JPS61252952A - Tensioner of entrained transmission of internal-combustion engine - Google Patents
Tensioner of entrained transmission of internal-combustion engineInfo
- Publication number
- JPS61252952A JPS61252952A JP9191185A JP9191185A JPS61252952A JP S61252952 A JPS61252952 A JP S61252952A JP 9191185 A JP9191185 A JP 9191185A JP 9191185 A JP9191185 A JP 9191185A JP S61252952 A JPS61252952 A JP S61252952A
- Authority
- JP
- Japan
- Prior art keywords
- plunger
- oil
- oil chamber
- high pressure
- chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- F16H2007/0859—Check valves
Landscapes
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
Description
【発明の詳細な説明】
Ａ１発明の目的
（１） 産業上の利用分野
一本発明は、内燃機関の巻掛伝動装置において、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、圧
油式オートアジャスタ付のテンショナ装置に関するもの
である。Detailed Description of the Invention A1 Object of the Invention (1) Industrial Field of Application 1 The present invention relates to a wrap transmission device for an internal combustion engine, which is suspended between a driving wheel and a driven wheel supported by an engine body. This invention relates to a tensioner device equipped with a hydraulic auto-adjuster that automatically applies a constant tension to an endless transmission band.
（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チェ
ノを懸回し、該チェノに圧接されるゴムに油圧式オート
アジャスタを連結し、これにより該チェノに一定の張力
を付与するようにしたものは公知（実公昭５０−２３４
６６号公報）２１′ある。(2) Prior art In a conventional internal combustion engine, an endless chain is suspended between the driving wheels and driven wheels, and a hydraulic auto-adjuster is connected to the rubber that is pressed into contact with the chain, thereby applying a constant tension to the chain. The system to which this is applied is publicly known (According to Utility Model Publication No. 50-234)
66 Publication) 21'.
（３）発明が解決しようとする問題点
ところが前記油圧式オートアジャスタは、そのシリンダ
とピストンとの摺動間隙が０リングによって油密にシー
ルされているので、チェノにかがる引張衝撃や過剰緊張
を吸収することが難しく、これがチェノの耐久性に影響
を及ぼしたり、伝動効率の低下を招く等の問題があった
。(3) Problems to be Solved by the Invention However, in the hydraulic auto adjuster, the sliding gap between the cylinder and the piston is oil-tightly sealed by an O-ring. It is difficult to absorb tension, which has problems such as affecting the durability of the chino and reducing transmission efficiency.
本発明は上記事情に鑑みてなされたもので、伝動帯にが
かる引張衝撃や過剰緊張を緩和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 circumstances, and it is an object of the present invention to provide a tensioner device for a wrap transmission in an internal combustion engine, which has a simple structure and is capable of alleviating tensile shock and excessive tension applied to the transmission band. It is.
Ｂ９発明の構成
（１１問題点を解決するための手段
本発明によれば、前記目的達成のため機関本体に支持さ
れる、駆動輪と被動輪間に無端状伝動帯を懸回し、該伝
動帯の緩み側にテンショナを圧接して該伝動帯に所定の
張力を付与するようにした、内燃機関における巻掛伝動
装置のテンショナ装置において、前記機関本体にプラン
ジャケースを設け、このプランジ中ケースに、前記テン
ショナに連結されるプランジャを摺合して前記プランジ
ャの下方に高圧油室を、またその内部に補給油室を形成
し、前記プランジャケースとプランジャとの摺合面間に
は、前記高圧油室内の高圧油の、前記補給油室へのリー
クを許容し得る摺動間隙を形成し、また前記高圧室内に
は、前記補給油室から該高圧室へのみ圧油の流れを許容
し得るチェック弁、および前記プランジャを伸長方向に
偏倚して前記テンションプーリを前記伝動帯に押圧する
緊張ばねを収容し、前記プランジ中には、加圧給油源に
連なる給油孔と、油溜に連なる排油孔とを穿設する。B9 Structure of the Invention (Means for Solving Problem 11) According to the present invention, in order to achieve the above object, an endless transmission band is suspended between a driving wheel and a driven wheel supported by an engine body, and the transmission band is In a tensioner device for a wrap transmission in an internal combustion engine, the tensioner is press-fitted to the slack side of the transmission band to apply a predetermined tension to the transmission band. A plunger connected to the tensioner is slid together to form a high-pressure oil chamber below the plunger and a replenishment oil chamber therein, and between the sliding surfaces of the plunger case and the plunger, there is a high-pressure oil chamber in the high-pressure oil chamber. a check valve that forms a sliding gap that allows high-pressure oil to leak into the replenishment oil chamber, and that is located in the high-pressure chamber and that allows pressure oil to flow only from the replenishment oil chamber to the high-pressure chamber; and a tension spring that biases the plunger in the extension direction and presses the tension pulley against the transmission band, and the plunge has an oil supply hole connected to a pressurized oil supply source and an oil drain hole connected to an oil sump. to be drilled.
