JP2003083402A - Driving force providing device for tensioner - Google Patents
Driving force providing device for tensionerInfo
- Publication number
- JP2003083402A JP2003083402A JP2001277119A JP2001277119A JP2003083402A JP 2003083402 A JP2003083402 A JP 2003083402A JP 2001277119 A JP2001277119 A JP 2001277119A JP 2001277119 A JP2001277119 A JP 2001277119A JP 2003083402 A JP2003083402 A JP 2003083402A
- Authority
- JP
- Japan
- Prior art keywords
- tensioner
- force
- pressing body
- rotary shaft
- propulsion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本出願発明は、例えば、内燃
機関のカムチェーン等の無端伝動帯に張力を与えるテン
ショナに用いられる推進力付与装置に関し、特に、送り
ネジ式の推進力付与装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a propulsion force applying device used in a tensioner for applying tension to an endless transmission belt of a cam chain of an internal combustion engine, and more particularly to a feed screw type propulsion force applying device. Is.
【０００２】[0002]
【従来技術】近年、品質感の高い内燃機関が要望される
に伴ない、騒音、振動の少ない内燃機関が求められてい
る。一方、内燃機関の高速化で内燃機関の耐久性向上が
求められている。2. Description of the Related Art In recent years, as an internal combustion engine with a high sense of quality is desired, an internal combustion engine with less noise and vibration is required. On the other hand, increasing the speed of the internal combustion engine is required to improve the durability of the internal combustion engine.
【０００３】一般にカムチェーンの耐久性向上を図る場
合、テンショナによるカムチェーンの張力を小さくする
ことが有利であるが、このカムチェーン張力の低下でカ
ムチェーンの回送音が増加する傾向がある。このため、
耐磨耗性の向上と静粛化を両立させる手段が求められて
いた。Generally, in order to improve the durability of the cam chain, it is advantageous to reduce the tension of the cam chain by the tensioner. However, the lowering of the tension of the cam chain tends to increase the revolving noise of the cam chain. For this reason,
There has been a demand for a means for achieving both improved wear resistance and quietness.
【０００４】カムチェーンに適正な張力を与えるテンシ
ョナに用いられる推進力付与装置の内、油圧によらず構
造が簡単で動作の確実な推進力付与装置として送りネジ
式推進力付与装置があり、前述した要求に対応した発明
として、特開２００１−８２５５７号公報記載の発明が
ある。Among the propulsion force imparting devices used in the tensioner for applying proper tension to the cam chain, there is a feed screw type propulsion force imparting device as a propulsion force imparting device having a simple structure and reliable operation regardless of hydraulic pressure. There is an invention described in Japanese Patent Laid-Open No. 2001-82557 as an invention corresponding to the demand.
【０００５】前記送りネジ式推進力付与装置では、押圧
体に螺合する回転軸の基端部が軸受け部材を介してケー
シングに回転可能に支持され、前記押圧体を常に突出さ
せる方向へ付勢するスプリングが設けられており、該ス
プリングの付勢力でもって前記押圧体が突出して、テン
ショナによりカムチェーンに所要の張力が付与されるよ
うになっている。In the feed screw type propulsive force applying device, the base end portion of the rotary shaft screwed to the pressing body is rotatably supported by the casing via the bearing member, and the pressing body is always biased in the protruding direction. Is provided, and the pressing body is projected by the biasing force of the spring, and a required tension is applied to the cam chain by the tensioner.
【０００６】前記特開２００１−８２５５７号公報記載
の発明では、前記回転軸の基端面および内周面の隅部と
軸受け部材の端面および外周面の角部のいずれか一方ま
たは両方が長期間の使用で磨耗し、接触部分の半径が小
さくなり、カムチェーンに対する押圧体の押圧力が低下
するのを防止するために、前記軸受け部材の中心線に対
し直交する平面に対し、該軸受け部材の基端面を所要角
度傾斜させ、耐久性の向上を図っていた。In the invention described in JP-A-2001-82557, one or both of the corners of the base end surface and the inner peripheral surface of the rotary shaft and the end surface and the outer peripheral surface of the bearing member are long-term. In order to prevent wear of the bearing, decrease of the radius of the contact portion, and reduction of the pressing force of the pressing body against the cam chain, the base of the bearing member is set against the plane orthogonal to the center line of the bearing member. The end face was inclined at the required angle to improve durability.
【０００７】そして、内燃機関の運転時に発生するカム
チェーンの回送音の静粛化を図るために、回転軸を付勢
するスプリングのバネ定数や、スプリングの初期付勢力
を管理してきた。In order to suppress the noise of the cam chain that is generated during the operation of the internal combustion engine, the spring constant of the spring for urging the rotating shaft and the initial urging force of the spring have been managed.
【０００８】[0008]
【解決しようとする課題】しかし、カムチェーンの騒音
レベルを大巾に低下させようとして、テンショナの推進
力付与装置の押し力を増大させると、カムチェーンの張
力が増加した時に、推進力付与装置に発生する押し戻し
力が著しく増大して、カムチェーンおよびテンショナの
磨耗が促進され、短期間でカムチェーンの張力が逆に低
下して、静粛性が損なわれる。[Problems to be Solved] However, if the pushing force of the thruster force imparting device of the tensioner is increased in an attempt to greatly reduce the noise level of the cam chain, when the tension of the cam chain increases, the thrust force imparting device is increased. The pushing-back force generated in the cam chain significantly increases, the wear of the cam chain and the tensioner is accelerated, and the tension of the cam chain decreases conversely in a short period of time, and the quietness is impaired.
【０００９】[0009]
【課題を解決するための手段および効果】本出願発明者
は、カムチェーンの回送時の音およびカムチェーン等の
耐久性が、推進力付与装置のテンショナーへの押し力だ
けによるものではなく、推進力付与装置の押圧体が押戻
されるときの抵抗力にもよることに着目した。そして、
かかる抵抗力を戻りトルクとして数値化し、この戻りト
ルクと押し力とを変数とする２次元マップ上で、前記磨
耗許容限界と音許容限界とで挟まれた両立範囲内に前記
戻りトルクと押し力を設定しようとする発想を持つに至
った。Means for Solving the Problems and Effects The inventors of the present application have proposed that the sound at the time of forwarding the cam chain and the durability of the cam chain, etc. do not depend only on the pushing force on the tensioner of the propulsion force imparting device, We paid attention to the fact that it also depends on the resistance force when the pressing body of the force application device is pushed back. And
The resistance force is quantified as a return torque, and the return torque and the pushing force are within a compatible range between the wear allowable limit and the sound allowable limit on a two-dimensional map having the return torque and the pressing force as variables. I came to have the idea of trying to set.
【００１０】前記押し力とは、前記スプリングの付勢に
より押圧体が突出する力と定義し、前記戻りトルクと
は、推進力付与装置の押し力に抵抗する方向に、一定の
荷重をかけ、スプリングの付勢力と摩擦力に打ち勝っ
て、回転軸を一定の回転数で逆転させるに必要なトルク
と定義する。The pushing force is defined as a force by which the pressing body projects due to the bias of the spring, and the return torque is applied with a constant load in a direction resisting the pushing force of the propulsion force applying device, It is defined as the torque required to reverse the rotating shaft at a constant speed by overcoming the urging force and frictional force of the spring.
