JPH0338427B2 - - Google Patents
Info
- Publication number
- JPH0338427B2 JPH0338427B2 JP13381482A JP13381482A JPH0338427B2 JP H0338427 B2 JPH0338427 B2 JP H0338427B2 JP 13381482 A JP13381482 A JP 13381482A JP 13381482 A JP13381482 A JP 13381482A JP H0338427 B2 JPH0338427 B2 JP H0338427B2
- Authority
- JP
- Japan
- Prior art keywords
- intake
- distribution box
- cylinder
- branch
- valve
- 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
Links
- 239000000446 fuel Substances 0.000 description 6
- 238000002485 combustion reaction Methods 0.000 description 5
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000009423 ventilation 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
- F02B31/085—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air inlets having two inlet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
- F02M35/108—Intake manifolds with primary and secondary intake passages
- F02M35/1085—Intake manifolds with primary and secondary intake passages the combustion chamber having multiple intake valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
- F02M35/112—Intake manifolds for engines with cylinders all in one line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
- F02M35/10216—Fuel injectors; Fuel pipes or rails; Fuel pumps or pressure regulators
-
- 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)
- Characterised By The Charging Evacuation (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、自動車用として好適な気筒当たり２
個の吸気弁を設けた多吸気弁式多気筒エンジンの
吸気装置に関し、特に吸気マニホールドの構造に
関するものである。[Detailed Description of the Invention] [Industrial Field of Application] The present invention provides two cylinders per cylinder suitable for use in automobiles.
The present invention relates to an intake system for a multi-intake valve type multi-cylinder engine provided with several intake valves, and particularly relates to the structure of an intake manifold.
従来、吸気マニホールドは大気に通じる集合部
と、そこから分岐し吸気弁を介して各気筒の燃焼
室へ通じる分枝部とを有しており、集合部と分枝
部との連結部には吸気通路方向と直交する方向に
長い吸気分配箱が設けられていた。そして、気筒
当り２個の吸気弁を設けた多吸気弁式多気筒エン
ジンに使用する吸気マニホールドでは、各気筒当
たり２個配されかつ断面円形に形成された分枝部
が吸気分配箱に対してその長手方向に並ぶように
接続されていた。
Conventionally, an intake manifold has a collecting part that communicates with the atmosphere and a branch part that branches from there and leads to the combustion chamber of each cylinder via an intake valve. A long intake air distribution box was provided in a direction perpendicular to the direction of the intake passage. In an intake manifold used in a multi-intake valve type multi-cylinder engine with two intake valves per cylinder, two branches are arranged for each cylinder and a branch part with a circular cross section is connected to the intake distribution box. They were connected in such a way that they lined up in the longitudinal direction.
しかるに、このように構成された吸気マニホー
ルドでは、吸気分配箱に多数の分枝部が接続され
ているため、吸気分配箱の一端側に接続された分
枝部と他端側に接続された分枝部とが吸気分配箱
の長手方向に離れることになるため、両者への吸
気の分配にばらつきが生じる恐れがあつた。
However, in the intake manifold configured in this way, a large number of branch parts are connected to the intake distribution box, so the branch part connected to one end of the intake distribution box and the branch part connected to the other end of the intake distribution box. Since the branch parts are separated from each other in the longitudinal direction of the intake air distribution box, there is a risk that the distribution of intake air to the two parts will be uneven.
本発明に係る多気筒エンジンの吸気装置は、分
枝部の吸気分配箱近傍における断面形状を、対向
して配した円弧部とそれら円弧部間を連結する直
線部とで形成された略小判形となし、隣合う気筒
の分枝部を、前記直線部を挟んで連なるように吸
気分配箱近傍の直線で互いに連結させて吸気分配
箱の長手方向に沿つて配列させたものである。
In the intake device for a multi-cylinder engine according to the present invention, the cross-sectional shape of the branch portion near the intake distribution box is approximately oval, which is formed by opposing circular arc portions and a straight portion connecting the circular arc portions. The branch parts of adjacent cylinders are connected to each other by a straight line near the intake air distribution box so as to be connected to each other with the straight line part in between, and are arranged along the longitudinal direction of the intake air distribution box.