（２）作 用
前記構成によれば、伝動帯にかかる引張衝撃や、その過
剰緊張を有効に吸収することができ伝動帯の耐久性を高
め、また伝動帯の効率のよい円滑、静粛な作動が保障さ
れる。(2) Function According to the above structure, the tensile impact applied to the transmission band and its excessive tension can be effectively absorbed, the durability of the transmission band can be increased, and the transmission band can operate efficiently, smoothly and quietly. is guaranteed.
（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実施例について説明する
。(3) Embodiments Hereinafter, embodiments in which the device of the present invention is implemented in a DOHC type four-stroke internal combustion engine will be described 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。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.
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。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５１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。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、その中間部の長孔９
１が案内軸１５に遊合されており、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。In FIGS. 1 to 3, between the driving pulley 3 and the other driven pulley 6, on the outside of the loose side 51 of the transmission belt 5,
A tension pulley 8 is provided, and 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 rocking lever 9 is pivotally supported on the end wall 13 of the engine body E with a support shaft 12 so as to be able to swing up and down, and is provided with a long hole 9 in the middle thereof.
1 is loosely engaged with the guide shaft 15, and the swing lever 9
A lubricating type auto adjuster A of the power transmission belt 5, which will be described in detail later, is connected to the tip of the belt. The tension pulley 8 is moved by the pressing force of the auto adjuster A to the transmission belt 5.
The belt 5 is pressed against the belt 5 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、テンションブーＩ７８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. The swing lever 9 is biased so as to swing counterclockwise around the support shaft 12, and the tension boob I78 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.
次にこの油圧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、
このプランジ中ケース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 hydraulic auto adjuster A will be mainly explained in the fifth section.
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 this plunge middle 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、それらの摺合面間にはシール部材は
介装されず、それらの間に摺動間隙Ｃが形成される。プ
ランジャ２３の開放上端２４にはプラグ２５が嵌着され
る。このプラグ２５の上部に形成した凹所２６にはスリ
ッパ部材２７がＯリング２９を介して嵌入され、このス
リッパ部材２７の頂面に効果処理を施したスリッパ面２
８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の下方には、その底壁
２３ｄと、プランジャケース２１とにより高圧油室３１
が形成され、またプランジャ２３内に補給油室３２が形
成される。Inside the plunger case 21, a plunger 23 is slidably movable up and down, no seal member is interposed between the sliding surfaces, and a sliding gap C is formed between them. A plug 25 is fitted into the open upper end 24 of the plunger 23. A slipper member 27 is fitted into the recess 26 formed in the upper part of the plug 25 via an O-ring 29, and the top surface of the slipper member 27 is treated with an effect.
8 is formed, 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. Below the plunger 23, a high pressure oil chamber 31 is formed by the bottom wall 23d and the plunger case 21.
is formed, and a replenishment oil chamber 32 is formed within the plunger 23.
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Ｏリング２２よりも下方において、プランジャケー
ス２１の側壁２１ｓには、給油孔３８が貫通して設けら
れ、この給油孔３８は、プランジャ２３の側壁２３Ｓに
穿設した油孔３９を介して補給油室３２に常時連通され
る。また前記給油孔３８は、アジャスタケース１７に穿
設した給油通路４０に連通される。Below the O-ring 22, an oil supply hole 38 is provided penetrating through the side wall 21s of the plunger case 21, and this oil supply hole 38 is supplied with oil through an oil hole 39 formed in the side wall 23S of the plunger 23. It is constantly communicated with the oil chamber 32. Further, the oil supply hole 38 communicates with an oil supply passage 40 formed in the adjuster case 17.