【００１１】本出願発明は、このような発想に基いてな
された発明であって、請求項１記載の発明は、前端をテ
ンショナに当接させるとともに、後部にネジを有する押
圧体が、その軸線まわりに回転せずに軸線方向へ移動可
能にケーシングに支持され、前記ネジに螺合するネジ部
を有する回転軸の後部と前記ケーシングとの間に、該回
転軸に加えられる推進反力を負担しながら該回転軸をそ
の軸線まわりに回転可能に支持する軸受け部材が介装さ
れ、前記ケーシングおよび回転軸間には、前記押圧体を
前進させる方向へ付勢するスプリングが設けられ、無端
伝動帯を前記テンショナを介し緊張方向に押圧して該無
端伝動帯に張力を与えるテンショナの推進力付与装置に
おいて、前記スプリングの付勢により前記押圧体が突出
する力である押し力と、該押圧体に一定の荷重を加えた
状態で、前記スプリングの付勢力と摩擦力に打ち勝ち該
押圧体を一定速度で退入させるべく、前記回転軸を回転
させるに必要な戻りトルクとを変数とする２次元マップ
上で、前記テンショナおよび無端伝動帯のいずれか一方
または両方が磨耗に耐えることができる磨耗許容限界
と、前記無端伝動帯が回送時に発生する音の音許容限界
とで挟まれた両立範囲内に、前記押し力と戻りトルクが
設定されたことを特徴とするものである。The invention of the present application is an invention made on the basis of such an idea. In the invention of claim 1, the pressing body having the front end abutting against the tensioner and having a screw at the rear part thereof has an axis line thereof. A propulsive reaction force applied to the rotary shaft is provided between the casing and the rear part of the rotary shaft that is supported by the casing so as to be movable in the axial direction without rotating around and has a threaded portion that is screwed into the screw. However, a bearing member that rotatably supports the rotating shaft around its axis is interposed, and a spring that urges the pressing body in the direction of advancing the pressing body is provided between the casing and the rotating shaft. In a tensioner propulsion force applying device that applies a tension to the endless transmission band by pressing in a tension direction via the tensioner, a pushing force that is a force by which the pressing body projects due to the bias of the spring. And a return torque necessary to rotate the rotary shaft in order to overcome the biasing force and the frictional force of the spring and withdraw the pressing body at a constant speed in a state where a constant load is applied to the pressing body. On a two-dimensional map that is a variable, it is sandwiched between a wear allowance limit at which one or both of the tensioner and the endless drive band can withstand wear and a sound allowance limit of sound generated when the endless drive band is forwarded. The pushing force and the return torque are set within the above-mentioned compatible range.
【００１２】請求項１記載の発明は前述したように構成
されているので、前記テンショナの推進力付与装置にお
けるネジの進み角と、回転軸および軸受け部材間の有効
摩擦直径と、スプリングのバネ定数とのいずれか一つま
たは二つ以上を変えるとともに、スプリングの初期付勢
力等を変えて、前記テンショナおよび無端伝動帯のいず
れか一方または両方が磨耗に耐えることができる磨耗許
容限界と、前記無端伝動帯が回送時に発生する音の許容
限界とで挟まれた両立範囲内に、前記押し力と戻りトル
クを設定し、無端伝動帯が発生する音と無端伝動帯およ
びテンショナの耐久性を最適な水準にすることができ
る。Since the invention according to claim 1 is configured as described above, the lead angle of the screw in the thruster imparting device of the tensioner, the effective friction diameter between the rotary shaft and the bearing member, and the spring constant of the spring. By changing any one or more of the above, and changing the initial biasing force of the spring, etc., a wear allowable limit that allows one or both of the tensioner and the endless transmission band to withstand wear, and the endless The pushing force and the return torque are set within the compatible range sandwiched between the transmission band and the allowable limit of sound generated during forwarding, and the sound generated by the endless transmission band and the durability of the endless transmission band and tensioner are optimized. Can be set to a standard.
【００１３】また、請求項２記載のように発明を構成す
ることにより、前記押圧体を内周面に雌ネジを有する筒
状に形成し、前記回転軸の外周面に雄ネジを形成した推
進力付与装置を提供することができる。According to the invention as set forth in claim 2, the pressing body is formed in a tubular shape having an internal thread on the inner peripheral surface and a male thread is formed on the outer peripheral surface of the rotary shaft. A force application device can be provided.
【００１４】さらに、請求項３記載のように発明を構成
することにより、請求項１記載の推進力付与装置の検査
を実行することができる。Further, by constructing the invention as described in claim 3, the inspection of the propulsive force applying device according to claim 1 can be executed.
【００１５】さらにまた、請求項４記載のように発明を
構成することにより、請求項１記載の推進力付与装置を
内燃機関のカムチェーンテンショナのリフタに適用する
ことができる。Further, by constructing the invention as described in claim 4, the propulsive force applying device according to claim 1 can be applied to the lifter of the cam chain tensioner of the internal combustion engine.
【００１６】しかも、請求項５記載のように発明を構成
することにより、請求項３記載の推進力付与装置の検査
方法を内燃機関のカムチェーンテンショナのリフタの検
査方法に適用することができる。Moreover, by constructing the invention as described in claim 5, the method for inspecting the propulsive force applying device according to claim 3 can be applied to the method for inspecting the lifter of the cam chain tensioner of the internal combustion engine.
【００１７】また、請求項６記載のように発明を構成す
ることにより、前記推進力付与装置の押し力と戻りトル
クの設定を確実に実行することができる。Further, by constructing the invention as described in claim 6, it is possible to reliably set the pushing force and the return torque of the propulsion force applying device.
【００１８】さらに、請求項７記載のように発明を構成
することにより、前記推進力付与装置の押し力をテンシ
ョナに効果的に加えることができる。Further, by constructing the invention as described in claim 7, the pushing force of the propulsive force applying device can be effectively applied to the tensioner.
【００１９】さらにまた、請求項８記載のように発明を
構成することにより、前記軸受け部材に耐磨耗性および
耐変形性を持たせることができる。Furthermore, by constructing the invention as described in claim 8, the bearing member can be provided with abrasion resistance and deformation resistance.
【００２０】また、請求項９記載のように発明を構成す
ることにより、前記回転軸を逆回転させるに必要なトル
クを低下させ、所定の回転軸端面径とネジ進み角とを変
えずに、磨耗許容限界と音許容限界とで挟まれる両立範
囲を拡げることができる。According to the present invention, the torque required to reversely rotate the rotary shaft is reduced, and the predetermined end face diameter of the rotary shaft and the screw advance angle are not changed. It is possible to expand the compatible range sandwiched between the wear allowance limit and the sound allowance limit.
【００２１】さらに、請求項１０記載のように発明を構
成することにより、前記押圧体から無端伝動帯に加えら
れる押し力に対する押し戻し力の急激な変動を緩衝する
ことができ、無端伝動帯および推進力付与装置の耐久性
を向上させることができる。Further, according to the invention as set forth in claim 10, it is possible to buffer a rapid change of the push-back force with respect to the pushing force applied from the pressing body to the endless transmission band, and the endless transmission band and propulsion. The durability of the force applying device can be improved.
【００２２】[0022]
【発明の実施の形態】以下、本発明を適用した図示の実
施形態について説明する。BEST MODE FOR CARRYING OUT THE INVENTION The illustrated embodiments to which the present invention is applied will be described below.
