JPS6343618B2 - - Google Patents

Info

Publication number
JPS6343618B2
JPS6343618B2 JP60054779A JP5477985A JPS6343618B2 JP S6343618 B2 JPS6343618 B2 JP S6343618B2 JP 60054779 A JP60054779 A JP 60054779A JP 5477985 A JP5477985 A JP 5477985A JP S6343618 B2 JPS6343618 B2 JP S6343618B2
Authority
JP
Japan
Prior art keywords
oil
adjuster
auto
transmission band
transmission
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.)
Expired
Application number
JP60054779A
Other languages
Japanese (ja)
Other versions
JPS61215849A (en
Inventor
Hidekazu Ichihara
Michio Sato
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 JP5477985A priority Critical patent/JPS61215849A/en
Priority to US06/840,831 priority patent/US4761155A/en
Priority to CA000504399A priority patent/CA1254770A/en
Priority to GB8606724A priority patent/GB2175064B/en
Priority to DE19863609232 priority patent/DE3609232A1/en
Publication of JPS61215849A publication Critical patent/JPS61215849A/en
Publication of JPS6343618B2 publication Critical patent/JPS6343618B2/ja
Priority to GB8823824A priority patent/GB2208905B/en
Priority to GB8823825A priority patent/GB2208906B/en
Granted legal-status Critical Current

Links

Classifications

    • 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
    • F16H7/0848—Means for varying tension of belts, ropes, or chains 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
    • F16H7/10—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
    • 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
    • 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
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0859—Check valves
    • 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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Description

【発明の詳細な説明】 Ａ 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ヨナ装置に関するものであ
る。Detailed Description of the Invention A. Purpose of the Invention (1) Industrial Field of Application The present invention provides 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 that applies a constant tension to the vehicle.

(2) 従来の技術 従来内燃機関において、駆動輪と被動輪間に無
端状伝動帯を懸回し、該伝動帯に圧接されるテン
シヨナに給油式オートアジヤスタを連結し、この
アジヤスタよりテンシヨナを介して該伝動帯に常
に一定の張力を付与するようにしたものは公知で
ある（特開昭59−208250号公報参照）。(2) Prior art In a conventional internal combustion engine, an endless transmission band is suspended between a driving wheel and a driven wheel, an oil-supplied auto-adjuster is connected to a tensioner that is pressed into contact with the transmission band, and the adjustment is carried out from this adjuster via the tensioner. A device in which a constant tension is always applied to the transmission band is known (see Japanese Patent Laid-Open No. 59-208250).

(3) 発明が解決しようとする問題点 ところで従来のテンシヨナ装置において、機関
運転中は給油式オートアジヤスタに絶えず圧力油
が強制給油されてその作動を確実なものとするこ
とができるが、機関の停止時には前記オートアジ
ヤスタへの給油が停止され油圧下降を生じるの
で、機関の再始動時にオートアジヤスタの作動が
時間的に遅れて伝動帯に一時的な緩みを生じ、伝
動帯と駆動輪との噛合歯に飛び越しを生起するこ
とがあるという問題があり、またかかる問題を回
避するためにオートアジヤスタの調整代を大きく
とろうとすればオートアジヤスタが大型化してコ
スト高を招くという問題もある。(3) Problems to be solved by the invention In the conventional tensioner device, pressure oil is continuously supplied to the oil-filled auto-adjuster during engine operation to ensure its operation. When the engine is stopped, the oil supply to the auto adjuster is stopped and the oil pressure drops, so when the engine is restarted, the auto adjuster's operation is delayed, causing temporary loosening of the transmission band, and the transmission band and drive wheel are There is a problem in that skipping may occur in the teeth meshing with the automatic adjuster, and if you try to increase the adjustment allowance for the auto adjuster to avoid this problem, the auto adjuster will become larger and the cost will increase. There is also.

本発明は上記問題を解決し得るコンパクトな前
記テンシヨナ装置を提供することを目的とする。 An object of the present invention is to provide a compact tensioner device that can solve the above problems.

