JPS6314225B2 - - Google Patents

Info

Publication number
JPS6314225B2
JPS6314225B2 JP60054775A JP5477585A JPS6314225B2 JP S6314225 B2 JPS6314225 B2 JP S6314225B2 JP 60054775 A JP60054775 A JP 60054775A JP 5477585 A JP5477585 A JP 5477585A JP S6314225 B2 JPS6314225 B2 JP S6314225B2
Authority
JP
Japan
Prior art keywords
oil
adjuster
case
auto
tensioner
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
JP60054775A
Other languages
Japanese (ja)
Other versions
JPS61215845A (en
Inventor
Jusuke Kinoshita
Junichi Araki
Itsuo Iwai
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
Tanaka Seimitsu Kogyo Co Ltd
Original Assignee
Honda Motor Co Ltd
Tanaka Seimitsu Kogyo 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, Tanaka Seimitsu Kogyo Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP5477585A priority Critical patent/JPS61215845A/en
Priority to US06/840,831 priority patent/US4761155A/en
Priority to CA000504399A priority patent/CA1254770A/en
Priority to DE19863609232 priority patent/DE3609232A1/en
Priority to GB8606724A priority patent/GB2175064B/en
Publication of JPS61215845A publication Critical patent/JPS61215845A/en
Publication of JPS6314225B2 publication Critical patent/JPS6314225B2/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
シヨナ本体にオートアジヤスタを連結し、これに
より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（実開昭57−202039号公
報）。(2) Prior art In a conventional internal combustion engine, an endless transmission band is suspended between a driving wheel and a driven wheel, and an auto-adjuster is connected to a tensioner body that is pressed into contact with the transmission band. A device in which a constant tension is applied is known (Japanese Utility Model Publication No. 57-202039).

(3) 発明が解決しようとする問題点 ところで前記オートアジヤスタを油圧式に構成
した場合には、油封入型と油補給型とが知られて
いるが、油封入型は油の補給路が不要である利点
はあるものの油の劣化および漏洩によりその信頼
性に問題があるのに対し、油補給型はかかる問題
が解消されるが、油の補給路が必要となり構造が
複雑となつて、コスト高を招くという別の問題を
生じる。(3) Problems to be Solved by the Invention Incidentally, when the auto-adjuster is constructed as a hydraulic type, there are two known types: an oil-filled type and an oil-supply type, but the oil-filled type has no oil supply path. Although it has the advantage of not being necessary, there are problems with its reliability due to oil deterioration and leakage, whereas the oil replenishment type solves this problem, but requires an oil supply path and has a complicated structure. Another problem arises in that it increases costs.

また上記油補給型のオートアジヤスタにおいて
は、テンシヨナに対する付勢力を常に適正に維持
するために、その油圧室に常に一定圧以上の高圧
油を供給する必要があり、また特に機関始動時に
アジヤスタ内油圧の立上りが遅れることによつて
アジヤスタの機能が低下するのを防止するには、
油供給源としての油圧ポンプからアジヤスタまで
を可及的に短い油路で連絡することが望ましい。 In addition, in the above-mentioned oil-supplied auto-adjuster, in order to maintain an appropriate biasing force against the tensioner, it is necessary to always supply high-pressure oil above a certain pressure to the hydraulic chamber. To prevent the adjuster function from deteriorating due to a delay in the rise of hydraulic pressure,
It is desirable to connect the hydraulic pump as an oil supply source to the adjuster with the shortest possible oil path.

本発明は上記に鑑み提案されたもので、前記オ
ートアジヤスタを油補給型に構成し、しかも油補
給路の構造を著しく簡素化し且つその長さを極め
て短かくできるようにした、内燃機関における巻
掛伝動装置のテンシヨナ装置を提供することを目
的とする。 The present invention has been proposed in view of the above, and is an internal combustion engine in which the auto adjuster is configured as an oil supply type, and the structure of the oil supply path can be significantly simplified and its length can be extremely shortened. It is an object of the present invention to provide a tensioner device for a wrap-around transmission.