分枝部における吸気分配箱近傍での気筒配列方
向に対する寸法が小さくなり、全ての分枝部を吸
気分配箱に接続した際の全幅が小さくなる。
The dimension of the branch part in the vicinity of the intake air distribution box in the cylinder arrangement direction becomes smaller, and the total width when all the branch parts are connected to the intake air distribution box becomes smaller.
以下、本発明の一実施例を第１図ないし第５図
によつて詳細に説明する。
Hereinafter, one embodiment of the present invention will be described in detail with reference to FIGS. 1 to 5.
第１図は本発明に係る多気筒エンジンの吸気装
置を示す断面図、第２図は第１図における−
線断面図、第３図は第１図における−線断面
図、第４図は第１図における−線断面図、第
５図は第４図における−線断面図である。こ
れらの図において、１はエンジン本体で、燃焼室
２を有する。燃焼室２はシリング３、シリダヘツ
ド４及びピストン５によつて形成されている。６
は点火栓である。燃焼室２に面したシリンダヘツ
ド４の壁面には２個の吸気弁７によつて開閉され
る吸気ポート８と排気弁９によつて開閉される排
気ポート１０とが開口している。各吸気ポート８
と各排気ポート１０とは共にシリンダヘツド４内
で集合するいわゆる双子形ポートをなしている。
１１は従来公知のツインカム形動弁機構、１２は
燃料噴射弁である。以上の構成は従来公知のエン
ジンと特に異なるところはない。 FIG. 1 is a sectional view showing an intake system for a multi-cylinder engine according to the present invention, and FIG. 2 is a -
3 is a sectional view taken along the - line in FIG. 1, FIG. 4 is a sectional view taken along the - line in FIG. 1, and FIG. 5 is a sectional view taken along the - line in FIG. 4. In these figures, 1 is an engine main body, which has a combustion chamber 2. The combustion chamber 2 is formed by a syringe 3, a cylinder head 4 and a piston 5. 6
is a spark plug. An intake port 8 opened and closed by two intake valves 7 and an exhaust port 10 opened and closed by an exhaust valve 9 are opened on the wall surface of the cylinder head 4 facing the combustion chamber 2. Each intake port 8
The exhaust ports 10 and 10 together form a so-called twin port that converges within the cylinder head 4.
11 is a conventionally known twin cam type valve mechanism, and 12 is a fuel injection valve. The above configuration is not particularly different from conventionally known engines.
吸気ポート８は後述する制御弁１４、吸気マニ
ホールド１５を介して大気に通じており、これら
は一連の吸気通路を形成する。吸気マニホールド
１５は大気に通じる集合部１６と吸気ポート８に
通じる分枝部１７とからなつており、両部１６，
１７は吸気分配箱１８によつて連結されている。
各吸気通路は分枝部１７から制御弁１４に至る間
を高負荷用通路１９と全域用通路２０とに区画
し、両通路１９，２０は吸気ポート８の一部８ａ
においてのみ互いに連通している。制御弁１４は
スペーサ状の弁胴１４ａと弁胴１４ａに形成され
た両通路１９，２０貫いて設けられた弁軸１４ｂ
及び前記弁軸１４ｂによつて高負荷用通路１９内
に支持された蝶形の弁板１４ｃとからなり、エン
ジンが所定の高負荷運転をしているときのみ高負
荷用通路１９を開く。前記弁軸１４ｂはその最外
端に固設したアーム１４ｄにおいて、ダイアフラ
ム（図示していない）に連結されており、そのダ
イアフラムは後述する絞り弁２３，２４より下流
側の吸気通路負圧に応動してその負圧が高い（圧
力が低い）とき、すなわち、エンジン負荷が小さ
いとき制御弁１４を閉じ、エンジン負荷が所定の
大きさに至つたとき開いて以後エンジンが高負荷
運転されている間、開弁状態に保たれる。 The intake port 8 communicates with the atmosphere via a control valve 14 and an intake manifold 15, which will be described later, and these form a series of intake passages. The intake manifold 15 consists of a gathering part 16 communicating with the atmosphere and a branching part 17 communicating with the intake port 8. Both parts 16,
17 are connected by an air intake distribution box 18.
