JP2724750B2 - Intake device for multi-cylinder internal combustion engine - Google Patents

Intake device for multi-cylinder internal combustion engine

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Publication number
JP2724750B2
JP2724750B2 JP17251189A JP17251189A JP2724750B2 JP 2724750 B2 JP2724750 B2 JP 2724750B2 JP 17251189 A JP17251189 A JP 17251189A JP 17251189 A JP17251189 A JP 17251189A JP 2724750 B2 JP2724750 B2 JP 2724750B2
Authority
JP
Japan
Prior art keywords
intake
valve
resonance
internal combustion
engine
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 - Fee Related
Application number
JP17251189A
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Japanese (ja)
Other versions
JPH0337325A (en
Inventor
康夫 北見
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
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Honda Motor Co Ltd
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Priority to JP17251189A priority Critical patent/JP2724750B2/en
Publication of JPH0337325A publication Critical patent/JPH0337325A/en
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Publication of JP2724750B2 publication Critical patent/JP2724750B2/en
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Expired - Fee Related legal-status Critical Current

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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、多気筒内燃機関において、吸気系内の吸気
圧力変動を制御することにより、前記機関の体積効率の
向上を図るようにした吸気装置の改良に関するものであ
る。
DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of the Invention The present invention is to improve the volumetric efficiency of a multi-cylinder internal combustion engine by controlling intake pressure fluctuation in an intake system in the engine. The present invention relates to an improvement of an air intake device in which

(2) 従来の技術 従来多気筒内燃機関の吸気装置において、機関の運転
状態に応じて吸気系の長さ、容積を可変制御することに
より吸気干渉を生じない気筒間の吸気圧力変動が共振す
る共鳴効果、あるいは各気筒毎において吸気開始時に生
じる負の圧力波が吸気系に設けられる容積拡大分配チャ
ンバで反射されて吸気ポート側に戻されることを利用し
た慣性効果を発揮させ、機関の低速から高速域まで体積
効率を高めるようにした吸気装置が既に種々提案されて
いる(例えば特開昭60−156930号公報参照)。
(2) Conventional technology In a conventional intake device for a multi-cylinder internal combustion engine, intake pressure fluctuation between cylinders that does not cause intake interference resonates by variably controlling the length and volume of the intake system according to the operating state of the engine. The resonance effect, or the inertial effect utilizing the fact that a negative pressure wave generated at the start of intake in each cylinder is reflected by the volume expansion distribution chamber provided in the intake system and returned to the intake port side, thereby exhibiting an inertia effect from the low speed of the engine. Various intake devices have been already proposed to increase the volumetric efficiency up to a high-speed range (for example, see Japanese Patent Application Laid-Open No. 60-156930).

上記吸気装置は、多気筒内燃機関の吸気系に設けた容
積拡大部と各気筒とを接続する分配管を前記容積拡大部
の外周を取り囲む如く配設するとともに、この分配管の
中間部と容積拡大部とを管長切換弁を介して短絡可能と
し、以て分配管の有効長さを長短切り換え可能としたも
のである。そして、機関の低速運転域で前記分配管の有
効長さを増加させて吸気系の固有振動数を減少させると
ともに、高速運転域で前記分配管の有効長さを減少させ
て吸気系の固有振動数を増加させ、機関の広い運転域に
おける慣性過給効果の向上が図られている。
In the intake device, a distribution pipe connecting each of the cylinders and a volume expansion section provided in an intake system of a multi-cylinder internal combustion engine is provided so as to surround an outer periphery of the volume expansion section, and a middle portion and a volume of the distribution pipe are provided. The enlargement section can be short-circuited via a pipe length switching valve, so that the effective length of the distribution pipe can be switched between long and short. In the low-speed operation range of the engine, the effective length of the distribution pipe is increased to reduce the natural frequency of the intake system, and in the high-speed operation range, the effective length of the distribution pipe is reduced to reduce the natural vibration of the intake system. By increasing the number, the effect of inertia supercharging in a wide operating range of the engine is improved.

(3) 発明が解決しようとする課題 しかしながら、上記従来の多気筒内燃機関の吸気装置
は、慣性過給系における通路長さを低速用および高速用
の2段階に切り換えるものであるため、機関の中速運転
域におけるトルクが減少し、これを防ぐために前記管長
切換弁の開閉制御に連動させてバルブタイミングの調整
を行っている。このために、吸気系の構造が複雑化かつ
大型化してコストが上昇するだけでなく、狭いエンジン
ルームへの機関のレイアウトの自由度が減少するという
問題が発生する。
(3) Problems to be Solved by the Invention However, the conventional intake device for a multi-cylinder internal combustion engine switches the passage length in an inertial supercharging system between two stages, one for low speed and one for high speed. In order to prevent the torque in the medium speed operation range from decreasing, the valve timing is adjusted in conjunction with the opening / closing control of the pipe length switching valve. For this reason, not only does the structure of the intake system become complicated and large, the cost increases, but also the degree of freedom in laying out the engine in a narrow engine room decreases.

本発明は、前述の事情に鑑みてなされたもので、共鳴
過給系と慣性過給系の切り換えと有効管長の切り換えが
可能であり、かつコンパクトで構造が簡単な吸気装置を
提供することを目的とする。
The present invention has been made in view of the above-described circumstances, and provides a compact and simple intake device capable of switching between a resonance supercharging system and an inertia supercharging system and switching an effective pipe length. Aim.