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第１発明は、機関
のクランク軸によつて駆動される油圧ポンプのポ
ンプケースと給油式オートアジヤスタのアジヤス
タケースとを一体に形成して、機関本体に装着さ
れるユニツトケースを構成し、そのユニツトケー
ス内に、前記油圧ポンプの吐出口とオートアジヤ
スタの給油孔とを直接連通させる給油通路を形成
したことを特徴とし、また本第２発明は、機関の
クランク軸によつて駆動される油圧ポンプのポン
プケースと給油式オートアジヤスタのアジヤスタ
ケースとを別体に形成するとともにその両ケース
間を着脱可能に直接接合して、機関本体に装着さ
れるユニツトケースを構成し、そのユニツトケー
ス内に、前記油圧ポンプの吐出口とオートアジヤ
スタの給油孔とを直接連通させる給油通路を形成
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 first invention provides a pump case for a hydraulic pump driven by the crankshaft of an engine and a lubricating auto adjuster. The adjuster case and the adjuster case are integrally formed to constitute a unit case that is attached to the engine body, and within the unit case is an oil supply passage that directly communicates the discharge port of the hydraulic pump and the oil supply hole of the auto adjuster. The second invention is characterized in that the pump case of the hydraulic pump driven by the crankshaft of the engine and the adjuster case of the oil-supplied auto-adjuster are formed separately, and both cases are separated. A unit case that is attached to the engine body is formed by directly removably joining the parts, and an oil supply passage is formed in the unit case to directly communicate the discharge port of the hydraulic pump and the oil supply hole of the auto adjuster. It is characterized by what it did.

(2) 作用 前記構成によれば、油圧ポンプからの圧油はそ
のポンプの吐出口よりユニツトケース内の給油通
路を経てオートアジヤスタの給油孔に達し、そこ
から該アジヤスタ内に補給される。(2) Effect According to the above configuration, the pressure oil from the hydraulic pump reaches the oil supply hole of the auto adjuster through the oil supply passage in the unit case from the discharge port of the pump, and is replenished into the adjuster from there.

(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 is constructed by suspending an endless transmission belt 5 between a driving pulley 3 fixed to a crankshaft 1 and driven pulleys 4 fixed to a pair of valve drive camshafts 2, respectively. be done. 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.

第１〜３図において前記駆動プーリ３と他の被
動プーリ６間において、伝動ベルト５の緩み側５
１の外側には、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１０にボール軸受１１を介
して回転自在に支承される。前記揺動レバー９の
基端は、支軸１２を以て機関本体Ｅの端壁１３に
上下に揺動自在に軸支され、また該揺動レバー９
の先端に後に詳述する、伝動ベルト５の給油式オ
ートアジヤスタＡが連結される。そしてこのオー
トアジヤスタＡの押圧力で前記テンシヨンプーリ
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。 In FIGS. 1 to 3, the loose side 5 of the transmission belt 5 is located between the driving pulley 3 and the other driven pulley 6.
A tension pulley 8 is arranged on the outside of 1 ,
The tension pulley 8 is rotatably supported via a ball bearing 11 on a pulley shaft 10 protruding from an intermediate portion of the swing lever 9. The base end of the swing lever 9 is pivotally supported by a support shaft 12 on an end wall 13 of the engine body E so as to be able to swing up and down.
An oil-supplied auto-adjuster A of the transmission belt 5, which will be described in detail later, is connected to the tip of the transmission belt 5. 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１４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
ヨンプーリ８を伝動ベルト５の緩み側５1外面に
圧接するように偏倚させる。 Moreover, at the upper part of the intermediate position of the swing lever 9,
The other end side of a tension spring 14 whose base end is tied to the end wall 13 of the engine body E is connected, and the tension force of this tension spring 14 causes the swinging lever 9 to move counterclockwise around the support shaft 12. The tension pulley 8 is biased so as to swing 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、その両ケース
１６，１７により本発明のユニツトケースＣが構
成される。 The adjuster case 17 of the oil-supplied auto-adjuster A is integrally cast on the outer surface of the pump case 16 of the hydraulic pump P, and both cases 16 and 17 constitute a unit case C of the present invention.

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 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、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部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 is slidably fitted into the plunger case 21 so as to be movable up and down.
A plug 25 is fitted into the open upper end 24 of. 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 slipper member 27, and an adjustment screw 30 is screwed into the slipper surface 28 so as to be adjustable at the tip of the swing lever 9.
The lower ends of are brought into contact. 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れ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 urges the plunger 23 upward 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 valve 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、ユニツトケースＣの一部である
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３
２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. , is communicated with an oil supply passage 40 bored in the adjuster case 17, which is a part of the unit case C, and the oil hole 39 is connected to the oil supply chamber 3.
2.

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 is operating, 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.

