JPS61169619A - Intake device for internal-combustion engine - Google Patents

Intake device for internal-combustion engine

Info

Publication number
JPS61169619A
JPS61169619A JP60009851A JP985185A JPS61169619A JP S61169619 A JPS61169619 A JP S61169619A JP 60009851 A JP60009851 A JP 60009851A JP 985185 A JP985185 A JP 985185A JP S61169619 A JPS61169619 A JP S61169619A
Authority
JP
Japan
Prior art keywords
engine
ignition plug
branch
liquid fuel
spark plug
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
Application number
JP60009851A
Other languages
Japanese (ja)
Inventor
Shigeo Muranaka
村中　重夫
Kozaburo Okawa
大川　晃三郎
Junichi Yokoyama
淳一 横山
Yutaka Matayoshi
豊 又吉
Shigeru Kamegaya
亀ケ谷　茂
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.)
Nissan Motor Co Ltd
Original Assignee
Nissan 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 Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP60009851A priority Critical patent/JPS61169619A/en
Priority to EP85113193A priority patent/EP0178663B1/en
Priority to DE8585113193T priority patent/DE3584936D1/en
Publication of JPS61169619A publication Critical patent/JPS61169619A/en
Priority to US07/258,048 priority patent/US4873953A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • 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
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • 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
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • 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
    • F02B2031/006—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air intake valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0606—Fuel temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
    • 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)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

PURPOSE:To prevent damping or smoking of an ignition plug thus to improve the starting and operating performance of an engine by arranging, in three valve intake system, an ignition plug between extended spaces of branch ports communicating independently with two intake valves and meet one another in the engine. CONSTITUTION:In three valve intake system of Siamese type, an ignition plug 5 is arranged between extended spaces of branch ports 6, 7. The ignition plug 5 is arranged, for example, at the inside of extended lines 6a, 7a of partition wall 8 of the branch ports 5, 6. Said ports 6, 7 are communicated independently with intake valves 3, 4 while combined into one in the engine. Consequently, the liquid fuel to be produced in abundant under cooling of engine is led along the inner wall of respective port 6, 7 into the combustion chamber, and never attack the ignition plug 5 directly thus to prevent damping or smoking of the ignition plug 5. Consequently, the starting and operating performance of engine can be improved under cooling of the engine.

Description

【発明の詳細な説明】 〈産業上の利用分野） 本発明は１気筒に１つの排気弁と２つの吸気弁とを備え
たいわゆる３弁式内燃機関の吸気装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an intake system for a so-called three-valve internal combustion engine, which has one exhaust valve and two intake valves per cylinder.

〈従来の技術〉 いわゆる３弁式内燃機関の吸気装置は、例えば第５図に
示すようなものがある（特開昭５９−９３９２６号、特
開昭５９−１０５９２５号及び特開昭５９−１０５９２
６号公報参照）。これは、１つの気筒１に関して、気筒
中心軸Ｃの一側に１つの排気弁２及び点火栓５を有し、
他側に２つの略同径の吸気弁３，４を有する。これらの
吸気弁３．４に夫々独立して連通ずる分岐ポート６．７
はシリンダヘッド９内で合流して取付端面に１つになっ
て開口するい勾ゆるサイミャーズドタイプとなっている
。前記点火栓５は、前記分岐ポート７側の隔壁８の略延
長上に配設される。<Prior art> For example, there is an intake system for a so-called three-valve internal combustion engine as shown in FIG.
(See Publication No. 6). This has one exhaust valve 2 and a spark plug 5 on one side of the cylinder center axis C for one cylinder 1,
It has two intake valves 3 and 4 of approximately the same diameter on the other side. Branch ports 6.7 each independently communicate with these intake valves 3.4.
They are of a sloping sizing type, merging in the cylinder head 9 and forming a single opening at the mounting end face. The ignition plug 5 is arranged on a substantially extension of the partition wall 8 on the side of the branch port 7.