【００２３】図１に図示された自動二輪車に搭載される
内燃機関１は、排気量８００ｃｃのＤＯＨＣ（ダブルオ
ーバーヘッドカムシャフト）式のＶ型４気筒４ストロー
クサイクル内燃機関であって、該内燃機関１の本体は、
図２に図示されるように、該シリンダブロック２と、該
シリンダブロック２のＶ状上部に配置されたシリンダヘ
ッド３と、前記シリンダブロック２の下方に配置された
クランクケース４とよりなり、これらシリンダブロック
２、シリンダヘッド３およびクランクケース４は、図示
されないボルトまたはスタッドボルトに螺合されるナッ
トにより、相互に一体に結合され、前記シリンダヘッド
３の上方にシリンダヘッドカバー５が一体に結合されて
いる。The internal combustion engine 1 mounted on the motorcycle shown in FIG. 1 is a DOHC (double overhead camshaft) type V four cylinder four stroke cycle internal combustion engine having a displacement of 800 cc. The body of
As shown in FIG. 2, the cylinder block 2, a cylinder head 3 arranged on the V-shaped upper portion of the cylinder block 2, and a crankcase 4 arranged below the cylinder block 2 are provided. The cylinder block 2, the cylinder head 3, and the crankcase 4 are integrally connected to each other by a nut screwed to a bolt or a stud bolt (not shown), and a cylinder head cover 5 is integrally connected above the cylinder head 3. There is.
【００２４】また、シリンダブロック２とクランクケー
ス４との合せ面には、クランクシャフト６が回転自在に
枢支され、シリンダヘッド３に形成された図示されない
シリンダ孔にピストン（図示されず）が摺動自在に嵌装
され、該ピストンと前記クランクシャフト６とは図示さ
れないコネクティングロッドを介して連結されており、
前記シリンダの燃焼室内で発生する燃焼ガスにより前記
ピストンが往復駆動されるに伴なって、クランクシャフ
ト６が回転駆動されるようになっている。A crankshaft 6 is rotatably supported by a mating surface between the cylinder block 2 and the crankcase 4, and a piston (not shown) slides in a cylinder hole (not shown) formed in the cylinder head 3. It is movably fitted, and the piston and the crankshaft 6 are connected via a connecting rod (not shown),
The crankshaft 6 is rotationally driven as the piston is reciprocally driven by the combustion gas generated in the combustion chamber of the cylinder.
【００２５】さらに、シリンダヘッド３とシリンダヘッ
ドカバー５の合せ面には、２本のカムシャフト７が回転
自在に枢支され、該カムシャフト７の一端にそれぞれド
リブンスプロケット８が一体に嵌着され、前記クランク
シャフト６の一端に一体に設けられたドライブスプロケ
ット９と前記ドリブンスプロケット８とに無端状のカム
チェーン10（歯付きベルトでも可）が架渡されており、
クランクシャフト６が回転すると、カムシャフト７はク
ランクシャフト６の１／２の回転速度で回転駆動される
ようになっている。Further, two cam shafts 7 are rotatably supported by the mating surfaces of the cylinder head 3 and the cylinder head cover 5, and a driven sprocket 8 is integrally fitted to one end of each of the cam shafts 7. An endless cam chain 10 (a toothed belt is also possible) is bridged between the drive sprocket 9 and the driven sprocket 8 which are integrally provided at one end of the crankshaft 6.
When the crankshaft 6 rotates, the camshaft 7 is driven to rotate at half the rotation speed of the crankshaft 6.
【００２６】さらにまた、シリンダヘッド３には、前記
燃焼室に連通する図示されない吸気通路および排気通路
が形成され、該燃焼室と吸気通路および排気通路とを連
通または遮断するように図示されない吸気弁および排気
弁が設けられ、該吸気弁および排気弁は図示されないロ
ッカアームまたはバルブリフタを介してカムシャフト７
のカム（図示されず）に連結されており、カムシャフト
７の回転に対応し、クランクシャフト６が２回転、カム
シャフト７が１回転する間に、所要のタイミングで前記
吸気弁および排気弁は開閉駆動されるようになってい
る。Furthermore, the cylinder head 3 is provided with an intake passage and an exhaust passage (not shown) communicating with the combustion chamber, and an intake valve (not shown) for communicating or blocking the combustion chamber and the intake passage and the exhaust passage. And an exhaust valve, and the intake valve and the exhaust valve are provided with a camshaft 7 via a rocker arm or a valve lifter (not shown).
Corresponding to the rotation of the camshaft 7, the crankshaft 6 makes two revolutions, and the camshaft 7 makes one revolution. It is designed to be opened and closed.
【００２７】また、クランクシャフト６に隣接してシリ
ンダブロック２にテンショナ11の基端11ａが揺動自在に
枢支されて、テンショナ11のチェーンシュー11ｂは、ク
ランクシャフト６のドライブスプロケット９とカムシャ
フト７のドリブンスプロケット８との間でカムチェーン
に当接され、テンショナ11の先端部に近い個所にて推進
力付与装置20がシリンダヘッド３に装着され、その反体
側にチェーンガイド12がカムチェーン10に添接されてお
り、前記推進力付与装置20による押し力がテンショナ11
の背部11ｃに加えられ、カムチェーン10は、後述するよ
うに、適正な張力で緊張されるようになっている。The base end 11a of the tensioner 11 is swingably supported by the cylinder block 2 adjacent to the crankshaft 6 so that the chain shoe 11b of the tensioner 11 is connected to the drive sprocket 9 and the camshaft of the crankshaft 6. The driven force applying device 20 is attached to the cylinder head 3 at a position near the tip of the tensioner 11, and the chain guide 12 is provided with the chain guide 12 on the opposite side thereof. And the pushing force by the propulsion force applying device 20 is applied to the tensioner 11
The cam chain 10 is added to the back portion 11c of the cam 11 and is tensioned with an appropriate tension as described later.
【００２８】次に、推進力付与装置20の構造について説
明する。Next, the structure of the propulsive force applying device 20 will be described.
【００２９】推進力付与装置20では、アルミニウム製ケ
ーシング21に収納孔22が形成されるとともに、その底部
に、収納孔22よりも小径の取り付け孔23が同芯状に形成
され、さらにその底方向に取り付け孔23よりも小径のネ
ジ孔24が同芯状に形成され、前記取り付け孔23には、底
に孔のあいた超硬度炭素工具鋼特にＳＫ材製の有底円筒
状の軸受け部材25が一体に嵌着されている。なお、ネジ
孔24は、後述するようにストッパ40の回転操作が終了
し、推進力付与装置20の押圧体30が突出し、カムチェー
ン10に適正な緊張力が働いた状態の後、図示されないネ
ジがネジ孔24に螺着されて、ネジ孔24が密閉されるよう
になっている。In the propulsion force imparting device 20, a housing hole 22 is formed in an aluminum casing 21, and a mounting hole 23 having a diameter smaller than that of the housing hole 22 is concentrically formed at the bottom of the housing hole 22. A screw hole 24 having a diameter smaller than that of the mounting hole 23 is formed in a concentric shape, and the mounting hole 23 is provided with a bottomed cylindrical bearing member 25 made of super hard carbon tool steel, especially SK material, having a hole at the bottom. It is fitted together. Note that the screw hole 24 is a screw hole (not shown) after the rotation operation of the stopper 40 is completed and the pressing body 30 of the propulsion force applying device 20 is projected and an appropriate tension force is exerted on the cam chain 10, as described later. Is screwed into the screw hole 24 to seal the screw hole 24.
