JPS61215845A - Tensioner apparatus in laying transmission apparatus for internal-combustion engine - Google Patents

Tensioner apparatus in laying transmission apparatus for internal-combustion engine

Info

Publication number
JPS61215845A
JPS61215845A JP5477585A JP5477585A JPS61215845A JP S61215845 A JPS61215845 A JP S61215845A JP 5477585 A JP5477585 A JP 5477585A JP 5477585 A JP5477585 A JP 5477585A JP S61215845 A JPS61215845 A JP S61215845A
Authority
JP
Japan
Prior art keywords
oil
adjuster
case
tensioner
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.)
Granted
Application number
JP5477585A
Other languages
Japanese (ja)
Other versions
JPS6314225B2 (en
Inventor
Yusuke Kinoshita
裕介 木下
Junichi Araki
荒木　純一
Itsuo Iwai
岩井　逸雄
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.)
TANAKA MACH KOGYO KK
Honda Motor Co Ltd
Original Assignee
TANAKA MACH KOGYO KK
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 TANAKA MACH KOGYO KK, Honda Motor Co Ltd filed Critical TANAKA MACH KOGYO KK
Priority to JP5477585A priority Critical patent/JPS61215845A/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 JPS61215845A publication Critical patent/JPS61215845A/en
Publication of JPS6314225B2 publication Critical patent/JPS6314225B2/ja
Priority to GB8823825A priority patent/GB2208906B/en
Priority to GB8823824A priority patent/GB2208905B/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)

Abstract

PURPOSE:To simplify the structure of an oil feeding passage by supplying the pressurized oil from a hydraulic pump into an autoadjustor from the discharge port of a pump case through an oil feeding hole on the autoadjustor. CONSTITUTION:The pump case 6 of a hydraulic pump P installed onto an engine body and the adjustor case 17 of an oil feeding type autoadjustor A are arranged contiguously to each other. Further, a discharge port 41 opened onto the pump case 6 and an oil feeding hole 8 formed on the adjustor case 17 are allowed to directly communicate with each other. With such constitution, working oil can be supplied directly from the hydraulic pump P, and the structure of the oil feeding system to the autoadjustor can be simplified.

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ョナ本体にオ
ートアジャスタを連結し、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) Conventional technology In conventional internal combustion engines, an endless transmission band is suspended between the driving wheels and the driven wheels, and an auto-adjuster is connected to the tensioner body that is pressed into contact with the transmission band. A device that applies a tension of 1 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ャ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って、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 By the way, when the auto adjuster is constructed as a hydraulic type, there are known two types: an oil-filled type and an oil-filled type, but the oil-filled type does not require an oil supply path. Although this type has the advantage of having a reliability problem due to oil deterioration and leakage, the oil replenishment type solves this problem, but requires an oil replenishment path, making the structure complicated and increasing costs. Another problem arises in that it leads to high blood pressure.

本発明に上記実情に鑑みてなされたもので前記オートア
ジャスタを油補給型に構成し、しかも油補給路の構造を
極めて簡素化できるようにした構成簡単な内燃機関にお
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 has been made in view of the above-mentioned circumstances, and the auto-adjuster is configured as an oil supply type, and the structure of the oil supply path can be extremely simplified.A tensioner device for a wrap transmission in an internal combustion engine with a simple structure. The purpose is to provide the following.