かかる構成の３弁式吸気装置によると、例えば機関高負
荷運転領域等では２つの吸気弁３．４から吸気を導入で
きるため、充填効率が良く機関の高出力化を図ることが
できる。また、低負荷運転領域等では一方の分岐ポート
を閉じて他方の分岐ポートのみから燃焼室内壁に沿わせ
て吸気を導入するため大きなスワールが発生し、吸気流
速を高めることができる。従って、急速燃焼をさせるこ
とができ、燃焼効率を高めることができる利点がある。According to the three-valve intake system having such a configuration, intake air can be introduced from the two intake valves 3.4 in, for example, a high engine load operating region, so that the filling efficiency is good and the engine output can be increased. Furthermore, in a low-load operating region, one branch port is closed and intake air is introduced along the combustion chamber wall only from the other branch port, so a large swirl is generated and the intake air flow velocity can be increased. Therefore, there is an advantage that rapid combustion can be performed and combustion efficiency can be improved.

（発明が解決しようとする問題点〉 しかし、上記従来例の吸気装置においては、点火栓が分
岐ポート隔壁の略延長線上に配設されるため、燃料の気
化が不十分な機関の低温運転時に液状燃料が点火栓を直
撃し、点火栓の濡れ、くすぶりの原因となっていた。す
なわち、液状燃料が前記分岐ポートの内壁に沿って流れ
るため、その慣性によって燃焼室内に導入される液状燃
料が点火栓に多く到達するためである。従って、冷機時
の始動性及び運転性の悪化が免れ得ぬものとなっていた
。(Problems to be Solved by the Invention) However, in the above-mentioned conventional intake system, the spark plug is disposed approximately on the extension line of the branch port partition wall, so when the engine is operated at low temperatures where fuel vaporization is insufficient, The liquid fuel directly hits the spark plug, causing it to become wet and smolder.In other words, since the liquid fuel flows along the inner wall of the branch port, its inertia causes the liquid fuel introduced into the combustion chamber to This is because many of the spark plugs reach the spark plug.Therefore, deterioration in startability and driveability when the engine is cold is unavoidable.

本発明は上記不都合を解消して、冷機時に点火栓に到達
する液状燃料を最小限に抑え、点火栓の濡れ、くすぶり
を防止し、以て機関の始動性、運転性を向上させること
を目的とする。The purpose of the present invention is to eliminate the above-mentioned disadvantages, minimize the amount of liquid fuel that reaches the ignition plug when the engine is cold, prevent the ignition plug from getting wet and smoldering, and thereby improve the startability and drivability of the engine. shall be.

く問題点を解決するための手段〉 そこで本発明では、いわゆる３弁式吸気装置において、
２つの吸気弁に夫々に独立して連通ずると共に機関内で
合流する分岐ボートの延長空間相互間に点火栓を配設す
る。Means for Solving the Problems> Therefore, in the present invention, in a so-called three-valve intake system,
A spark plug is disposed between the extension spaces of a branch boat that independently communicate with the two intake valves and merge within the engine.

く作用〉 上記のように、点火栓を配設することにより、冷機時に
分岐ボートの内壁に沿って流れる液状燃料が、点火栓を
直撃することが防止される。従って、点火栓の濡れ、く
すぶりの発生を抑止できる。Effect> As described above, by providing the spark plug, the liquid fuel flowing along the inner wall of the branch boat when the engine is cold is prevented from directly hitting the spark plug. Therefore, wetting of the ignition plug and occurrence of smoldering can be suppressed.

〈実施例〉 以下に本発明の実施例を図面に基づいて説明する。尚、
従来例と同一要素には第５図と同一符号を付して説明を
省略する。<Example> Examples of the present invention will be described below based on the drawings. still,
Elements that are the same as those in the conventional example are designated by the same reference numerals as in FIG. 5, and their explanation will be omitted.

すなわち、第１図及び第２図はいわゆるサイミャーズド
タイプの３弁式吸気装置を示し、分岐ポー）６．７の延
長空間相互間に点火栓５が配設される。すなわち、点火
栓５は例えば分岐ボート６゜７の隔壁８の延長線５ａ、
７ａの内側に配設される。このように、点火線５を配設
することによって、冷機時に多（発生する液状燃料が分
岐ボート６．７の内壁に沿って燃焼室内に導入されても
、点火栓５を直撃することがなく、濡れ、くすぶりの発
生を抑止できる。従って、冷機時における機関の始動性
及び運転性を向上させることができる。That is, FIGS. 1 and 2 show a so-called cylindrical three-valve intake system, in which a spark plug 5 is disposed between the extension spaces of branch ports 6.7. That is, the spark plug 5 is, for example, an extension line 5a of the bulkhead 8 of the branch boat 6°7,
It is arranged inside 7a. By arranging the ignition line 5 in this manner, even if a large amount of liquid fuel generated during cold engine is introduced into the combustion chamber along the inner wall of the branch boat 6.7, it will not directly hit the ignition plug 5. , wetting, and smoldering can be suppressed.Therefore, the startability and drivability of the engine when the engine is cold can be improved.