B.発明の構成 (1) 課題を解決するための手段 本発明によれば、前記目的を達成するため、容積拡大
部内を一対の共鳴チャンバに区画し、各共鳴チャンバ
は、その上流側を外気に通じる共鳴管に、その下流側を
吸気行程が連続しない気筒群に接続する複数の分配管に
連通し、さらに前記容積拡大部には、機関の運転状態に
応じて前記両共鳴チャンバ相互を連通し、あるいは遮断
するようにした開閉弁が設けられる多気筒内燃機関の吸
気装置において、前記分配管が前記容積拡大部の外周を
取り囲む如く配設されるとともに、この容積拡大部に接
する前記分配管の中間部に管長切換弁が設けられ、該管
長切換弁を開放制御することにより前記分配管の中間部
を前記容積拡大部に短絡することを特徴とする。
B. Configuration of the Invention (1) Means for Solving the Problems According to the present invention, in order to achieve the above object, the inside of the volume expansion section is partitioned into a pair of resonance chambers, and each resonance chamber has its upstream side open to the outside air. And a plurality of distribution pipes connecting the downstream side thereof to a group of cylinders whose intake strokes are not continuous with each other, and further communicates the two resonance chambers with each other in accordance with the operating state of the engine. Or an intake device for a multi-cylinder internal combustion engine provided with an on-off valve configured to shut off the air, wherein the distribution pipe is disposed so as to surround an outer periphery of the volume expansion section, and the distribution pipe is in contact with the volume expansion section. A pipe length switching valve is provided at an intermediate portion of the pipe, and the intermediate portion of the distribution pipe is short-circuited to the volume expansion section by opening control of the pipe length switching valve.

(2) 作用 前記特徴によれば、開閉弁および管長切換弁を共に閉
弁制御することにより、容積拡大部に形成した左,右共
鳴チャンバ相互の連通と該容積拡大部と分配管の連通が
遮断されて2系統の共鳴過給系が構成され、機関の低速
運転域における体積効率が向上する。開閉弁を開弁制御
すると、左,右共鳴チャンバが相互に連通することによ
り、前記2系統の共鳴過給系がキャンセルされて新たに
慣性過給系が構成され、機関の中速運転域における体積
効率が向上する。さらに開閉弁および管長切換弁を共に
開弁制御すると、分配管の中間部が容積拡大部に短絡し
てその有効長さが減少し、機関の高速運転域での体積効
率が向上する。
(2) Operation According to the above feature, by closing both the on-off valve and the pipe length switching valve, communication between the left and right resonance chambers formed in the volume expansion section and communication between the volume expansion section and the distribution pipe are achieved. The two systems are shut off to form a two-system resonance supercharging system, and the volume efficiency in the low-speed operation range of the engine is improved. When the on-off valve is controlled to open, the left and right resonance chambers communicate with each other, thereby canceling the two resonance supercharging systems and newly forming an inertial supercharging system. Volumetric efficiency is improved. Further, when both the on-off valve and the pipe length switching valve are controlled to open, the middle part of the distribution pipe is short-circuited to the volume expansion part, the effective length of which is reduced, and the volume efficiency in the high-speed operation range of the engine is improved.

そして、各分配管はその上流側に接続する容積拡大部
の外周を取り囲む如く配設されており、しかもこの容積
拡大部に接する前記分配管の中間部に管長切換弁が設け
られているので、容積拡大部および分配管が合理的に一
体化されて吸気系をコンパクトに形成することが可能と
なる。
Each distribution pipe is disposed so as to surround the outer periphery of the volume expansion section connected to the upstream side thereof, and furthermore, since a pipe length switching valve is provided at an intermediate portion of the distribution pipe contacting this volume expansion section, The volume expansion section and the distribution pipe are rationally integrated, and the intake system can be formed compact.

(3) 実施例 以下、図面により本発明の実施例を説明する。(3) Example Hereinafter, an example of the present invention will be described with reference to the drawings.

第1〜6図は本発明の一実施例を示すもので、第1図
は本発明装置を備えたV型6気筒内燃機関の要部縦断面
図、第2図はそのシリンダブロックの平面図、第3図、
第1図III−III線に沿う拡大部分平面図、第4図は、第
1図IV−IV線に沿う拡大部分平面図、第5図は、第4図
V−V線に沿う断面図、第6図は、第5図VI−VI線に沿
う断面図である。
1 to 6 show one embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a main part of a V-type six-cylinder internal combustion engine equipped with the device of the present invention, and FIG. 2 is a plan view of a cylinder block thereof. , FIG. 3,
FIG. 1 is an enlarged partial plan view along the line III-III, FIG. 4 is an enlarged partial plan view along the line IV-IV in FIG. 1, FIG. 5 is a cross-sectional view along the line VV in FIG. FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG.

