diameter (D2) of the screw portion (35a). The internal combustion engine according to claim 2, wherein an annular recess (53) having an inner diameter is formed so as to surround the support shaft portion (35d) while defining an inner peripheral edge of the contact surface (49). Screw type tensioner lifter. 前記支持軸部（３５ｄ）の前記支持筒部（３７ｃ）内での軸方向長さ（Ｌ１）が、当該支持軸部（３５ｄ）の外径（Ｄ４）よりも大きく設定されることを特徴とする請求項２または３に記載の内燃機関のねじ式テンショナリフター。   An axial length (L1) of the support shaft portion (35d) in the support cylinder portion (37c) is set to be larger than an outer diameter (D4) of the support shaft portion (35d). The screw type tensioner lifter for an internal combustion engine according to claim 2 or 3. 前記被支持部（３５ｂ）の最大外径（Ｄ３）が、前記ねじ部（３５ａ）の外径（Ｄ２）よりも大きく、かつ前記ねじ部（３５ａ）の外径（Ｄ２）の３倍以下に設定されることを特徴とする請求項２〜４のいずれか１項に記載の内燃機関のねじ式テンショナリフター。   The maximum outer diameter (D3) of the supported portion (35b) is larger than the outer diameter (D2) of the screw portion (35a) and not more than three times the outer diameter (D2) of the screw portion (35a). The screw type tensioner lifter for an internal combustion engine according to any one of claims 2 to 4, wherein the tension type lifter is set. 前記シャフト（３５）のうち少なくとも前記支持軸部（３５ｄ）と、前記シャフト受け部材（３７）の前記支持筒部（３７ｃ）とに、すり割り（５４，５８）が形成されることを特徴とする請求項２〜５のいずれか１項に記載の内燃機関のねじ式テンショナリフター。   A slit (54, 58) is formed in at least the support shaft portion (35d) of the shaft (35) and the support tube portion (37c) of the shaft receiving member (37). The screw type tensioner lifter for an internal combustion engine according to any one of claims 2 to 5.
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