更に本実施例においては、液状燃料が点火栓５に到達す
る量を最も少なくする点火栓５の位置及び分岐ボート６
．７の隔壁８の形状等の詳細を次に示す実験によって求
めた。Furthermore, in this embodiment, the position of the ignition plug 5 and the branch boat 6 are set so that the amount of liquid fuel reaching the ignition plug 5 is minimized.
．． Details such as the shape of the partition wall 8 of No. 7 were determined through the following experiment.

すなわち、第３図に）、■は、冷機時における点火栓５
への液状燃料の到達量を、隔壁８ａの長さ１、分岐ボー
ト６．７の径Ｗ９点火栓５の位置り及び径ｄ（第２図）
夫々を変え、そのときの液状燃料の点火栓５への到達量
を測定した実験結果を示す。第３囲繞に示す実験結果は
隔壁８ａの長さｉと分岐ボート６．７の径Ｗとの比を一
定（ｌ／Ｗ＝１．０）として、点火栓５の位置りと径ｄ
の比（ｈ／ｄ）を変え、第３図囚は点火栓５の位置りと
径ｄの比を一定（ｈ／ｄ＝１．５）として、隔壁８ａの
長さｉと分岐ボート６．７の径Ｗの比（１２／Ｗ＞を変
えた場合の液状燃料の点火栓５への到達量を示している
。これらの実験結果から、点火栓５の濡れを生じない好
ましい値が存在することが分かる。In other words, in Fig. 3), ■ indicates the spark plug 5 when the machine is cold.
The amount of liquid fuel arriving at
The results of an experiment in which the amount of liquid fuel reaching the ignition plug 5 at each time was measured are shown below. The experimental results shown in the third box are based on the position of the spark plug 5 and the diameter d, with the ratio of the length i of the bulkhead 8a and the diameter W of the branch boat 6.7 being constant (l/W=1.0).
The ratio (h/d) of the bulkhead 8a and the length i of the bulkhead 8a and the branch boat 6. 7 shows the amount of liquid fuel reaching the spark plug 5 when the ratio (12/W>) of the diameter W of I understand that.

すなわち、第３囲繞から点火栓５の位置りと径ｄの比は
１以上（ｈ／ｄ≧１）であれば液状燃料の到達量が微小
となり、それ以上に大きくしても大きな変化はない。し
かし、各内燃機関のボア等の制約上、点火栓５の位置り
を無制限に大きくすることはできないので、ｈ／ｄ≧１
．０とし各エンジンの特性を考慮して燃焼効率等の良い
位置に配設する。このように、点火栓５をその中心から
隔壁８の延長線６ａ、７．ａまでの距離が、点火栓５の
径ｄ以上になるように配設することにより、液状燃料の
到達量を最も少なくできる。In other words, if the ratio between the position of the spark plug 5 and the diameter d from the third enclosure is 1 or more (h/d≧1), the amount of liquid fuel arriving will be minute, and even if it is made larger than that, there will be no big change. . However, due to restrictions such as the bore of each internal combustion engine, the position of the spark plug 5 cannot be increased indefinitely, so h/d≧1
．． 0, and place it in a position with good combustion efficiency, considering the characteristics of each engine. In this way, the ignition plug 5 is extended from the center of the partition wall 8 by the extension lines 6a, 7. By arranging the spark plug 5 so that the distance to a is equal to or greater than the diameter d of the spark plug 5, the amount of liquid fuel that reaches the spark plug 5 can be minimized.

−力筒３図■から隔壁８の形状は、その隔壁８ａの長さ
ｌと分岐ボート７の径Ｗとの比が０．８以上（１／Ｗ≧
０．８）であれば、液状燃料の到達量が微小となるが、
第３囲繞と同様にそれ以上になっても到達量に大きな変
化はない。従って、隔壁８ａの長さｌと分岐ボート７の
径Ｗとの比は、０．８以上であれば良いことになる。こ
の場合も、各エンジンの特性を考慮して吸気の分配性等
がよくかつＩｔ／ｗ≧１．０となるように、隔壁８ａの
長さｌと分岐ボート６．７の径Ｗを決定する。- The shape of the bulkhead 8 is determined by the ratio of the length l of the bulkhead 8a to the diameter W of the branch boat 7 to be 0.8 or more (1/W≧
0.8), the amount of liquid fuel reached will be minute, but
As with the third box, there is no significant change in the amount reached beyond that. Therefore, it is sufficient that the ratio between the length l of the partition wall 8a and the diameter W of the branch boat 7 is 0.8 or more. In this case, the length l of the bulkhead 8a and the diameter W of the branch boat 6.7 are determined in consideration of the characteristics of each engine so that the intake air distribution is good and It/w≧1.0. .