第1,2図において、前記6気筒内燃機関の機関本体E
は、互いにV字型に配設される一対の左,右機関ブロッ
クBl,Brを備えており、左,右機関ブロックBl,Brは、そ
れぞれシリンダブロック1l,1rと、そのデッキ面に接合
されるシリンダヘッド2l、2rとを有し、左側シリンダブ
ロック1lには3つの左側気筒3l‥が直列に形成され、ま
た右側シリンダブロック1rにも、3つの気筒3r‥が直列
に形成されている。左側の3つの気筒3l‥は吸気行程の
連続しない、すなわち吸気弁10がオーバラップしない左
側気筒群Clを構成し、また右側の3つの気筒3r‥も吸気
行程の連続しない、すなわち後述の吸気弁10がオーバラ
ップしない右側気筒群Crを構成している。
1 and 2, an engine body E of the six-cylinder internal combustion engine is shown.
Has a pair of left and right engine blocks Bl, Br arranged in a V-shape with each other, and the left and right engine blocks Bl, Br are respectively joined to the cylinder blocks 11l, 1r and the deck surface thereof. The left cylinder block 11 has three left cylinders 3l # formed in series, and the right cylinder block 1r also has three cylinders 3r # formed in series. The three left cylinders 3l # constitute a left cylinder group Cl in which the intake strokes do not continue, that is, the intake valves 10 do not overlap, and the three right cylinders 3r # also have no consecutive intake strokes, that is, the intake valves described later. 10 constitute the right cylinder group Cr that does not overlap.

前記左,右気筒3l‥,3r‥には、それぞれ通常のよう
にピストン4が摺動自在に嵌合され、これらのピストン
4はコンロッド5を介してクランク軸6に連動される。
また前記左,右シリンダヘッド2l,2rには、それぞれピ
ストン4に対面する燃焼室7および該燃焼室7に連通す
る吸,排気ポート8,9が形成され、各吸気ポート8に
は、該ポート8が開閉する吸気弁10がそれぞれ設けら
れ、また各排気ポート9には、該ポート9を開閉する排
気弁11がそれぞれ設けられる。そして吸,排気弁10,11
は従来公知の動弁機構12により所定のタイミングを以て
開閉作動される。
Pistons 4 are slidably fitted to the left and right cylinders 3l, 3r, respectively, as usual, and these pistons 4 are interlocked with a crankshaft 6 via connecting rods 5.
A combustion chamber 7 facing the piston 4 and intake and exhaust ports 8 and 9 communicating with the combustion chamber 7 are formed in the left and right cylinder heads 21 and 2r, respectively. An intake valve 10 that opens and closes 8 is provided, and each exhaust port 9 is provided with an exhaust valve 11 that opens and closes the port 9. And intake and exhaust valves 10,11
Is opened and closed by a conventionally known valve mechanism 12 at a predetermined timing.

前記左,右シリンダヘッド2l,2rの複数の吸気ポート
8‥には、後に詳述する吸気系Inが接続され、また左,
右シリンダヘッド2l,2rの複数の排気ポート9‥には従
来公知の排気系(図示せず)が接続される。
A plurality of intake ports 8 # of the left and right cylinder heads 2l, 2r are connected to an intake system In, which will be described in detail later.
A conventionally known exhaust system (not shown) is connected to the plurality of exhaust ports 9 # of the right cylinder heads 21 and 2r.

次に第2〜6図を参照して前記吸気系Inの構成を詳細
に説明すると、この吸気系Inは前記左,右エンジンブロ
ック1l,1r間のV空間C内に配設され、エアクリーナAc
と、このエアクリーナAcの出口に接続される吸気通路Pi
と、該吸気通路Piの下流端に接続される左,右一対の共
鳴チャンバCr−l,Cr−rを有するボックス状の容積拡大
部Bgと、この容積拡大部Bgの外周に一体に形成され、前
記左,右シリンダブロック1l,1rの、吸気ポート8‥が
開口される端面に接合されて前記左,右共鳴チャンバCr
−l,Cr−rと、左,右気筒群Cl,Crとをそれぞれ連通す
る吸気マニホールドMiとよりなる。
Next, the configuration of the intake system In will be described in detail with reference to FIGS. 2 to 6. The intake system In is disposed in the V space C between the left and right engine blocks 11 and 1r, and the air cleaner Ac is provided.
And an intake passage Pi connected to an outlet of the air cleaner Ac.
And a box-shaped volume expansion portion Bg having a pair of left and right resonance chambers Cr-1 and Cr-r connected to the downstream end of the intake passage Pi, and integrally formed on the outer periphery of the volume expansion portion Bg. The left and right resonance chambers Cr are joined to end faces of the left and right cylinder blocks 11l and 1r where the intake ports 8 # are opened.
-L, Cr-r, and an intake manifold Mi that communicates the left and right cylinder groups Cl, Cr, respectively.

前記吸気通路Piは、第3図に示すようにエアクリーナ
Acに連なる上流側吸気通路14の下流端にスロットルボデ
ィ15を介して下流側吸気通路16が一体に接続して構成さ
れる。上流側吸気通路14はエアクリーナAcからの吸気を
吸入すべく中空筒状により構成され、スロットルボディ
ー15はその軸方向両端を前記上流側吸気通路14と下流側
吸気通路16にそれぞれボルト17‥,18‥で固着され、そ
の内部に操作部19により開閉制御されるスロットル弁20
が設けられる。
The intake passage Pi is provided with an air cleaner as shown in FIG.
A downstream intake passage 16 is integrally connected to a downstream end of the upstream intake passage 14 connected to Ac via a throttle body 15. The upstream intake passage 14 is formed in a hollow cylindrical shape to take in the intake air from the air cleaner Ac, and the throttle body 15 has bolts 17 ‥ and 18 at its axial ends at the upstream intake passage 14 and the downstream intake passage 16 respectively. Throttle valve 20 fixed by ‥ and controlled to open and close by operation unit 19 inside
Is provided.