Each intake passage is divided into a high-load passage 19 and a wide-area passage 20 between the branch portion 17 and the control valve 14, and both passages 19 and 20 are part 8a of the intake port 8.
They communicate with each other only in The control valve 14 includes a spacer-shaped valve body 14a and a valve shaft 14b provided through both passages 19 and 20 formed in the valve body 14a.
and a butterfly-shaped valve plate 14c supported in the high-load passage 19 by the valve shaft 14b, and opens the high-load passage 19 only when the engine is operating at a predetermined high load. The valve shaft 14b is connected to a diaphragm (not shown) at an arm 14d fixed at its outermost end, and the diaphragm responds to negative pressure in the intake passage downstream of throttle valves 23 and 24, which will be described later. When the negative pressure is high (pressure is low), that is, when the engine load is low, the control valve 14 is closed, and when the engine load reaches a predetermined level, it is opened, and thereafter, while the engine is being operated at high load. , the valve is kept open.
高負荷用通路１９と全域用通路２０との断面形
状は、吸気分配箱１８近傍では第５図で示すよう
に対向して配した円弧部２１，２１とそれら円弧
部間を連結する直線部２２，２２とで形成された
略小判形をなしており、各分枝部１７の幅を狭く
してある。また、下流側の制御弁付近では第３図
で示すように略Ｄ字を２個向合わせた形に配さ
れ、大きな断面積を持つ吸気通路を狭い空間に合
理的に通してある。なお、前記弁板１４ｃもそれ
にならつて同形に形成してある。前記直線部２２
を構成する隔壁は第４図で示すように気筒間を区
画する部分が、高負荷用通路１９と全域用通路２
０とを区画する部分より寸法Ｌだけ長くして、隣
接する気筒の吸気流が互いに干渉しないよう配慮
してある。また、前記燃料噴射弁１２の開口位置
は前記吸気ポート８をなす双子形ポートの先端部
中央よりｓだけ偏倚しているが、噴射方向は先端
部中央を指向しており、全負荷時に噴射された燃
料が２個の吸気ポートの一方へ偏ることがないよ
うにしてある。２３，２４は吸気流量を制御する
一次側と二次側との絞り弁、２５は冷機始動時に
吸気通路内へ燃料を供給する始動用燃料噴射ノズ
である。 The cross-sectional shapes of the high-load passage 19 and the wide-area passage 20 are as follows: near the intake distribution box 18, as shown in FIG. , 22, and has a substantially oval shape, and each branch portion 17 has a narrow width. Further, in the vicinity of the control valve on the downstream side, as shown in FIG. 3, the intake passages are arranged in the shape of two D-shapes facing each other, and an intake passage having a large cross-sectional area is rationally passed through a narrow space. Note that the valve plate 14c is also formed in the same shape. Said straight part 22
As shown in FIG. 4, the partition wall constituting the
It is made longer by a dimension L than the part that separates 0 and 0, in order to prevent the intake air flows of adjacent cylinders from interfering with each other. Furthermore, the opening position of the fuel injection valve 12 is offset by s from the center of the tip of the twin-shaped port forming the intake port 8, but the injection direction is directed toward the center of the tip, and the fuel is injected at full load. This prevents the fuel from being diverted to one of the two intake ports. Reference numerals 23 and 24 indicate throttle valves on the primary side and secondary side for controlling the intake flow rate, and 25 indicates a starting fuel injection nozzle that supplies fuel into the intake passage at the time of starting a cold engine.