Ｂ 発明の構成 (1) 問題点を解決するための手段 上記目的を達成するために本発明は、機関本体
に支承される駆動輪と被動輪間に無端状伝動帯を
懸回し、この伝動帯には、それの緩み側に配設さ
れるテンシヨナを介して給油式オートアジヤスタ
により張力を付与するようにした、内燃機関の巻
掛伝動装置におけるテンシヨナ装置において、機
関本体には前記テンシヨナを支承した揺動レバー
を揺動可能に軸支し、その揺動レバーにはその自
由端部に前記給油式オートアジヤスタを、またそ
の中間部に、該給油式オートアジヤスタと協働し
て前記テンシヨナを伝動帯に向けて偏倚する補助
ばねをそれぞれ連結するとともに、該オートアジ
ヤスタおよび補助ばねを前記揺動レバーを挟んで
その両側に配設したことを特徴とする。B. Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention involves suspending an endless transmission band between a driving wheel and a driven wheel supported by an engine body. In this tensioner device in a wrap transmission for an internal combustion engine, tension is applied by an oil-supplied auto-adjuster via a tensioner disposed on the slack side of the tensioner, and the tensioner is supported on the engine body. A swinging lever is pivotally supported for swinging, and the swinging lever has the above-mentioned oil-filled auto-adjuster at its free end, and has the above-mentioned oil-filled auto-adjuster at its intermediate part in cooperation with the oil-filled auto-adjuster. Auxiliary springs for biasing the tensioner toward the transmission band are connected to each other, and the auto adjuster and the auxiliary springs are disposed on both sides of the swing lever.

(2) 作 用 上記構成によれば、内燃機関の運転停止時にも
テンシヨナには補助ばねにより一定の張力が付与
されることにより強制給油式オートアジヤスタの
作動遅れによつても伝動帯には緩みを生じること
なく、しかも伝動帯の調整代を大きくとることが
できる。(2) Effect According to the above configuration, even when the internal combustion engine is stopped, a constant tension is applied to the tensioner by the auxiliary spring. It is possible to have a large adjustment allowance for the transmission band without causing loosening.

(3) 実施例 以下、第１〜６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第１実施
例について説明する。(3) Example Hereinafter, as shown in Figs. 1 to 6, the device of the present invention was
A first embodiment in which the present invention is applied to a four-stroke internal combustion engine will be described.

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、クラン
ク軸１に固着される駆動プーリ３と、一対の動弁
カム軸２にそれぞれ固着される被動プーリ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によつて機関本体Ｅの
冷却用水ポンプ７が駆動される。 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 operating camshafts 2 of a valve operating mechanism. This timing winding transmission device T has an endless transmission belt 5 suspended between a driving pulley 3 fixed to a crankshaft 1 and driven pulleys 4 fixed to a pair of valve drive camshafts 2, respectively. configured.
Another driven pulley 6 is suspended in the middle of the transmission belt 5, and a cooling water pump 7 of the engine body E is driven by this driven pulley 6.

駆動プーリ３と、水ポンプ７の駆動用被動プー
リ間において、前記クランク軸１の略真上にはテ
ンシヨンプーリ８が配設され、このテンシヨンプ
ーリ８は揺動レバー９の中間部に突設したプーリ
軸部９1にボール軸受１１を介して回転自在に支
承される。 A tension pulley 8 is disposed approximately directly above the crankshaft 1 between the drive pulley 3 and the driven pulley for driving the water pump 7, and this tension pulley 8 projects from the middle of the swing lever 9. It is rotatably supported via a ball bearing 11 on a pulley shaft portion 9 1 provided therein.

前記揺動レバー９は第３図に明瞭に示すように
その基端が支軸１２をもつて機関本体Ｅの端壁１
３に上下に揺動自在に軸支される。揺動レバー９
のプーリ軸部９1の端部には前記支軸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の端壁１３に固着した案内軸１５に遊
合されており、この円弧孔１０と案内軸１５とが
相互に係合して揺動レバー９の揺動角が規制され
る。 As clearly shown in FIG.
3, it is pivoted so that it can swing up and down. Swing lever 9
An arcuate hole 10 centered on the support shaft 12 is bored at the end of the pulley shaft portion 91 , and this arcuate hole 10 is loosely engaged with a guide shaft 15 fixed to an end wall 13 of the engine body E. The arcuate hole 10 and the guide shaft 15 engage with each other to regulate the swing angle of the swing lever 9.

前記揺動レバー９の自由端部には、後に詳述す
る強制給油式オートアジヤスタＡが連結され、こ
のアジヤスタＡの押圧力は揺動レバー９を介して
テンシヨンプーリ８を伝動帯５の緩み側５1に圧
接し、また該揺動レバー９の中間部には、基端を
機関本体Ｅに支持１４1した引張ばねよりなる補
助ばね１４の他端が連結されており、この補助ば
ね１４の弾発力は揺動レバー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ヨンプ
ーリ８を補助的に伝動ベルト５の緩み側５1外面
に圧接する。 A forced lubrication type auto adjuster A, which will be described in detail later, is connected to the free end of the swing lever 9, and the pressing force of the adjuster A is applied to the tension pulley 8 via the swing lever 9 to the transmission band 5. The other end of an auxiliary spring 14 is connected to the intermediate portion of the swinging lever 9 , which is in pressure contact with the slack side 51 , and is made of a tension spring whose base end is supported on the engine body E. The elastic force 14 biases the swinging lever 9 to swing counterclockwise around the support shaft 12, and presses the tension pulley 8 auxiliary against the outer surface of the loose side 51 of the transmission belt 5.

