JPH0649864Y2 - Intake device for V-type multi-cylinder internal combustion engine - Google Patents

Intake device for V-type multi-cylinder internal combustion engine

Info

Publication number
JPH0649864Y2
JPH0649864Y2 JP6474289U JP6474289U JPH0649864Y2 JP H0649864 Y2 JPH0649864 Y2 JP H0649864Y2 JP 6474289 U JP6474289 U JP 6474289U JP 6474289 U JP6474289 U JP 6474289U JP H0649864 Y2 JPH0649864 Y2 JP H0649864Y2
Authority
JP
Japan
Prior art keywords
valve
length switching
pipe
intake
switching 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.)
Expired - Lifetime
Application number
JP6474289U
Other languages
Japanese (ja)
Other versions
JPH035929U (en
Inventor
泰昭 浅木
康夫 北見
整男 柳本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP6474289U priority Critical patent/JPH0649864Y2/en
Publication of JPH035929U publication Critical patent/JPH035929U/ja
Application granted granted Critical
Publication of JPH0649864Y2 publication Critical patent/JPH0649864Y2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Description

【考案の詳細な説明】 A.考案の目的 (1)産業上の利用分野 本考案は、V型多気筒内燃機関において、吸気系の通路
長さを可変として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. Purpose of the Invention (1) Field of Industrial Application The present invention, in a V-type multi-cylinder internal combustion engine, controls the intake pressure fluctuation by making the passage length of the intake system variable.
The present invention relates to an improvement of an intake device that aims to improve the volumetric efficiency of the engine.

(2)従来の技術 従来多気筒内燃機関の吸気装置において、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
る容積拡大部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61−226515号公報参
照)。
(2) Related Art In an intake system of a conventional multi-cylinder internal combustion engine, it is used that a negative pressure wave generated at the start of intake in each cylinder is reflected by a volume expansion part provided in the intake system and returned to the intake port side. There have already been proposed various intake devices which exhibit the above-mentioned inertial effect and enhance the volumetric efficiency from the low speed to the high speed region of the engine (for example, see JP-A-61-226515).

上記吸気装置は、多気筒内燃機関の複数の気筒を各気筒
毎に独立した分配管を介して第1容積拡大部に連通し、
更にこの第1容積拡大部の上流をスロットル弁を介して
大気に連通するとともに、前記分配管の中間部を短い分
岐通路を介して第2容積拡大部に連通し、前記分岐通路
に機関の運転状態に応じて開閉制御される管長切換弁を
設けたものであり、前記管長切換弁を開放制御すること
により第2容積拡大部と各気筒を直線的な短い通路を介
して連通するように構成されている。
The above intake device communicates a plurality of cylinders of a multi-cylinder internal combustion engine with the first volume expanding section via independent distribution pipes for each cylinder,
Further, the upstream side of the first volume expanding section is connected to the atmosphere via a throttle valve, and the intermediate section of the distribution pipe is connected to the second volume expanding section via a short branch passage to operate the engine in the branch passage. A pipe length switching valve that is controlled to open and close according to the state is provided, and by controlling the opening of the pipe length switching valve, the second volume enlargement portion and each cylinder are made to communicate with each other through a straight short passage. Has been done.

しかして、機関の低速運転域で前記管長切換弁を閉鎖す
ることにより、各気筒から分配管の全長を介して第1容
積拡大部に連通する通路長さの長い慣性過給系を構成し
て機関の低速運転域での体積効率を向上させ、また機関
の高速運転域で前記管長切換弁を開放することにより、
各気筒から分配管の下流部分および前記分岐通路を介し
て第2容積拡大部に連通する通路長さの短い慣性過給系
を構成して機関の高速運転域での体積効率を向上させて
いる。そして、前記高速運転域において第2容積拡大部
と各気筒を直線的な通路を介して連通させることによ
り、圧力波の伝播速度を増加させて該高速運転域での体
積効率をより高い値に確保するようになっている。
Therefore, by closing the pipe length switching valve in the low speed operation range of the engine, an inertia supercharging system having a long passage communicating with each cylinder through the entire length of the distribution pipe to the first volume expanding portion is formed. By improving the volumetric efficiency in the low speed operation range of the engine, and by opening the pipe length switching valve in the high speed operation range of the engine,
An inertial supercharging system having a short passage communicating with the second volume expanding portion from each cylinder through the downstream portion of the distribution pipe and the branch passage is provided to improve the volumetric efficiency in the high speed operation range of the engine. . Then, in the high-speed operation range, the second volume expansion section and each cylinder are communicated with each other via a linear passage to increase the propagation speed of the pressure wave and to increase the volume efficiency in the high-speed operation range to a higher value. It is supposed to be secured.

(3)考案が解決しようとする課題 ところで上記従来の吸気装置は直列多気筒内燃機関に適
用されたものであり、V型多気筒内燃機関の狭いV空間
に前記吸気装置を配設するための特別の考慮はなされて
いない。
(3) Problem to be Solved by the Invention By the way, the above conventional intake system is applied to an in-line multi-cylinder internal combustion engine, and is for installing the intake system in a narrow V space of a V-type multi-cylinder internal combustion engine. No special consideration has been given.

本考案は、前述の事情に鑑みてなされたもので、多気筒
内燃機関の各気筒に接続する分配管の長さを管長切換弁
を介して可変とする吸気装置を、V型多気筒内燃機関の
狭いV空間内に合理的にレイアウトすることを目的とす
る。
The present invention has been made in view of the above-mentioned circumstances, and a V-type multi-cylinder internal combustion engine having an intake device in which the length of the distribution pipe connected to each cylinder of the multi-cylinder internal combustion engine is variable via a pipe length switching valve. The purpose is to rationally lay out in a narrow V space.

B.考案の構成 (1)課題を解決するための手段 本考案によれば、前記目的を達成するため、下流端が
左,右気筒群に各別に接続する複数の分配管と、機関の
運転状況に応じて開閉制御される管長切換弁を介して前
記分配管の中間部が連通する管長切換チャンバとをV型
空間に配設したV型多気筒内燃機関の吸気装置におい
て、前記分配管を逆U字状に湾曲させてその上部に前記
管長切換チャンバを設けるとともに、前記分配管の下流
側を直線的に左,右気筒群に接続し、且つ前記分配管の
湾曲部の外側壁面に前記管長切換チャンバに連通する開
口を形成することにより、管長切換チャンバと左,右気
筒群を直線的な通路を介して連通することを第1の特徴
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-mentioned object, a plurality of distribution pipes whose downstream ends are respectively connected to the left and right cylinder groups, and the operation of the engine. In a V-type multi-cylinder internal combustion engine intake device in which a pipe length switching chamber, which communicates with an intermediate portion of the distribution pipe through a pipe length switching valve that is controlled to open and close according to the situation, is arranged in a V-shaped space, It is curved in an inverted U shape and the pipe length switching chamber is provided on the upper part thereof, the downstream side of the distribution pipe is linearly connected to the left and right cylinder groups, and the outer wall surface of the curved portion of the distribution pipe is The first feature is that the pipe length switching chamber and the left and right cylinder groups are communicated with each other through a linear passage by forming an opening that communicates with the pipe length switching chamber.

また本考案は前記第1の特徴に加えて、前記開口にバタ
フライ型の弁体を有する管長切換弁を装着し、該開口を
開放して前記管長切換チャンバと左,右気筒群を接続す
る際、前記弁体を管長切換チャンバと左,右気筒群を結
ぶ通路と平行な位置へ回動させることを第2の特徴とす
る。
In addition to the first feature of the present invention, when a pipe length switching valve having a butterfly type valve body is attached to the opening and the opening is opened to connect the pipe length switching chamber to the left and right cylinder groups. The second feature is that the valve element is rotated to a position parallel to a passage connecting the pipe length switching chamber and the left and right cylinder groups.

(2)作用 前記第1の特徴によれば、機関の低速運転域で管長切換
弁を閉弁制御すると、各分配管と管長切換チャンバの連
通が遮断され、各分配管の全長が有効な吸気通路として
機能する。これにより、固有振動数の比較的小さな過給
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。一方、機関の高速運転域で管長切換弁を開弁制
御すると、各分配管はその中間部に形成した開孔を介し
て管長切換チャンバに連通する。これにより、固有振動
数の比較的大きな過給系が構成され、機関の高速運転域
におけむる積効率が向上する。
(2) Operation According to the first feature, when the pipe length switching valve is controlled to be closed in the low speed operation range of the engine, the communication between the respective distribution pipes and the pipe length switching chamber is cut off, and the entire length of each distribution pipe is effectively intake. Functions as a passage. As a result, a supercharging system having a relatively small natural frequency is formed, and the volumetric efficiency in the low speed operation range of the engine is improved. On the other hand, when the pipe length switching valve is controlled to open in the high speed operation region of the engine, each distribution pipe communicates with the pipe length switching chamber through the opening formed in the intermediate portion. As a result, a supercharging system having a relatively large natural frequency is formed, and the product efficiency in the high speed operation range of the engine is improved.

そして、逆U字状に湾曲させた分配管の上部に管長切換
チャンバを設けることによりV空間のスペースの有効利
用が図られ、しかも前記分配管の下流側を直線的に左,
右気筒群に接続し、且つ前記分配管の湾曲部の外側壁面
に前記管長切換チャンバに連通する開口を形成して管長
切換チャンバと左,右気筒群をストレートな通路を介し
て連通させることにより、圧力波の伝播速度を増加させ
て体積効率の向上を図ることができる。
By providing a pipe length switching chamber on the upper portion of the distribution pipe curved in an inverted U shape, the space in the V space can be effectively utilized, and the downstream side of the distribution pipe is linearly left,
By connecting to the right cylinder group and forming an opening in the outer wall surface of the curved portion of the distribution pipe that communicates with the pipe length switching chamber, the pipe length switching chamber and the left and right cylinder groups are communicated via a straight passage. The volumetric efficiency can be improved by increasing the propagation speed of the pressure wave.

また本考案の第2の特徴によれば、前記開口を開閉する
弁体をバタフライ型とし、その開成位置において該弁体
が管長切換チャンバと各気筒を結ぶ通路と平行な位置へ
回動させているので、高速運転域での管長切換チャンバ
と各気筒間の圧力波の伝播がスムーズに行われ、より高
い体積効率が確保される。
According to a second feature of the present invention, the valve body that opens and closes the opening is of a butterfly type, and in its open position, the valve body is rotated to a position parallel to a passage connecting the pipe length switching chamber and each cylinder. Therefore, the pressure wave is smoothly propagated between the pipe length switching chamber and each cylinder in the high speed operation range, and higher volume efficiency is secured.

(3)実施例 以下、図面により本考案の実施例を説明する。(3) Embodiment An embodiment of the present invention will be described below with reference to the drawings.

第1〜7図は本考案の一実施例を示すもので、第1図は
本考案装置を備えた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、第7図は、第5図VII−VII線に沿う断
面図である。
1 to 7 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a main part of a V-type 6 cylinder internal combustion engine equipped with the device of the present invention, and FIG. 2 is a plan view of its cylinder block. 3 is an enlarged partial plan view taken along the line III-III in FIG. 1, FIG. 4 is an enlarged partial plan view taken along the line IV-IV in FIG. 1, and FIG.
FIG. 4 is a cross-sectional view taken along the line VV, FIG. 6 is FIG.
Sectional drawing which follows the line, FIG. 7 is sectional drawing which follows the VII-VII line 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1,1r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1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。
In FIGS. 1 and 2, the engine body E of the 6-cylinder internal combustion engine is shown.
Is equipped with a pair of left and right engine blocks Bl, Br which are arranged in a V shape with each other. The left and right engine blocks Bl, Br are respectively joined to the cylinder blocks 1, 1r and their deck surfaces. , Which have three cylinders 2l, 2R, three left cylinders 3l are formed in series in the left cylinder block 1, and three cylinders 3r are also formed in the right cylinder block 1r.
Are formed in series. The three left cylinders 3l ... constitute a left cylinder group Cl in which the intake stroke is not continuous, that is, the intake valves 10 do not overlap, and the three right cylinders 3r ...
Also constitutes the right cylinder group Cr in which the intake stroke is not continuous, that is, the intake valves 10 described later do 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,I1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 in the left and right cylinders 3l ..., 3r ... as usual, respectively.
Is linked to the crankshaft 6 via the connecting rod 5. Further, the left and right cylinder heads 2l and 2r are respectively formed with a combustion chamber 7 facing the piston 4 and intake and exhaust ports 8 and 9 communicating with the combustion chamber 7, and each intake port 8 has
An intake valve 10 for opening and closing the port 8 is provided, and an exhaust valve 11 for opening and closing the port 9 is provided for each exhaust port 9.
Are provided respectively. The intake / exhaust valves 10 and I1 are opened / closed at a predetermined timing by a conventionally known valve operating mechanism 12.

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
シリンブヘッド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。
Intake ports 8 of the left and right cylinder heads 2l, 2r
An intake system In, which will be described in detail later, is connected to ... And a conventionally known exhaust system (not shown) is connected to the plurality of exhaust ports 9 of the left and right cylinder heads 2l and 2r.

次に第2〜7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1,1r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、前記左,右シリンダブロック1,1r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 structure of the intake system In will be described in detail with reference to FIGS. 2 to 7. The intake system In is disposed in the V space C between the left and right engine blocks 1 and 1r, and the air cleaner Ac
And the intake passage Pi connected to the outlet of this air cleaner Ac.
A box-shaped volume expansion portion Bg having a pair of left and right resonance chambers Cr-l, Cr-r connected to the downstream end of the intake passage Pi, and intake air of the left and right cylinder blocks 1, 1r. The left and right resonance chambers Cr-l, Cr-r are joined to the end faces where the ports 8 are opened, and the intake manifold Mi for communicating 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 Ac as shown in FIG.
At the downstream end of the upstream intake passage 14
A downstream side intake passage 16 is integrally connected via 15. The upstream intake passage 14 is formed of a hollow cylinder to suck intake air from the air cleaner Ac, and has a throttle body.
The axial end of 15 is fixed to the upstream intake passage 14 and the downstream intake passage 16 by bolts 17, ..., 18, respectively, and a throttle valve 20 whose opening / closing is controlled by an operating portion 19 is provided inside thereof.

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,22r
に仕切られている。そして前記左,右分岐共鳴通路22l,
22rの上流端は、前記スロットルボディ15に接続され
る。前記下流側吸気通路16の下流側寄りにおいて、前記
隔壁21には、開閉弁23が設けられる。すなわち前記隔壁
21には左,右分岐共鳴通路22l,22r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, and the inside thereof is a partition wall.
Left and right branch resonance passages 22l, 22r parallel to each other by 21
It is divided into The left and right branch resonance passages 22l,
The upstream end of 22r is connected to the throttle body 15. An opening / closing valve 23 is provided in the partition wall 21 near the downstream side of the downstream side intake passage 16. That is, the partition wall
21 is provided with a valve holder 25 that opens a valve port 24 that communicates the left and right branch resonance passages 22l, 22r.
A valve shaft 26 extending along the axial direction of the downstream side intake passage 16 is rotatably supported, and a rectangular plate-shaped valve body 27 for opening and closing the valve port 24 is fixed to the valve shaft 26 with screws 28. ing. One end of the valve shaft 26 penetrates the end wall of the valve holder 25 and projects to the outside of the downstream side intake passage 16, and a conventionally known actuator 29 is connected to the projecting end. The actuator 29 is actuated and controlled according to the operating state of the engine to open / close the opening / closing valve 23. The on-off valve 23 is sometimes controlled to open.

前記下流側吸気通路16の左右両側には、該吸気通路16を
挟むようにして容積拡大部Bgの左,右共鳴チャンバCr−
l,Cr−rが、該下流側吸気通路16と並列して一体に形成
される。
On the left and right sides of the downstream side intake passage 16, the left and right resonance chambers Cr- of the volume expansion part Bg are arranged so as to sandwich the intake passage 16.
l, Cr-r are formed integrally in parallel with the downstream side intake passage 16.

第1,5図に示すように左,右共鳴チャンバCr−l,Cr−r
および前記下流側吸気通路16は前記マニホールドMiの下
部に複数のボルト32…で結合された箱状体31よりなる容
積拡大部Bgの内部に一体に形成される。下流側吸気通路
16の下流端において、その左右両側には、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が開口されている。そして、該左,右連通口33l,33r
は、前記弁口24の近傍位置にあって、該弁口24の両側に
対面するように並列される。
As shown in Figs. 1 and 5, the left and right resonance chambers Cr-l, Cr-r
Also, the downstream side intake passage 16 is integrally formed inside the volume expansion portion Bg including the box-shaped body 31 connected to the lower portion of the manifold Mi by a plurality of bolts 32. Downstream intake passage
At the downstream end of 16, on the left and right sides thereof, left and right communication ports 33l, which communicate with the resonance chambers Cr-l, Cr-r, respectively.
33r is opened. And the left and right communication ports 33l, 33r
Are arranged in the vicinity of the valve opening 24 and are arranged in parallel so as to face both sides of the valve opening 24.

前記弁体27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に各独立して連通するようになってお
り、2系統の共鳴過給吸気系を構成する。
When the valve body 27 is closed, the left and right branch resonance passages 22l and 22r are independently connected to the left and right resonance chambers Cr-l and Cr-r through the communication ports 33l and 33r, respectively. And forms two resonance supercharged intake systems.

また前記弁体27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,33
rを介して連通し、第3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。
When the valve body 27 is opened, the left and right resonance chambers Cr-
l, Cr-r is the valve port 24 and the left and right communication ports 33l, 33
A large volume inertial supercharging distribution chamber Ch shown by a two-dot chain line diagonal line in FIG.

前記左,右共鳴チャンバCr−l,Cr−rの上壁には、その
長手方向に沿ってそれぞれ3つの長円形状をなす左,右
排出ポート34l…,34r…が開口される。そして左側共鳴
チャンバCr−lの3つの排出ポート34l…は、後述する
吸気マニホールドMiを介して左側共鳴チャンバCr−lと
は反対側に位置する右側シリンダブロック1rの3つの気
筒3r…(吸気順序が連続しない)にそれぞれ連通され、
同じく右側共鳴チャンバCr−rの3つの排出ポート34r
…は、後述する吸気マニホールドMiを介して右側共鳴チ
ャンバCr−rとは反対側に位置する左側シリンダブロッ
ク1の3つの気筒3l…(吸気順序が連続しない)にそ
れぞれ連通される。
On the upper walls of the left and right resonance chambers Cr-l, Cr-r, three left and right exhaust ports 34l ..., 34r ... Each having an oval shape are opened along the longitudinal direction thereof. The three exhaust ports 34l of the left resonance chamber Cr-1 are connected to the three cylinders 3r of the right cylinder block 1r located on the opposite side of the left resonance chamber Cr-1 via an intake manifold Mi described later (intake order). Are not continuous),
Similarly, three exhaust ports 34r of the right resonance chamber Cr-r
Are communicated with three cylinders 3l of the left cylinder block 1 located on the opposite side of the right resonance chamber Cr-r (intake order is not continuous) via an intake manifold Mi described later.

第4〜7図に示すように前記吸気マニホールドMiは、上
流側が上方に凸に彎曲し下流側が概略直線状をなす6本
の第1〜第6分配管351〜356が下流側吸気通路16および
左,右共鳴チャンバCr−l,Cr−rの長手方向と略直交す
る方向に一体に並設されて交互に逆方向に交差して左右
にのびており、これらのうち一つ置きの3つの第2,第4
および第6分配管352,354および356の上流端は左側共
鳴チャンバCr−lの3つの排出ポート34l…にそれぞれ
連通されたのち前記共鳴チャンバCr−lと反対側にのび
てそれらの下流端が右側シリンダブロック1rの3つの気
筒3r…にそれぞれ連通され、また残りの、一つ置きの3
つの第1,第3および第5分配管351,353および355の上
流端は右側共鳴チャンバCr−rの3つの排出ポート34r
…にそれぞれ連通さそれたのち前記共鳴チャンバCr−r
と反対側にのび、それらの下流端が左側シリンダブロッ
ク1の3つの気筒3l…にそれぞれ連通される。
As shown in FIGS. 4 to 7, in the intake manifold Mi, the six first to sixth distribution pipes 35 1 to 35 6 in which the upstream side is curved upwardly and the downstream side is substantially linear are the downstream side intake passages. 16 and the left and right resonance chambers Cr-l, Cr-r are arranged side by side in a direction substantially orthogonal to the longitudinal direction and alternately intersect in opposite directions and extend left and right. Second, fourth
And sixth minutes pipe 35 2, 35 4 and 35 upstream ends of 6 extends on the opposite side of the resonance chamber Cr-l after passed through each communicating three exhaust ports 34l ... to the left resonance chamber Cr-l thereof The downstream end communicates with each of the three cylinders 3r ... of the right cylinder block 1r.
One of the first, third and fifth minute pipe 35 1, 35 3 and 35 of the upstream end of the 5 three right resonance chamber Cr-r exhaust port 34r
, Respectively, and then the resonance chamber Cr-r
To the three cylinders 3l ... Of the left cylinder block 1 respectively.

吸気マニホールドMiの上面には複数のボルト36…により
カバー37が固着され、6本の第1〜第6分配管351〜356
の彎曲する上面外側壁との間に管長切換チャンバCcが形
成される。上記第1〜第6分配管351〜356と管長切換チ
ャンバCcとの境界部にはバタフライ型の左右の管長切換
弁38l,38rが設けられる。すなわち、第1〜第6分配管3
51〜356の彎曲部の下流端、かつ彎曲方向外側の壁面に
は分配管351〜356の開口としての弁口391〜396が開設さ
れており、左側共鳴チャンバCr−lから延びる3本の分
配管352,354,356に形成した弁口392,394,396は前記
管長切換チャンバCcの下面右側に連通するとともに、右
側共鳴チャンバCr−rから延びる3本の分配管351,3
53,355に形成した弁口391,393,395は前記管長切換チ
ャンバCcの下面左側に連通する。吸気マニホールドMiの
両側を貫通して回転自在に指示された左右一対の弁軸40
l,40rは、それぞれ左側の3個の弁口391,393,395と右
側の3個の弁口392,394,396の中央を横切り、その位
置において各弁口391〜396を開閉する弁体411〜416がビ
ス42を以て固着される。第4図から明らかなように、前
記弁体411〜416は楕円形形状の板体よりなり、その短軸
を前記弁軸40l,40rの方向に一致させた状態で固着され
る。両弁軸40l,40rの吸気マニホールドMi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,38
r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、
高速回転域では開弁制御されるようになっている。
A cover 37 is fixed to the upper surface of the intake manifold Mi by a plurality of bolts 36, and the six first to sixth distribution pipes 35 1 to 35 6
A tube length switching chamber Cc is formed between the curved upper outer wall and the outer wall. The first to sixth of the pipe 35 1-35 6 and pipe length switching chamber Cc tube length of the right and left of the butterfly type in the boundary portion between the switching valve 38l, 38r is provided. That is, the first to sixth distribution pipes 3
5 1-35 6 downstream end of the curved portion of, and the wall surface of the curved outward and valve port 39 1 to 39 6 as the opening of the distributor pipe 35 1-35 6 is opened, the left resonance chamber Cr-l with 3 distributing pipes 35 2, 35 4, 35 valve port 39 formed in the 6 2, 39 4, 39 6 communicates with the lower surface right of the pipe length switching chamber Cc extending from, extending from the right resonance chamber Cr-r Three distribution pipes 35 1 , 3
5 3, 35 5 valve port 39 1 formed in, 39 3, 39 5 communicates with the lower surface left side of the pipe length switching chamber Cc. A pair of left and right valve shafts 40 rotatably instructed to penetrate both sides of the intake manifold Mi
l and 40r cross the center of each of the three valve openings 39 1 , 39 3 , 39 5 on the left side and the three valve openings 39 2 , 39 4 , 39 6 on the right side, and each valve opening 39 1 at that position. the valve body 41 1-41 6 for opening and closing the ~ 39 6 are fixed with a screw 42. As is clear from FIG. 4, the valve bodies 41 1 to 4 16 are made of elliptical plate bodies and are fixed in a state where their short axes are aligned with the directions of the valve shafts 40l and 40r. The ends of both valve shafts 40l, 40r projecting from the intake manifold Mi are connected to an actuator 43, and pipe length switching valves 38l, 38
It is designed to open and close r, and for example, pipe length switching valves 38l, 38r are controlled to be closed in the medium speed range of the engine or lower,
The valve opening is controlled in the high speed rotation range.

第5図から明らかなように、前記弁口391〜396の中央を
通過する弁軸40l,40rは分配管351〜356の彎曲した外側
壁の概略延長線上に位置しており、弁体411〜416は実線
で示す閉鎖位置において前記弁口391〜396を形成するた
めに切り取られた分配管351〜356の外側壁を補うように
配設されている。これにより、弁体411〜416が閉成した
とき、分配管351〜356の断面積が弁口391〜396の部分で
急変しないように構成されている。また、弁体411〜416
が鎖線で示す開放位置にあるとき、分配管351〜356の概
略直線状をなす下流側と管長切換チャンバCcは直線的な
通路を介して接続されるように形成されている。
As it is apparent from Figure 5, the valve port 39 1 to 39 the valve shaft passing through the center of the 6 40 l, 40r are located on schematic extension distributing pipes 35 1 to 35 6 curved outer wall, the valve body 41 1-41 6 is arranged to compensate for the distributor pipe 35 1-35 6 outer wall of which is cut away to form the valve port 39 1 to 39 6 in the closed position shown by solid lines. Thus, when the valve body 41 1-41 6 is closed, the cross-sectional area of the distributor pipe 35 1-35 6 is configured not to sudden change in the portion of the valve ports 39 1 to 39 6. Also, the valve bodies 41 1 to 4 16
There when in the open position shown by a chain line, downstream and pipe length switching chamber Cc forming the distributor pipe 35 1-35 6 schematically straight is formed so as to be connected via a straight path.

第1図および第4図に示すように第1〜第6の分配管35
1〜356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。
As shown in FIGS. 1 and 4, the first to sixth distribution pipes 35
Each of the upper wall of the 1-35 6 downstream end of the fuel injection nozzle 44 ...
Is provided.

次に本考案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個のアクシュエータ29,43が
作動制御され、たとえばその低速運転状態では左右の管
長切換弁38l,38rが第5図実線に示すように閉弁制御さ
れるとともに、開閉弁23が第3図実線に示すように閉弁
制御される。すると下流側吸気通路16の左,右分岐共鳴
通路22l,22r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Cr−l,Cr−rと、気筒群別の左,右分配管351,3
52,353,354,355,356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。
The two actuators 29, 43 are actuated and controlled according to the operating state of the engine. For example, in the low speed operating state, the left and right pipe length switching valves 38l, 38r are closed and controlled as shown by the solid line in FIG. The on-off valve 23 is controlled to be closed as shown by the solid line in FIG. Then, the communication of the left and right branch resonance passages 22l, 22r of the downstream side intake passage 16 is cut off, and the branch resonance passages 22l, 22r for each cylinder group as an intake system and the left and right resonance chambers Cr-l for each cylinder group are provided. Cr-r and left and right distribution pipes 35 1 , 3 for each cylinder group
Two intake systems consisting of 5 2 , 35 3 , 35 4 , 35 5 , and 35 6 , that is, two resonances from each of the three cylinders 3l ..., 3r ... to the upstream of the intake passage Pi without intake interference. A supercharging system is configured, and the resonance supercharging system has a relatively long passage length, and its natural frequency is that of each intake valve 10 in the low speed rotation range of the engine.
The opening and closing cycle of ... Can be made substantially coincident with each other, the resonance supercharging effect can be effectively exhibited, and the volume efficiency in the low speed rotation range of the engine can be enhanced.

また上述の管長切換弁38l,38rが閉弁制御された状態で
は、その弁口391〜396を閉鎖する弁体411〜416が分配管
351〜356の外壁の一部を構成するため、該分配管351〜3
56に断面積の急変部が生じることがない。したがって、
圧力波の減衰が防止されるとともに吸気のスムーズに流
れが確保されて体積効率の増加が可能となる。
The above-mentioned pipe length changeover valve 38l, in the state in which 38r is closed controlled valve 41 1-41 6 distributor pipe to close the valve port 39 1 to 39 6
For constituting a part of the outer wall 35 1-35 6,該分pipe 35 1-3
No sudden change in cross-sectional area occurs at 5 6 . Therefore,
Attenuation of pressure waves is prevented, and a smooth flow of intake air is ensured, so that volumetric efficiency can be increased.

機関が中速運転状態になると、開閉弁23が第3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3図二点鎖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. 3, and the left and right resonance chambers Cr-l, Cr
-R communicates with each other to form a large volume inertial supercharging distribution chamber Ch indicated by a chain double-dashed line in FIG.
Are commonly communicated with the left and right cylinders 3l ... and 3r. Then, in this state, the two resonance supercharging systems are capsulated, 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 wave is generated in each cylinder 3l.
, 3r ... Inertial supercharging system is formed by propagating to the intake port 8 and the passage length of the negative pressure wave and the positive pressure wave is shortened. The volume efficiency in the medium speed operation range is increased in accordance with the opening / closing cycle of the intake valves.

また機関が高速運転状態に到れば、更に管長切換弁38l,
38rが第5図鎖線に示すように開弁制御されて、気筒群C
lに接続する分配管351,353,355の中間部が弁口391,3
93,395を介して管長切換チャンバCcに連通するととも
に、気筒群Crに接続する分配管352,354,356の中間部
が弁口392,394,396を介して管長切換チャンバCcに連
通する。そして前記管長切換チャンバCcは分配管351〜3
56の上流側を介して前記慣性過給分配チャンバChに挿通
して拡張された慣性過給分配チャンバCh′を構成する
(第5図二点鎖線参照)。したがって上記拡張された慣
性過給分配チャンバCh′と左,右気筒群Cl,Crは分配管3
51〜356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。
When the engine reaches high speed operation, the pipe length switching valve 38l,
The valve opening of 38r is controlled as shown by the chain line in FIG.
The intermediate parts of the distribution pipes 35 1 , 35 3 , 35 5 connected to l are valve ports 39 1 , 3
9 3, 39 5 communicates with the pipe length switching chamber Cc through the middle portion of the distribution pipe 35 2, 35 4, 35 6 to connect to the cylinder groups Cr via the valve port 39 2, 39 4, 39 6 It communicates with the pipe length switching chamber Cc. And the pipe length switching chamber Cc is a distribution pipe 35 1 to 3
The inertial supercharging distribution chamber Ch is inserted through the upstream side of 5 6 to form an expanded inertial supercharging distribution chamber Ch '(see the chain double-dashed line in FIG. 5). Therefore, the expanded inertial supercharging distribution chamber Ch ′ and the left and right cylinder groups Cl and Cr are connected to the distribution pipe 3
5 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 The pressure cycle can be matched with the opening / closing cycle of the intake valve 10 during high-speed operation of the engine to enhance the volumetric efficiency in the operating range.

このとき、第1,5図から明らかなように管長切換弁38l,3
8rの弁口391〜396が分配管351〜356の彎曲部の外側壁面
に形成されており、しかも前記弁口391〜396に装着され
た弁体411〜416が管長切換弁チャンバCcと各気筒3l…,3
r…を結ぶ通路と平行な位置へ開弁操作されるので、管
長切換弁チャンバCcと各気筒3l…,3r…が概略直線的な
通路を介して接続されるとともに、前記弁体411〜416
該通路の障害物になることがない。したがって高速運転
域における圧力波の伝播速度が増加して該運転域におけ
る体積効率の向上が可能となる。
At this time, as apparent from Figs. 1 and 5, the pipe length switching valves 38l, 3
Valve port 39 1 to 39 6 8r is formed on the outer wall surface of the curved portion of the distributor pipe 35 1-35 6, the valve element 41 1-41 6 And attached to the valve port 39 1 to 39 6 Pipe length switching valve chamber Cc and each cylinder 3l ..., 3
Since the valve opening operation is performed at a position parallel to the passage connecting r ..., The pipe length switching valve chamber Cc and each cylinder 3l ..., 3r ... Are connected through a substantially linear passage, and the valve elements 41 1 ... 41 6 does not become obstacle of the passage. Therefore, the propagation speed of the pressure wave in the high speed operation region is increased, and the volume efficiency in the operation region can be improved.

なお上記実施例において、分配管351〜356の中間部が短
絡する管長切換チャンバCcは吸気行程が連続しない気筒
群Cl,Crどうしを連通して慣性過給系を構成するもので
あるが、本考案にいう管長切換チャンバCcは共鳴過給系
を構成するための所謂共鳴チャンバをも含むものとす
る。
In the above embodiment, the pipe length switching chamber Cc in which the middle portion of the distribution pipes 35 1 to 35 6 is short-circuited is such that the cylinder groups Cl and Cr whose intake strokes are not continuous communicate with each other to form an inertial supercharging system. The pipe length switching chamber Cc referred to in the present invention also includes a so-called resonance chamber for forming a resonance supercharging system.

また上記実施例においては、分配管351〜356と管長切換
チャンバCcが弁口391〜396を介して直接連通している
が、前記分配管351〜356と管長切換チャンバCcの間に短
い分岐管を介装して該分岐管と分配管351〜356の接続部
に管長切換弁38l,38rを装着してもよい。
In the above embodiment, the distributor pipe 35 1-35 6 and pipe length switching chamber Cc is communicated directly via the valve port 39 1 to 39 6, the distribution pipe 35 1-35 6 and pipe length switching chamber Cc short branch pipe is interposed in the branch pipe and the distributor pipe 35 1-35 6 connecting portion in the pipe length switching valve 38l, may be attached to 38r between.

C.考案の効果 以上のように本考案の第1の特徴によれば、左,右気筒
群に各別に接続する複数の分配管を逆U字状に湾曲させ
て、その上部に管長切換チャンバを設けることによりV
型多気筒内燃機関の狭いV空間のスペースの有効利用を
図ることができる。しかも前記分配管の下流側を直線的
に左,右気筒群に接続し、且つ前記分配管の湾曲部の外
側壁面に前記管長切換チャンバに連通する開口を形成し
て管長切換チャンバと左,右気筒群をストレートな通路
を介して連通させることにより圧力波の伝播速度が増加
し、高速運転域でのより高い体積効率が確保される。
C. Effect of the Invention As described above, according to the first feature of the present invention, a plurality of distribution pipes that are separately connected to the left and right cylinder groups are curved in an inverted U shape, and a pipe length switching chamber is provided above the distribution pipes. By providing V
It is possible to effectively utilize the space of the narrow V space of the multi-cylinder internal combustion engine. Moreover, the downstream side of the distribution pipe is linearly connected to the left and right cylinder groups, and an opening communicating with the pipe length switching chamber is formed on the outer wall surface of the curved portion of the distribution pipe to form the pipe length switching chamber and the left and right cylinders. By communicating the cylinder groups through the straight passages, the propagation speed of the pressure wave is increased, and higher volume efficiency in the high speed operation range is secured.

また本考案の第2の特徴によれば、前記開口を開閉する
弁体をバタフライ型とし、その開成位置において該弁体
が管長切換チャンバと各気筒を結ぶ通路と平行な位置へ
回動するので、高速運転域での管長切換チャンバと各気
筒間の圧力波の伝播がスムーズに行われ、より高い体積
効率が確保される。
Further, according to the second feature of the present invention, the valve body that opens and closes the opening is a butterfly type, and at its open position, the valve body rotates to a position parallel to the passage connecting the pipe length switching chamber and each cylinder. In the high speed operation range, the pressure wave is smoothly propagated between the pipe length switching chamber and each cylinder, and higher volume efficiency is secured.

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

第1〜7図は本考案の第1実施例を示すもので、第1図
は本考案装置を備えた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、第7図は、第5図VII−VII線に沿う断面図で
ある。 C…V空間、Cc……管長切換チャンバ、Cl,Cr……気筒
群 351〜356……分配管、38l,38r……管長切換弁、391〜39
6……弁口(開口)、411〜416……弁体
1 to 7 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a V type 6 cylinder internal combustion engine equipped with the device of the present invention, and FIG. Fig. 3 is an enlarged partial plan view taken along line III-III in Fig. 1, Fig. 4 is an enlarged partial plan view taken along line IV-IV in Fig. 1, and Fig. 5 is taken along line VV in Fig. 4. 6 is a sectional view taken along line VI-VI in FIG. 5, and FIG. 7 is a sectional view taken along line VII-VII in FIG. C ... V space, Cc ... tube length switching chamber, Cl, Cr ... cylinder group 35 1 to 35 6 ... Distribution pipe, 38l, 38r ... pipe length switching valve, 39 1 to 39
6 …… Valve mouth (opening), 41 1 to 41 6 …… Valve

Claims (2)

【実用新案登録請求の範囲】[Scope of utility model registration request] 【請求項1】下流端が左,右気筒群(Cl,Cr)に各別に
接続する複数の分配管(351〜356)と、機関の運転状況
に応じて開閉制御される管長切換弁(38l,38r)を介し
て前記分配管(351〜356)の中間部が連通する管長切換
チャンバ(Cc)とをV空間(C)に配設したV型多気筒
内燃機関の吸気装置において、 前記分配管(351〜356)を逆U字状に湾曲させてその上
部に前記管長切換チャンバ(Cc)を設けるとともに、前
記分配管(351〜356)の下流側を直線的に左,右気筒群
(Cl,Cr)に接続し、且つ前記分配管(351〜356)の湾
曲部の外側壁面に前記管長切換チャンバ(Cc)に連通す
る開口(391〜396)を形成することにより、管長切換チ
ャンバ(Cc)左,右気筒群(Cl,Cr)を直線的な通路を
介して連通することを特徴とするV型多気筒内燃機関の
吸気装置。
1. A pipe length switching valve downstream end left, right cylinder group and (Cl, Cr) a plurality of distribution pipes connected to each other in (35 1 to 35 6) are opened and closed controlled in accordance with the operating condition of the engine (38l, 38r) intermediate portion of the intake device for a V-type multi-cylinder internal combustion engine and a pipe length switching chamber (Cc) is disposed in the V-space (C) which communicates said distribution pipe through a (35 1 to 35 6) straight in, together with the distribution pipe (35 1 to 35 6) is curved in an inverted U-shape providing the tube length switching chamber thereon (Cc), the downstream side of the distribution pipe (35 1 to 35 6) to the left, right cylinder group (Cl, Cr) connected to, and the distribution pipe (35 1 to 35 6) opening (39 1 communicating with the duct length switching chamber (Cc) on the outside wall surface of the curved portion of the ~ 39 6 ) is formed to connect the left and right cylinder groups (Cl, Cr) of the pipe length switching chamber (Cc) via a linear passage, and a V-type multi-cylinder internal combustion engine. Intake device.
【請求項2】前記開口(391〜396)にバタフライ型の弁
体(411〜416)を有する管長切換弁(38l,38r)を装着
し、該開口(391〜396)を開放して前記管長切換チャン
バ(Cc)と左,右気筒群(Cl,Cr)を接続する際、前記
弁体(411〜416)を管長切換チャンバ(Cc)と左,右気
筒群(Cl,Cr)を結ぶ通路と平行な位置へ回動させるこ
とを特徴とする請求項記載のV型多気筒内燃機関の吸
気装置。
Wherein said opening butterfly type valve body (39 1 to 39 6) (41 1 to 41 6) pipe length changeover valve having (38l, 38r) attached to, opening (39 1 to 39 6) and left, right cylinder group to open the duct length switching chamber (Cc) (Cl, Cr) when connecting the said valve body (41 1 to 41 6) a pipe length switching chamber (Cc) and the left, right cylinder group The intake system for a V-type multi-cylinder internal combustion engine according to claim 1, wherein the intake system is rotated to a position parallel to a passage connecting (Cl, Cr).
JP6474289U 1989-06-02 1989-06-02 Intake device for V-type multi-cylinder internal combustion engine Expired - Lifetime JPH0649864Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP6474289U JPH0649864Y2 (en) 1989-06-02 1989-06-02 Intake device for V-type multi-cylinder internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6474289U JPH0649864Y2 (en) 1989-06-02 1989-06-02 Intake device for V-type multi-cylinder internal combustion engine

Publications (2)

Publication Number Publication Date
JPH035929U JPH035929U (en) 1991-01-21
JPH0649864Y2 true JPH0649864Y2 (en) 1994-12-14

Family

ID=31595958

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6474289U Expired - Lifetime JPH0649864Y2 (en) 1989-06-02 1989-06-02 Intake device for V-type multi-cylinder internal combustion engine

Country Status (1)

Country Link
JP (1) JPH0649864Y2 (en)

Also Published As

Publication number Publication date
JPH035929U (en) 1991-01-21

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