以上のように、第２図に示す前記点火栓５の中心と前記
隔壁延長線６ａ、７ａ夫々との距離りを前記点火栓５の
直径ｄ以上とし、点火栓５と気筒中心軸周りに近い側の
分岐ボート７側の隔壁８ａの長さｌを、吸気ボート７の
径Ｗの０．８倍以上となるように形成することによって
、点火栓５に到達する液状燃料の量を最小限にすること
ができる。As described above, the distance between the center of the ignition plug 5 and each of the partition wall extension lines 6a and 7a shown in FIG. By forming the length l of the bulkhead 8a on the side branch boat 7 to be at least 0.8 times the diameter W of the intake boat 7, the amount of liquid fuel that reaches the ignition plug 5 can be minimized. can do.

更に点火栓５の濡れ、くすぶりを防止する手段として本
実施例においては、次に説明するように分岐ボート６．
７の断面形状を形成する。Furthermore, in this embodiment, as a means to prevent the spark plug 5 from getting wet and smoldering, a branch boat 6.
7 is formed.

すなわち、第４図に示す分岐ボート６．７は、その最下
稜線が吸気弁座近傍で夫々点火栓５がら最も離れるよう
に形成したものである。このように、分岐ボート６．７
を形成した場合は、分岐ボート６．７の下側内壁を流れ
る多くの液状燃料が前記稜線に沿って流れるため、点火
栓への液状燃料の到達量は更に減少する。すなわち、分
岐ボートの軸心が略同様でも、断面略円形の従来例に比
べ、液状燃料が点火栓５から更に離れる方向に燃焼室内
に導入され、液状燃料が点火栓５を直撃する危険性は大
幅に低減される６ 以上説明したように本、実施例による吸気装置では、冷
機時に燃料の気化が不十分なために発生する液状燃料は
、従来と同様に夫々の分岐ボート６゜７の内壁に略沿っ
て燃焼室内に導入されるが、点火栓５に到達する液状燃
料の量を微小に抑えることができる。すなわち、点火栓
５を分岐ボート６゜７の延長空間相互間に配設すること
によって、液状燃料の直撃を防止でき、更に上記実験結
果から明らかなようにｈ／ｄ≧１．０．１／Ｗ≧０．８
とし、分岐ボート６．７の断面形状を上記のように形成
することによって点火栓５に到達する液状燃料の量を大
幅に減少させることができる。このため、点火栓５の濡
れ、くすぶりを防止でき、冷機時の始動性、運転性が大
幅に向上する。That is, the branch boats 6 and 7 shown in FIG. 4 are formed so that their lowest ridge lines are farthest from the respective spark plugs 5 near the intake valve seats. In this way, branch boat 6.7
In this case, much of the liquid fuel flowing along the lower inner wall of the branch boat 6.7 flows along the ridge line, and the amount of liquid fuel reaching the ignition plug further decreases. That is, even if the axes of the branch boats are approximately the same, compared to the conventional example with a substantially circular cross section, the liquid fuel is introduced into the combustion chamber in a direction further away from the ignition plug 5, and there is less risk of the liquid fuel directly hitting the ignition plug 5. 6 As explained above, in the intake systems according to the present invention and the embodiment, the liquid fuel generated due to insufficient vaporization of the fuel when the engine is cold is removed from the inner wall of each branch boat 6 and 7, as in the conventional case. However, the amount of liquid fuel that reaches the spark plug 5 can be kept to a very small amount. That is, by arranging the spark plug 5 between the extension spaces of the branch boats 6.7, direct impact of liquid fuel can be prevented, and as is clear from the above experimental results, h/d≧1.0.1/ W≧0.8
By forming the cross-sectional shape of the branch boat 6.7 as described above, the amount of liquid fuel that reaches the spark plug 5 can be significantly reduced. Therefore, wetting and smoldering of the ignition plug 5 can be prevented, and startability and drivability when the engine is cold are greatly improved.