Ｂ、発明の構成 （１）　　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、この伝動帯の緩み側に
テンショナを配設し、このテンショナには、給油式オー
トアジャスタを連結し、この給油式オートアジャスタは
前記テンショナを前記伝動帯の緩み側に圧接するととも
に、前記伝動帯の緩み側の、張力変動に応動して自動的
に作動し、前記伝動帯に常に一体の張力を付与するよう
にした内燃機関におけるテンショナ装置において、前記
機関本体に設けら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ャスタのアジャスタケースとを隣接
配置し、前記ポンプケースに開口される吐出口と、前記
アジャスタケースに穿設される給油孔とを直接連通する
。B. Structure of the Invention (1) Means for Solving the Problems 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 the engine body, and this transmission band is A tensioner is disposed on the slack side of the band, and a lubricating type auto-adjuster is connected to this tensioner, and the lubricating type auto-adjuster presses the tensioner against the slack side of the transmission band, and also connects the tensioner to the slack side of the transmission band. In the tensioner device for an internal combustion engine, which operates automatically in response to tension fluctuations and always applies a uniform tension to the transmission band, the tensioner device includes a pump case of a hydraulic pump provided in the engine body and the oil supply. An adjuster case of the type auto adjuster is arranged adjacent to the pump case, and a discharge port opened in the pump case is directly communicated with an oil supply hole drilled in the adjuster case.

（２）作　用 前記構成によれば、油圧ポンプからの圧油は、ポンプケ
ースに開口した吐出口より、給油型オートアジャスタの
アジャスタケースに開口した給油口を通って該オートア
ジャスタに補給される。(2) Effect According to the above configuration, pressure oil from the hydraulic pump is supplied to the auto-adjuster from the discharge port opened in the pump case through the oil supply port opened in the adjuster case of the oil-supplied auto-adjuster. .

（３）実施例 以下、第１〜６図により本発明装置をＤｏ）（Ｃ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) Embodiment A first embodiment in which the device of the present invention is applied to a C-type four-stroke internal combustion engine will be described below with reference to FIGS. 1 to 6.

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ｌ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に固着される駆動ブーＩ
Ｊ　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によって機関本体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 the engine body E of the internal combustion engine for interlocking a crankshaft l and a pair of valve operating camshafts 2 of a valve operating mechanism. This timing winding transmission T is a drive boot I fixed to the crankshaft 1.
An endless transmission belt 5 is suspended between the J 3 and driven pulleys 4 fixed to a pair of valve drive camshafts 2, respectively. 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ブーＵ　３と他の被動ブー
ＩＪ　６間において、伝動ベルト５の緩み側５、の外側
には、テンションプーリ８が配設され、このテンション
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。In FIGS. 1 to 3, a tension pulley 8 is disposed on the outer side of the loose side 5 of the transmission belt 5 between the driving boob U 3 and the other driven boob IJ 6, and this tension pulley 8 swings. The lever 9 is rotatably supported via a ball bearing 11 on a pulley shaft 10 protruding from the middle portion of the lever 9 .

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。The base end of the swing lever 9 is connected to the engine body E using a support shaft 12.
The swing lever 9 is pivotally supported on an end wall 13 so as to be able to swing up and down, and an oil-supplied auto adjuster A for the transmission belt 5, which will be described in detail later, is connected to the tip 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！［ｉｒＺ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 14 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. Supports the swing lever 9! [The tension pulley 8 is biased so as to swing counterclockwise around irZ, and the tension pulley 8 is moved to the loose 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 lubricated 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Ｏリング２２が介装される。Next, we will mainly explain the structure of this oil-filled auto adjuster A in Section 5.
Referring to FIG. 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.
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.

前記プランジャケース２１内には、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。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. A slipper member 27 is attached to an O-ring 29 in a recess 26 formed in the upper part of this plug 25.
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 seated on the valve seat of the valve port 33, a valve cage 36 housing the valve body 35, and a tension spring 34 that springs the valve upward. It is composed of a valve spring 37 that urges the valve body 35 in the valve closing direction.

前記０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、および袖口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 a refueling hole 38 that constantly communicates with each other, and a cuff 3.
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。このレギエ
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に戻すようになっ
ている。As clearly shown in FIG. 6, 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. This regie eletor R consists of a piston 46 that is slidably fitted into the downstream 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 oil pressure of the spring 47 increases to a predetermined value or more, the spring 47
The piston 46 is slid in the opening direction against the elastic force of the piston 46, 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 bottom of the engine body E. It looks like this.