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側の側壁２ｓには、排油孔４
９が穿設される。この排油孔４９は、プランジヤ
ケース２１とプランジヤ２３間に形成される環状
油室５１およびハウジング１９に形成した排油通
路５０を通して機関本体Ｅ内の油溜４８に連通さ
れている。 Between the O-ring 22 and the oil supply hole 38, there is an oil drain hole 4 in the side wall 2s on the plunger case 21 side.
9 is drilled. The oil drain hole 49 communicates with an oil reservoir 48 in the engine body E through an annular oil chamber 51 formed between the plunger case 21 and the plunger 23 and an oil drain passage 50 formed in the housing 19.

プランジヤ２３内の補給油室３２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を通して環状油室５
１に連通されており、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を通つて環状
油室５１に流れ、さらに該環状油室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 replenishment oil chamber 32 in the plunger 23 is connected to the annular oil chamber 5 through a leak passage 56 formed between the open upper end 24 of the plunger 23 and the fitting surface of the plug 25.
1, the oil in the replenishment oil chamber 32 flows together with trapped air through the leak passage 56 to the annular oil chamber 51, and further from the annular oil chamber 51 to the oil drain hole 49 and the oil drain passage. 50 and is returned to the oil reservoir 48 in the engine body E.

さらに第５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, the bottom of the housing 19 includes a lower part of the high pressure oil chamber 31 and an oil pump P
An air bleed passage 52 communicating with the discharge port 41 is bored, and this air bleed passage 52 is used to bleed out the air sealed in the oil chamber 57 when the plunger case 21 is assembled into the housing 19. .

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。 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.

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
つて環状油室５１に至り、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。したがつて油圧ポンプＰ、オー
トアジヤスタＡ間の給油系は閉油回路を構成して
オートアジヤスタＡの補給油室３２には機関の運
転中絶えず潤滑油が供給され、しかも前記閉油回
路から外部に潤滑油が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 together with the trapped air sealed in the chamber 32 to the annular oil chamber 51, 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. Therefore, the oil supply system between the hydraulic pump P and the auto adjuster A constitutes a closed oil circuit, and lubricating oil is constantly supplied to the replenishment oil chamber 32 of the auto adjuster A during engine operation. No lubricating oil leaks to the outside.

そして給油通路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 passage 40 exceeds a predetermined value, the piston 46 of the regulator R is activated by the spring 47.
The oil sump communication hole 44 communicates with the oil supply passage 40 and pressurized oil in the passage 40 is returned to the oil sump 48 .

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。 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 adjusting 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 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.

而してこの場合高圧油室３１内の圧油は、プラ
ンジヤケース２１とプランジヤ２３間の摺動間隙
や高圧油室３１の油が内部に若干の気泡を含んで
いることに起因して、実際にはプランジヤ２３は
僅かながら沈み込みこれによつて伝動ベルト５の
緩み側５1に作用する引張衝撃を緩和することが
できる。 In this case, the pressure oil in the high-pressure oil chamber 31 is not actually the same due to the sliding gap between the plunger case 21 and the plunger 23 and the fact that the oil in the high-pressure oil chamber 31 contains some air bubbles inside. In this case, the plunger 23 sinks slightly, thereby alleviating the tensile impact acting 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。 In the above embodiment, the drive pulley 3, driven pulley 4, transmission belt 5, and tension pulley 8 constitute a driving wheel, a driven wheel, a transmission band, and a tensioner in the present invention.

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が直接接合され、その両ケー
ス１６，１７によりユニツトケースＣが構成され
る。 In this second embodiment, a pump case 16 and an adjuster case 17 are formed separately, and the adjuster case 17 is directly joined to the outer end surface of the pump case 16 with a plurality of bolts 60. 17 constitutes a unit case C.

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.