次にこの実施例エンジンの作動を説明する。エ
ンジンが始動すると、大気が集合部１６から吸入
され、絞り弁２３，２４で流量を計量され吸気分
配１８で各分枝部１７に分配される。そして、制
御弁１４が閉じている低負荷運転時は全域用通路
２０のみを、また制御弁１４が開いている高負荷
運転時は両通路１９，２０を経て燃焼室２に至
る。よつて、低負荷運転時にも吸気の流速を高速
に維持できる。すなわち、吸気通路の断面積が減
少しているので、吸気流速が速く高い充填効率が
得られ、急加速が可能となる。ここでエンジン出
力を増すべく一次側の絞り弁２３、或いな双方の
絞り弁２３，２４を大きく開弁すると、それより
下流側の吸気通路負圧が低下し（圧力が高い）制
御弁１４は高負荷用通路１９を開く。このように
して吸気通路の断面積が拡大するので、多量の吸
気が大きな通気抵抗を受けること無く吸入され容
易に大出力が得られる。 Next, the operation of this embodiment engine will be explained. When the engine starts, atmospheric air is taken in from the collecting section 16, the flow rate is measured by the throttle valves 23 and 24, and the air is distributed to each branch section 17 by the intake air distribution 18. The combustion chamber 2 is reached through only the wide area passage 20 during low load operation when the control valve 14 is closed, and through both passages 19 and 20 during high load operation when the control valve 14 is open. Therefore, the intake air flow rate can be maintained at a high speed even during low load operation. That is, since the cross-sectional area of the intake passage is reduced, the intake air flow rate is high, high filling efficiency is obtained, and rapid acceleration is possible. If the throttle valve 23 on the primary side or both throttle valves 23 and 24 are opened wide in order to increase the engine output, the negative pressure in the intake passage on the downstream side decreases (the pressure is high), and the control valve 14 Open the high load passage 19. Since the cross-sectional area of the intake passage is expanded in this way, a large amount of intake air is taken in without being subjected to large ventilation resistance, and a large output can be easily obtained.
したがつて、このような構成された本発明に係
る多気筒エンジンの吸気装置によれば、分枝部１
７における吸気分配箱１８近傍での気筒配列方向
に対する寸法が小さくなるので、全ての分枝部１
７を吸気分配箱１８に接続した際の全幅が小さく
なる。このため、吸気分配箱１８における分枝部
接続部分の長手方向の寸法を小さくすることがで
きる。 Therefore, according to the intake device for a multi-cylinder engine according to the present invention configured as described above, the branch portion 1
Since the dimension in the cylinder arrangement direction near the intake distribution box 18 in 7 becomes smaller, all the branch parts 1
7 is connected to the intake air distribution box 18, the overall width becomes smaller. Therefore, the longitudinal dimension of the branch connection portion in the intake air distribution box 18 can be reduced.
また、本実施例で示したように各分枝部１７に
おける下流側の制御弁付近の断面形状を、第３図
で示すように略Ｄ字形の孔を２個向い合わせた形
状とすると、大きな断面積を持つ吸気通路をシリ
ンダヘツド４の一気筒分の狭い空間に合理的に接
続できて、分枝部１７やシリダ３をクランク室へ
固定するスタツドボルトと吸気通路とが干渉する
ことがなく、この種エンジンの設計が著しく容易
になる。 Further, as shown in this embodiment, if the cross-sectional shape near the downstream control valve in each branch portion 17 is made into a shape with two approximately D-shaped holes facing each other as shown in FIG. The intake passage having a cross-sectional area can be rationally connected to the narrow space for one cylinder in the cylinder head 4, and the intake passage does not interfere with the stud bolts that fix the branch part 17 and the cylinder 3 to the crank chamber. , the design of this type of engine becomes significantly easier.