【００３０】また、軸受け部材25には、回転軸26の基端
円柱部27が回転自在に嵌装され、該回転軸26の先端部に
は、後記押圧体30が突出または後退しうるストロークよ
りも長めの雄ネジ28が形成されている。なお、基端円柱
部27には、基端面から所定の深さと巾で直径方向に指向
した溝29が形成されている。Further, the base end cylindrical portion 27 of the rotary shaft 26 is rotatably fitted to the bearing member 25, and the distal end portion of the rotary shaft 26 has a stroke such that the pressing body 30 described later can project or retract. Also, a longer male screw 28 is formed. In addition, in the base end cylindrical portion 27, a groove 29 is formed which is diametrically oriented at a predetermined depth and width from the base end surface.
【００３１】さらに、押圧体30は、基端筒状部31と、そ
の先端にピン32ａにより一体に取り付けられた先端部材
32と、該先端部材32に弾性体33ａを介して一体に嵌着さ
れた当接体33とよりなり、前記基端筒状部31の基端部に
は前記雄ネジ28の約１／４以上またネジの２ピッチ以上
の長さの雌ネジ34が形成されており、該雌ネジ34に前記
雄ネジ28が螺合されている。そして、基端筒状部31の外
周面には、円柱面の外両側方に相互に平行な平坦面が形
成され、後記キャップ36の孔36ａの平行部と基端筒状部
の平坦面とで、押圧体30の回転が阻止されるようになっ
ている。Further, the pressing body 30 comprises a base end tubular portion 31 and a tip end member integrally attached to the tip end thereof by a pin 32a.
32 and an abutment body 33 integrally fitted to the tip end member 32 via an elastic body 33a, and the base end portion of the base end tubular portion 31 has about 1/4 of the male screw 28. Further, a female screw 34 having a length of 2 pitches or more is formed, and the male screw 28 is screwed into the female screw 34. Then, on the outer peripheral surface of the proximal end tubular portion 31, flat surfaces parallel to each other are formed on both outer sides of the cylindrical surface, and the flat portions of the parallel portions of the holes 36a of the cap 36 and the proximal end tubular portion are formed. Thus, rotation of the pressing body 30 is blocked.
【００３２】さらにまた、回転軸26の基端円柱部27にガ
イド筒35が遊嵌され、該ガイド筒35に押圧体30の基端筒
状部31の基端が摺動自在に装入され、該ガイド筒35の突
出を阻止し、かつ押圧体30の基端筒状部31の両側平坦面
に接触して、該基端筒状部31の回転を阻止するためのキ
ャップ36が、該基端筒状部31に嵌合され、該キャップ36
に半径方向へ周方向に亘り複数個突出する係合爪37がケ
ーシング21の先端切り欠き21ａに係合され、ケーシング
21の先端円周溝21ｂに止め輪38が装着されて、キャップ
36がケーシング21の先端に係止されている。Furthermore, a guide cylinder 35 is loosely fitted to the base end cylindrical portion 27 of the rotary shaft 26, and the base end of the base end cylindrical portion 31 of the pressing body 30 is slidably inserted into the guide cylinder 35. A cap 36 for preventing the guide cylinder 35 from protruding and contacting both flat surfaces of the proximal end tubular portion 31 of the pressing body 30 to prevent the proximal end tubular portion 31 from rotating. The cap 36 is fitted to the proximal tubular portion 31.
A plurality of engaging claws 37 protruding in the radial direction in the circumferential direction are engaged with the notches 21 a at the tip of the casing 21,
Retaining ring 38 is attached to the tip circumferential groove 21b of 21, and the cap is
36 is locked to the tip of the casing 21.
【００３３】しかも、ケーシング21の収納孔22と回転軸
26の基端円柱部27およびガイド筒35との間にコイルスプ
リング39が介装され、該コイルスプリング39の基端39ａ
は直角に折曲されて、基端円柱部27の溝29に係合され、
該コイルスプリング39の先端39ｂはケーシング21より外
方へ突出してその切り欠き段部21ｃに係止されている。Moreover, the housing hole 22 of the casing 21 and the rotary shaft
A coil spring 39 is interposed between the base end cylindrical portion 27 of 26 and the guide tube 35, and the base end 39 a of the coil spring 39.
Is bent at a right angle and is engaged with the groove 29 of the base end cylindrical portion 27,
The tip 39b of the coil spring 39 projects outward from the casing 21 and is locked to the notch step 21c.
【００３４】なお、ケーシング21には、ケーシング21の
先端より取り付け孔23に向いオイル供給孔21ｄが形成さ
れるとともに、ネジ孔24の下端外周に、該ネジ孔24の外
方中心線から見て十字状の係止切り欠き21ｅが形成され
ている。An oil supply hole 21d is formed in the casing 21 from the front end of the casing 21 to the mounting hole 23, and the outer periphery of the lower end of the screw hole 24 is seen from the outer center line of the screw hole 24. A cross-shaped locking notch 21e is formed.
【００３５】図３に図示の推進力付与装置20において
は、回転軸26の基端円柱部27に形成された溝29にコイル
スプリング39の基端折曲部39ａが係合されるとともに、
コイルスプリング39の先端39ａがケーシング21の切り欠
き段部21ｃに係合されたまま、回転軸26およびコイルス
プリング39がケーシング21の収納孔22内に装入さえてい
る。このような状態において、ケーシング21のネジ孔24
の開口端からストッパ40を挿入し、該ストッパ40の先端
40ａを基端円柱部27の溝29に係合し、図３にてＡ方向と
逆の方向から見て反時計方向へストッパ40を所定回転数
捩回して、コイルスプリング39に時計方向へ回転しよう
とする戻りトルクを与えた後、該ストッパ40の基端張り
出し部40ｂをケーシング21の係止切り欠き21ｅに係合
し、回転軸26が回転することができないように回転軸26
を固定する。In the propulsive force applying device 20 shown in FIG. 3, the base end bent portion 39a of the coil spring 39 is engaged with the groove 29 formed in the base end cylindrical portion 27 of the rotary shaft 26, and
The rotary shaft 26 and the coil spring 39 are inserted into the housing hole 22 of the casing 21 while the tip 39a of the coil spring 39 is engaged with the notch step portion 21c of the casing 21. In such a state, the screw hole 24 of the casing 21
Insert the stopper 40 from the open end of the
40a is engaged with the groove 29 of the base end cylindrical portion 27, and the stopper 40 is twisted counterclockwise by a predetermined number of rotations when viewed from the direction opposite to the direction A in FIG. After the return torque to be applied is applied, the base end projecting portion 40b of the stopper 40 is engaged with the locking notch 21e of the casing 21 to prevent the rotation shaft 26 from rotating.
To fix.
【００３６】さらに、キャップ36を基端筒状部31に嵌合
したまま、押圧体30の雌ネジ34を回転軸26の雄ネジ28の
先端に当てがい、Ａ方向から見て時計方向へ押圧体30を
回転させ、雌ネジ34を雄ネジ28の基端に向けて螺入し、
キャップ36の係合爪37をケーシング21の先端切り欠き21
ａに係合した後、止め輪38をケーシング21の先端円周溝
21ｂに装着することにより、推進力付与装置20に押し力
を発生させることができる。Further, with the cap 36 still fitted in the base end tubular portion 31, the female screw 34 of the pressing body 30 is applied to the tip of the male screw 28 of the rotary shaft 26, and is pressed in the clockwise direction when viewed from the A direction. Rotate the body 30, screw the female screw 34 toward the base end of the male screw 28,
Insert the engaging claw 37 of the cap 36 into the notch 21
After engaging with a, the retaining ring 38 is attached to the tip circumferential groove of the casing 21.
By attaching to 21b, a thrust force can be generated in the propulsion force applying device 20.