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、テンシヨナを伝動帯の緩み側に圧接すると
ともに伝動帯の緩み側の張力変動に応動して自動
的に作動し、伝動帯に一定の張力を付与するよう
にした給油式オートアジヤスタを備えた内燃機関
におけるテンシヨナ装置において、機関のクラン
ク軸によつて駆動される油圧ポンプのポンプケー
スと前記給油式オートアジヤスタのアジヤスタケ
ースとを一体に形成または直接接合して、機関本
体に装着されるユニツトケースを構成し、そのユ
ニツトケース内に、前記油圧ポンプの吐出口とオ
ートアジヤスタの給油孔とを直接連通させる給油
通路を形成したので、給油式オートアジヤスタと
油圧ポンプとの間を特別に配管する必要がない
上、その間のシール構造も不要もしくは極めて簡
素化することができ、従つてオートアジヤスタへ
の給油系の構造が極めて簡単でコストの低減およ
び組立性の向上に大いに寄与することができる。
その上、オートアジヤスタとそれの油供給源であ
る油圧ポンプとの間を互いに近接させてその間の
油路を極めて短かくできるから、機関始動時にお
いても油圧ポンプからの圧油をアジヤスタに迅速
に供給できてアジヤスタ内油圧の立上りの遅れを
少なくすることができ、機関始動直後よりアジヤ
スタを有効に機能させることができる。C. Effects of the Invention As is clear from the above embodiments, according to the present invention, the tensioner is pressed against the loose side of the transmission band and automatically operates in response to tension fluctuations on the loose side of the transmission band. In a tensioner device for an internal combustion engine, which is equipped with an oil-filled auto-adjuster that applies a constant tension to A unit case is formed integrally with the case or is directly connected to the unit case to be attached to the engine body, and within the unit case is an oil supply passage that directly communicates the discharge port of the hydraulic pump and the oil supply hole of the auto adjuster. , there is no need for special piping between the oil-supplied auto-adjuster and the hydraulic pump, and the seal structure between them is also unnecessary or can be extremely simplified. The structure is extremely simple and can greatly contribute to reducing costs and improving ease of assembly.
Furthermore, since the auto adjuster and the hydraulic pump, which is its oil supply source, can be placed close to each other and the oil path between them can be made extremely short, pressure oil from the hydraulic pump can be quickly delivered to the adjuster even when the engine is started. It is possible to reduce the delay in the rise of the oil pressure in the adjuster, and the adjuster can be made to function effectively immediately after the engine is started.

また特に第２発明によれば、ポンプケースとア
ジヤタケースとが別体に形成されてその間が着脱
可能に直接接合されるので、オートアジヤスタの
メンテナンスが容易となり、ポンプケースに対す
るアジヤスタケースの取付自由度が増し、そのレ
イアウトがし易くなるものである。 In particular, according to the second invention, the pump case and the adjuster case are formed separately and are directly connected to each other in a removable manner, so maintenance of the auto adjuster is easy and the adjuster case can be freely attached to the pump case. This increases the efficiency and makes the layout easier.

【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
スの一部の正面図、第８図は第７図の―線断
面図である。 Ｅ……機関本体、Ａ……給油式オートアジヤス
タ、Ｐ……油圧ポンプ、Ｃ……ユニツトケース、
３……駆動プーリ、４……被動プーリ、５……伝
動ベルト、５1……緩み側、８……テンシヨンプ
ーリ、１６……ポンプケース、１７……アジヤス
タケース、３８……給油孔、４１……吐出口。 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. Figure 3 is an enlarged sectional view taken along the line from Figure 1, Figure 4 is a back view of the pump case taken along the line from Figure 2, and Figure 5 is an enlarged sectional view taken along the line from Figure 2. FIG. 6 is an enlarged sectional view taken along the line of FIG. 5, and 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...Oil-filled auto adjuster, P...Hydraulic pump, C...Unit case,
3... Drive pulley, 4... Driven pulley, 5... Transmission belt, 5 1 ... Loose side, 8... Tension pulley, 16... Pump case, 17... Adjuster case, 38... Oil supply hole , 41...Discharge port.

Claims (1)