前記給油通路４０は前記油圧ポンプＰの吐出口４１ （
第６図）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 is connected to the discharge port 41 of the hydraulic pump P (
(Fig. 6). 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。このレギュ
レタＲは、下流側通路４０コ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. The regulator R includes a piston 46 that is slidably fitted into the downstream passage 40 to open and close the oil reservoir communication hole 44, and a spring 47 that biases the piston 46 toward the closing side. When the oil pressure within the spring 47 rises above a predetermined value, 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Ｏ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２１ｓ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間に形成されるリーク油室５１をハウジング１
９に形成した排油通路５０に連通しており、この排油通
路５０は機関本体Ｅ内の油溜４８（第６図）に連通され
る。Between the O-ring 22 and the oil supply hole 38, an oil drain hole 49 is bored in the side wall 21s on the plunger case 21 side. This oil drain hole 49 connects a leak oil chamber 51 formed between the plunger case 21 and the plunger 23 to the housing 1.
It communicates with an oil drain passage 50 formed at 9, and this oil drain passage 50 communicates with an oil reservoir 48 (FIG. 6) in the engine body E.
プランジャ２３の開放上端２４とプラグ２５との嵌合面
間にはリーク通路５６が形成され、このリーク通路５６
を通して補給油室３２はリーク油室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を通ってリーク油室５１に流れ、さらに該リ
ーク油室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。A leak passage 56 is formed between the open upper end 24 of the plunger 23 and the fitting surface of the plug 25.
The replenishment oil chamber 32 is communicated with the leak oil chamber 51 through the replenishment oil chamber 32, and the oil in the replenishment oil chamber 32 flows together with trapped air through the leak passage 56 to the leak oil chamber 51, and further from the leak oil chamber 51 to the leak oil chamber 51. Oil drain hole 49 and oil drain passage 50
The oil passes through the engine body E and is returned to the oil reservoir 48.
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
む際にハウジング１９の底部に形成される空室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 venting the air sealed in the cavity 57 formed at the bottom of the housing 19 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伸縮性ブーツ５３の下端が締付リ
ング５４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５
３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間の外部開放端を油密
に封緘しており、リーク油室５１内の油が外部に漏洩す
ることがない。The lower end of an elastic boot 53 formed 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 fitted around the outer periphery of the plug 25 in an oil-tight manner. And this boots 5
3 expands and contracts to follow the rise and fall of the plunger 23, and oil-tightly seals the external open end between the plunger case 21 and the plug 25, so that the oil in the leak oil chamber 51 does not leak to the outside.
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、および被動ブーＩＪ ４よりな
る調時巻掛伝動装置Ｔを介して７対の動弁カム軸２に伝
達される。When the engine is operated now, the rotation of the crankshaft 1 is transmitted to the seven pairs of valve drive camshafts 2 via a timing winding transmission T consisting of a drive pulley 3, a transmission belt 5, and a driven boot IJ 4. Ru.
前記伝動ベルト５の緩み側５１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 51 of 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 51 of the transmission belt 5. A constant tension is applied to the transmission belt 5.
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内には、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を通って密閉状リーク油室５１に至り、
そこから排油孔４９、排油通路５ｏ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、オートアジヤス°りＡおよび油溜４８間を流れる油
は機関本体Ｅの外部に漏洩することがなく、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
が供給される。The same oil as the lubricating oil of the engine is injected into the high pressure oil chamber 31 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. Also, the replenishment oil room 32
The oil inside passes through the leak passage 56 together with the trapped air sealed in the cough chamber 32 and reaches the sealed leak oil chamber 51.
From there, it passes through the oil drain hole 49 and the oil drain passage 5o to the engine body E.
The oil is refluxed into the oil sump 48 at the bottom. Therefore, the oil flowing between the hydraulic pump P, the auto adjuster A, and the oil reservoir 48 does not leak to the outside of the engine body E, and lubricating oil is constantly supplied to the replenishment oil chamber 32 of the auto adjuster A during engine operation. Ru.