前記下流側吸気通路16は、横断面方形状をなして機関
のクランク軸6方向に沿ってのびており、その内部は隔
壁21によって互いに並列する左,右分岐共鳴通路22l,22
rに仕切られている。この左,右分岐共鳴通路22l,22rの
下流端の左右両側には、前記共鳴チャンバCr−l,Cr−r
にそれぞれ連通する左,右連通口33l,33rが開口されて
おり、該連通口33l,33rの間には開閉弁23が設けられ
る。すなわち前記隔壁21には左,右共鳴チャンバCr−l,
Cr−rを連通する弁口24を開口した弁ホルダ25が設けら
れ、この弁ホルダ25には、下流側吸気通路16の軸方向に
沿ってのびる弁軸26が回動自在に支承され、この弁軸26
には、前記弁口24を開閉する矩形板状の弁体27がビス28
を以て固着されている。前記弁軸26の一端は弁ホルダ25
の端壁を貫通して下流側吸気通路16外に突出しており、
その突出端には、従来公知のアクチュエータ29が連結さ
れている。このアクチュエータ29は機関の運転状態に応
じて作動制御され、前記開閉弁23を開閉制御するように
なっており、たとえば機関の低速運転時には開閉弁23を
閉成し、またその中速および高速回転時には開閉弁23を
開放制御する。
The downstream side intake passage 16 has a rectangular cross section and extends along the direction of the crankshaft 6 of the engine. The inside of the downstream intake passage 16 is divided into left and right branch resonance passages 22l, 22
It is divided into r. On the left and right sides of the downstream ends of the left and right branch resonance passages 22l and 22r, the resonance chambers Cr-1 and Cr-r are provided.
The left and right communication ports 33l, 33r are respectively opened to communicate with each other, and the open / close valve 23 is provided between the communication ports 33l, 33r. That is, the partition 21 has left and right resonance chambers Cr-l,
A valve holder 25 having an opening 24 communicating with Cr-r is provided, and a valve shaft 26 extending in the axial direction of the downstream intake passage 16 is rotatably supported on the valve holder 25. Valve shaft 26
In addition, a rectangular plate-shaped valve body 27 for opening and closing the valve port 24 is provided with a screw 28.
It is fixed with. One end of the valve shaft 26 is a valve holder 25
Projecting out of the downstream intake passage 16 through the end wall of
A conventionally known actuator 29 is connected to the protruding end. The operation of the actuator 29 is controlled in accordance with the operating state of the engine, and the opening and closing of the on-off valve 23 is controlled. At times, the opening / closing valve 23 is controlled to open.

したがって、前記開閉弁23の閉成時には左,右分岐共
鳴通路22l,22rはそれぞれ前記連通口33l,33rを介して
左,右共鳴チャンバCr−l,Cr−rに各独立して連通して
2系統の共鳴過給系を構成する。また前記開閉弁23の開
弁時には、左,右共鳴チャンバCr−l,Cr−rが、前記弁
口24および前記左,右連通口33l、33rを介して連通し、
第3図および第5図に二点鎖線斜線で示す大なる容積の
慣性過給分配チャンバChが構成され1系統の慣性過給吸
気系が構成される。
Therefore, when the on-off valve 23 is closed, the left and right branch resonance passages 22l, 22r communicate with the left and right resonance chambers Cr-l, Cr-r independently via the communication ports 33l, 33r, respectively. Two resonance supercharging systems are configured. When the on-off valve 23 is opened, the left and right resonance chambers Cr-1, Cr-r communicate with each other through the valve port 24 and the left and right communication ports 33l, 33r,
In FIGS. 3 and 5, a large-volume inertial supercharging distribution chamber Ch indicated by a two-dot chain line and a diagonal line is formed, and one system of inertia supercharging intake system is formed.

第1,5図に示すように、容積拡大部Bgは前記下流側吸
気通路16が一体に形成された上下面開放の中間ケーシン
グ311、およびその上下に位置する下面開放の上部ケー
シング312と上面開放の下部ケーシング313の3つの部材
を重ね合わせて複数のボルト32‥で結合することにより
構成されている。
As shown in 1,5 figures, intermediate casing 31 1 of volume expanding portion Bg the downstream side intake passage 16 is formed integrally with the upper and lower surfaces open, and the upper casing 312 of the lower surface opening positioned above and below by overlapping three members of the lower casing 313 of the open top are configured by combining a plurality of bolts 32 ‥.