機関本体Ｅの端壁１３には、該本体Ｅの各被潤
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１に直結されて駆動される。そして機
関本体Ｅ内の貯留油を吸込通路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 for forcibly supplying lubricating oil etc. to each lubricated part of the main body E is fixed to the end wall 13 of the engine main body E, and this hydraulic pump P
It is directly connected to the crankshaft 1 and driven. Then, the oil stored in the engine body E is sucked up from the suction passage Pi (Fig. 4) and discharged to the 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ヤスタＡのアジヤスタ
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-supplied auto-adjuster A is integrally cast.

次にこの給油式オートアジヤスタＡの構造を主
に第５，６図を参照して説明すると、前記オート
アジヤスタＡのアジヤスタケース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
ヤスタケース１７には、開放上端１８を有する中
空円筒状のハウジング１９が形成される。このハ
ウジング１９内には同じく開放上端２０を有する
中空円筒状のプランジヤケース２１が嵌着され、
このプランジヤケース２１の上部外周とハウジン
グ１９の内周面間にＯリング２２が介装される。 Next, the structure of this oil-supplied auto-adjuster A will be explained mainly with reference to FIGS. 5 and 6. The adjuster case 17 of the auto-adjuster A is integrally formed on the upper outer surface of the pump case 16. . A hollow cylindrical housing 19 having an open upper end 18 is formed in the adjuster case 17 . A hollow cylindrical plunger case 21 having an open upper end 20 is fitted into the housing 19.
An O-ring 22 is interposed between the upper outer circumference of the plunger case 21 and the inner circumference of the housing 19.

前記プランジヤケース２１内には、上部を先細
り状に形成したプランジヤ２３が昇降可能に摺合
され、このプランジヤ２３の解放上端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にはスリツパ部材２７がＯリン
グ２９を介して嵌入され、このスリツパ部材２７
の頂面にスリツパ面２８が形成され、このスリツ
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。
前記プランジヤ２３はプランジヤケース２１内の
下部に高圧油室３１を、またその上部に補給油室
３２を画成する。 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.
A slipper surface 28 is formed on the top surface of the swing lever 9, and the lower end of an adjusting screw 30 that is adjustably screwed onto the tip of the swing lever 9 is brought into contact with this slipper surface 28.
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 upper part thereof.

前記プランジヤ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を開閉するチエツク
弁Ｖと、前記プランジヤ２３の上方へ弾発する緊
張ばね３４とが収容されており、前記チエツク弁
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を収容するバルブケージ３６
と、この弁体３５を閉弁方向に付勢する弁ばね３
７とより構成される。 A valve port 33 is provided on the bottom wall 23d of the plunger 23.
is opened, and the high pressure oil chamber 31 and the replenishment oil chamber 32 are communicated through the valve port 33. A check valve V that opens and closes the valve port 33 and a tension spring 34 that springs upward of the plunger 23 are housed in the high pressure oil chamber 31. The check valve V is mounted on the valve seat of the valve port 33. Seated spherical valve body 35
and a valve cage 36 that accommodates this valve body 35.
and a valve spring 3 that urges this valve body 35 in the valve closing direction.
It consists of 7.

前記Ｏリング２２よりも下方において、プラン
ジヤケース２１の側壁２１ｓ、およびプランジヤ
２３の側壁２３ｓには、相互に常時連通する給油
孔３８、および油口３９が貫通して設けられ、前
記給油孔３８は、アジヤスタケース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 23s of the plunger 23 are provided with an oil supply hole 38 and an oil port 39 penetrating through the side wall 21s of the plunger case 21 and the side wall 23s of the plunger 23. , communicates with an oil supply passage 40 bored in the adjuster case 17, and also communicates with the oil hole 39.
is communicated with the replenishment oil 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。したがつて機関の運転にとも
なつてクランク軸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を通つて補給油室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, the pressurized oil is constantly supplied to the discharge port 41, the oil supply passage 40, the oil supply hole 38, and the oil hole. The oil is forcibly supplied to the replenishment oil chamber 32 through 39.