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のずストン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を油溜４８に短絡し、該通路４０内の油圧を一
定に保つ。When the oil pressure in the oil supply passage 40 exceeds a predetermined value, the regulator R spring 46 retreats against the elastic force of the spring 47, and the oil sump communication hole 44 communicates with the oil supply passage 40. 40 is short-circuited to an oil sump 48 to keep the oil pressure in the passage 40 constant.
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
５Ｉ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. Thereby, the tension pulley 8 presses the loose side 5I of the transmission belt 5 inward, and applies 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への張力付与を助勢する。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５．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ブーＩ７８の後退を抑制する。During operation of the timing winding transmission T, the slack side 5 of the transmission belt 5 is caused by torque fluctuations acting on the crankshaft 1, valve drive camshaft 2, etc. When a tensile force is applied to , this tensile force acts to push back the tension pulley 8 and further acts 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 the oil from flowing back into the replenishment oil chamber 32. The hydraulic pressure inside the loose side of the transmission belt 5 5. By resisting the tensile force of , the tension boob I78 is prevented from retreating.
伝動ベルト５の緩み側５Ｉから引張力が解除されると、
緊張ばね３４の弾発作用によりプランジャ２３は再度上
昇し、揺動レバー９を介してテンションプーリ８が伝動
ベルト５の緩み側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。そしてプランジャ２３の上昇
により減圧する高圧油室３１内には補給油室３２内の油
が補給される。When the tensile force is released from the loose side 5I of the transmission belt 5,
The plunger 23 rises again due to the elastic action of the tension spring 34, and the tension pulley 8 presses the loose side 51 of the transmission belt 5 via the swing lever 9, applying a constant tension to the transmission belt 5 again, and the transmission is stopped. If the belt 5 has elongation, this can be compensated for. The oil in the replenishment oil chamber 32 is replenished into the high pressure oil chamber 31, which is depressurized by the rise of the plunger 23.
而して前記オートアジャスタＡの作動中において、機関
本体Ｅ周囲の温度変化等による伝動ベルト自体の縮みや
機関本体の熱膨張により駆、被動ブーＩＪ３．４の回転
軸間の距離の増大等に起因して伝動ベルト５に過大な引
張力が作用したり、また伝動ベルト５に何らかの原因に
よって引張衝撃が作用した場合には、オートアジャスタ
Ａのプランジャ２３は僅かに沈み込んで前記過大な引張
力や引張衝撃を以下の作用により有効に吸収することが
でき、伝動ベルト５にかかる過大な負荷を低減すること
ができる。すなわちアジャスタケース２１と、それに摺
合されるプランジ中２３間には積極的に摺動間隙Ｃが形
成されることにより、プランジ中２３に過大な押込方向
の負荷が作用したときには高圧油室３１内の高圧油が前
記摺動間隙Ｃより補給油室３２側へ漏洩して、プランジ
ャ２３は僅かに沈み込み、これによって伝動ベルト５に
かかる過剰緊張、引張衝撃が吸収される。Therefore, during the operation of the auto adjuster A, the distance between the rotation axes of the drive and driven boob IJ3.4 increases due to shrinkage of the transmission belt itself due to changes in the temperature around the engine body E, etc., and thermal expansion of the engine body. If this causes an excessive tensile force to act on the transmission belt 5, or if a tensile shock acts on the transmission belt 5 for some reason, the plunger 23 of the auto-adjuster A sinks slightly and removes the excessive tensile force. It is possible to effectively absorb the vibration and tensile impact by the following action, and the excessive load applied to the transmission belt 5 can be reduced. In other words, a sliding gap C is actively formed between the adjuster case 21 and the plunger 23 that slides thereon, so that when an excessive load in the pushing direction is applied to the plunger 23, the pressure inside the high-pressure oil chamber 31 is reduced. High-pressure oil leaks from the sliding gap C toward the supply oil chamber 32 side, and the plunger 23 sinks slightly, thereby absorbing excessive tension and tensile shock applied to the transmission belt 5.