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側の側壁２Ｓには、排油孔４９が穿設される
。この排油孔４９は、プランジャケース２１とプランジ
ャ２３間に形成される環状油室５１およびハウジング１
９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, an oil drain hole 49 is bored in the side wall 2S on the plunger case 21 side. This oil drain hole 49 is connected to an annular oil chamber 51 formed between the plunger case 21 and the plunger 23 and the housing 1.
It communicates with an oil reservoir 48 in the engine body E through an oil drain passage 50 formed at 9.

プランジャ２３内の補給油室３２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を通して環状−泊室５１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を通って環状油室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を通っ
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 communicated with the annular chamber 51 through a leak passage 56 formed between the open upper end 24 of the plunger 23 and the fitting surface of the plug 25. The oil flows along with the trapped air into the annular oil chamber 51 through the leak passage 56, and further from the annular oil chamber 51 through the oil drain hole 49 and oil drain passage 50 into the oil sump 48 in the engine body E. is refluxed to.

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を抜くためのもので
ある。Further, as shown in FIG. 5, 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 removing 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間を油密に封誠する。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 elevation and descent of the plunger 23, and seals 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.

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。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、咳室３２内に封入
された噛込みエアとともにリーク通路５６を通って環状
油室５１に至り、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。した
がって油圧ポンプＰ、オートアジャスタＡ間の給油系は
閉油回路を構成してオートアジャスタ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 supply oil chamber 32 in the plunger case 21 in advance. Also, a hydraulic pump P for lubricating the engine connected to the crankshaft 1
A portion of the pressurized oil from the outlet 41 and the oil supply passage 40. The replenishing oil chamber 32 is always forcibly supplied with oil through the oil supply hole 38 and the oil hole -39, and the replenishing oil chamber 32 is filled with oil. In addition, the oil in the supply oil chamber 32 passes through the leak passage 56 together with the trapped air sealed in the cough chamber 32 to reach the annular oil chamber 51, and from there passes through the oil drain hole 49 and the oil drain passage 50 to the engine engine. The oil is refluxed into the oil reservoir 48 at the bottom of the main body E. Therefore, the oil supply system between the hydraulic pump P and the auto-adjuster A constitutes a closed oil circuit, and the replenishing oil chamber 32 of the auto-adjuster A
Lubricating oil is constantly supplied to the engine during operation of the engine, and the lubricating oil does not leak outside from the closed oil circuit.

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 retreats against the elastic force of the spring 47, and the oil sump communication hole 44 communicates with the oil supply passage 40. The pressurized oil inside 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Ｖ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 V is forced to close the valve port 3 due to the pressure difference with the replenishment oil chamber 32.
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Ｖ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プーリ８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 V closes the valve port 33, thereby preventing 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 pulley 8, the tension pulley 8 is prevented from retreating.

而してこの場合高圧油室３１内の圧油は、プランジャケ
ース２１とプランジャ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、
実際にはプランジャ２３は僅かながら沈み込みこれによ
って伝動ベルト５の緩み側５．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 absorbed by the sliding gap between the plunger case 21 and the plunger 23 and the high pressure oil chamber 31.
This is due to the fact that the oil contains some air bubbles inside.
In reality, the plunger 23 sinks slightly, thereby causing the loose side 5 of the transmission belt 5. It is possible to alleviate the tensile impact acting on the

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ブーＩ７８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 boob I78 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、およびテンションプーリ８は本発明に
おける駆動輪、被動輪、伝動帯およびテンショナを構成
する 第７，８図には本発明の第２実施例が示される。In the above embodiment, the driving pulley 3 and the driven pulley 4
, the transmission belt 5, and the tension pulley 8 constitute a driving wheel, a driven wheel, a transmission band, and a tensioner in the present invention.A second embodiment of the present invention is shown in FIGS. 7 and 8.