第６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によつて閉
じられる。下流側給油路４０ｄ内には、調圧用レ
ギユレタＲが内蔵される。このレギユレタＲは、
下流側通路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４７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に戻すようになつている。 As clearly shown in FIG.
consists of a downstream passage 40d on the side of the replenishment oil 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 closed by a stopper 42. A pressure regulating regulator R is built in the downstream oil supply path 40d. This Regulator R is
It consists of a piston 46 that is slidably fitted into the downstream passage 40d and opens and closes the oil sump communication hole 44, and a spring 47 that biases the piston 46 toward the closing side.
When the oil pressure in the oil supply passage 40 rises above a predetermined value, the piston 46 resists the elastic force of the spring 47.
is slid in the opening direction, the oil sump communication hole 44 is communicated with the oil supply passage 40, and the pressurized oil in the oil supply passage 40 is returned to the oil sump 48 at the lower part of the engine body E.

プランジヤ２３の先細り状上部の外周とプラン
ジヤケース２１との間には環状のエア抜通路５１
が形成され、このエア抜通路５１は、プランジヤ
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Ｏリング２２と給油
孔３８間において、プランジヤケース２１の側壁
２１ｓには、前記エア抜通路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
ヤケース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 vent passage 51 is provided between the outer periphery of the tapered upper part of the plunger 23 and the plunger case 21.
The air vent passage 51 is connected to the replenishment oil chamber 32 through a leak passage 56 formed between the open upper end 24 of the plunger 23 and the fitting surface of the plug 25.
is communicated with. Further, between the O-ring 22 and the oil supply hole 38, an oil drain hole 49 that opens to the air vent passage 51 is bored in the side wall 21s of the plunger case 21, and this oil drain hole 49 is bored in the plunger case 17. It communicates with an oil reservoir 48 in the engine body E through an oil drain passage 50 provided therein.

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を通つてエア抜通路５１に流れ、
さらに該通路５１から前記排油孔４９、および排
油通路５０を通つて機関本体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 passage 51,
Further, the oil is returned from the passage 51 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５図に示すようにハウジング１９の底
部には油室５７の下部とオイルポンプＰの吐出口
４１とを連通するエア抜通路５２が穿設され、こ
のエア抜通路５２はハウジング１９内にプランジ
ヤケース２１を組込む際の油室５７内に封入され
るエアを抜くためのものである。 Further, as shown in FIG. 5, an air vent passage 52 is formed in the bottom of the housing 19 to communicate the lower part of the oil chamber 57 and the discharge port 41 of the oil pump P. This is for removing air sealed in the oil chamber 57 when the plunger case 21 is assembled.

プランジヤケース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５４によつて油密に纒着され、ま
た該ブーツ５３の上端部は、反転されて締付リン
グ５５によつて前記プラグ２５の外周に油密に纒
着される。そしてこのブーツ５３はプランジヤ２
３の昇降に追従するように伸縮し、プランジヤケ
ース２１とプラグ２５間を油密に封緘する。 The lower end of a boot 53 made of rubber, synthetic resin, etc. is oil-tightly attached to the upper outer peripheral surface of the plunger case 21 by a tightening ring 54, and the upper end of the boot 53 is inverted. The tightening ring 55 is secured to the outer periphery of the plug 25 in an oil-tight manner. And this boot 53 is plunger 2
It expands and contracts to follow the elevation of the plunger case 21 and the plug 25, thereby sealing the space between the plunger case 21 and the plug 25 in an oil-tight manner.

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５1に配設されるテ
ンシヨンプーリ８は、オートアジヤスタ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５1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。また前記
補助ばね１４はその弾発力によりテンシヨンプー
リ８を伝動帯５の緩み側５1に補助的に圧接する。 The tension pulley 8 disposed on the slack side 5 1 of the transmission belt 5 is pressed against the transmission belt 5 by an auto adjuster A, and is automatically adjusted in response to tension fluctuations on the slack side 5 1 of the transmission belt 5. The transmission belt 5 is operated to apply a constant tension to the transmission belt 5. Further, the auxiliary spring 14 additionally presses the tension pulley 8 against the loose side 5 1 of the transmission band 5 by its elastic force.