またプランジャ２３の伸長時には、前述のように高圧油
室３１内には直ちに補給油室３２の加圧油が補給されて
高圧油室３１は所定の高圧に保たれ、オートアジャスタ
Ａは前記過大負荷の吸収作用があるにもかかわらず伝動
ベルト５の伸びに対する応答性が極めて良く、伝動ベル
ト５の張力か常に一定に保たれる。Furthermore, when the plunger 23 is extended, the pressurized oil from the supply oil chamber 32 is immediately replenished into the high pressure oil chamber 31 as described above, and the high pressure oil chamber 31 is maintained at a predetermined high pressure, and the auto adjuster A is activated by the overload. Despite the absorbing action, the transmission belt 5 has extremely good responsiveness to elongation, and the tension of the transmission belt 5 is always kept constant.
尚、前記実施例において、駆動プーリ３、被動プーリ４
、伝動ベルト５テンシッンプ−Ｉ７８および油圧ポンプ
Ｐは、それぞれ本発明における駆動輪、被動輪、伝動帯
、テンショナおよび加圧給油源を構成する。In the above embodiment, the driving pulley 3 and the driven pulley 4
, the transmission belt 5 tension I78, and the hydraulic pump P respectively constitute a driving wheel, a driven wheel, a transmission band, a tensioner, and a pressurized oil supply source in the present invention.
Ｃ６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
関本体にプランジャケースを設け、このプランジャケー
スに、前記テンショナに連結されるプランジャを摺合し
て前記プランジャの下方に高圧油室を、またその内部に
補給油室を形成し、前記プランジャケースとプランジャ
との摺合面間には、前記高圧油室内の高圧油の、前記補
給油室へのリークを許容し得る摺動間隙を形成し、また
前記高圧室内には、前記補給油室から該高圧室へのみ圧
油の流れを許容し得るチェック弁、および前記プランジ
ャを伸長方向に偏倚して前記テンションプーリを前記伝
動帯に押圧する緊張ばねを収容し、前記プランジャには
、加圧給油源に連なる給油孔と、油溜に連なる排油孔と
を穿設したので、伝動帯に過大な引張荷重や衝撃がかか
った場合にはオートアジャスタの僅かな沈み込み作用に
よって前記荷重、衝撃を吸収することができ、伝動帯に
無理な力をかけることなくその耐久性を高めることがで
きるとともに静粛で円滑軽快な巻掛伝動装置の作動を可
能にし、しかも前述の過大荷重、衝撃の吸収作用を保有
するにも拘らず高圧油室内には加圧油が直ちに補給され
て伝動帯の伸びに対する応答性は極めてよく該伝動帯に
一定の張力を付与することができ、巻掛伝動装置の伝動
効率が高められる。C6 Effects of the Invention As is clear from the above embodiments, according to the present invention, a plunger case is provided in the engine body, a plunger connected to the tensioner is slidably connected to the plunger case, and high-pressure oil is supplied below the plunger. A chamber and a replenishment oil chamber are formed therein, and a sliding gap is provided between the sliding surfaces of the plunger case and the plunger to allow leakage of high pressure oil in the high pressure oil chamber to the replenishment oil chamber. and a check valve in the high pressure chamber that allows pressure oil to flow only from the replenishment oil chamber to the high pressure chamber, and a check valve that biases the plunger in the extension direction to move the tension pulley to the transmission band. The plunger accommodates a tension spring for pressing, and has an oil supply hole connected to a pressurized oil supply source and an oil drain hole connected to an oil sump, so that if an excessive tensile load or impact is applied to the transmission band, The above-mentioned load and impact can be absorbed by the slight sinking action of the auto adjuster, increasing the durability of the transmission band without applying excessive force, and creating a quiet, smooth, and light wrap-around transmission device. In addition, despite having the above-mentioned overload and shock absorption function, pressurized oil is immediately replenished into the high-pressure oil chamber, and the response to the elongation of the transmission band is extremely good. A constant tension can be applied, and the transmission efficiency of the wrap transmission device is improved.