容積拡大部Bgの内部には、前記下流側吸気通路16の
左,右分岐共鳴通路22l,22rの下流にそれぞれ連通する
左,右共鳴チャンバCr−l,Cr−rが前記3個のケーシン
グ311,312,313にわたって形成されている。左,右共鳴
チャンバCr−l,Cr−rには、前記中間ケーシング311
下部ケーシング313の結合部においてそれぞれ3つの長
円形状をなす左,右排出ポート34l‥,34r‥が設けられ
ている(第3図参照)。そして左側共鳴チャンバCr−l
の3つの排出ポート34l‥は容積拡大部Bgの外周を略360
゜にわたって取り囲むように形成された3本の分配管35
1,353,355によって左側のシリンダブロック1lの吸気順
序が連続しない3つの気筒3lに連通するとともに、右側
共鳴チャンバCr−rの3つの排出ポート34r‥は容積拡
大部Bgの外周を同じく略360゜にわたって取り囲むよう
に形成された他の3本の分配管352,354,356によって右
側のシリンダブロック1rの吸気順序が連続しない3つの
気筒3rに連通している。すなわち、容積拡大部Bgの外周
には1本おきに交互に逆方向に巻き付くように配設され
た6本の分配管351〜356よりなる吸気マニホールドMiが
一体に形成され、その内部に前記一対の共鳴チャンバCr
−l,Cr−rが取り囲まれるように位置している。
Inside the volume expansion portion Bg, left and right resonance chambers Cr-1 and Cr-r communicating with the left and right branch resonance passages 22l and 22r of the downstream side intake passage 16 respectively are provided with the three casings 31. 1, 31 is formed over 2, 31 3. Left, right resonance chamber Cr-l, the Cr-r, the intermediate casing 31 1 and the left, respectively forming the three oblong in the coupling portion of the lower casing 313, the right exhaust ports 34l ‥, is 34r ‥ provided (See FIG. 3). And left resonance chamber Cr-1
The three discharge ports 34l ‥ of the outer circumference of the volume expansion portion Bg are approximately 360
Three distribution pipes 35 formed to surround over ゜
1 , 35 3 and 35 5 communicate with the three cylinders 3l in which the intake order of the left cylinder block 1l is not continuous, and the three discharge ports 34r # of the right resonance chamber Cr-r share the same outer circumference of the volume expansion portion Bg. communicates with the three cylinders 3r intake order of the right cylinder block 1r is not continuous with the other 3 distributing pipes 35 2, 35 4, 35 6 formed to surround substantially over 360 °. That is, the intake manifold Mi consisting six distributing pipes 35 1 to 35 6 disposed to wind around in opposite directions alternately in every other are formed integrally on the outer periphery of the volume expanding portion Bg, therein The pair of resonance chambers Cr
−l, Cr−r are positioned so as to be surrounded.

第4図〜第6図に示すように、上記第1〜第6分配管
351〜356と左,右共鳴チャンバCr−l,Cr−rとの境界部
には左右のバタフライ型の管長切換弁38l,38rが設けら
れる。すなわち、右側共鳴チャンバCr−rから下部ケー
シング313および中間ケーシング311を通って延びる3本
の分配管352,354,356の中間部は、上部ケーシング312
形成した弁口392,394,396を介して左側の共鳴チャンバC
r−lの上部に連通するとともに、左側共鳴チャンバCr
−lから下部ケーシング313および中間ケーシング311
通って延びる3本の分配管351,353,355の中間部は上部
ケーシング312に形成した弁口391,393,395を介して右側
の共鳴チャンバCr−rの上部に連通している。
As shown in FIG. 4 to FIG. 6, the above first to sixth distribution pipes
35 1-35 6 and the left and right resonance chambers Cr-l, the boundary between the Cr-r right butterfly type pipe length switching valve 38l, 38r is provided. That is, the intermediate portion of the right resonance chamber Cr-r from the lower casing 31 3 and of the intermediate casing 31 three extending through a distribution tube 35 2, 35 4, 35 6, valve port formed in the upper casing 31 2 39 2, 39 4, 39 of the left side 6 through the resonance chamber C
rl and the left resonance chamber Cr
Distributor pipe 35 1 of the three extending through the lower casing 31 3 and the intermediate casing 31 from 1 -l, 35 3, 35 middle part of the 5 valve ports 39 1 formed in the upper casing 31 2, 39 3, 39 5 Through the upper portion of the right resonance chamber Cr-r.

上部ケーシング312を貫通して回転自在に支持された
管長切換弁38l,38rの左右一対の弁軸40l,40rは、それぞ
れ左側の3個の弁口392,394,396と右側の3個の弁口3
91,393,395の中央を横切り、その位置において各弁口39
1〜396を開閉する弁体411〜416がビス42を以て固着され
る。両弁軸40l,40rの上部ケーシング312から突出する端
部はアクチュエータ43に接続されて管長切換弁38l,38r
を開閉制御するようになっており、たとえば機関の中速
回転域以下では管長切換弁38l,38rが閉弁制御され、前
記開閉弁23が開弁制御された状態にある高速回転域にお
いて前記管長切換弁38l,38rは開弁制御される。そし
て、前記一対の管長切換弁38l,38rを開弁制御すると、
各分配管351〜356の中間部が共通の慣性過給分配チャン
バChに連通して前記分配管351〜356の有効長さが減少す
るように管長切換が行われる。
Rotatably supported pipe length switching valve 38l through the upper casing 312, a pair of left and right valve shaft 40l of 38r, 40r includes three valve ports 39 2 of the left side, respectively, 39 4, 39 6 and right 3 valve openings 3
9 1 , 39 3 , 39 5 Cross the center of 5 and at that position each valve port 39
The valve body 41 1-41 6 for opening and closing the 1-39 6 is secured with a screw 42. Ryobenjiku 40 l, end which projects from the upper casing 31 and second 40r is connected to the actuator 43 by pipe length switching valve 38l, 38r
For example, the pipe length switching valves 38l and 38r are controlled to be closed below the medium speed rotation range of the engine, and the pipe length is controlled in a high speed rotation range where the opening and closing valve 23 is controlled to be opened. The switching valves 38l, 38r are controlled to open. When the pair of pipe length switching valves 38l and 38r are controlled to open,
Each intermediate portion of the distribution pipe 35 1-35 6 pipe length switching as effective length of the distribution pipe 35 1-35 6 communicates with a common inertial supercharging distribution chamber Ch is reduced is performed.