〈発明の効果〉 本発明は以上説明したように、いわゆる３弁式吸気装置
において、２つの吸気弁に夫々に独立して連通ずると共
に機関内で合流する分岐ボートの延長空間相互間に点火
栓を配設することにより、燃料の気化が不十分な冷機時
に液状燃料が点火栓を直撃することがなく、点火栓の濡
れ、くすぶりが発生することが防止される。このため、
冷機時の始動性及び運転性を向上させることができる。<Effects of the Invention> As explained above, the present invention provides a so-called three-valve intake system in which a spark plug is provided between the extension spaces of the branch boats that communicate with each of the two intake valves independently and merge within the engine. By providing this, liquid fuel will not directly hit the ignition plug when the engine is cold and the fuel is insufficiently vaporized, and the ignition plug will be prevented from getting wet and smoldering. For this reason,
Startability and drivability when the machine is cold can be improved.

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

第１図は本発明の一実施例を示す平面図、第２図は同上
における寸法関係を示す平面図、第３図囚、■は夫々同
上における液状燃料の点火栓への到達量を示すグラフ、
第４図■、ｅ、（Ｃ：ｌは夫々同上における分岐ボート
の断面形状を示す平面図、第５図は従来例を示す平面図
である。 ｌ・・・気筒　　２・・・排気弁　　３．４・・・吸気
弁５・・・点火栓　　６，７・・・分岐ボート　　ｃ・
・・気筒中心軸 特許出願人　　日産自動車株式会社 代理人　弁理士　笹　島　　冨二雄 １２図 第３図（Ａ） 第３図（Ｂ） Ｌ／ｗ 第４図（Ｂ）Fig. 1 is a plan view showing an embodiment of the present invention, Fig. 2 is a plan view showing the dimensional relationship in the above, Fig. 3 is a graph showing the amount of liquid fuel reaching the ignition plug in the above, respectively. ,
Fig. 4 ■, e, (C:l are plan views showing cross-sectional shapes of branch boats in the above, respectively, and Fig. 5 is a plan view showing a conventional example. l...Cylinder 2...Exhaust valve 3 .4... Intake valve 5... Spark plug 6,7... Branch boat c.
... Cylinder center axis patent applicant Nissan Motor Co., Ltd. Agent Patent attorney Fujio Sasashima 12 Figure 3 (A) Figure 3 (B) L/w Figure 4 (B)

Claims (1)

【特許請求の範囲】[Claims] １つの気筒に対してその気筒中心軸まわりに１つの排気
弁、点火栓、２つの吸気弁を備えかつ前記２つの吸気弁
に夫々に独立して連通すると共に機関内で合流する分岐
ポートが設けられた内燃機関において、前記分岐ポート
の延長空間相互間に前記点火栓を配設することを特徴と
する内燃機関の吸気装置。One cylinder is provided with one exhaust valve, a spark plug, and two intake valves around the cylinder center axis, and a branch port is provided that communicates with each of the two intake valves independently and merges within the engine. An intake device for an internal combustion engine, characterized in that the spark plug is disposed between extension spaces of the branch ports.
JP60009851A 1984-10-17 1985-01-24 Intake device for internal-combustion engine Pending JPS61169619A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP60009851A JPS61169619A (en) 1985-01-24 1985-01-24 Intake device for internal-combustion engine
EP85113193A EP0178663B1 (en) 1984-10-17 1985-10-17 Induction port arrangement for internal combustion engine having multiple inlet valves per combustion chamber
DE8585113193T DE3584936D1 (en) 1984-10-17 1985-10-17 INLET CHANNEL SYSTEM FOR AN INTERNAL COMBUSTION ENGINE WITH SEVERAL INLET VALVES PER COMBUSTION ROOM.
US07/258,048 US4873953A (en) 1984-10-17 1988-10-17 Induction port arrangement for internal combustion engine having multiple inlet valves per combustion chamber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60009851A JPS61169619A (en) 1985-01-24 1985-01-24 Intake device for internal-combustion engine

Publications (1)

Publication Number Publication Date
JPS61169619A true JPS61169619A (en) 1986-07-31

Family

ID=11731632

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60009851A Pending JPS61169619A (en) 1984-10-17 1985-01-24 Intake device for internal-combustion engine

Country Status (1)

Country Link
JP (1) JPS61169619A (en)

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