JPS61218857A - Tensioner device in wrapping transmission for internal-combustion engine - Google Patents

Tensioner device in wrapping transmission for internal-combustion engine

Info

Publication number
JPS61218857A
JPS61218857A JP5806285A JP5806285A JPS61218857A JP S61218857 A JPS61218857 A JP S61218857A JP 5806285 A JP5806285 A JP 5806285A JP 5806285 A JP5806285 A JP 5806285A JP S61218857 A JPS61218857 A JP S61218857A
Authority
JP
Japan
Prior art keywords
oil
engine body
transmission
lever
tension
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP5806285A
Other languages
Japanese (ja)
Inventor
Nobuo Abu
阿武　信夫
Hidekazu Ichihara
市原　英一
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP5806285A priority Critical patent/JPS61218857A/en
Priority to CA000504399A priority patent/CA1254770A/en
Priority to US06/840,831 priority patent/US4761155A/en
Priority to GB8606724A priority patent/GB2175064B/en
Priority to DE19863609232 priority patent/DE3609232A1/en
Publication of JPS61218857A publication Critical patent/JPS61218857A/en
Priority to GB8823825A priority patent/GB2208906B/en
Priority to GB8823824A priority patent/GB2208905B/en
Pending legal-status Critical Current

Links

Classifications

    • 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
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F16H7/129—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path with means for impeding reverse motion
    • 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
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/06—Endless member is a belt
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • 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
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • 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
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

PURPOSE:To improve the transmission efficiency by rolling the tension pulley and the rolling lever without contacting directly with the engine body and the guide shaft. CONSTITUTION:An arched hole 10 is made around a shaft 12 through the pulley shaft section 91 to enable vertical rolling of lever 9 within the angular range limited by said hole 10. A spacer S2 is placed between the endface 13 of the engine body and the rolling lever 9. Second spacer S2 and first spacer S1 arranged at the shaft section of the rolling lever 9 will co-operate to avoid direct contact between the rolling lever 9 and the engine body. Consequently, the tension pulley and the rolling lever will roll without contacting with the engine body and the guide shaft resulting in improvement of transmission efficiency of wrapping transmission.

Description

【発明の詳細な説明】 Ａ０発明の目的 （１）　　産業上の利用分野 本発明は、内燃機関において、機関本体に支持される駆
動輪と被動輪間に懸回される無端状伝動帯に自動的に一
定の張力を付与するようにした巻掛伝動装置のテンショ
ナ装置に関するものである。Detailed Description of the Invention A0 Object of the Invention (1) Industrial Application Field The present invention relates to an internal combustion engine in which an endless power transmission band suspended between a driving wheel and a driven wheel supported by an engine body has an automatic The present invention relates to a tensioner device for a wrap-around transmission device that applies a constant tension.

（２）従来の技術 従来機関本体に支持される、駆動輪と被動輪間に無端状
伝動帯を懸回し、該伝動帯の緩み側に機関本体に揺動レ
バーを介して支持されるテンションプーリを圧接して該
伝動帯に一定の張力を付与するようにした内燃機関にお
ける巻掛伝動装置のテンショナ装置は従来公知である（
特開昭５９−２０８２５１号公報参照）。(2) Prior Art Conventionally, an endless transmission band is suspended between a driving wheel and a driven wheel supported by the engine body, and a tension pulley is supported by the engine body via a swing lever on the slack side of the transmission band. A tensioner device for a wrap transmission in an internal combustion engine that applies a constant tension to the transmission band by applying pressure to the transmission band is conventionally known (
(See Japanese Patent Application Laid-open No. 59-208251).

（３）　　発明が解決しようとする問題点ところが前記
テンショナ装置において、テンションプーリは揺動レバ
ーとともに無端状伝動帯の張力変動をうけて揺動運転を
繰返し、また伝動ベルトの振動をうけて軸方向に遊動し
、機関本体に対して浮き上がり傾向になり、特に機関が
高速になればその傾向が大きくなるという問題がある。(3) Problems to be Solved by the Invention However, in the above tensioner device, the tension pulley, together with the swing lever, repeatedly swings in response to tension fluctuations in the endless transmission belt, and also in the axial direction due to the vibrations of the transmission belt. There is a problem that there is a tendency for the engine to float around and float up relative to the engine body, and this tendency becomes more pronounced especially as the engine speeds up.

本発明は上記事情に鑑みてなされたもので、テンション
プーリおよび揺動レバーは機関本体、および案内軸に対
して接触することなく揺動し、また揺動レバー・および
テンションプーリはその軸方向の遊動が抑止されるよう
にした内燃機関における巻掛伝動装置のテンショナ装置
を提供することを目的とするものである。The present invention was made in view of the above circumstances, and the tension pulley and swing lever swing without contacting the engine body and the guide shaft, and the swing lever and tension pulley swing in the axial direction. It is an object of the present invention to provide a tensioner device for a wrap transmission in an internal combustion engine in which drift is suppressed.

Ｂ１発明の構成 （１１問題点を解決するための手段 本発明によれば、前記目的達成のため機関本体に支持さ
れる、駆動輪と被動輪間に無端状伝動帯を懸回し、該伝
動帯の緩み側にテンションプーリを圧接して該伝動帯に
所定の張力を付与するようにした内燃機関における巻掛
伝動装置のテンショナ装置において、前記機関本体には
前記テンションプーリを回転自在に支承する揺動レバー
を揺動自在に軸支するとともに該揺動レバーの揺動を案
内するための案内軸を固着し、前記機関本体および案内
軸を含む固定部と前記テンションブーりおよび揺動レバ
ーを含む可動部との接触部間に、それらの直接接触を避
けるためのスペーサを介装される。B1 Structure of the Invention (Means for Solving Problems 11) According to the present invention, in order to achieve the above object, an endless transmission band is suspended between a driving wheel and a driven wheel supported by an engine body, and the transmission band is In a tensioner device for a wrap transmission in an internal combustion engine, the tensioner device is configured to apply a predetermined tension to the transmission band by pressing a tension pulley against the slack side of the transmission band. A movable lever is pivotally supported so as to be freely swingable, and a guide shaft for guiding the rocking of the rocking lever is fixed, and includes a fixed part including the engine main body and the guide shaft, the tension boob and the rocking lever. A spacer is interposed between the contact parts with the movable part to avoid direct contact between them.

（２）作　用 前記構成によれば、テンションプーリと、揺動レバーは
、機関本体および案内軸と直接接触せず揺動運動を繰り
返すことができ、またテンションプーリの軸方向の浮上
がりが抑止され、巻掛伝動装置の伝動効率が高められる
。(2) Effect According to the above configuration, the tension pulley and the swing lever can repeat the swing motion without directly contacting the engine body and the guide shaft, and the lifting of the tension pulley in the axial direction is suppressed. This increases the transmission efficiency of the wrap-around transmission.

（３）実施例 以下、第１〜７図により本発明装置をＤＯＨＣ型四サイ
クル内燃機関に実施した場合の実施例について説明する
。　　、 第１図において、前記内燃機関の機関本体Ｅの一端面に
は、クランク軸１と、動弁機構の一対の動弁カム軸２と
を連動する調時巻掛伝動装置Ｔが設けられる。この調時
巻掛伝動装置Ｔは従来公知の構造のもので、クランク軸
１に固着される駆動ブーＩＪ　３と、一対の動弁カム軸
２にそれぞれ固着される被動ブーＵ　４との間に無端状
伝動ベルト５を懸回して構成される。伝動ベルト５の途
中には、他の被動°プーリ６が懸回され、この被動プー
リ６によって機関本体Ｅの冷却用水ポンプ７が駆動され
る。(3) Embodiments Hereinafter, embodiments in which the device of the present invention is implemented in a DOHC four-stroke internal combustion engine will be described with reference to FIGS. 1 to 7. In FIG. 1, a timing winding transmission T is provided on one end surface of an engine body E of the internal combustion engine for interlocking a crankshaft 1 and a pair of valve drive camshafts 2 of a valve drive mechanism. This timing winding transmission T has a conventionally known structure, and is located between a driving boob IJ 3 fixed to the crankshaft 1 and a driven boob U 4 fixed to a pair of valve drive camshafts 2, respectively. It is constructed by suspending an endless transmission belt 5. Another driven pulley 6 is suspended in the middle of the transmission belt 5, and this driven pulley 6 drives a cooling water pump 7 for the engine body E.

第１〜４図において、前記駆動ブーＩ７３と他の被動ブ
ーＩＪ　６間で、伝動ベルト５の緩み側５Ｉの外側に圧
接されて該伝動ベルト５に所定の張力を付与するテンシ
ョンプーリ８が機関本体Ｅに揺動可能に支持される。In FIGS. 1 to 4, a tension pulley 8 that is pressed against the outside of the loose side 5I of the transmission belt 5 to apply a predetermined tension to the transmission belt 5 is installed between the drive boob I73 and the other driven boob IJ6. It is swingably supported by the main body E.

次に前記テンションプーリ８の支持構造を主に第３，４
図を参照して説明すると、機関本体Ｅには支軸１２をも
って揺動レバー９が上下に揺動自在に軸支され、この支
軸１２と揺動レバー９間にはグロメット状の合成樹脂製
第１スペーサＳ１が介在され、これにより機関本体Ｅと
揺動レバー９との直接接触が避けされる。揺動レバー９
の中央部には、ポール軸受１１を介してテンションプー
リ８を回転自在に支承したプーリ軸部９１が一体に設け
られ、このプーリ軸部９１には前記支軸１２を中心とす
る円弧孔１０が穿設され、この円弧孔１０は、機関本体
Ｅに固着した案内軸１５に遊嵌され、揺動レバー９は円
弧孔１０に規制された角度範囲で上下に揺動し得る。揺
動レバー９のプーリ軸部９Ｉの内面には合成樹脂製の第
２スペーサＳ２が取付けられ、このスペーサＳ２は、機
関本体Ｅの端面１３と揺動レバー９間に介装される。Next, the support structure of the tension pulley 8 will be
To explain with reference to the figure, a swinging lever 9 is pivotally supported on the engine body E with a support shaft 12 so as to be able to swing up and down, and a grommet-shaped synthetic resin The first spacer S1 is interposed, thereby avoiding direct contact between the engine body E and the swing lever 9. Swing lever 9
A pulley shaft portion 91 that rotatably supports the tension pulley 8 via a pole bearing 11 is integrally provided in the center of the pulley shaft portion 91, and the pulley shaft portion 91 has an arcuate hole 10 centered on the support shaft 12. A guide shaft 15 fixed to the engine body E is loosely fitted into the arcuate hole 10, and the swing lever 9 can swing up and down within an angular range regulated by the arcuate hole 10. A second spacer S2 made of synthetic resin is attached to the inner surface of the pulley shaft portion 9I of the swing lever 9, and this spacer S2 is interposed between the end surface 13 of the engine body E and the swing lever 9.

そして第２スペーサＳ２と、揺動レバー９の軸支部に設
けた第１スペーサＳＩとが協働して揺動レバー９と機関
本体Ｅとの直接の接触が避けられる。The second spacer S2 and the first spacer SI provided on the shaft support of the swing lever 9 cooperate to prevent direct contact between the swing lever 9 and the engine body E.

またプーリ軸部９．の外面と、前記案内軸１５の外端部
間には、合成樹脂製第３スペーサＳ３が介装され、この
第３スペーサＳ３は前記第２スペーサと協働してテンシ
ョンプーリ８および揺動レバー９の軸方向の遊動を防止
する。Also, the pulley shaft portion 9. A third spacer S3 made of synthetic resin is interposed between the outer surface of the guide shaft 15 and the outer end of the guide shaft 15, and this third spacer S3 cooperates with the second spacer to control the tension pulley 8 and the swing lever. 9 to prevent axial movement.

前記揺動レバー９の自由端には伝動ベルト５の給油式オ
ートアジャスタＡが連結される。そしてこのオートアジ
ャスタＡの押圧力で前記テンションプーリ８は、伝動ベ
ルト５に圧接され、該ベルト５に一定の張力が付与され
る。A lubrication type auto adjuster A of the transmission belt 5 is connected to the free end of the swing lever 9. The tension pulley 8 is pressed against the transmission belt 5 by the pressing force of the auto-adjuster A, and a constant tension is applied to the belt 5.

また前記揺動レバー９の中間位置の上部には、基端を機
関本体Ｅの端壁１３に結着される引張ばねＩ４の他端側
が連結されており、この引張ばね１４の引張力は、前記
揺動レバー９を支軸１２回りに反時計方向に揺動するよ
うに偏倚し、テンションプーリ８を伝動ベルト５の緩み
側５．外面に圧接するように偏倚させる。Further, the other end side of a tension spring I4 whose base end is tied to the end wall 13 of the engine body E is connected to the upper part of the intermediate position of the swing lever 9, and the tension force of this tension spring 14 is as follows. The swing lever 9 is biased so as to swing counterclockwise around the support shaft 12, and the tension pulley 8 is moved to the slack side 5. of the transmission belt 5. It is biased so that it comes into pressure contact with the outer surface.

機関本体Ｅの端壁１３には、該本体Ｅの各被滑部に潤滑
油等を強制給油するための従来公知の油圧ポンプＰが固
着され、この油圧ポンプＰは、クランク軸ｌに直結され
て駆動される。そして機関本体Ｅ内の貯留池を吸込通路
Ｐｉ（第４図）より吸上げ吐出通路Ｐｏへ吐出する。A conventionally known hydraulic pump P is fixed to the end wall 13 of the engine body E for forcibly supplying lubricating oil or the like to each sliding part of the engine body E, and this hydraulic pump P is directly connected to the crankshaft l. It is driven by Then, the reservoir in the engine body E is discharged from the suction passage Pi (FIG. 4) to the suction and discharge passage Po.

前記油圧ポンプＰのポンプケース１６の外面には、前記
給油式オートアジャスタＡのアジャスタケース１７が一
体に鋳造成形される。On the outer surface of the pump case 16 of the hydraulic pump P, an adjuster case 17 of the oil supply type auto adjuster A is integrally cast.

次にこの給油式オートアジャスタへの構造を主に第６，
７図を参照して説明すると、前記オートアジャスタＡの
アジャスタケース１７は、ポンプケース１６の外面上部
に一体に形成される。アジャスタケース１７には、開放
上端１日を有する中空円筒状のハウジング１９が形成さ
れる。こめハウジング１９内には同じ（開放上端２０を
有する中空円筒状のプランジャケース２１が嵌着され、
このプランジャケース２１の上部外周とハウジング１９
の内周面間に０リング２２が介装される。Next, we will mainly develop the structure of this oil-filled auto adjuster into the 6th,
Referring to FIG. 7, the adjuster case 17 of the auto adjuster A is integrally formed on the upper outer surface of the pump case 16. The adjuster case 17 is formed with a hollow cylindrical housing 19 having an open upper end. The same (hollow cylindrical plunger case 21 having an open upper end 20) is fitted into the housing 19,
The upper outer periphery of the plunger case 21 and the housing 19
An O-ring 22 is interposed between the inner circumferential surfaces of the .

前記プランジャケース２１内には、上部を先細り状に形
成したプランジャ２３が昇降可能に摺合され、このプラ
ンジャ２３の開放上端２４にはプラグ２５が嵌着される
。このプラグ２５の上部に形成した凹所２６にはスリッ
パ部材２７がＯリング２９を介して嵌入され、このスリ
ッパ部材２７の頂面にスリッパ面２８が形成され、この
スリッパ面２８に、前記揺動レバー９の先端に調節自在
に螺合される調節ねじ３０の下端が当接される。A plunger 23 having a tapered upper portion is slidably movable up and down inside the plunger case 21, and a plug 25 is fitted into the open upper end 24 of the plunger 23. A slipper member 27 is fitted into the recess 26 formed in the upper part of the plug 25 via an O-ring 29, and a slipper surface 28 is formed on the top surface of the slipper member 27. The lower end of an adjusting screw 30 that is adjustably screwed into the tip of the lever 9 is brought into contact.

前記プランジャ２３はプランジャケース２１内の下部に
高圧油室３１を、またその圧部に補給油室３２を画成す
る。The plunger 23 defines a high pressure oil chamber 31 in the lower part of the plunger case 21, and a replenishment oil chamber 32 in the pressure part thereof.

前記プランジャ２３の底壁２３ｄには弁口３３が開口さ
れ、この弁口３３を通して前記高圧油室３１と、前記補
給油室３２とが連通される。高圧油室３１内には前記弁
口３３を開閉するチェック弁Ｖと、前記プランジャ２３
を上方へ弾発する緊張ばね３４とが収容されており、前
記チェック弁Ｖは、弁口３３の弁座に着座される球状弁
体３５と、この弁体３５を収容するパルプケージ３６と
、この弁体３５を閉弁方向に付勢する弁ばね３７とより
構成される。A valve port 33 is opened in the bottom wall 23d of the plunger 23, and the high pressure oil chamber 31 and the replenishment oil chamber 32 communicate with each other through the valve port 33. Inside the high pressure oil chamber 31, there is a check valve V for opening and closing the valve port 33, and a plunger 23.
The check valve V includes a spherical valve body 35 that is seated on the valve seat of the valve port 33, a pulp cage 36 that accommodates the valve body 35, and a pulp cage 36 that accommodates the valve body 35. It is composed of a valve spring 37 that urges the valve body 35 in the valve closing direction.

前記Ｏリング２２よりも下方において、プランジャケー
ス２１の側壁２１ｓ、およびプランジャ２３の側壁２３
ｓには、相互に常時連通する給油孔３８、および油口３
９が貫通して設けられ、前記給油孔３８は、アジャスタ
ケース１７に穿設した給油通路４０に連通され、また前
記油孔３９は、前記補給油室３２に連通される。Below the O-ring 22, a side wall 21s of the plunger case 21 and a side wall 23 of the plunger 23.
s includes an oil supply hole 38 and an oil port 3 that are in constant communication with each other.
The oil supply hole 38 is communicated with an oil supply passage 40 bored in the adjuster case 17, and the oil hole 39 is communicated with the oil supply chamber 32.

前記給油通路４０は前記油圧ポンプＰの吐出口４１に連
通される。したがって機関の運転にともなってクランク
軸１に連結される油圧ポンプＰが駆動されれば、そこか
らの加圧油は常時前記吐出口４１、給油通路４０、給油
孔３８、および油孔３９を通って補給油室３２へ強制給
油される。The oil supply passage 40 communicates with a discharge port 41 of the hydraulic pump P. Therefore, when the hydraulic pump P connected to the crankshaft 1 is driven as the engine operates, pressurized oil from the pump always passes through the discharge port 41, the oil supply passage 40, the oil supply hole 38, and the oil hole 39. The refueling oil chamber 32 is forcibly refueled.

第７図に明瞭に示すように前記給油通路４０は、補給油
室３２側の下流側通路４０ｄと、油圧ポンプＰ側の上流
側通路４０ｕとよりなり、前記下流側通路４０ｄの開口
端は栓体４２によって閉じられる。下流側給油路４０ｄ
内には、調圧用レギュレタＲが内蔵される。このレギュ
レタＲは、下流側給油路４０ｄ内に摺動自在に嵌合され
て油溜連通孔４４を開閉するピストン４６と、このピス
トン４６を閉じ側に付勢するばね４７よりなり、給油通
路４０内の油圧が所定値以上に上昇すると、前記ばね４
７の弾発力に抗してピストン４６を開き方向に摺動し、
油溜連通孔４４を給油通路４０に連通して給油通路４０
内の加圧油を機関本体Ｅ下部の油溜４８に戻すようにな
っている。As clearly shown in FIG. 7, the oil supply passage 40 consists of a downstream passage 40d on the side of the oil supply chamber 32 and an upstream passage 40u on the side of the hydraulic pump P, and the open end of the downstream passage 40d is a plug. It is closed by a body 42. Downstream oil supply path 40d
A pressure regulating regulator R is built inside. The regulator R includes a piston 46 that is slidably fitted into the downstream oil supply passage 40d to open and close the oil sump communication hole 44, and a spring 47 that biases the piston 46 toward the closing side. When the hydraulic pressure within the spring 4 rises above a predetermined value, the spring 4
sliding the piston 46 in the opening direction against the elastic force of 7;
The oil sump communication hole 44 is connected to the oil supply passage 40 to form the oil supply passage 40.
The pressurized oil inside is returned to the oil sump 48 at the bottom of the engine body E.

プランジャ２３の先細り状上部の外周とプランジャケー
ス２１との間には環状のエア抜道路５１が形成され、こ
のエア抜道路５１は、プランジャ２３の開放上端２４と
プラグ２５との嵌合面間に形成されるリーク通路５６を
介して補給油室３２に連通されている。また前記０リン
グ２２と給油孔３８間において、プランジャケース２１
の側壁２Ｓには、前記エア抜道路５１に開口する排油孔
４９が穿設され、この排油孔４９は、プランジャケース
１７に穿設した排油通路５０を介して機関本体Ｅ内の油
溜４８に連通される。An annular air bleed road 51 is formed between the outer periphery of the tapered upper part of the plunger 23 and the plunger case 21, and this air bleed road 51 is formed between the fitting surface of the open upper end 24 of the plunger 23 and the plug 25. It communicates with the replenishment oil chamber 32 via a leak passage 56 formed therein. Further, between the O-ring 22 and the oil supply hole 38, the plunger case 21
An oil drain hole 49 that opens to the air bleed road 51 is bored in the side wall 2S of the engine, and this oil drain hole 49 drains the oil in the engine body E through an oil drain passage 50 bored in the plunger case 17. It communicates with the reservoir 48.

補給油室３２内の油は噛込みエアとともに前記リーク通
路５６を通ってエア抜道路５１に流れ、さらに該通路５
１から前記排油孔４９、および排油通路５０を通って機
関本体Ｅ内の油溜４８内に還流される。The oil in the replenishment oil chamber 32 flows together with the trapped air through the leak passage 56 to the air vent road 51, and further flows through the passage 5.
1, the oil is returned to the oil reservoir 48 in the engine body E through the oil drain hole 49 and the oil drain passage 50.

さらに第６図に示すようにハウジング１９の底部には前
記高圧油室３１の下部とオイルポンプＰの吐出口４１と
を連通ずるエア抜道路５２が穿設され、このエア抜道路
５２はハウジング１９内にプランジャケース２１を組込
む際の油室５７内に封入されるエアえ抜くためのもので
ある。Further, as shown in FIG. 6, an air vent road 52 is bored at the bottom of the housing 19 to communicate the lower part of the high pressure oil chamber 31 with the discharge port 41 of the oil pump P. This is for venting the air sealed in the oil chamber 57 when the plunger case 21 is assembled therein.

プランジャケース２１の上端外周面には、ゴム、合成樹
脂等により形成されるブーツ５３の下端が締付リング５
４によって油密に纏着され、また該ブーツ５３の上端部
は、反転されて締付リング５５によって前記プラグ２５
の外周に油密に纏着される。そしてこのブーツ５３はプ
ランジャ２３の昇降に追従するように伸縮し、プランジ
ャケース２１とプラグ２５間お油密に封誠する。A tightening ring 5 is attached to the lower end of a boot 53 formed of rubber, synthetic resin, etc. on the outer peripheral surface of the upper end of the plunger case 21.
4, and the upper end of the boot 53 is inverted and attached to the plug 25 by a tightening ring 55.
It is oil-tightly wrapped around the outer periphery of the The boot 53 expands and contracts to follow the rise and fall of the plunger 23, thereby creating an oil-tight seal between the plunger case 21 and the plug 25.

次に本発明の実施例の作用について説明する。Next, the operation of the embodiment of the present invention will be explained.

いま機関が運転されると、クランク軸１の回転は駆動プ
ーリ３、伝動ベルト５、および被動プーリ４よりなる調
時巻掛伝動装置Ｔを介して一対の動弁カム軸２に伝達さ
れる。When the engine is operated, the rotation of the crankshaft 1 is transmitted to a pair of valve drive camshafts 2 via a timed winding transmission T consisting of a drive pulley 3, a transmission belt 5, and a driven pulley 4.

前記伝動ベルト５の緩み側５．に配設されるテンション
プーリ８は、オートアジャスタＡにより伝動ベルト５に
圧接され、該伝動ベルト５の緩み側５Ｉの張力変動に応
動して自動的に作動し、該伝動ベルト５に一定の張力を
付与する。Loose side of the transmission belt 55. A tension pulley 8 disposed on the transmission belt 5 is pressed against the transmission belt 5 by an auto adjuster A, and automatically operates in response to tension fluctuations on the slack side 5I of the transmission belt 5, thereby maintaining a constant tension on the transmission belt 5. Grant.

而してテンションプーリ８を支承した揺動レバー９は、
伝動ベルト５の緩み側５．の張力変動や振動に追従する
ように支軸１２回りに上下に揺動を繰り返すがその場合
に揺動レバー９は合成樹脂製第１．第２スペーサＳｒ、
Ｓｔを介して機関本体Ｅの端面１３に接触するので、揺
動レバー９の揺動抵抗が低減されて、その円滑、軽快な
揺動が可能となる。また第２、第３スペーサＳｚ、Ｓｓ
の協働によりテンションプーリ８は揺動レバー９ととも
にその軸方向の遊動が規制される。Therefore, the swing lever 9 supporting the tension pulley 8 is
Loose side of transmission belt 55. The swing lever 9 repeatedly swings up and down around the support shaft 12 to follow the tension fluctuations and vibrations of the synthetic resin first. second spacer Sr,
Since it comes into contact with the end surface 13 of the engine body E via St, the swinging resistance of the swinging lever 9 is reduced, and smooth and light swinging thereof becomes possible. Also, the second and third spacers Sz, Ss
Through the cooperation of the tension pulley 8 and the swing lever 9, the axial movement of the tension pulley 8 is restricted.

次に前記オートアジャスタＡの作用についてさらに詳細
に説明する。Next, the function of the auto-adjuster A will be explained in more detail.

プランジャケース２１内の高圧油室３１、および補給油
室３２には、機関の潤滑油と同じ油が予め注入される。The same oil as the lubricating oil of the engine is injected into the high-pressure oil chamber 31 and the supply oil chamber 32 in the plunger case 21 in advance.

またクランク軸１に連結される機関の潤滑用油圧ポンプ
Ｐからの加圧油の一部は吐出口４１、給油通路４０、給
油孔３８および油孔３９を通って補給油室３２内に常時
強制給油され、該補給油室３２は油によって満たされて
いる。また補給油室３２内の油は、該室３２内に封入さ
れた噛込みエアとともにリーク通路５６を通ってエア抜
道路５１を通りそこから排油孔４９、排油通路５０を通
って機関本体Ｅ下部の油溜４８内に還流される。この場
合補給通路３２内の油に噛み込まれたエアはその上部の
リーク孔５６を通り容易にエア抜道路５１から排油孔４
９へと排出される。Also, a part of the pressurized oil from the hydraulic pump P for lubricating the engine connected to the crankshaft 1 is constantly forced into the replenishment oil chamber 32 through the discharge port 41, the oil supply passage 40, the oil supply hole 38, and the oil hole 39. The replenishment oil chamber 32 is filled with oil. In addition, the oil in the replenishment oil chamber 32 passes through the leak passage 56 and the air bleed road 51 together with the trapped air sealed in the chamber 32, and then passes through the oil drain hole 49 and the oil drain passage 50 to the engine body. It is refluxed into the oil sump 48 at the bottom of E. In this case, the air trapped in the oil in the supply passage 32 passes through the leak hole 56 at the upper part of the supply passage 32 and easily flows from the air vent road 51 to the oil drain hole 4.
It is discharged to 9.

そして油圧ポンプＰ１オートアジャスタＡ　、ｑ’　ｄ
−ｖ“油溜４８間を流れる油は機関本体Ｅ外に漏洩する
ことがない。and hydraulic pump P1 auto adjuster A, q' d
-v"The oil flowing between the oil sump 48 does not leak outside the engine body E.

給油通路４０内の油圧が所定値を超えると、前記レギュ
レタＲのピストン４６がばね４７の弾発力に抗して後退
し、油溜連通孔４４が給油通路４０に連通して該通路４
０内の加圧油を油溜４８に戻す。When the oil pressure in the oil supply passage 40 exceeds a predetermined value, the piston 46 of the regulator R retreats against the elastic force of the spring 47, the oil sump communication hole 44 communicates with the oil supply passage 40, and the passage 4
The pressurized oil in 0 is returned to the oil reservoir 48.

オートアジャスタＡ内において、高圧油室３１内の緊張
ばね３４は、その弾発力でプランジャ２３を上方に押上
げ、スリッパ部材２７、および調節ねじ３０を介して揺
動レバー９を第１図において反時計方向に揺動する。こ
れによりテンションプーリ８は、伝動ベルト５の緩み側
５．を内方に押圧し、伝動ベルト５に一定の張力を付与
する。In the auto adjuster A, the tension spring 34 in the high pressure oil chamber 31 pushes up the plunger 23 with its elastic force, and moves the swing lever 9 via the slipper member 27 and the adjustment screw 30 as shown in FIG. Swings counterclockwise. As a result, the tension pulley 8 is applied to the slack side 5. of the transmission belt 5. is pressed inward to apply a constant tension to the transmission belt 5.

また前記引張ばね１４の弾発力も揺動レバー９を第１図
において反時計方向に揺動するように付勢するので、伝
動ベルト５への張力付与を助成する。The elastic force of the tension spring 14 also urges the swinging lever 9 to swing counterclockwise in FIG. 1, thereby assisting in applying tension to the transmission belt 5.

伝動ベルト５の伸び等に追従してプランジャ２３が上昇
すれば、高圧油室３１が減圧するので、補給油室３２と
の圧力差によりチェック弁■の球状弁体３５は、弁口３
３を開き、補給油室３２内の油は弁口３３を通って高圧
油室３１に補給される。When the plunger 23 rises following the elongation of the transmission belt 5, the pressure in the high-pressure oil chamber 31 is reduced, and the spherical valve body 35 of the check valve 2
3 is opened, and the oil in the replenishment oil chamber 32 is supplied to the high pressure oil chamber 31 through the valve port 33.

調時巻掛伝動装置Ｔの作動中、クランク軸１、動弁カム
軸２等に作用するトルク変動により伝動ベルト５の緩み
側５１に引張力が作用すると、この引張力はテンション
プーリ８を押し戻すように働き、さらに揺動レバー９を
介してプランジャ２３を押し下げるように働く。これに
より高圧油室３１の油圧が上昇してチェック弁■の球状
弁体３５が弁口３３を閉じるので、補給油室３２への油
の逆流を阻止することができ、結局高圧油室３１内の油
圧が、伝動ベルト５の緩み側５．の引張力に対抗するこ
とによりテンションブー９８の後退を抑制する。During the operation of the timing winding transmission T, when a tensile force is applied to the loose side 51 of the transmission belt 5 due to torque fluctuations acting on the crankshaft 1, valve drive camshaft 2, etc., this tensile force pushes back the tension pulley 8. It also works to push down the plunger 23 via the swing lever 9. As a result, the oil pressure in the high-pressure oil chamber 31 increases and the spherical valve body 35 of the check valve ■ closes the valve port 33, which prevents oil from flowing back into the replenishment oil chamber 32, and eventually inside the high-pressure oil chamber 31. The hydraulic pressure of 5. on the loose side of the transmission belt 5. By resisting the tensile force of the tension boob 98, the tension boob 98 is prevented from retreating.