第1図に示すように第1〜第6分配管351〜356の下流
端の上壁にはそれぞれ燃料噴射ノズル44‥が設けられ
る。
Each fuel injection nozzle 44 in the upper wall of the downstream end of the first to sixth of the pipe 35 1 to 35 6 ‥ is provided as shown in Figure 1.

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 described.

機関の運転状態に応じて2個のアクチュエータ29,43
が作動制御され、たとえばその低速運転状態では第5図
に示すように開閉弁23と左右の管長切換弁38l,38rが共
に閉弁制御される。すると左,右共鳴チャンバCr−l,Cr
−r相互の連通が遮断され、吸気系として気筒群別の分
岐共鳴通路22l,22rと、気筒群別の左,右共鳴チャンバC
r−l,Cr−rと、気筒群別の左,右分配管351,352,353,3
54,355,356とからなる2系統の吸気系、すなわち各3つ
の気筒3l‥、3r‥から吸気通路Piの上流に至る吸気干渉
の生じない2系統の共鳴過給系が構成され、しかもこの
共鳴過給系はその通路長さが比較的長く、その固有振動
数は機関の低速回転域での各吸気弁10‥の開閉周期と略
一致させることができ共鳴過給効果を有効に発揮させて
機関の低速回転域での体積効率が高められる。
Two actuators 29, 43 according to the operating state of the engine
For example, in the low-speed operation state, both the on-off valve 23 and the left and right pipe length switching valves 38l, 38r are controlled to close as shown in FIG. Then left and right resonance chambers Cr-1 and Cr
-R is disconnected from each other, the branch resonance passages 22l and 22r for each cylinder group as the intake system, and the left and right resonance chambers C for each cylinder group.
r−l, Cr−r and left and right distribution pipes 35 1 , 35 2 , 35 3 , 3
Two intake systems consisting of 5 4 , 35 5 , and 35 6 , that is, two resonance supercharging systems that do not cause intake interference from the three cylinders 3 l ‥ and 3 r 上流 to the upstream of the intake passage Pi are configured. Moreover, this resonance supercharging system has a relatively long passage length, and its natural frequency can be made substantially coincident with the opening / closing cycle of each intake valve 10 ° in the low-speed rotation range of the engine, so that the resonance supercharging effect is effective. To increase the volumetric efficiency in the low-speed rotation range of the engine.

機関が中速運転状態になると、開閉弁23が第5図鎖線
に示すように開弁制御されて左,右共鳴チャンバCr−l,
Cr−rは相互に連通し、第5図二点鎖線斜線で示される
大なる容積の慣性過給分配チャンバChを形成し、該チャ
ンバChは左右の気筒3l‥と、3r‥とに共通に連通され
る。そしてこの状態では、前記2系統の共鳴過給系がキ
ャセルされ、機関吸気行程で生じる負圧波が前記大容積
の慣性過給分配チャンバChで反射、反転され、正圧波が
各気筒3l‥,3r‥の吸気ポート8に伝播されて慣性過給
系が構成され、しかも前記負圧波、および正圧波の伝播
する通路長さが短くなるため、吸気圧力周期が機関の中
速運転時の吸気弁10‥の開閉周期に一致して該中速運転
域での体積効率が高められる。
When the engine is in the medium speed operation state, the on-off valve 23 is controlled to open as shown by the chain line in FIG. 5, and the left and right resonance chambers Cr-1,
Cr-r communicates with each other to form a large-volume inertial supercharging distribution chamber Ch shown by a two-dot chain line in FIG. 5, and the chamber Ch is shared by the left and right cylinders 3l ‥ and 3r ‥. Communicated. In this state, the two resonance supercharging systems are cancelled, the negative pressure wave generated in the engine intake stroke is reflected and inverted by the large-volume inertial supercharging distribution chamber Ch, and the positive pressure waves are converted into the respective cylinders 3l ‥, 3r. The inertia supercharging system is constituted by being propagated to the intake port 8 of ‥, and the length of the passage through which the negative pressure wave and the positive pressure wave propagate is shortened. The volume efficiency in the medium speed operation range is increased in accordance with the opening / closing cycle of 高 め.