【００３７】そして、図２に図示するように、この推進
力付与装置20の当接体33がテンショナ11の背部11ｃに当
接するように、推進力付与装置20のケーシング21をシリ
ンダヘッド３に一体に装着した後、ストッパ40を引き抜
けば、Ａ方向から見て回転軸26を時計方向へ回転させよ
うとするコイルスプリング39の復元バネトルクが解放さ
れ、回転軸26がその方向へ回転するために押圧体30はキ
ャップ36によって回転を阻止されながら突出し、テンシ
ョナ11を介してカムチェーン10に張力を与えることがで
きる。As shown in FIG. 2, the casing 21 of the propulsion force applying device 20 is integrated with the cylinder head 3 so that the contact body 33 of the propulsion force applying device 20 contacts the back portion 11c of the tensioner 11. When the stopper 40 is pulled out after being mounted on, the restoring spring torque of the coil spring 39 that tries to rotate the rotary shaft 26 clockwise when viewed from the A direction is released, and the rotary shaft 26 rotates in that direction. The pressing body 30 projects while being prevented from rotating by the cap 36, and can apply tension to the cam chain 10 via the tensioner 11.
【００３８】この押圧体30が突出する押し力Ｎは、コイ
ルスプリング39の復元バネトルクと、回転軸26の端面直
径Ｄ１と、該回転軸26、軸受け部材25間の摩擦係数と、
雄ネジ28および雌ネジ34の進み角αと該雄ネジ28、雌ネ
ジ34間の摩擦係数とによって決まり、また、当接体33が
テンショナ11の背部11ｃに当接し、カムチェーン10の張
力によりテンショナ11を介して押圧体30が押し戻される
際に発生する押し戻し抵抗力も、前述したと同様な値で
決まる。The pushing force N by which the pressing body 30 projects is the restoring spring torque of the coil spring 39, the end surface diameter D 1 of the rotary shaft 26, and the friction coefficient between the rotary shaft 26 and the bearing member 25.
Determined by the lead angle α of the male screw 28 and the female screw 34 and the friction coefficient between the male screw 28 and the female screw 34, the contact body 33 contacts the back portion 11c of the tensioner 11, and the tension of the cam chain 10 causes The push-back resistance force generated when the pressing body 30 is pushed back through the tensioner 11 is also determined by the same value as described above.
【００３９】そして、押圧体30が突出する押し力Ｎも、
押圧体30が押し戻される際に発生する押し戻し抵抗力
も、或る値以上大きくないと、カムチェーン10の回送の
際の波打ち現象が阻止されずに騒音が発生し、逆に前記
押し力や押し戻し抵抗力が大き過ぎると、カムチェーン
10に大きな張力が発生するとともにカムチェーン10とテ
ンショナ11との間の摩擦力が大巾に増大し、カムチェー
ン10およびテンショナ11が磨耗されて耐久性が低下す
る。The pushing force N by which the pushing body 30 projects is also
If the pushing-back resistance force generated when the pressing body 30 is pushed back is also not larger than a certain value, the waving phenomenon at the time of forwarding of the cam chain 10 is not prevented and noise is generated, conversely the pushing force and the pushing-back resistance. If the force is too large, the cam chain
A large tension is generated in 10 and the frictional force between the cam chain 10 and the tensioner 11 is greatly increased, the cam chain 10 and the tensioner 11 are worn, and the durability is reduced.
【００４０】前記押し戻し抵抗力は静的なものでなく、
動的なものであるので、本願発明者は、図４に図示され
た試験装置50を用いて、動的な押し戻し抵抗力を推定す
ることができる戻りトルクＴを測定した。The push-back resistance force is not static,
Since it is dynamic, the inventor of the present application measured the return torque T capable of estimating the dynamic push-back resistance force by using the test apparatus 50 shown in FIG.
【００４１】図４に図示の試験装置50では、推進力付与
装置20のケーシング21を安定して保持する保持筒53が架
台51の天板52上に設置され、該天板52には、ストッパ40
を挿入しうるとともに回転させることができる孔54が形
成されている。In the test device 50 shown in FIG. 4, a holding cylinder 53 that stably holds the casing 21 of the propulsion force applying device 20 is installed on the top plate 52 of the pedestal 51, and the top plate 52 has a stopper. 40
There is formed a hole 54 into which can be inserted and which can be rotated.
【００４２】試験装置50を用いて戻りトルクＴを測定す
るには、天板52の下方から図示されない回転駆動装置を
配置し、この回転先端爪（図示されず）を基端円柱部27
の溝29に係合し、押圧体30がケーシング21より所定長さ
突出した状態において、基端筒状部31に所定の重量の重
錘55を載せて固定し、押圧体30を突出させようと付勢す
るコイルスプリング39のバネ力に打ち勝って、前記回転
駆動装置により回転軸26をＡ方向から見て反時計方向に
回転させ、押圧体30を所定速度で引き戻す換言すれば押
圧体30をケーシング21内に退入させるに必要なトルクを
前記回転駆動装置中のトルクセンサで測定する。このト
ルクがすなわち戻りトルクＴである。In order to measure the return torque T using the test device 50, a rotary drive device (not shown) is arranged from below the top plate 52, and this rotary tip claw (not shown) is used as the base end cylindrical portion 27.
In a state in which the pressing body 30 is engaged with the groove 29 of the casing 21 and protrudes from the casing 21 by a predetermined length, a weight 55 having a predetermined weight is placed and fixed on the proximal end tubular portion 31, and the pressing body 30 is projected. By overcoming the spring force of the coil spring 39 that urges the rotating body 26 to rotate the rotary shaft 26 counterclockwise when viewed from the direction A, the pressing body 30 is pulled back at a predetermined speed. The torque required to retract into the casing 21 is measured by the torque sensor in the rotary drive device. This torque is the return torque T.
【００４３】前述した押圧体30の押し力Ｎを横軸に、戻
りトルクＴを変数とする２次元マップに、前述した測定
データを記入すると、図５の■、□を結んだ線Ｘ、▲、
△を結んだ線Ｙ、◆、◇を結んだ線Ｚが得られる。When the above-mentioned measurement data is entered in a two-dimensional map in which the pushing force N of the pressing body 30 is plotted on the abscissa and the return torque T is set as a variable, the line X, ▲ in FIG. ,
A line Y connecting Δ and a line Z connecting ♦ and ◇ are obtained.
【００４４】■、□を結んだ線Ｘは、回転軸26の基端円
柱部27の端面直径Ｄ１を１２ｍｍに、雄ネジ28および雌
ネジ34の進み角αを１２度に設定した場合の特性線であ
り、また、▲、△を結んだ線Ｙは、前記端面直径Ｄ１を
１２ｍｍに、前記進み角αを１４度に設定した場合の特
性線であり、さらに、◆、◇を結んだ線Ｚは、前記端面
直径Ｄ１を９ｍｍに、前記進み角のαを１２度に設定し
た場合の特性線である。A line X connecting (1) and (2) indicates that the diameter D 1 of the base end cylindrical portion 27 of the rotary shaft 26 is set to 12 mm and the lead angle α of the male screw 28 and the female screw 34 is set to 12 degrees. A characteristic line, and a line Y connecting ▲ and Δ is a characteristic line when the end face diameter D 1 is set to 12 mm and the advance angle α is set to 14 degrees, and further, ◆ and ◇ are connected. The curved line Z is a characteristic line when the end surface diameter D 1 is set to 9 mm and the advance angle α is set to 12 degrees.