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ｍ−ｍ線に沿う拡大断面図、第４図は、第２図ｒ
Ｖ−ＩＶ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Ｖｌ
−Ｖｌ線に沿う゛アジャスタケースの断面図
Ｅ・・・機関本体、■・・・チェック弁、Ｐ・・・加圧
給油としての油圧ポンプ、Ｃ・・・摺動間隙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、８・・・
テンショナとしてのテンションプーリ、２１・・・プラ
ンジャケース、２３・・・プランジャ、３１・・・高圧
油室、３２・・・補給油室、３４・・・緊張ばね、３８
・・・給油孔、４８・・・油溜、４９・・・排油孔特
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
す
第４図
第５図
第６図
り。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 from the line ■ in FIG. 1, and FIG. The enlarged sectional view, Figure 4, is the same as Figure 2r.
5 is an enlarged sectional view taken along line V-V in FIG. 2, and FIG. 6 is a back view of the pump case taken along line V-IV.
- Cross-sectional view of the adjuster case along the Vl line E...Engine body, ■...Check valve, P...Hydraulic pump for pressurized oil supply, C...Sliding gap 3...Drive wheel 4... A driven pulley as a driven wheel, 5... A transmission belt as a transmission band, 8...
Tension pulley as tensioner, 21... Plunger case, 23... Plunger, 31... High pressure oil chamber, 32... Supply oil chamber, 34... Tension spring, 38
... Oil supply hole, 48 ... Oil sump, 49 ... Oil drain hole
Applicant: Honda Motor Co., Ltd. Tanaka Machine Co., Ltd. Figure 3, Figure 4, Figure 5, Figure 6.
Claims (1)
帯を懸回し、該伝動帯の緩み側にテンショナを圧接して
該伝動帯に所定の張力を付与するようにした、内燃機関
における巻掛伝動装置のテンショナ装置において、前記
機関本体にプランジャケースを設け、このプランジャケ
ースに、前記テンショナに連結されるプランジャを摺合
して前記プランジャの下方に高圧油室を、またその内部
に補給油室を形成し、前記プランジャケースとプランジ
ャとの摺合面間には、前記高圧油室内の高圧油の、前記
補給油室へのリークを許容し得る摺動間隙を形成し、ま
た前記高圧室内には、前記補給油室から該高圧室へのみ
圧油の流れを許容し得るチエック弁、および前記プラン
ジャを伸長方向に偏倚して前記テンションプーリを前記
伝動帯に押圧する緊張ばねを収容し、前記プランジャに
は、加圧給油源に連なる給油孔と、油溜に連なる排油孔
とを穿設したことを特徴とする内燃機関における巻掛伝
動装置のテンショナ装置。An internal combustion engine that is supported by an engine body and has an endless transmission band suspended between a driving wheel and a driven wheel, and a tensioner is pressed against the loose side of the transmission band to apply a predetermined tension to the transmission band. In the tensioner device for a wrap transmission device, a plunger case is provided in the engine body, and a plunger connected to the tensioner is slidably connected to the plunger case to provide a high pressure oil chamber below the plunger and supply the inside thereof. An oil chamber is formed, and a sliding gap is formed between the sliding surfaces of the plunger case and the plunger to allow leakage of high pressure oil in the high pressure oil chamber to the supply oil chamber, and contains a check valve that allows pressure oil to flow only from the supply oil chamber to the high pressure chamber, and a tension spring that biases the plunger in the extension direction and presses the tension pulley against the transmission band, A tensioner device for a wrap transmission in an internal combustion engine, wherein the plunger is provided with an oil supply hole connected to a pressurized oil supply source and an oil drain hole connected to an oil reservoir.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9191185A JPS61252952A (en) | 1985-04-29 | 1985-04-29 | Tensioner of entrained transmission of internal-combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9191185A JPS61252952A (en) | 1985-04-29 | 1985-04-29 | Tensioner of entrained transmission of internal-combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61252952A true JPS61252952A (en) | 1986-11-10 |
| JPH0438942B2 JPH0438942B2 (en) | 1992-06-26 |
Family
ID=14039761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9191185A Granted JPS61252952A (en) | 1985-04-29 | 1985-04-29 | Tensioner of entrained transmission of internal-combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61252952A (en) |
-
1985
- 1985-04-29 JP JP9191185A patent/JPS61252952A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0438942B2 (en) | 1992-06-26 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |