JPS588230A - Suction device for multi-cylinder internal combustion engine - Google Patents
Suction device for multi-cylinder internal combustion engineInfo
- Publication number
- JPS588230A JPS588230A JP56107532A JP10753281A JPS588230A JP S588230 A JPS588230 A JP S588230A JP 56107532 A JP56107532 A JP 56107532A JP 10753281 A JP10753281 A JP 10753281A JP S588230 A JPS588230 A JP S588230A
- Authority
- JP
- Japan
- Prior art keywords
- load
- low
- intake
- cylinder
- secondary side
- 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.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 20
- 230000009977 dual effect Effects 0.000 claims description 5
- 239000000203 mixture Substances 0.000 abstract description 27
- 238000002347 injection Methods 0.000 abstract description 5
- 239000007924 injection Substances 0.000 abstract description 5
- 230000035939 shock Effects 0.000 abstract 1
- 239000000446 fuel Substances 0.000 description 26
- 239000006200 vaporizer Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 210000003128 head Anatomy 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 210000001747 pupil Anatomy 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
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
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B31/08—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air inlets
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、内燃機関において出力の向上と、燃料消費量
の低減等を図ることを目的とする吸気装置に関するもの
であ゛る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an air intake device intended to improve output and reduce fuel consumption in an internal combustion engine.
内燃機関の低負荷・低回転域での着火燃焼性を向上する
ために、２連式気化器から各気筒の吸気弁近傍に至るま
での吸気通路を、２連式気化器における一次側気化器か
らの低負荷用吸気通路と、二次側気化器からの高負荷用
吸気通路との２つの独立した系統とし、機関の低負荷・
低回転域では、低負荷用吸気通路を通して混合気を燃燗
室に導入することにより、燃焼室内での混合気のスワー
ルあるいは乱れを高めることが知られている。In order to improve ignition combustibility in the low load and low rotation range of internal combustion engines, the intake passage from the dual carburetor to the vicinity of the intake valve of each cylinder is connected to the primary side carburetor of the dual carburetor. The system has two independent systems: a low-load intake passage from the engine and a high-load intake passage from the secondary side carburetor.
It is known that in a low rotation range, the swirl or turbulence of the air-fuel mixture in the combustion chamber can be increased by introducing the air-fuel mixture into the combustion chamber through the low-load intake passage.
そして、この種の吸気装置に関する先行技術には、実公
昭４６−９９３０号公報及び実開昭５Ｆｒ−３９３４８
ち公報がある。すなわち、前者は、二次側気化器から各
気筒に至る各高負荷用吸気通路中に、二次側気化器のス
ロットル弁に連動し丁開閉する制御弁を各々設けること
により、低負荷運転域において低負荷用吸気通路内の混
合気が吸気脈動等によって高負荷用吸気通路内に流入し
て、流速が低下したり空燃比が変１したシするのを防止
するものであるが、このものは二次側気化器のスロット
ル弁に対する各制御弁の開度を、当該制御弁が高負荷用
吸気通路内での混合気に対して大きな絞り抵抗とか、混
合気の応答性を阻害しないように構成しなければならな
いため、後者では、各制御弁を、二次側気化器のスロッ
トル弁が開き始める前に開くようにすることを提案して
いる。Prior art related to this type of intake device includes Utility Model Publication No. 46-9930 and Utility Model Application Publication No. 5Fr-39348.
There is a public notice. In other words, the former provides a control valve that opens and closes in conjunction with the throttle valve of the secondary side carburetor in each high-load intake passage from the secondary side carburetor to each cylinder. This prevents the air-fuel mixture in the low-load intake passage from flowing into the high-load intake passage due to intake pulsation, resulting in a decrease in flow velocity or a change in the air-fuel ratio. The opening degree of each control valve relative to the throttle valve of the secondary side carburetor is adjusted so that the control valve does not create a large throttling resistance to the air-fuel mixture in the high-load intake passage or impede the responsiveness of the air-fuel mixture. The latter proposes that each control valve be opened before the throttle valve of the secondary carburetor begins to open.
しかし、このように各制御弁を、二次側気化器のスロッ
トル弁よ、りも前に開くよって構成することは、その構
造が著しく複雑になるばかりか、二次側気化器のスロッ
トル弁が開く直前の運転域において、各制御弁が開くこ
とにより、高負荷吸気通路へ低負荷吸気通路からの混合
気の流入が発生し、その結果として、低負荷吸気通路内
の流速が低下し、混合気の乱れが弱まって、狙いとする
効果が得られない状態となる。また混合気の各気筒への
配分上、制御弁の開度をバランスよく調整しなけれ１ば
ならない。However, configuring each control valve to open earlier than the throttle valve of the secondary side carburetor not only significantly complicates the structure, but also causes the throttle valve of the secondary side carburetor to open earlier than the throttle valve of the secondary side carburetor. In the operating range immediately before opening, each control valve opens, causing the air-fuel mixture from the low-load intake passage to flow into the high-load intake passage.As a result, the flow velocity in the low-load intake passage decreases, and the mixture The disturbance of Qi weakens and the desired effect cannot be obtained. Furthermore, in order to distribute the air-fuel mixture to each cylinder, the opening degree of the control valve must be adjusted in a well-balanced manner.
本発明は、このように２連式気化器から各気筒への吸気
系を低負荷用吸気通路と高負荷用吸気通路との２系統と
し、各気筒への高負荷用吸気通路中に、当該高負荷用吸
気通路へ混合気の流入を防止するための制御弁を設ける
において、前記制御弁を二次側気化器から各気筒への方
向にのみ開くようにした逆止弁とすることにより、これ
と二次側気化器のスロットル弁との連動機構を不要にし
て構造の簡略化を図ると共に、気化器の２次弁が閉じて
いる低回転、または低負荷運転域での低負荷吸気通路に
おける混合気の流速および方向性を高めシリ：／ター中
での混合気のスクールを強化すること、また均質な混合
気の生成により燃焼の向上を行ったものである。In this way, the present invention has two systems for the intake system from the dual carburetor to each cylinder, a low-load intake passage and a high-load intake passage. In providing a control valve for preventing the air-fuel mixture from flowing into the high-load intake passage, by making the control valve a check valve that opens only in the direction from the secondary side carburetor to each cylinder, In addition to simplifying the structure by eliminating the need for an interlocking mechanism between this and the throttle valve of the secondary side carburetor, the low-load intake passage can be used at low rotation speeds or in low-load operating ranges when the secondary valve of the carburetor is closed. This improves combustion by increasing the flow velocity and directionality of the air-fuel mixture in the cylinder, strengthening the school of the air-fuel mixture in the cylinder, and generating a homogeneous air-fuel mixture.
以下実施例の図面について説明すると、図において囚は
第１気筒（Ａ１）及び第２気筒（Ａ２）を有する２気筒
内燃機関、（１）は−次側気化器（２）Ｃ以下−次側と
いう。）と二次側気化器ｔ３） （、以下二次側という
。）とを有する従来公知の２連式気イヒ器を各々示し、
該気化器（１）における二次側（３）には、−次側（２
）におけるスロットル弁（４）が全開又は全開近くに開
いたときから開くようにしたスロットル弁（５）を備え
、また、機関における各気筒（ＡＩ）（Ａ２）には、燃
焼室（６）に開口する吸気弁（８）付き吸気ポート（７
）と、該吸気ホード（７）Ｋ連通ずる高負荷用吸気ポー
ト（９）とを各々備えると共に、両気＠（Ａ□）（Ａ２
）の間の部位に、一本の低負荷用吸気ホー） （ＩＧ
を備え、該低負荷用吸気ポート００は、シリシタヘッド
内において各気筒の吸気ボート（７）に連通ずる２つの
噴出ポー ） （ｏ：Ｈ＋＋Ｈに分岐している。この場
合、両噴出ボート（１１）の吸気ボート（７）内への開
口部は、吸気弁（８）の略背面＠所において、吸気ボー
ト（７）及び燃焼室（６）に対して共に略接線方向に、
換言すれば、噴出ポー１−ｉｌｌ）・から吸気ボート（
７）への混合流は、吸気ホード（７）内で旋回すると共
に燃・婉室（６）内での旋回を強化するような方向に方
向づけること、および噴出りも小さくする。To explain the drawings of the embodiment below, in the drawings, the figure shows a two-cylinder internal combustion engine having a first cylinder (A1) and a second cylinder (A2), (1) shows a - next side carburetor (2) below C - next side. That's what it means. ) and a secondary side vaporizer t3) (hereinafter referred to as the secondary side).
The secondary side (3) of the vaporizer (1) has a negative side (2
) is equipped with a throttle valve (5) that opens when the throttle valve (4) in the engine is fully open or close to fully open. Intake port (7) with opening intake valve (8)
) and a high-load intake port (9) that communicates with the intake hoard (7)K, and both air @(A□)(A2
) (IG
The low-load intake port 00 is branched into two injection ports (o:H++H) that communicate with the intake boats (7) of each cylinder in the silicator head.In this case, both injection ports (11) The opening into the intake boat (7) is substantially tangential to both the intake boat (7) and the combustion chamber (6) at the substantially rear side of the intake valve (8).
In other words, from the ejection port 1-ill) to the intake port (
The mixed flow to 7) is directed in such a way that it swirls in the intake hood (7) and enhances the swirl in the combustion chamber (6), and also reduces blowout.
１１２＋ ６１ ｔｉｒ′Ｊ記気化器（１）と客気ｆ％
ｊ（ＡＩ）（Ａ２）とをつなぐ吸気マニホールドを示し
、該吸気マニホールド（１２）は、気イと器（１）にお
ける−次側（２）の下流部（１３）を前記低負荷用吸気
ポートαＧにつなぐ低負荷吸気通路圓を蝋えると共に、
二次側（３）の下流側における集合部（１５）から各気
筒における高負荷用吸気ポート（９）て向って分岐する
高負荷用吸気ポートＱ６）：ｌ１ｌｉｌを＠えている。112+ 61 tir'J vaporizer (1) and customer air f%
The intake manifold (12) connects the downstream part (13) of the downstream side (2) of the air intake device (1) to the low-load intake port. In addition to melting the low-load intake passage circle that connects to αG,
A high-load intake port Q6) branching from a gathering part (15) on the downstream side of the secondary side (3) toward a high-load intake port (9) in each cylinder is provided.
そして、前記各気筒における高負荷用吸気ホード（９）
又は高負荷用吸気通路！１６）内に、二次側気化器（３
）から各気筒への方向にのみ開くようにした逆止弁０７
）を各々設けて成るものである。and a high-load intake hoard (9) in each cylinder.
Or intake passage for high loads! 16), the secondary side carburetor (3
) Check valve 07 that opens only in the direction toward each cylinder
).
なお、前記゛逆正弁瞳としては、図示のように断面Ｖ量
弁座体′Ｊ８）の両弁座部１９：］１９）に、各々ゴム
等の弾性弁板２０１１２０＋を接当して構成したもの（
で限らず、他の形式の逆止弁にしても良く、また、噴流
ポート（１１）は第１図に示すようにシリシタヘッド内
で分岐せずに、低負荷用吸気ホードα０、低負荷用吸気
通路（１４）の任意の位置から分岐させるようにしても
良い。さらに、噴流ボー） １１１１の開口部位は第２
図に示すように吸気ホード（７〕部でなく、第二の吸気
弁を介して直接燃焼室に開口させるようにしても良い。In addition, the above-mentioned "reverse positive valve pupil" is constructed by abutting elastic valve plates 201120+ made of rubber or the like on both valve seat parts 19:]19) of the cross-sectional V-volume valve seat body'J8) as shown in the figure. What I did (
However, other types of check valves may be used, and the jet port (11) does not branch within the silicitor head as shown in Fig. The passage (14) may be branched from any position. Furthermore, the opening part of the jet bow) 1111 is the second one.
As shown in the figure, it may be opened directly into the combustion chamber through the second intake valve instead of through the intake air intake hole (7).
この構成において、−次側（２）のスロットル弁（４）
のみを開いている低負荷または低回転定常運転域では、
機関への吸入空気は一次側（２）のみから導入され、二
次側（３）からの吸入空気の導入はなく各高負荷用吸気
ボー）Ｈは逆止弁（１７）を介して、シリジター負圧を
ホールドする。In this configuration, the throttle valve (4) on the negative side (2)
In low-load or low-speed steady-state operating ranges where only the
The intake air to the engine is introduced only from the primary side (2), and there is no intake air introduced from the secondary side (3). Hold negative pressure.
一方、逆止弁同下流の各高負荷用吸入ボート（９）は、
低速系吸気噴出口（Ｉｔ）を介して、低速用吸気通路（
Ｉ４）と連通していることおよび、弁才−バーラップ時
の吹き返しのため同部分における負圧は、前記のボート
（１６）より低く、たとえば第１気筒（Ａ１）が吸気行
程になって、吸気弁（８）が開いた時、第２気筒〔Ａ２
）１７ｉｌ：２ける高負荷用吸入ボート（９）の混合気
は、第２気筒（Ａ２）制逆止弁（１７）を介して、第１
気筒（Ａ１〕側に流入することはない。On the other hand, each high-load suction boat (9) downstream of the check valve is
The low speed intake passage (
I4) and because of the blowback during valve burlap, the negative pressure in this part is lower than that of the boat (16), and for example, when the first cylinder (A1) is in the intake stroke, the intake valve (8) opens, the second cylinder [A2
) 17il: The air-fuel mixture in the high-load suction boat (9) in the second cylinder is transferred to the first cylinder (A2) through the check valve (17).
It does not flow into the cylinder (A1) side.
従って、低負荷、または低回転域における定常運転時に
は低負荷用吸気噴出口（ｌりのみを通して、混合気のほ
ぼ全量が燃焼室へ流入することになるので、Ｚ混合気の
流速を高めかつ方向性を強化することができるので、吸
気ホード内および、シリンター内におけるスワールの強
化が得られると共に、吸気混合気の空燃比の変動がなり
、シかも、低負荷用吸気通路（１４）及び吸気ボートｕ
Ｏ内での燃料の霧化が良く均質な混合気を得ることがで
きて、低負荷・低回転域での着火燃焼性を著しく促進で
きるから、低負荷および低回転域での燃焼の安定化を達
成することができて、燃料消費量を低減できると共に、
混合気の通路容積を小さくした時と同様、混合気の応答
性が向上し低温時におけるドライ゛バーピリティーの悪
化を防止できるのである。Therefore, during steady operation in a low load or low rotation range, almost the entire amount of the mixture flows into the combustion chamber through the low load intake nozzle (l), increasing the flow velocity of the Z mixture and increasing the direction. As a result, the swirl inside the intake hoard and cylinder can be strengthened, and the air-fuel ratio of the intake air-fuel mixture can be reduced, which may cause the low-load intake passage (14) and the intake boat to be u
The fuel is atomized well in the O and a homogeneous air-fuel mixture can be obtained, which significantly promotes ignition and combustion in the low load and low rotation range, resulting in stable combustion in the low load and low rotation range. can be achieved, reducing fuel consumption and
Similar to when the air-fuel mixture passage volume is made smaller, the response of the air-fuel mixture is improved and deterioration of driveability at low temperatures can be prevented.
そして、−次側（２）のスロットル弁（４）に次いで二
次側（３）のスロットル弁〔５〕が開くような運転域に
なる七、二次側（３）からの吸入混合気の流れに応じて
逆止弁す力が自動的に開くことにより、燃焼室（６）に
は高負荷用吸気ボート（９）と低負荷用吸気ボートＣ１
Ｏの噴出ホード（１１の両方から混合気が導入されるの
であり、この場合、逆止弁！＋７）／／′ｉ、高負荷用
吸気通路！Ｉ６）内に二次側（３〕から燃焼室（６）方
向への流れかないとき閉じていて、当該流れが生じたと
きからこれに追従して開くもので、高負荷用吸気通路・
Ｉ６）内に二次側（３）からの吸気混合気の流れがない
以前に開くことがなく、二次側（３）におけるスロット
ル弁（５）が開くまでの間における混合気の流入を確実
に防止するから、機関への吸気作動が、−次側（２）の
みの吸気から一次側（２）及び二次側（３）の吸気に移
行するときにおける、低負荷用吸気系での一時的な流速
の低下及び空燃比の変動はないのである。また、逆止弁
Ｕηは、低負荷捷たは低回転域において低負荷用吸気系
から高負荷用吸気系への混合気の流入を防止するだけの
もので、その弁に対するばね定数は極めて弱いもので良
いから、当該逆止弁（１７）による流れ抵抗は少ないの
である。Then, the operating range is such that the throttle valve [5] on the secondary side (3) opens after the throttle valve (4) on the negative side (2). By automatically opening the check valve according to the flow, a high-load intake boat (9) and a low-load intake boat C1 are installed in the combustion chamber (6).
The air-fuel mixture is introduced from both of the O injection hoards (11, in this case the check valve!+7) //'i, the high-load intake passage! It is closed when there is no flow from the secondary side (3) toward the combustion chamber (6) in I6), and opens to follow the flow when the flow occurs.
There is no flow of intake air mixture from the secondary side (3) into I6), which does not open beforehand, and ensures the inflow of the air-fuel mixture until the throttle valve (5) on the secondary side (3) opens. In order to prevent There is no significant decrease in flow velocity or fluctuation in air-fuel ratio. In addition, the check valve Uη only prevents the air-fuel mixture from flowing from the low-load intake system to the high-load intake system in low-load switching or low-speed ranges, and the spring constant for this valve is extremely weak. Flow resistance caused by the check valve (17) is small.
以上の通り本発明は、機関への吸気系を、低負荷用吸気
系と高負荷用吸気系との２系統にする場合において、低
負荷用吸気系から高負荷用吸気系への混合気の流入を二
次側気化器から気筒への方向にのみ開くようにした逆止
弁によって防止するもので、従来のバタフライ型制御弁
のように、これを連動して開閉する機構を必要としない
から、構造を著しく簡略化することができると共に、二
次側気化器が吸気作動を開始する前後において機関の出
力に変動がなく、いわゆる七カニ／タリーシコックを確
実に防止しながら強力なスワールにより燃焼の改善が可
能な効果を有する。As described above, the present invention allows the air-fuel mixture to be transferred from the low-load intake system to the high-load intake system when the intake system for the engine is divided into two systems: a low-load intake system and a high-load intake system. The inflow is prevented by a check valve that opens only in the direction from the secondary side carburetor to the cylinder, and there is no need for a mechanism to open and close it in conjunction with the conventional butterfly type control valve. In addition to significantly simplifying the structure, there is no fluctuation in engine output before and after the secondary side carburetor starts intake operation, and a powerful swirl improves combustion while reliably preventing so-called seven-crab/tally-shock. It has an effect that can be improved.
図は本発明の実施例を示し、第１図は機関の一部切欠平
面図、第２図は第１図のｎ−■視断面図である。
（２）・・・機関、（Ａ１〕（Ａ２〕・・・気筒、（６
）・・・燃焼室、（７）・・・吸気ホード、（８）・・
・吸気弁、（９）・・・高負荷用吸気ボート、００・・
・低負荷用吸気ボート、（ｌす°゛°噴出ホード、（１
）・・・２連式気化器、（２） °°°−次側気化器、
（３）・°°二次側気化器、（１４）・・・低負荷用吸
気通路、！Ｉ６）・・・高負荷用吸気通路、Ｕη・・・
逆止弁。
特許出願人 タイハツ工業株式会社
代 理 人 弁理士 石 井 暁 夫、＜７−：７、
く ′The drawings show an embodiment of the present invention, in which FIG. 1 is a partially cutaway plan view of the engine, and FIG. 2 is a sectional view taken along line n--2 in FIG. 1. (2)... Engine, (A1] (A2)... Cylinder, (6
)...Combustion chamber, (7)...Intake hood, (8)...
・Intake valve, (9)...Intake boat for high load, 00...