【特許請求の範囲】 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の緩
み側５1にテンシヨナ８を配設し、このテンシヨ
ナ８には、給油式オートアジヤスタＡを連結し、
この給油式オートアジヤスタＡは前記テンシヨナ
８を前記伝動帯５の緩み側５1に圧接するととも
に、前記伝動帯５の緩み側５1の張力変動に応動
して自動的に作動し、前記伝動帯５に常に一定の
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ヨナ装置において、機関のク
ランク軸１によつて駆動される油圧ポンプＰのポ
ンプケース１６と前記給油式オートアジヤスタＡ
のアジヤスタケース１７とを一体に形成して、機
関本体Ｅに装着されるユニツトケースＣを構成
し、そのユニツトケースＣ内に、前記油圧ポンプ
Ｐの吐出口４１とオートアジヤスタＡの給油孔３
８とを直接連通させる給油通路４０を形成したこ
とを特徴とする、内燃機関における巻掛伝動装置
のテンシヨナ装置。 ２ 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の緩
み側５1にテンシヨナ８を配設し、このテンシヨ
ナ８には、給油式オートアジヤスタＡを連結し、
この給油式オートアジヤスタＡは前記テンシヨナ
８を前記伝動帯５の緩み側５1に圧接するととも
に、前記伝動帯５の緩み側５1の張力変動に応動
して自動的に作動し、前記伝動帯５に常に一定の
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ヨナ装置において、機関のク
ランク軸１によつて駆動される油圧ポンプＰのポ
ンプケース１６と前記給油式オートアジヤスタＡ
のアジヤスタケース１７とを別体に形成するとと
もにその両ケース１６，１７間を着脱可能に直接
接合して、機関本体Ｅに装着されるユニツトケー
スＣを構成し、そのユニツトケースＣ内に、前記
油圧ポンプＰの吐出口４１とオートアジヤスタＡ
の給油孔３８とを直接連通させる給油通路４０を
形成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ヨナ装置。[Claims] 1. Drive wheel 3 and driven wheel 4 supported by engine body E
An endless transmission belt 5 is suspended between them, a tensioner 8 is disposed on the loose side 51 of the transmission belt 5, and an oil-supplied auto-adjuster A is connected to the tensioner 8.
This oil-supplied auto-adjuster A presses the tensioner 8 against the loose side 5 1 of the transmission band 5, and operates automatically in response to tension fluctuations on the slack side 5 1 of the transmission band 5. In a tensioner device for a wrap transmission in an internal combustion engine, which always applies a constant tension to a band 5, a pump case 16 of a hydraulic pump P driven by a crankshaft 1 of the engine and the oil-supplied auto-adjuster are provided. Star A
and the adjuster case 17 are integrally formed to constitute a unit case C that is attached to the engine body E. Inside the unit case C, there are provided the discharge port 41 of the hydraulic pump P and the oil supply hole of the auto adjuster A. 3
8. A tensioner device for a wrap transmission in an internal combustion engine, characterized in that a refueling passage 40 is formed in direct communication with a tensioner device. 2 Drive wheel 3 and driven wheel 4 supported by engine body E
An endless transmission band 5 is suspended between them, a tensioner 8 is disposed on the loose side 51 of the transmission band 5, and an oil-supplied auto adjuster A is connected to the tensioner 8.
This oil-supplied auto-adjuster A presses the tensioner 8 against the loose side 5 1 of the transmission band 5, and operates automatically in response to tension fluctuations on the slack side 5 1 of the transmission band 5. In a tensioner device for a wrap transmission in an internal combustion engine, which always applies a constant tension to a band 5, a pump case 16 of a hydraulic pump P driven by a crankshaft 1 of the engine and the oil-supplied auto-adjuster are provided. Star A
The adjuster case 17 and the adjuster case 17 are formed separately, and the two cases 16 and 17 are directly connected removably to form a unit case C that is attached to the engine body E, and inside the unit case C, The discharge port 41 of the hydraulic pump P and the auto adjuster A
A tensioner device for a wrap transmission in an internal combustion engine, characterized in that an oil supply passage 40 is formed in direct communication with an oil supply hole 38 of an internal combustion engine.
JP5477585A 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine Granted JPS61215845A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
JP5477585A JPS61215845A (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
DE19863609232 DE3609232A1 (en) 1985-03-19 1986-03-19 TENSIONING DEVICE IN A STRAP CONNECTING DRIVE DEVICE FOR AN INTERNAL COMBUSTION ENGINE
GB8606724A GB2175064B (en) 1985-03-19 1986-03-19 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
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
JP5477585A JPS61215845A (en) 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine

Publications (2)

Publication Number Publication Date
JPS61215845A JPS61215845A (en) 1986-09-25
JPS6314225B2 true JPS6314225B2 (en) 1988-03-30

Family

ID=12980144

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5477585A Granted JPS61215845A (en) 1985-03-19 1985-03-19 Tensioner apparatus in laying transmission apparatus for internal-combustion engine

Country Status (1)

Country Link
JP (1) JPS61215845A (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2549817Y2 (en) * 1991-01-31 1997-10-08 株式会社椿本チエイン Hydraulic tensioner with integrated mounting plate and gasket
JP6767656B2 (en) * 2016-09-26 2020-10-14 株式会社椿本チエイン Tensioner

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5712296U (en) * 1980-06-21 1982-01-22

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5712296U (en) * 1980-06-21 1982-01-22

Also Published As

Publication number Publication date
JPS61215845A (en) 1986-09-25

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