この第２実施例では、ポンプケース１６とアジャスタケ
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を以てアジャスタケース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ャスタＡの
メンテナンスが容易となり、また該オートアジャスタＡ
の、ポンプケース１６に対する取付は自由度が増し、そ
のレイアウトがし易くなる。Therefore, in this second embodiment, the maintenance of the auto adjuster A is easy, and the auto adjuster A is easy to maintain.
The degree of freedom in attaching the pump to the pump case 16 increases, and the layout becomes 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.

Ｃ０発明の効果 ば、テンショ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
ジャスタを備えた内燃機関におけるテンショナ装置にお
いて、機関本体に設けら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ャスタのアジャスタケースと
を隣接配置し、前記ポンプケースに開口される吐出口と
、前記アジャスタケースに穿設される給油孔とを直接連
通したので、前記給油式アジャスタへの作動油の供給を
油圧ポンプから直接行なうことができ、配管の必要がな
く、且つ作動油の漏洩の心配もない、またポンプケース
とアジャスタケースとに単に吐出口と、給油孔を穿設す
るだけで済み、シール部材も不要もしくは極めて簡単な
もので足り全体としてオートアジャスタへの給油系の構
造が極めて簡単となり、コストを低減することができる
。The advantage of the C0 invention is that 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 to apply a constant tension to the transmission band. In a tensioner device for an internal combustion engine equipped with an adjuster, a pump case of a hydraulic pump provided in the engine body and an adjuster case of the oil-feeding auto adjuster are arranged adjacent to each other, and a discharge port opened in the pump case and a Since it communicates directly with the oil supply hole drilled in the case, hydraulic oil can be supplied directly to the oil supply adjuster from the hydraulic pump, eliminating the need for piping and eliminating the risk of hydraulic oil leakage. In addition, it is only necessary to simply drill a discharge port and an oil supply hole in the pump case and adjuster case, and there is no need for a sealing member or a very simple one is sufficient.The overall structure of the oil supply system to the auto adjuster is extremely simple. Cost can be reduced.

また前記第１実施例のようにポンプケースとアジャスタ
ケースとを一体に形成すれば、前記吐出口と給油孔とが
一体となってそれらを一挙に穿設することができ、しか
も連接部がなくシールが不要となり、一層のコスト低減
を図ることができる。Furthermore, if the pump case and adjuster case are integrally formed as in the first embodiment, the discharge port and the oil supply hole can be integrated and drilled at once, and there is no connecting part. Seals are no longer required, and costs can be further reduced.

また前記第２実施例のようにポンプケースとアジャスタ
ケースとを別体に形成すれば、オートアジャスタのメン
テナンスが容易となり、ポンプケースに対するアジャス
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。Furthermore, if the pump case and adjuster case are formed separately as in the second embodiment, maintenance of the auto-adjuster becomes easier, the degree of freedom in attaching the adjuster case to the pump case increases, and the layout becomes easier. It is.

【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ＩＩＩ−ＩＩＩ線に沿う拡大断面図、第４図は、
第２図ＩＶ−ｒＶ線に沿うポンプケースの裏面図、第５
図は、第２図Ｖ−Ｖ線に沿う拡大断面図、第６図は、第
５図ｖｒ−ｖｔ線に沿うアジャ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・・・給油式オートアジャスタ、
Ｐ・・・油圧ポンプ ３・・・駆動プーリ、４・・・被動プーリ、５・・・伝
動ベルト、５．・・・緩み側、８・・・テンションプー
リ、１６・・・ポンプケース、１７・・・アジャスタケ
ース、３８・・・給油孔、４１・・・吐出口 時　許　出　願　人　本田技研工業株式会社株式会社田
中マシン工業 第３図 第４図Figures 1 to 6 show an embodiment of the device of the present invention.
The figure is a front view of a timing winding transmission device for an internal combustion engine equipped with the device of the present invention, FIG. 2 is a side view taken along the line ■ in FIG. 1, and FIG. The enlarged sectional view, Figure 4, is
Figure 2: Back view of the pump case along line IV-rV, No. 5
The figures are an enlarged sectional view taken along the line V-V in FIG. 2, FIG. 6 is a sectional view of the adjuster case taken along the line vr-vt in FIG. 7 is a front view of a part of the pump case, and FIG. 8 is a sectional view taken along the line ■-■ in FIG. 7. E... Engine body, A... Lubrication type auto adjuster,
P... Hydraulic pump 3... Drive pulley, 4... Driven pulley, 5... Transmission belt, 5. ... Loose side, 8 ... Tension pulley, 16 ... Pump case, 17 ... Adjuster case, 38 ... Oil supply hole, 41 ... At discharge port Applicant Honda Motor Co., Ltd. Tanaka Machine Industry Co., Ltd.Figure 3Figure 4