・Intake boat for low load, (l°゛° jetting hoard, (1
)...double carburetor, (2) °°°-next side vaporizer,
(3)・°°Secondary side carburetor, (14)...Low load intake passage,! I6)...High load intake passage, Uη...
non-return valve. Patent applicant Taihatsu Kogyo Co., Ltd. Representative Patent attorney Akio Ishii, <7-:7,
Ku '
Claims (2)
筒への吸気系路を、前記２連式気イヒ器における一次側
気化器からの低負荷用吸気系路と、二次側気化器からの
高負荷用吸気系路との２系統にし、前記高負荷用吸気系
路には、二次側気化器から各気筒への分岐部以降に、二
次側気化器から各気筒への方向にのみ開くようにした逆
比弁を設けたことを特徴とする多気筒内燃機関の吸気装
置。(1) The intake system path from the dual carburetor to each cylinder in the multi-cylinder engine is connected to a low-load intake system path from the primary side carburetor in the dual carburetor, and a secondary side carburetor. The high-load intake system path includes a high-load intake system path from the secondary side carburetor to each cylinder after the branch point from the secondary side carburetor to each cylinder. An intake system for a multi-cylinder internal combustion engine, characterized by being provided with a reverse ratio valve that opens only when the valve is opened.
ワールを強化する方向に指向させたことを特徴とする特
許請求の範囲第１項に記載の多気筒内燃機関の吸気装置
。(2) The intake system for a multi-cylinder internal combustion engine according to claim 1, wherein the low-load intake passage is oriented in a direction that strengthens the intake swirl in the cylinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56107532A JPS588230A (en) | 1981-07-08 | 1981-07-08 | Suction device for multi-cylinder internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56107532A JPS588230A (en) | 1981-07-08 | 1981-07-08 | Suction device for multi-cylinder internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS588230A true JPS588230A (en) | 1983-01-18 |
Family
ID=14461572
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56107532A Pending JPS588230A (en) | 1981-07-08 | 1981-07-08 | Suction device for multi-cylinder internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS588230A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5092286A (en) * | 1991-04-08 | 1992-03-03 | General Motors Corporation | Intake venting system for reed valves |
| US5129367A (en) * | 1991-04-08 | 1992-07-14 | General Motors Corporation | Intermittent bypass system for a check valve |
| DE3711859C2 (en) * | 1986-04-19 | 2003-04-17 | Volkswagen Ag | Multi-cylinder reciprocating internal combustion engine |
-
1981
- 1981-07-08 JP JP56107532A patent/JPS588230A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3711859C2 (en) * | 1986-04-19 | 2003-04-17 | Volkswagen Ag | Multi-cylinder reciprocating internal combustion engine |
| US5092286A (en) * | 1991-04-08 | 1992-03-03 | General Motors Corporation | Intake venting system for reed valves |
| US5129367A (en) * | 1991-04-08 | 1992-07-14 | General Motors Corporation | Intermittent bypass system for a check valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS6052292B2 (en) | Dual intake passage internal combustion engine | |
| JP2639721B2 (en) | Combustion chamber of internal combustion engine | |
| JPS5950850B2 (en) | Internal combustion engine intake system | |
| JPS6060010B2 (en) | Intake system for multi-cylinder internal combustion engine | |
| JPS6025604B2 (en) | Intake control method for internal combustion engine | |
| JPH076395B2 (en) | Internal combustion engine intake system | |
| US4484549A (en) | 4-Cycle internal combustion engine | |
| JPS58187519A (en) | Intake device of engine | |
| US5704333A (en) | Fuel injection system for a lean burn engine | |
| JPH048606B2 (en) | ||
| JPS588230A (en) | Suction device for multi-cylinder internal combustion engine | |
| JP2002221036A (en) | Intake system for engine | |
| JPH021967B2 (en) | ||
| JPS61201826A (en) | Intake device of internal-combustion engine | |
| JPH0133792Y2 (en) | ||
| JPH1122470A (en) | Fuel injection device of lean burn engine | |
| JPS606602Y2 (en) | Internal combustion engine intake system | |
| JPS597539Y2 (en) | Double intake internal combustion engine | |
| JP2533172Y2 (en) | Intake manifold for internal combustion engine | |
| JP2530953Y2 (en) | Diesel engine exhaust recirculation system | |
| JP2523564Y2 (en) | Intake device for internal combustion engine | |
| JP2568842B2 (en) | Multi-cylinder engine intake system | |
| JPH0693941A (en) | Fuel feeding device for internal combustion engine | |
| JPS628627B2 (en) | ||
| JPH0465232B2 (en) |