また機関が高速運転状態に至れば、更に管長切換弁38
l,38rが第5図鎖線に示すように開弁制御されて、共鳴
チャンバCr−lから延びる分配管351,353,355の中間部
が管長切換弁38rを介して前記慣性過給分配チャンバCh
に短絡するともに、共鳴チャンバCr−rから延びる分配
管352,354,356の中間部が管長切換弁38lを介して前記慣
性過給分配チャンバChに短絡する。したがって、前記慣
性過給分配チャンバChと左,右気筒群Cl,Crは分配管351
〜356の前記弁口391〜396よりも下流部分を介して接続
されて通路長さが最も短く、かつ固有振動数の大きい慣
性過給系が構成されることになり、吸気圧力周期を機関
の高速運転時の吸気弁10の開閉周期に一致させて該運転
域での体積効率を高めることができる。
Further, when the engine reaches a high-speed operation state, the pipe length switching valve 38 is further increased.
l, 38r is in the valve opening control as shown in FIG. 5 chain lines, the distribution pipe 35 1 which extends from the resonance chamber Cr-l, 35 3, 35 5 of the intermediate portion is the inertia supercharging via a pipe length changeover valve 38r Distribution chamber Ch
Both shorted to the intermediate portion of the distribution pipe 35 2, 35 4, 35 6 extending from the resonant chamber Cr-r is shorted to the inertia supercharging distribution chamber Ch via a pipe length changeover valve 38l. Therefore, the inertial supercharging distribution chamber Ch and the left and right cylinder groups Cl and Cr are connected to the distribution pipe 35 1.
35 6 is the shortest the valve ports 39 1 to 39 6 is connected via a downstream portion than in passage length of, and will be larger inertial supercharging system natural frequency is configured, the intake pressure cycle Can be matched with the opening / closing cycle of the intake valve 10 at the time of high-speed operation of the engine, and the volumetric efficiency in the operating region can be increased.

そして上記高速運転域において管長切換のために各分
配管351〜356の中間部が連通する容積拡大部として左,
右共鳴チャンバCr−l,Cr−r(すなわち、管長切換チャ
ンバCh)を利用しているので、管長切換のための特別に
容積拡大部を設ける必要がなくなり、吸気系の寸法をコ
ンパクトに形成することが可能となる。また、分配管35
1〜356が左,右共鳴チャンバCr−l,Cr−rの外周を取り
囲むように配設されており、この共鳴チャンバCr−l,Cr
−rに接する分配管351〜356の中間部に管長切換弁38l,
38rが設けられているので、吸気系全体が一層コンパク
トに形成される。
The left as the volume expanding portion of the intermediate portion of each distribution tube 35 1-35 6 for the pipe length switching in the high speed operating range are communicated,
Since the right resonance chambers Cr-1 and Cr-r (that is, the tube length switching chamber Ch) are used, it is not necessary to provide a specially enlarged volume for the tube length switching, and the dimensions of the intake system are made compact. It becomes possible. In addition, distribution pipe 35
1-35 6 left, right resonance chamber Cr-l, is disposed so as to surround the outer periphery of the Cr-r, the resonance chamber Cr-l, Cr
Pipe length switching valve 38l in the middle portion of the distributor pipe 35 1-35 6 in contact with -r,
Since the 38r is provided, the entire intake system is formed more compactly.

以上、本発明の実施例を詳述したが、本発明は前記実
施例に限定されるものではなく、特許請求の範囲に記載
された本発明を逸脱することなく種々の小設計変更を行
うことが可能である。
As described above, the embodiments of the present invention have been described in detail. However, the present invention is not limited to the above embodiments, and various small design changes can be made without departing from the present invention described in the claims. Is possible.

例えば、一方の共鳴チャンバから延びる分配管の中間
部を他方の共鳴チャンバに連通させる代わりに、同じ側
の共鳴チャンバに連通させてもよい。
For example, instead of connecting the middle part of the distribution pipe extending from one resonance chamber to the other resonance chamber, it may be connected to the resonance chamber on the same side.

C.発明の効果 以上のように本発明によれば、開閉弁によって互いに
連通可能な一対の共鳴チャンバを形成した容積拡大部を
備え、この容積拡大部と各気筒とをそれぞれ接続する分
配管を前記容積拡大部の外周を取り囲むように配設する
とともに、この分配管の中間部を管長切換弁によって容
積拡大部に短絡可能としたので、共鳴過給系と慣性過給
系の切り換えが可能となるだけでなく、慣性過給系の有
効管長をさらに2段階に切り換えることができる。した
がって、機関の低速、中速、高速の全ての運転域におい
て高い体積効率を得ることが可能となる。しかも前記容
積拡大部と分配管が合理的に一体化され、この容積拡大
部に開閉弁と管長切換弁が配設されるので吸気系全体の
寸法を極めてコンパクトに形成することができ、狭い空
間に対する内燃機関のレイアウトの自由度を増加させる
ことが可能となる。
C. Effects of the Invention As described above, according to the present invention, a volume expansion section is provided that forms a pair of resonance chambers that can communicate with each other by an on-off valve, and a distribution pipe that connects the volume expansion section to each cylinder is provided. It is arranged so as to surround the outer periphery of the volume expansion section, and the middle part of the distribution pipe can be short-circuited to the volume expansion section by the pipe length switching valve, so that it is possible to switch between the resonance supercharging system and the inertia supercharging system. Not only that, the effective pipe length of the inertial supercharging system can be further switched to two stages. Therefore, high volumetric efficiency can be obtained in all operating ranges of the engine at low, medium, and high speeds. In addition, the volume expansion portion and the distribution pipe are rationally integrated, and the opening / closing valve and the pipe length switching valve are provided in the volume expansion portion. , It is possible to increase the degree of freedom of the layout of the internal combustion engine with respect to.