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

プランジヤケース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。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を通つて補給油室３２内に常時強制給油さ
れ、該補給油室３２は油によつて満たされてい
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
つてエア抜通路５１を通りそこから排油孔４９、
排油通路５０を通つて機関本体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
り容易にエア抜通路５１から排油孔４９へと排出
される。そして油圧ポンプＰ、オートアジヤスタ
Ａおよび油溜４８間を流れる油は機関本体Ｅ外に
漏洩することがない。 The same oil as the lubricating oil of the engine is injected into the high-pressure oil chamber 31 and the replenishment oil chamber 32 in the plunger case 21 in advance. 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. Further, the oil in the replenishment oil chamber 32 passes through the leak passage 56 and the air vent passage 51 together with the trapped air sealed in the chamber 32, and from there the oil drain hole 49,
The oil sump 48 at the bottom of the engine body E passes through the oil drain passage 50.
It is refluxed into the interior. In this case, the air trapped in the oil in the supply passage 32 passes through the leak hole 56 in the upper part and is easily discharged from the air vent passage 51 to the oil drain hole 49. The oil flowing between the hydraulic pump P, the auto adjuster A, and the oil reservoir 48 does not leak outside the engine body E.

給油通路路４０内の油圧が所定値を超えると、
前記レギユレタ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４０内の加圧油を油溜４８
に戻す。 When the oil pressure in the oil supply passageway 40 exceeds a predetermined value,
The piston 46 of the regulator R retreats against the elastic force of the spring 47, and the oil sump communication hole 44 communicates with the oil supply passage 40 to transfer the pressurized oil in the passage 40 to the oil sump 48.
Return to

オートアジヤスタ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ヤ２
３を上方に押上げ、スリツパ部材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。これによりテンシヨン
プーリ８は、伝動ベルト５の緩み側５1を内方に
押圧し、伝動ベルト５に一定の張力を付与する。
また前記補助ばね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への張力付与を助勢す
る。 In the auto adjuster A, the high pressure oil chamber 31
The inner tension spring 34 pushes the plunger 2 with its elastic force.
3 upward, and swing the swing lever 9 counterclockwise in FIG. 1 via the slipper member 27 and the adjustment screw 30. As a result, the tension pulley 8 presses the loose side 51 of the transmission belt 5 inward and applies a constant tension to the transmission belt 5.
The elastic force of the auxiliary 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ヤ２
３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エツク弁Ｖの球
状弁体３５は、弁口３３を開き、補給油室３２内
の油は弁口３３を通つて高圧油室３１に補給され
る。 The plunger 2 follows the elongation of the transmission belt 5, etc.
3 rises, the pressure in the high pressure oil chamber 31 decreases, so
Due to the pressure difference with the replenishment oil chamber 32, the spherical valve body 35 of the check valve V opens the valve port 33, 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
の引張力はテンシヨンプーリ８を押し戻すように
働き、さらに揺動レバー９を介してプランジヤ２
３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エツク弁Ｖの球状弁体３
５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５1の引張力
に対抗することによりテンシヨンプーリ８の後退
を抑制する。 During the operation of the timing winding transmission T, the crankshaft 1,
When a tensile force is applied to the loose side 51 of the transmission belt 5 due to torque fluctuations acting on the valve camshaft 2, etc., this tensile force acts to push back the tension pulley 8, and further pushes the plunger through the swing lever 9. 2
It works to push down 3. As a result, the oil pressure in the high pressure oil chamber 31 increases and the spherical valve body 3 of the check valve V
5 closes the valve port 33, it is possible to prevent oil from flowing back into the replenishment oil chamber 32, and eventually the high pressure oil chamber 31
The hydraulic pressure inside suppresses the retreat of the tension pulley 8 by counteracting the tensile force on the loose side 51 of the transmission belt 5.

伝動ベルト５の緩み側５1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
ヤ２３は再度上昇し、揺動レバー９を介してテン
シヨンプーリ８が伝動ベルト５の緩み側５1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。そしてプランジヤ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。 When the tensile force is released from the loose side 51 of the transmission belt 5, the plunger 23 rises again due to the elastic force of the tension spring 34, and the tension pulley 8 moves via the swing lever 9 to the slack side of the transmission belt 5. 5 Press 1 to apply a certain tension to the transmission belt 5 again,
If the transmission belt 5 has elongation, this can be compensated for. The oil in the replenishment oil chamber 32 is replenished as described above into the high pressure oil chamber 31, which is depressurized by the rise of the plunger 23.

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つて
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. By constantly replenishing oil into the replenishing oil chamber 32,
It is also easier to discharge trapped air into the chamber 32,
Overall, the tension of the transmission belt can be automatically adjusted more accurately.

而して機関の運転中、すなわち油圧ポンプＰの
作動中はオートアジヤスタＡは該油圧ポンプＰか
らの圧油をうけて前述のように作動するので、テ
ンシヨンプーリ８にはオートアジヤスタＡの押圧
力と前記補助ばね１４の弾発力が共に作用して伝
動帯５に所定の張力を付与しているが、機関の運
転が停止されると油圧ポンプＰの作動も停止する
のでオートアジヤスタＡへの圧油の供給も停止さ
れ、機関の再始動時にオートアジヤスタＡへの給
油が遅れて該アジヤスタＡが一時的な作動遅れを
生じることがある。ここでもし前記補助ばね１４
の弾発力が伝動帯５に作用していないと仮定すれ
ば、該伝動帯５に緩みを生じて伝動帯５と、駆動
輪３および被動輪４，６との噛合歯相互間に飛び
越し現象を生じ、それらに衝撃を与え、伝動帯の
歯を損傷する懸念を生じるが、本発明では機関の
運転停止中でも補助ばね１４は常に伝動帯５に一
定の張力を付与しているので前記懸念が解消され
る。 During operation of the engine, that is, when the hydraulic pump P is in operation, the auto adjuster A receives pressure oil from the hydraulic pump P and operates as described above. The pressing force of the auxiliary spring 14 and the elastic force of the auxiliary spring 14 act together to apply a predetermined tension to the transmission band 5. However, when the engine operation is stopped, the operation of the hydraulic pump P is also stopped, so the auto-adjustment is stopped. The supply of pressure oil to the adjuster A is also stopped, and when the engine is restarted, the oil supply to the auto adjuster A may be delayed, causing a temporary delay in the operation of the adjuster A. Here, if the auxiliary spring 14
Assuming that no elastic force is acting on the transmission band 5, the transmission band 5 becomes loose and a jump phenomenon occurs between the meshing teeth of the transmission band 5 and the driving wheels 3 and driven wheels 4 and 6. However, in the present invention, the auxiliary spring 14 always applies a constant tension to the transmission band 5 even when the engine is stopped, so the above-mentioned concern can be avoided. It will be resolved.

また補助ばね１４は、伝動帯５の張力付与の一
部を分担することによりオートアジヤスタＡにか
かる負荷が軽減され、その結果オートアジヤスタ
Ａを揺動レバー９の揺動支軸１２に近づけてもオ
ートアジヤスタＡは、伝動帯５からの負荷に耐え
得るようになり、同じ容量のオートアジヤスタＡ
で伝動帯９の調整代を大きくとれるばかりでな
く、かつ短い揺動レバー９の使用を可能にしてテ
ンシヨナ装置全体のコンパクト化が可能になる。 In addition, the auxiliary spring 14 reduces the load on the auto-adjuster A by sharing part of the tensioning of the transmission band 5, and as a result, brings the auto-adjuster A closer to the swinging shaft 12 of the swinging lever 9. Even if the auto adjuster A has the same capacity, it can withstand the load from the transmission band 5.
This not only allows for a large adjustment allowance for the transmission band 9, but also allows the use of a short swinging lever 9, making it possible to make the entire tensioner device more compact.

第７，８図には本発明の第２実施例が示され
る。 A second embodiment of the invention is shown in FIGS. 7 and 8.

この第２実施例では、ポンプケース１６とアジ
ヤスタケース１７とが別体に形成され、ポンプケ
ース１６の外端面に複数個のボルト６０を以てア
ジヤスタケース１７が直接固着される。 In this second embodiment, a pump case 16 and an adjuster case 17 are formed separately, and the adjuster case 17 is directly fixed to the outer end surface of the pump case 16 with a plurality of bolts 60.

而してこの第２実施例のものではオートアジヤ
スタＡのメンテナンスが容易となり、また該オー
トアジヤスタＡの、ポンプケース１６に対する取
付け自由度が増し、そのレイアウトがし易くな
る。 Therefore, in this second embodiment, maintenance of the auto adjuster A becomes easy, and the degree of freedom in attaching the auto adjuster A to the pump case 16 increases, making the layout easier.

他の構造においては前記第１実施例のものと同
じである。 The other structures are the same as those of the first embodiment.

なお、前記実施例における補助プーリ３、被動
プーリ４、伝動ベルト５およびテンシヨンプーリ
８は、本発明における駆動輪、被動輪、伝動帯お
よびテンシヨナを構成する。また前記実施例では
本発明をベルト式巻掛伝動装置に実施した場合を
説明たが、これをチエン式その他の巻掛伝動装置
にも実施できる。 The auxiliary pulley 3, the driven pulley 4, the transmission belt 5, and the tension pulley 8 in the embodiment described above constitute a driving wheel, a driven wheel, a transmission band, and a tensioner in the present invention. Further, in the above embodiments, the present invention is applied to a belt-type wrap-around transmission, but it can also be applied to a chain-type or other wrap-around transmission.

Ｃ 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、機関本体に支承される駆動輪と被動輪間に
無端状伝動帯を懸回し、この伝動帯には、それの
緩み側に配設されるテンシヨナを介して給油式オ
ートアジヤスタにより張力を付与するようにし
た、内燃機関の巻掛伝動装置におけるテンシヨナ
装置において、機関本体には前記テンシヨナを支
承した揺動レバーを揺動可能に軸支し、その揺動
レバーにはその自由端部に前記給油式オートアジ
ヤスタを、またその中間部に、該給油式オートア
ジヤスタと協動して前記テンシヨナを伝動帯に向
けて偏倚する補助ばねをそれぞれ連結するととも
に、該オートアジヤスタおよび補助ばねを前記揺
動レバーを挟んでその両側に配設したので、機関
運転中は、給油式オートアジヤスタおよび補助ば
ねより、揺動レバーとテンシヨナを介して伝動帯
に対し所定の張力を的確に付与して、巻掛伝動装
置の伝動効率を高めることができ、しかも機関の
始動初期などに給油式オートアジヤスタに作動遅
れがあつても、伝動帯には補助ばねにより一定の
張力が与えられて該伝動帯に一時的な緩みを生起
することがない。その上、テンシヨナを介して伝
動帯に付与すべき張力の一部を補助ばねが分担す
るので、オートアジヤスタが揺動レバーの自由端
部に連結されることと相俟つてオートアジヤスタ
の負荷を大幅に軽減することができ、それだけオ
ートアジヤスタを揺動レバーの揺動支点に近付け
られるから、同アジヤスタの調整代を大きくとれ
るばかりでなく、揺動レバーの有効長さを短くで
きてテンシヨナ装置のコンパクト化に寄与し得
る。C. 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 the transmission band has a loose side. In a tensioner device in a wrap transmission for an internal combustion engine, tension is applied by an oil-supplied auto-adjuster via a tensioner installed in the engine body. The swinging lever has the oil-filled auto-adjuster at its free end, and the oil-filled auto-adjuster at its intermediate portion, which cooperates with the oil-filled auto-adjuster to direct the tensioner toward the transmission band. The biasing auxiliary springs are connected to each other, and the auto adjuster and the auxiliary springs are placed on both sides of the swing lever, so that when the engine is running, the lubricating auto adjuster and the auxiliary springs prevent the swing from moving. It is possible to accurately apply a predetermined tension to the transmission band via the lever and tensioner, increasing the transmission efficiency of the wrap transmission device, and also prevents the delay in operation of the oil-filled auto-adjuster at the beginning of engine startup. Even when the transmission band is in a fixed position, a constant tension is applied to the transmission band by the auxiliary spring, so that the transmission band does not become temporarily loosened. Furthermore, since the auxiliary spring shares part of the tension that should be applied to the transmission band via the tensioner, the auto-adjuster is connected to the free end of the swing lever, and the load on the auto-adjuster is reduced. Since the auto adjuster can be moved closer to the swing fulcrum of the swing lever, not only can the adjustment allowance for the adjuster be increased, but also the effective length of the swing lever can be shortened and the tensioner can be moved closer to the swing fulcrum of the swing lever. This can contribute to making the device more compact.

またオートアジヤスタと補助ばねとを揺動レバ
ーを挟んでその両側に配設したので、オートアジ
ヤスタおよび補助ばねは相互に干渉し合うことな
く揺動レバー近傍に纒めてコンパクトに配備する
ことができる。 In addition, the auto adjuster and auxiliary spring are arranged on both sides of the swing lever, so the auto adjuster and the auxiliary spring can be arranged compactly near the swing lever without interfering with each other. Can be done.

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

第１〜６図は本発明装置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−線に沿う拡大
断面図、第４図は、第２図−線に沿うポンプ
ケースの裏面図、第５図は、第２図−線に沿
う拡大断面図、第６図は、第５図−線に沿う
アジヤスタケースの断面図、第７，８図は本発明
の第２実施例を示すもので、第７図はポンプケー
の一部の正面図、第８図は第７図の−線断面
図である。 Ｅ……機関本体、Ａ……強制給油式オートアジ
ヤスタ、３……駆動輪としての駆動プーリ、４…
…被動輪としての被動プーリ、５……伝動帯とし
ての伝動ベルト、５1……緩み側、８……テンシ
ヨナとしてのテンシヨンプーリ、９……揺動レバ
ー、１４……補助ばね。 Figures 1 to 6 show an embodiment of the device of the present invention. Figure 1 is a front view of a timed winding transmission for an internal combustion engine equipped with the device of the present invention, and Figure 2 is the same as that of Figure 1. 3 is an enlarged sectional view taken along the line in FIG. 1, FIG. 4 is a back view of the pump case taken along the line in FIG. 2, and FIG. 5 is an enlarged sectional view taken along the line in FIG. 6 is a sectional view of the adjuster case taken along the line of FIG. 5, FIGS. 7 and 8 show a second embodiment of the present invention, and FIG. FIG. 8 is a sectional view taken along the - line in FIG. 7. E...Engine body, A...Forced lubrication type auto adjuster, 3...Drive pulley as a drive wheel, 4...
...Driven pulley as a driven wheel, 5...Transmission belt as a transmission band, 5 1 ...Loose side, 8...Tension pulley as a tensioner, 9...Swing lever, 14...Auxiliary spring.

Claims (1)

【特許請求の範囲】[Claims] １ 機関本体Ｅに支承される駆動輪３と被動輪４
間に無端状伝動帯５を懸回し、この伝動帯５に
は、それの緩み側５1に配設されるテンシヨナ８
を介して給油式オートアジヤスタＡにより張力を
付与するようにした、内燃機関の巻掛伝動装置に
おけるテンシヨナ装置において、機関本体Ｅには
前記テンシヨナ８を支承した揺動レバー９を揺動
可能に軸支し、その揺動レバー９にはその自由端
部に前記給油式オートアジヤスタＡを、またその
中間部に、該給油式オートアジヤスタＡと協働し
て前記テンシヨナ８を伝動帯５に向けて偏倚する
補助ばね１４をそれぞれ連結するとともに、該オ
ートアジヤスタＡおよび補助ばね１４を前記揺動
レバー９を挟んでその両側に配設したことを特徴
とする、内燃機関の巻掛伝動装置におけるテンシ
ヨナ装置。1 Drive wheel 3 and driven wheel 4 supported by engine body E
An endless transmission band 5 is suspended between them, and a tensioner 8 disposed on the loose side 51 of the transmission band 5 is attached to the transmission band 5.
In a tensioner device in a wrap transmission for an internal combustion engine, in which tension is applied by an oil-supplied auto adjuster A through The swinging lever 9 has the oil-filled auto-adjuster A at its free end, and the tensioner 8 is attached to the transmission band 5 in cooperation with the oil-filled auto-adjuster A at its intermediate portion. A wrap-around transmission for an internal combustion engine, characterized in that auxiliary springs 14 biased toward are connected to each other, and the auto adjuster A and auxiliary springs 14 are disposed on both sides of the swing lever 9 with the swing lever 9 in between. Tensioner device in equipment.
JP5477985A 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine Granted JPS61215849A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
JP5477985A JPS61215849A (en) 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus 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
CA000504399A CA1254770A (en) 1985-03-19 1986-03-18 Tensioner device in wrapping connector driving 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
GB8823824A GB2208905B (en) 1985-03-19 1988-10-11 Tensioner device in wrapping connector driving device for internal combustion engine
GB8823825A GB2208906B (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
JP5477985A JPS61215849A (en) 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine

Publications (2)

Publication Number Publication Date
JPS61215849A JPS61215849A (en) 1986-09-25
JPS6343618B2 true JPS6343618B2 (en) 1988-08-31

Family

ID=12980254

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5477985A Granted JPS61215849A (en) 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine

Country Status (1)

Country Link
JP (1) JPS61215849A (en)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5920825A (en) * 1982-07-28 1984-02-02 Hitachi Cable Ltd Method for measuring temperature of cable conductor
JPS59208250A (en) * 1983-05-10 1984-11-26 Honda Motor Co Ltd Automatic tensile device of wound power transmitting component in internal-combustion engine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6121632Y2 (en) * 1981-05-01 1986-06-28

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5920825A (en) * 1982-07-28 1984-02-02 Hitachi Cable Ltd Method for measuring temperature of cable conductor
JPS59208250A (en) * 1983-05-10 1984-11-26 Honda Motor Co Ltd Automatic tensile device of wound power transmitting component in internal-combustion engine

Also Published As

Publication number Publication date
JPS61215849A (en) 1986-09-25

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