以上説明したように本発明に係る多気筒エンジ
ンの吸気装置は、分枝部の吸気分配箱近傍におけ
る断面形状を、対向して配した円弧部とそれら円
弧部間を連結する直線部とで形成された略小判形
となし、隣合う気筒の分枝部を、前記直線部を挟
んで連なるように吸気分配箱近傍の直線部で互い
に連結させて吸気分配箱の長手方向に沿つて配列
させたため、分枝部における吸気分配箱近傍での
気筒配列方向に対する寸法が小さくなり、全ての
分枝部を吸気分配箱に接続した際の全幅が小さく
なる。したがつて、吸気分配箱における分子部接
続部分の長手方向の寸法を小さくすることができ
るから、各気筒へ吸気を均等に分配することがで
きる。
As explained above, in the intake system for a multi-cylinder engine according to the present invention, the cross-sectional shape of the branch portion near the intake distribution box is formed by opposing arcuate portions and a straight portion connecting the arcuate portions. The branch parts of adjacent cylinders are connected to each other at the straight part near the intake distribution box so that the branch parts of adjacent cylinders are connected to each other at the straight part near the intake distribution box, and are arranged along the longitudinal direction of the intake distribution box. , the dimension of the branch portion in the vicinity of the intake air distribution box in the cylinder arrangement direction becomes smaller, and the overall width when all the branch portions are connected to the intake air distribution box becomes smaller. Therefore, since the longitudinal dimension of the molecular connection portion in the intake air distribution box can be reduced, the intake air can be evenly distributed to each cylinder.
第１図は本発明に係る多気筒エンジンの吸気装
置を示す断面図、第２図は第１における−線
断面図、第３図は第１図における−線断面
図、第４図は第１図における−線断面図、第
５図は第４図における−線断面図である。
７……吸気弁、１５……吸気マニホールド、１
６……集合部、１７……分枝部、１８……吸気分
配箱。
FIG. 1 is a cross-sectional view showing an intake system for a multi-cylinder engine according to the present invention, FIG. 2 is a cross-sectional view taken along the - line in FIG. FIG. 5 is a sectional view taken along the line - in FIG. 4. FIG. 7...Intake valve, 15...Intake manifold, 1
6...Gathering part, 17...Branch part, 18...Intake distribution box.
Claims (1)
筒を有し、各気筒の吸気通路を各吸気弁に通じる
分枝部毎に吸気分配箱内へ開口させてマニホール
ドを構成した多気筒エンジンにおいて、前記分枝
部の吸気分配箱近傍における断面形状を、対向し
て配した円弧部とそれら円孤部間を連結する直線
部とで形成された略小判形となし、隣合う気筒の
分枝部を、前記直線部を挟んで連なるように吸気
分配箱近傍の直線部で互いに連結させて吸気分配
箱の長手方向に沿つて配列させてなる多気筒エン
ジンの吸気装置。1. In a multi-cylinder engine having a complex number of cylinders each having at least two intake valves, the intake passage of each cylinder is opened into an intake distribution box at each branch part leading to each intake valve to form a manifold. , the cross-sectional shape of the branch portion near the intake distribution box is approximately oval-shaped formed by opposing arcuate portions and a straight portion connecting these arcuate portions, and the branch portion of the adjacent cylinder is An intake system for a multi-cylinder engine, in which the sections are connected to each other at a straight section near the intake distribution box so as to be connected to each other with the straight section interposed therebetween, and are arranged along the longitudinal direction of the intake distribution box.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57133814A JPS5925071A (en) | 1982-08-02 | 1982-08-02 | Suction device for multi-cylinder engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57133814A JPS5925071A (en) | 1982-08-02 | 1982-08-02 | Suction device for multi-cylinder engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5925071A JPS5925071A (en) | 1984-02-08 |
| JPH0338427B2 true JPH0338427B2 (en) | 1991-06-10 |
Family
ID=15113658
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57133814A Granted JPS5925071A (en) | 1982-08-02 | 1982-08-02 | Suction device for multi-cylinder engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5925071A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH022934Y2 (en) * | 1985-05-10 | 1990-01-24 | ||
| JP5777955B2 (en) * | 2011-07-03 | 2015-09-16 | 本田技研工業株式会社 | Intake manifold |
-
1982
- 1982-08-02 JP JP57133814A patent/JPS5925071A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5925071A (en) | 1984-02-08 |
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