【図面の簡単な説明】[Brief description of the drawings]

第1〜6図は本発明の一実施例を示すもので、第1図は
本発明装置を備えたV型6気筒内燃機関の要部縦断面
図、第2図はそのシリンダブロックの平面図、第3図は
第1図III−III線に沿う拡大部分平面図、第4図は、第
1図IV−IV線に沿う拡大部分平面図、第5図は、第4図
V−V線に沿う断面図、第6図は、第5図VI−VI線に沿
う断面図である。 Bg……容積拡大部、Cr−l,Cr−r……左,右共鳴チャン
バ、Cl,Cr……気筒群 22l,22r……共鳴管、23……開閉弁、351〜356……分配
管、38l,38r……管長切換弁
1 to 6 show one embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a main part of a V-type six-cylinder internal combustion engine equipped with the device of the present invention, and FIG. 2 is a plan view of a cylinder block thereof. FIG. 3 is an enlarged partial plan view along the line III-III in FIG. 1, FIG. 4 is an enlarged partial plan view along the line IV-IV in FIG. 1, and FIG. 5 is a line VV in FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG. Bg: Volume expansion part, Cr-1, Cr-r: Left and right resonance chambers, Cl, Cr: Cylinder groups 22l, 22r: Resonance tubes, 23: On-off valve, 35 1 to 35 6 ... Distribution pipe, 38l, 38r …… Pipe length switching valve

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項1】容積拡大部(Bg)内を一対の共鳴チャンバ
(Cr−l,Cr−r)に区画し、各共鳴チャンバ(Cr−l,Cr
−r)は、その上流側を外気に通じる共鳴管(22l,22
r)に、その下流側を吸気行程が連続しない気筒群(Cl,
Cr)に接続する複数の分配管(351〜356)に連通し、さ
らに前記容積拡大部(Bg)には、機関の運転状態に応じ
て前記両共鳴チャンバ(Cr−l,Cr−r)相互を連通し、
あるいは遮断するようにした開閉弁(23)が設けられる
多気筒内燃機関の吸気装置において、 前記分配管(351〜356)が前記容積拡大部(Bg)の外周
を取り囲む如く配設されるとともに、この容積拡大部
(Bg)に接する前記分配管(351〜356)の中間部に管長
切換弁(38l,38r)が設けられ、該管長切換弁(38l,38
r)を開放制御することにより前記分配管(351〜356
の中間部を前記容積拡大部(Bg)に短絡することを特徴
とする多気筒内燃機関の吸気装置。
The interior of a volume expansion section (Bg) is partitioned into a pair of resonance chambers (Cr-1, Cr-r), and each of the resonance chambers (Cr-1, Cr-r) is partitioned.
-R) is a resonance tube (221, 22) communicating with the outside air on the upstream side.
r), a cylinder group (Cl,
Communicating with the plurality of distribution pipes (35 1 to 35 6) connected to Cr), and more the volume expanding portion (Bg), in response to said operating state of the engine both resonance chambers (Cr-l, Cr-r ) Communicate with each other,
Or in the intake system of a multi-cylinder internal combustion engine Blocked way opening and closing valve (23) is provided, said distribution pipe (35 1 to 35 6) is arranged as surrounding an outer periphery of the volume expanding portion (Bg) with, pipe length changeover valve in an intermediate portion (38l, 38r) is provided in the volume expanding portion and the distribution pipe in contact with the (Bg) (35 1 ~35 6 ), tube length switching valve (38l, 38
said distribution pipe by opening control r) (35 1 ~35 6)
An intake device for a multi-cylinder internal combustion engine, wherein an intermediate portion of the internal combustion engine is short-circuited to the volume expansion portion (Bg).
JP17251189A 1989-07-04 1989-07-04 Intake device for multi-cylinder internal combustion engine Expired - Fee Related JP2724750B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP17251189A JP2724750B2 (en) 1989-07-04 1989-07-04 Intake device for multi-cylinder internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP17251189A JP2724750B2 (en) 1989-07-04 1989-07-04 Intake device for multi-cylinder internal combustion engine

Publications (2)

Publication Number Publication Date
JPH0337325A JPH0337325A (en) 1991-02-18
JP2724750B2 true JP2724750B2 (en) 1998-03-09

Family

ID=15943317

Family Applications (1)

Application Number Title Priority Date Filing Date
JP17251189A Expired - Fee Related JP2724750B2 (en) 1989-07-04 1989-07-04 Intake device for multi-cylinder internal combustion engine

Country Status (1)

Country Link
JP (1) JP2724750B2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112796872B (en) * 2020-12-21 2022-03-15 中国船舶重工集团公司第七一一研究所 Diesel engine system with resonant air intake

Also Published As

Publication number Publication date
JPH0337325A (en) 1991-02-18

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