伝動ベルト５の緩み側５．から引張力が解除されると、
緊張ばね３４の弾発作用によりプランジャ２３は再度上
昇し、揺動レバー９を介してテンションプーリ８が伝動
ベルト５の緩み側５．を押圧し、伝動ベルト５に再び一
定の張力を付与し、伝動ベルト５に伸びがあればこれを
補償することができる。そしてプランジャ２３の上昇に
より減圧する高圧油室３１内には前述のように補給油室
３２内の油が補給される。Loose side of transmission belt 55. When the tensile force is released from
The plunger 23 rises again due to the elastic force of the tension spring 34, and the tension pulley 8 is moved to the slack side 5. of the transmission belt 5 via the swing lever 9. is pressed to apply a constant tension to the transmission belt 5 again, and if there is any elongation in the transmission belt 5, this can be compensated for. The high-pressure oil chamber 31, which is depressurized by the rise of the plunger 23, is replenished with the oil in the replenishment oil chamber 32 as described above.

前記作動において、補給油室３２内には前述のように油
圧ポンプＰからの加圧油が常時供給されるので、補給油
室３２の油に多少の漏洩があってもこれを直ちに補償す
ることができ、また補給油室３２内へは絶えず油が補給
されることにより、該室３２内への噛込みエアの排出も
容易になり、全体として伝動ベルトの緊張度の自動調節
がより適確に行われる。During the above operation, pressurized oil from the hydraulic pump P is constantly supplied into the replenishment oil chamber 32 as described above, so even if there is some leakage of oil in the replenishment oil chamber 32, this can be compensated for immediately. In addition, by constantly replenishing oil into the replenishment oil chamber 32, it becomes easier to discharge trapped air into the chamber 32, and as a whole, the automatic adjustment of the tension of the transmission belt becomes more accurate. It will be held on.

而して上記実施例において駆動プーリ３、被動プーリ４
、伝動ベルト５および第１〜第３スペーサ５Ｉ−８３は
本発明における駆動輪、被動輪、伝動帯およびスペーサ
を構成する。In the above embodiment, the driving pulley 3 and the driven pulley 4
, the transmission belt 5, and the first to third spacers 5I-83 constitute a driving wheel, a driven wheel, a transmission band, and a spacer in the present invention.

尚、上記実施例では本発明をベルト弐巻掛伝動装置に実
施した場合を説明したが、これをチェン式その他の巻掛
伝動装置にも実施できることは勿論である。In the above embodiments, the present invention is applied to a two-belt transmission, but it goes without saying that the present invention can also be applied to a chain-type or other belt-wrapped transmission.

Ｃ３発明の効果 以上の実施例により明らかなように本発明によれば、機
関本体に支持される、駆動輪と被動輪間に無端状伝動帯
を懸回し、該伝動帯の緩み側にテンションブーりを圧接
して該伝動帯に所定の張力を付与するようにした内燃機
関における巻掛伝動装置のテンショナ装置において、前
記機関本体には前記テンションブ・−リを回転自在に支
承する揺動レバーを揺動自在に軸支するとともに該揺動
レバーの揺動を案内するための案内軸を固着し、前記機
関本体および案内軸を含む固定部と前記テンションプー
リおよび揺動レバーを含む可動部との接触部間に、それ
らの直接接触を避けるためのスペーサを介装されるので
、テンションプーリおよび揺動レバーを含む可動部は機
関本体および案内軸を含む固定部に対してスペーサを介
して揺動され、機関本体との直接接触が避けられ揺動レ
バーの揺動抵抗が低減され、しかもテンションプーリと
揺動レバーは伝動帯からの振動をうけてもその軸方向の
遊動が防止され、その結果テンションプーリを支承した
揺動レバーの常に軽快、円滑な揺動が可能となり、巻掛
伝動装置の伝動効率を高めることができる。C3 Effects of the Invention As is clear from the above embodiments, according to the present invention, an endless transmission band is suspended between the driving wheel and the driven wheel supported by the engine body, and a tension boot is provided on the loose side of the transmission band. In a tensioner device for a wrap transmission in an internal combustion engine, the tensioner device is configured to apply a predetermined tension to the transmission band by press-contacting the transmission band. A fixed part including the engine main body and the guide shaft, a movable part including the tension pulley and the swing lever, and a guide shaft for guiding the swing of the swing lever are fixedly supported. A spacer is interposed between the contact parts to avoid direct contact between them, so the movable parts including the tension pulley and the swing lever can swing against the fixed parts including the engine body and the guide shaft via the spacer. This reduces the swinging resistance of the swinging lever by avoiding direct contact with the engine body, and also prevents the tension pulley and swinging lever from axially shifting even if they receive vibrations from the transmission band. As a result, the swinging lever supporting the tension pulley can always swing easily and smoothly, and the transmission efficiency of the wrap-around transmission can be improved.