【００４５】これをさらに説明すると、特性線Ｘは、回
転軸26の基端円柱部27の端面直径Ｄ １が大きく、雄ネジ
28および雌ネジ34の進み角αが小さい場合の特性を示し
て、一定の押し力Ｎに対して摩擦力の影響が大きく作用
した戻りトルクＴの大きなケースであり、特性線Ｙは、
前記端面直径Ｄ１はＸと同一であるが、前記進み角αが
大きくて、一定の押し力Ｎに対する摩擦力の影響が小さ
く作用した戻りトルクＴの小さなケースであり、特性線
Ｚは、前記進み角αはＸと同一であるが、前記端面直径
Ｄ１が小さくて、一定の押し力Ｎに対する摩擦力の影響
がさらに小さく作用した戻りトルクＴの一段と小さなケ
ースである。To further explain this, the characteristic line X is
End face diameter D of base end cylindrical portion 27 of rolling shaft 26 1Has a large, male screw
28 shows the characteristics when the lead angle α of female screw 34 and female screw 34 is small.
The frictional force has a large effect on the constant pushing force N.
This is a case where the return torque T is large and the characteristic line Y is
The end surface diameter D1Is the same as X, but the advance angle α is
Large, small influence of frictional force on constant pushing force N
This is a case where the return torque T that has acted well is small, and the characteristic line
Z is the same as X in the advance angle α, but the end surface diameter is
D1Is small, the influence of frictional force on constant pushing force N
Is smaller than the return torque T.
It is the source.
【００４６】さらに、前記特性線Ｘ、Ｙ、Ｚにおいて、
左側の部分は、コイルスプリング39に加える捩回回転数
が少なくて、押し力Ｎと戻りトルクＴが小さな値を示し
たものであり、右側の部分は、前記捩回回転数が多く
て、押し力Ｎと戻りトルクが大きな値を示したものであ
る。Further, in the characteristic lines X, Y and Z,
The left side shows a small value of the pushing force N and the return torque T due to the small number of twisting rotations applied to the coil spring 39, and the right side shows a large number of the twisting rotations and the pushing torque N. The force N and the return torque show large values.
【００４７】そして、前記推進力付与装置20を前記排気
量８００ｃｃのＶ型４気筒内燃機関１の前側シリンダヘ
ッド３に設置した場合において、カムチェーン10が発生
する音の許容レベル以下に抑制するに必要な押し力Ｎと
戻りトルクＴの音限界は、図５のＳで示され、この音許
容限界Ｓ以下に押し力Ｎと戻りトルクＴが小さいと、カ
ムチェーン10が発生する音が許容レベルを越えることに
なり、この音許容限界Ｓ以上に押し力Ｎと戻りトルクＴ
を大きくすることが必要であることを本願発明者は、実
験の結果、判明した。When the propulsive force applying device 20 is installed in the front cylinder head 3 of the V-type 4-cylinder internal combustion engine 1 having a displacement of 800 cc, the noise generated by the cam chain 10 can be suppressed below the allowable level. The sound limit of the required pushing force N and the return torque T is shown by S in FIG. 5, and when the pushing force N and the return torque T are smaller than the sound allowable limit S, the sound generated by the cam chain 10 is at an allowable level. Is exceeded, and the pushing force N and the return torque T exceed the sound allowable limit S.
As a result of experiments, the inventor of the present invention has found that it is necessary to increase.
【００４８】また、前記推進力付与装置20を前記排気量
８００ｃｃのＶ型４気筒内燃機関１の前側シリンダヘッ
ド３に設置した場合において、カムチェーン10およびテ
ンショナ11の磨耗が許容レベル以下に維持するに必要な
押し力Ｎと戻りトルクＴの磨耗許容限界は、図５のＷで
示され、この磨耗許容限界Ｗ以上に押し力Ｎと戻りトル
クＴが大きいと、カムチェーン10およびテンショナ11の
磨耗が激しくなり、この磨耗許容限界Ｗ以下に押し力Ｎ
と戻りトルクＴを小さくすることが必要であることを本
願発明者は、実験の結果、判明した。When the propulsion device 20 is installed on the front cylinder head 3 of the V-type 4-cylinder internal combustion engine 1 having a displacement of 800 cc, the wear of the cam chain 10 and the tensioner 11 is kept below the allowable level. The allowable wear limit of the pushing force N and the return torque T required for the above is shown by W in FIG. 5. When the pushing force N and the return torque T are larger than the wear allowance limit W, the wear of the cam chain 10 and the tensioner 11 is increased. Becomes severer and the pushing force N
As a result of experiments, the inventor of the present application has found that it is necessary to reduce the return torque T.
【００４９】そして、本願発明者は、前記推進力付与装
置20を前記排気量８００ｃｃのＶ型４気筒内燃機関１の
前側シリンダヘッド３に設けられた前記推進力付与装置
20において、この音許容限界Ｓと磨耗許容限界Ｗとで挟
まれた両立範囲ＡＬに押し力Ｎと戻りトルクＴを設定す
ることにより、カムチェーン10の発生騒音を許容できる
程度の音以下にすることができるとともに、実用に供す
ることができる程度の耐久性をカムチェーン10およびテ
ンショナ11に与えることができる。Then, the inventor of the present application installed the propulsive force applying device 20 on the front side cylinder head 3 of the V-type 4-cylinder internal combustion engine 1 having the displacement of 800 cc.
In FIG. 20, by setting the pushing force N and the return torque T in the compatible range AL sandwiched between the sound allowable limit S and the wear allowable limit W, the noise generated by the cam chain 10 is reduced to an allowable sound or less. It is possible to provide the cam chain 10 and the tensioner 11 with durability that can be used for practical purposes.
【００５０】しかも、前述した３種類の試験の結果、特
性線Ｙの特性を有する回転軸26の基端円柱部27の端面直
径Ｄ１が１２ｍｍで、進み角αが１４度の推進力付与装
置20が最も好ましいことが分った。Moreover, as a result of the above-mentioned three types of tests, the propulsive force imparting device having the end face diameter D 1 of the base end cylindrical portion 27 of the rotary shaft 26 having the characteristic of the characteristic line Y of 12 mm and the advance angle α of 14 degrees. It turns out that 20 is the most preferred.
【００５１】また、軸受け部材25、回転軸26および押圧
体30の少なくとも一つにメッキを施すことにより、推進
力付与装置20における摩擦力を軽減し、図５における耐
磨耗限界Ｗを上方へ移動させて、各推進力付与装置20に
おける両立範囲ＡＬを通る特性線Ｘ、Ｙ、Ｚの長さ
Ｘ１、Ｙ１、Ｚ１を長くすることができる。Further, by plating at least one of the bearing member 25, the rotary shaft 26 and the pressing body 30, the frictional force in the propulsion force applying device 20 is reduced, and the wear resistance limit W in FIG. The lengths X 1 , Y 1 , and Z 1 of the characteristic lines X, Y, and Z passing through the compatibility range AL in each propulsive force applying device 20 can be lengthened by moving.
【００５２】さらに、推進力付与装置20は、テンショナ
11の基端11ａと背部11ｃとを結ぶ線に対し略直角に近い
角度に向いているため、推進力付与装置20の押し力と戻
り抵抗力とを有効に負担することができる。Further, the thrust applying device 20 is a tensioner.
Since it is oriented at an angle close to a right angle to the line connecting the base end 11a of 11 and the back portion 11c, the pushing force and the return resistance force of the propulsion force applying device 20 can be effectively beared.
【００５３】前記実施形態においては、回転軸26を回転
させるように付勢するスプリングはコイルスプリング39
であったが、これを渦巻状に巻回した渦巻状スプリング
にしてもよい。In the above embodiment, the spring for urging the rotating shaft 26 to rotate is the coil spring 39.
However, it may be a spiral spring in which the spiral spring is wound.
【００５４】また、前記実施形態においては、回転軸26
に雄ネジ28を形成するとともに、押圧体30の基端筒状部
31に雌ネジ34を形成したが、回転軸26に雌ネジ34を、基
端筒状部31に雄ネジ28を形成してもよい。In the above embodiment, the rotary shaft 26
The male screw 28 is formed on the
Although the female screw 34 is formed on the 31, the female screw 34 may be formed on the rotary shaft 26 and the male screw 28 may be formed on the proximal end tubular portion 31.
【図１】 本願発明のテンショナの推進力付与装置を有
する内燃機関を搭載した自動二輪車の右側面図である。FIG. 1 is a right side view of a motorcycle equipped with an internal combustion engine having a tensioner propulsive force imparting device of the present invention.
【図２】 図１に図示の内燃機関の要部を縦断した側面
図である。FIG. 2 is a side view in which a main part of the internal combustion engine shown in FIG. 1 is longitudinally cut.
【図３】 本願発明のテンショナの推進力付与装置の一
実施形態を縦断した縦断側面図である。FIG. 3 is a vertical cross-sectional side view of an embodiment of the thruster thrust applying device of the present invention.
【図４】 本願発明の推進力付与装置の一実施形態の検
査方法を図示した縦断側面図である。FIG. 4 is a vertical cross-sectional side view illustrating an inspection method of an embodiment of the propulsive force imparting device of the present invention.
【図５】 推進力付与装置における押し力Ｎと戻りトル
クＴを変数とする２次元マップである。FIG. 5 is a two-dimensional map in which the pushing force N and the return torque T in the propulsion force applying device are variables.
０…自動二輪車、１…内燃機関、２…シリンダブロッ
ク、３…シリンダヘッド、４…クランクケース、５…シ
リンダヘッドカバー、６…クランクシャフト、７…カム
シャフト、８…ドリブンスプロケット、９…ドライブス
プロケット、10…カムチェーン、11…テンショナ、12…
チェーンガイド、20…推進力付与装置、21…ケーシン
グ、22…収納孔、23…取り付け孔、24…ネジ孔、25…軸
受け部材、26…回転軸、27…基端円柱部、28…雄ネジ、
29…溝、30…押圧体、31…基端筒状部、32…先端部材、
33…当接体、34…雌ネジ、35…ガイド筒、36…キャッ
プ、37…係合爪、38…止め輪、39…コイルスプリング、
40…ストッパ、50…試験装置、51…架台、52…天板、53
…保持筒、54…孔、55…重錘。0 ... Motorcycle, 1 ... Internal combustion engine, 2 ... Cylinder block, 3 ... Cylinder head, 4 ... Crankcase, 5 ... Cylinder head cover, 6 ... Crankshaft, 7 ... Camshaft, 8 ... Driven sprocket, 9 ... Drive sprocket, 10 ... Cam chain, 11 ... Tensioner, 12 ...
Chain guide, 20 ... Propulsion force imparting device, 21 ... Casing, 22 ... Storage hole, 23 ... Mounting hole, 24 ... Screw hole, 25 ... Bearing member, 26 ... Rotating shaft, 27 ... Base end cylindrical portion, 28 ... Male screw ,
29 ... Groove, 30 ... Pressing body, 31 ... Base end tubular portion, 32 ... Tip member,
33 ... Abutment body, 34 ... Female screw, 35 ... Guide tube, 36 ... Cap, 37 ... Engaging claw, 38 ... Retaining ring, 39 ... Coil spring,
40 ... Stopper, 50 ... Testing device, 51 ... Stand, 52 ... Top plate, 53
… Holding cylinder, 54… Hole, 55… Weight.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 飯塚 徹 埼玉県和光市中央１丁目４番１号 株式会 社本田技術研究所内 (72)発明者 飯野 一明 埼玉県和光市中央１丁目４番１号 株式会 社本田技術研究所内 Ｆターム(参考） 3J049 AA08 BB02 BB13 BB22 BC01 BC07 CA02 CA05 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Toru Iizuka 1-4-1 Chuo Stock Market, Wako City, Saitama Prefecture Inside Honda Research Laboratory (72) Inventor Kazuaki Iino 1-4-1 Chuo Stock Market, Wako City, Saitama Prefecture Inside Honda Research Laboratory F term (reference) 3J049 AA08 BB02 BB13 BB22 BC01 BC07 CA02 CA05
Claims (10)
ネジを有する押圧体が、その軸線まわりに回転せずに軸
線方向へ移動可能にケーシングに支持され、前記ネジに
螺合するネジ部を有する回転軸の後部と前記ケーシング
との間に、該回転軸に加えられる推進反力を負担しなが
ら該回転軸をその軸線まわりに回転可能に支持する軸受
け部材が介装され、前記ケーシングおよび回転軸間に
は、前記押圧体を前進させる方向へ付勢するスプリング
が設けられ、無端伝動帯を前記テンショナを介し緊張方
向に押圧して該無端伝動帯に張力を与えるテンショナの
推進力付与装置において、 前記スプリングの付勢により前記押圧体が突出する力で
ある押し力と、 該押圧体に一定の荷重を加えた状態で、前記スプリング
の付勢力と摩擦力に打ち勝ち該押圧体を一定速度で退入
させるべく、前記回転軸を回転させるに必要な戻りトル
クとを変数とする２次元マップ上で、 前記テンショナおよび無端伝動帯のいずれか一方または
両方が磨耗に耐えることができる磨耗許容限界と、前記
無端伝動帯が回送時に発生する音の音許容限界とで挟ま
れた両立範囲内に、前記押し力と戻りトルクが設定され
たことを特徴とするテンショナの推進力付与装置。1. A front end is brought into contact with a tensioner, and
A pressing body having a screw is supported by the casing so as to be movable in the axial direction without rotating around the axis thereof, and the rotating body is provided between the casing and a rear portion of a rotary shaft having a screw portion screwed into the screw. A bearing member for rotatably supporting the rotary shaft around its axis while bearing a propulsive reaction force applied to the shaft is interposed, and a biasing member is urged between the casing and the rotary shaft in a direction to advance the pressing body. In the tensioner propulsion force imparting device that is provided with a spring that presses the endless transmission band in the tension direction via the tensioner to apply tension to the endless transmission band, the pressing force of the pressing body is projected by the biasing force of the spring. With a certain pressing force and a constant load applied to the pressing body, the rotary shaft is rotated so as to overcome the biasing force and the frictional force of the spring and retract the pressing body at a constant speed. On a two-dimensional map with the return torque required to drive the variable, one or both of the tensioner and the endless transmission belt can withstand wear, and the endless transmission belt is generated during forwarding. A propulsion force imparting device for a tensioner, wherein the pushing force and the return torque are set within a compatible range sandwiched by a sound allowable limit.
た筒状押圧体であり、前記回転軸のネジ部は、雄ネジで
あることを特徴とする請求項１記載のテンショナの推進
力付与装置。2. The tensioner according to claim 1, wherein the pressing body is a cylindrical pressing body having an internal thread formed on an inner peripheral surface thereof, and the threaded portion of the rotary shaft is a male thread. Propulsion device.
ネジを有する押圧体が、その軸線まわりに回転せずに軸
線方向へ移動可能にケーシングに支持され、前記ネジに
螺合するネジ部を有する回転軸の後部と前記ケーシング
との間に、該回転軸に加えられる推進反力を負担しなが
ら該回転軸をその軸線まわりに回転可能に支持する軸受
け部材が介装され、前記ケーシングおよび回転軸間に
は、前記押圧体を前進させる方向へ付勢するスプリング
が設けられ、無端伝動帯を前記テンショナを介し緊張方
向に押圧して該無端伝動帯に張力を与えるテンショナの
推進力付与装置の検査方法において、 前記スプリングの付勢により前記押圧体が突出する力で
ある押し力と、 該押圧体に一定の荷重を加えた状態で、前記スプリング
の付勢力と摩擦力に打ち勝ち該押圧体を一定速度で退入
させるべく、前記回転軸を回転させるに必要な戻りトル
クとを変数とする２次元マップ上で、 前記テンショナおよび無端伝動帯のいずれか一方または
両方が磨耗に耐えることができる磨耗許容限界と、前記
無端伝動帯が回送時に発生する音の音許容限界とで挟ま
れた両立範囲内に、前記押し力と戻りトルクが存在する
か否かを判定基準とするテンショナの推進力付与装置の
検査方法。3. The front end is brought into contact with a tensioner, and
A pressing body having a screw is supported by the casing so as to be movable in the axial direction without rotating around the axis thereof, and the rotating body is provided between the casing and a rear portion of a rotary shaft having a screw portion screwed into the screw. A bearing member for rotatably supporting the rotary shaft around its axis while bearing a propulsive reaction force applied to the shaft is interposed, and a biasing member is urged between the casing and the rotary shaft in a direction to advance the pressing body. In a method of inspecting a tensioner propulsion force imparting device that applies a tension to the endless transmission band by pressing the endless transmission band in the tension direction via the tensioner, the pressing body is projected by the biasing of the spring. In order to overcome the urging force and the frictional force of the spring and to withdraw the pressing body at a constant speed, the pressing force, which is the force to move the pressing body, is applied to the pressing body with a constant load. On a two-dimensional map in which the return torque required to rotate the shaft is used as a variable, the wear allowance limit at which one or both of the tensioner and the endless transmission belt can withstand abrasion, and the endless transmission belt are fed. A method of inspecting a thruster propulsion device for a tensioner, wherein a criterion is whether or not the pushing force and the return torque are present within a compatible range sandwiched between a sound allowable limit of a sound generated at times.
関のカムチェーンテンショナのリフタであることを特徴
とするテンショナの推進力付与装置。4. A propulsion force imparting device for a tensioner, wherein the propulsive force imparting device according to claim 1 is a lifter for a cam chain tensioner of an internal combustion engine.
が、内燃機関のカムチェーンテンショナのリフタの検査
方法であることを特徴とするテンショナの推進力付与装
置。5. A propulsion force applying device for a tensioner, wherein the inspection method for the propulsive force applying device according to claim 3 is a method for inspecting a lifter for a cam chain tensioner of an internal combustion engine.
転軸の端面径と前記ネジの進み角のいずれか一方または
両方の変更で行なうことを特徴とする請求項１記載のテ
ンショナの推進力付与装置。6. The propulsion of a tensioner according to claim 1, wherein the pushing force and the return torque are set by changing one or both of the end face diameter of the rotary shaft and the lead angle of the screw. Power application device.
の推進力付与装置の前端およびテンショナの接触点とを
結ぶ線に対して、略直角方向に該推進力付与装置の押し
力が加わるように、該推進力付与装置を設けたことを特
徴とするテンショナの推進力付与装置。7. A pushing force of the propulsion force imparting device in a direction substantially perpendicular to a line connecting the swinging pivot shaft of the tensioner and the front end of the propulsion force imparting device according to claim 1 and the contact point of the tensioner. A propulsion force applying device for a tensioner, wherein the propulsion force applying device is provided so that
具鋼であることを特徴とする請求項１記載のテンショナ
の推進力付与装置。8. The thruster thrust imparting device according to claim 1, wherein the bearing member is a superhard carbon tool steel such as SK material.
なくとも一つにメッキが施されて、前記押し力と戻りト
ルクとが設定されたことを特徴とする請求項１記載のテ
ンショナの推進力付与装置。9. The propulsive force for the tensioner according to claim 1, wherein at least one of the pressing body, the rotary shaft and the bearing member is plated to set the pushing force and the return torque. Applicator.
あるいは弾性体を介して当接部材が付設されたことを特
徴とする請求項１記載のテンショナの推進力付与装置。10. An elastic body is attached to a front end of the pressing body,
Alternatively, the propulsion force applying device for the tensioner according to claim 1, wherein a contact member is attached via an elastic body.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001277119A JP3995439B2 (en) | 2001-09-12 | 2001-09-12 | Inspection method for tensioner propulsion device |
| CN 02130262 CN1196872C (en) | 2001-09-12 | 2002-08-22 | Propulsive force giving apparatus for tension device |
| BR0203530A BR0203530B1 (en) | 2001-09-12 | 2002-09-05 | propelling force device for tensioner and method for inspecting said device. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001277119A JP3995439B2 (en) | 2001-09-12 | 2001-09-12 | Inspection method for tensioner propulsion device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003083402A true JP2003083402A (en) | 2003-03-19 |
| JP3995439B2 JP3995439B2 (en) | 2007-10-24 |
Family
ID=19101702
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001277119A Expired - Fee Related JP3995439B2 (en) | 2001-09-12 | 2001-09-12 | Inspection method for tensioner propulsion device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP3995439B2 (en) |
| CN (1) | CN1196872C (en) |
| BR (1) | BR0203530B1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112513500A (en) * | 2018-08-01 | 2021-03-16 | 日本发条株式会社 | Tensioner |
| CN113412380A (en) * | 2019-03-28 | 2021-09-17 | 本田技研工业株式会社 | Tensioning regulator |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4934815B2 (en) * | 2007-03-08 | 2012-05-23 | 日本発條株式会社 | Tensioner |
| JP4934816B2 (en) * | 2007-03-08 | 2012-05-23 | 日本発條株式会社 | Tensioner |
| JP6612838B2 (en) * | 2017-12-21 | 2019-11-27 | 本田技研工業株式会社 | Screw type tensioner lifter for internal combustion engine |
| DE102020209370A1 (en) * | 2019-08-08 | 2021-02-11 | Sram Deutschland Gmbh | Bicycle rear derailleur, especially with a spring / damper assembly |
-
2001
- 2001-09-12 JP JP2001277119A patent/JP3995439B2/en not_active Expired - Fee Related
-
2002
- 2002-08-22 CN CN 02130262 patent/CN1196872C/en not_active Expired - Fee Related
- 2002-09-05 BR BR0203530A patent/BR0203530B1/en not_active IP Right Cessation
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112513500A (en) * | 2018-08-01 | 2021-03-16 | 日本发条株式会社 | Tensioner |
| CN112513500B (en) * | 2018-08-01 | 2023-08-29 | 大同工业株式会社 | tensioner |
| CN113412380A (en) * | 2019-03-28 | 2021-09-17 | 本田技研工业株式会社 | Tensioning regulator |
| CN113412380B (en) * | 2019-03-28 | 2024-05-17 | 本田技研工业株式会社 | Tensioning regulator |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1196872C (en) | 2005-04-13 |
| CN1403725A (en) | 2003-03-19 |
| BR0203530A (en) | 2003-09-09 |
| JP3995439B2 (en) | 2007-10-24 |
| BR0203530B1 (en) | 2011-07-26 |
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