Claims (3)

【特許請求の範囲】[Claims] （１）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、この伝動帯の緩み側にテンショナを配
設し、このテンショナには、給油式オートアジャスタを
連結し、この給油式オートアジャスタは前記テンショナ
を前記伝動帯の緩み側に圧接するとともに、前記伝動帯
の緩み側の、張力変動に応動して自動的に作動し、前記
伝動帯に常に一定の張力を付与するようにした内燃機関
におけるテンショナ装置において、前記機関本体に設け
られる油圧ポンプのポンプケースと、前記給油式オート
アジャスタのアジャスタケースとを隣接配置し、前記ポ
ンプケースに開口される吐出口と、前記アジャスタケー
スに穿設される給油孔とを直接連通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。(1) An endless transmission band is suspended between a driving wheel and a driven wheel supported by the engine body, a tensioner is provided on the slack side of this transmission band, and a oil-supplied auto adjuster is connected to this tensioner, This oil-supplied auto adjuster presses the tensioner against the loose side of the transmission band, and operates automatically in response to tension fluctuations on the slack side of the transmission band, thereby always applying a constant tension to the transmission band. In the tensioner device for an internal combustion engine, a pump case of a hydraulic pump provided in the engine main body and an adjuster case of the oil supply type auto adjuster are arranged adjacent to each other, and a discharge port opened in the pump case; A tensioner device for a wrap transmission in an internal combustion engine, characterized in that the tensioner device is in direct communication with an oil supply hole drilled in an adjuster case. （２）前記特許請求の範囲第（１）項記載の内燃機関に
おける巻掛伝動装置のテンショナ装置において、前記給
油ポンプのポンプケースと給油式オートアジャスタのア
ジャスタケースとを一体に形成してなる内燃機関におけ
る巻掛伝動装置のテンショナ装置。(2) A tensioner device for a wrap-around transmission in an internal combustion engine as set forth in claim (1), wherein a pump case of the refueling pump and an adjuster case of the refueling auto-adjuster are integrally formed. A tensioner device for a wrapped transmission in an engine. （３）特許請求の範囲第（１）項記載の内燃機関におけ
る巻掛伝動装置のテンショナ装置おいて、前記油圧ポン
プのポンプケースと前記給油式オートアジャスタのアジ
ャスタケースとを別体に構成し、それらを一体に結合し
てなる内燃機関における巻掛伝動装置のテンショナ装置
。(3) In the tensioner device for a wrap transmission in an internal combustion engine according to claim (1), the pump case of the hydraulic pump and the adjuster case of the oil-filled auto adjuster are constructed separately, A tensioner device for a wrap transmission in an internal combustion engine, which is formed by combining these parts into one body.
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
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
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 true JPS61215845A (en) 1986-09-25
JPS6314225B2 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)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4202775A1 (en) * 1991-01-31 1992-08-06 Tsubakimoto Chain Co HYDRAULIC TENSIONER
JP2018053909A (en) * 2016-09-26 2018-04-05 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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4202775A1 (en) * 1991-01-31 1992-08-06 Tsubakimoto Chain Co HYDRAULIC TENSIONER
JP2018053909A (en) * 2016-09-26 2018-04-05 株式会社椿本チエイン Tensioner

Also Published As

Publication number Publication date
JPS6314225B2 (en) 1988-03-30

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