【図面の簡単な説明】[Brief explanation of the drawing]

図面は本発明の一実施例を示すもので、第１図は本発明
装置を備えた、内燃機関の調時巻掛伝動装置の正面図、
第２図は第１図の■線矢視側面図、第３図は第１図１１
１−Ｉ［［線に沿う拡大断面図、第４図は、第３図ＩＶ
−ＩＶ線断面図、第５図は、第２図■−■線に沿うポン
プケースの裏面図、第６図は、第２図Ｖｌ−Ｖｌ線に沿
う拡大断面図、第７図は第６図■−■線に沿うアジャス
タケースの断面図である。 Ｅ・・・機関本体、Ｓｌ・・・スペーサとしての第１ス
ペーサ、Ｓ２・・・スペーサとしての第２スペーサＳ、
・・・スペーサとしての第３スペーサ３・・・駆動輪、
４・・・被動輪、５Ｉ・・・伝動帯、８・・・テンショ
ンプーリ、９・・・揺動レバー、１５・・・案内特　許
　出　願　人　本田技研工業株式会社第６図 し、−一The drawings show one embodiment of the present invention, and FIG. 1 is a front view of a timing winding transmission device for an internal combustion engine equipped with the device of the present invention;
Figure 2 is a side view taken along the line ■ in Figure 1, Figure 3 is Figure 111.
1-I[[An enlarged sectional view along the line, FIG.
5 is a back view of the pump case taken along line ■-■ in FIG. 2, FIG. 6 is an enlarged sectional view taken along line Vl-Vl in FIG. FIG. 3 is a cross-sectional view of the adjuster case taken along the line shown in FIG. E...engine body, Sl...first spacer as a spacer, S2...second spacer S as a spacer,
...Third spacer 3 as a spacer...Drive wheel,
4... Driven wheel, 5I... Transmission band, 8... Tension pulley, 9... Rocking lever, 15... Guide patent applicant Honda Motor Co., Ltd. Figure 6 - one

Claims (1)

【特許請求の範囲】[Claims] 機関本体に支持される、駆動輪と被動輪間に無端状伝動
帯を懸回し、該伝動帯の緩み側にテンションプーリを圧
接して該伝動帯に所定の張力を付与するようにした内燃
機関における巻掛伝動装置のテンショナ装置において、
前記機関本体には前記テンションプーリを回転自在に支
承する揺動レバーを揺動自在に軸支するとともに該揺動
レバーの揺動を案内するための案内軸を固着し、前記機
関本体および案内軸を含む固定部と前記テンションプー
リおよび揺動レバーを含む可動部との接触部間に、それ
らの直接接触を避けるためのスペーサを介装したことを
特徴とする内燃機関における巻掛伝動装置のテンショナ
装置。An internal combustion engine that is supported by an engine body and has an endless transmission band suspended between a driving wheel and a driven wheel, and a tension pulley is pressed against the loose side of the transmission band to apply a predetermined tension to the transmission band. In a tensioner device for a wrap-around transmission,
A rocking lever that rotatably supports the tension pulley is rotatably supported on the engine body, and a guide shaft for guiding the rocking of the rocking lever is fixed to the engine body, and the engine body and the guide shaft are fixed to the engine body. A tensioner for a wrap transmission in an internal combustion engine, characterized in that a spacer is interposed between the fixed part including the tension pulley and the movable part including the tension pulley and the swing lever to avoid direct contact therebetween. Device.
JP5806285A 1985-03-19 1985-03-22 Tensioner device in wrapping transmission for internal-combustion engine Pending JPS61218857A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
JP5806285A JPS61218857A (en) 1985-03-22 1985-03-22 Tensioner device in wrapping transmission for internal-combustion engine
CA000504399A CA1254770A (en) 1985-03-19 1986-03-18 Tensioner device in wrapping connector driving device for internal combustion engine
US06/840,831 US4761155A (en) 1985-03-19 1986-03-18 Tensioner for wrapping connector transmission device for internal combustion engine
GB8606724A GB2175064B (en) 1985-03-19 1986-03-19 Tensioner device in wrapping connector driving device for internal combustion engine
DE19863609232 DE3609232A1 (en) 1985-03-19 1986-03-19 TENSIONING DEVICE IN A STRAP CONNECTING DRIVE DEVICE FOR AN INTERNAL COMBUSTION ENGINE
GB8823825A GB2208906B (en) 1985-03-19 1988-10-11 Tensioner device in wrapping connector driving device for internal combustion engine
GB8823824A GB2208905B (en) 1985-03-19 1988-10-11 Tensioner device in wrapping connector driving device for internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP5806285A JPS61218857A (en) 1985-03-22 1985-03-22 Tensioner device in wrapping transmission for internal-combustion engine

Publications (1)

Publication Number Publication Date
JPS61218857A true JPS61218857A (en) 1986-09-29

Family

ID=13073421

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5806285A Pending JPS61218857A (en) 1985-03-19 1985-03-22 Tensioner device in wrapping transmission for internal-combustion engine

Country Status (1)

Country Link
JP (1) JPS61218857A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021008830A (en) * 2019-06-28 2021-01-28 三菱自動車工業株式会社 Engine oil supply device

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS587162U (en) * 1981-07-06 1983-01-18 宇都木　貞 Experiment bench with aspirator

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS587162U (en) * 1981-07-06 1983-01-18 宇都木　貞 Experiment bench with aspirator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021008830A (en) * 2019-06-28 2021-01-28 三菱自動車工業株式会社 Engine oil supply device

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