JPH0221570Y2 - - Google Patents
Info
- Publication number
- JPH0221570Y2 JPH0221570Y2 JP4694985U JP4694985U JPH0221570Y2 JP H0221570 Y2 JPH0221570 Y2 JP H0221570Y2 JP 4694985 U JP4694985 U JP 4694985U JP 4694985 U JP4694985 U JP 4694985U JP H0221570 Y2 JPH0221570 Y2 JP H0221570Y2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- intake
- cylinder head
- flow path
- pair
- 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
Links
- 230000000694 effects Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
Landscapes
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Description
【考案の詳細な説明】
「産業上の利用分野」
本考案は、内燃機関の4弁式シリンダヘツドに
おける吸排気構造に関する。[Detailed Description of the Invention] "Industrial Application Field" The present invention relates to an intake and exhaust structure in a four-valve cylinder head of an internal combustion engine.
「従来の技術」
従来、内燃機関の4弁式シリンダヘツドにおけ
る吸排気構造としては、例えば、第4図ないし第
6図に示すものが知られている。これは、一対の
吸気口1,1と一対の排気口2,2が下面(第5
図もしくは第6図における下方側の面でシリンダ
内部側の面)に形成されたシリンダヘツド3の内
部に、一端が上記吸気口1,1に連通し、他端が
該シリンダヘツド3の側方側下面に開口する吸気
流路4と、一端が上記排気口2,2に連通し、他
端が該シリンダヘツド3の側方に開口する排気流
路5と、を形成したものである。``Prior Art'' Conventionally, as an intake and exhaust structure for a four-valve cylinder head of an internal combustion engine, for example, those shown in FIGS. 4 to 6 are known. This is because a pair of intake ports 1, 1 and a pair of exhaust ports 2, 2 are located on the lower surface (the fifth
Inside the cylinder head 3 formed on the lower surface in the figure or the surface on the inside of the cylinder in FIG. An intake flow path 4 that opens to the lower side surface, and an exhaust flow path 5 that communicates with the exhaust ports 2 at one end and opens to the side of the cylinder head 3 at the other end are formed.
「考案が解決しようとする問題点」
ところが、上記従来の吸排気構造では、シリン
ダヘツドの高さに制約がある(通常、該高さはボ
ア径に略等しい)ことなどから、上記吸気流路4
と排気流路5とは略同じ高さで並んで同一の水平
方向に延びており、このために吸排気抵抗が大き
く、機関性能が悪いという欠点があつた。また、
上記吸気流路4と排気流路5を相互に逆方向に水
平に延ばして、吸排気抵抗を低減した構造も知ら
れているが、その吸排気抵抗の低減効果は小さ
く、満足すべきものではなかつた。``Problem to be solved by the invention'' However, in the conventional intake and exhaust structure described above, there is a restriction on the height of the cylinder head (normally, the height is approximately equal to the bore diameter), so the intake flow path is limited. 4
The exhaust flow path 5 and the exhaust flow path 5 are lined up at approximately the same height and extend in the same horizontal direction, resulting in large intake and exhaust resistance and poor engine performance. Also,
A structure is also known in which the intake flow path 4 and the exhaust flow path 5 are extended horizontally in opposite directions to reduce intake and exhaust resistance, but the effect of reducing intake and exhaust resistance is small and is not satisfactory. Ta.
本考案は、上記事情に鑑みてなされたもので、
吸排気抵抗をさらに低減して機関性能を一段と高
めた4弁式シリンダヘツドにおける吸排気構造を
提供することを目的とする。 This invention was made in view of the above circumstances,
An object of the present invention is to provide an intake and exhaust structure for a four-valve cylinder head that further reduces intake and exhaust resistance and further improves engine performance.
「問題点を解決するための手段」
上記目的を達成するために、本考案の吸排気構
造は、シリンダヘツドの内部の下方部位に、各一
端が一対の吸気口にそれぞれ連通し、各他端が該
シリンダヘツドの下面にそれぞれ開口する一対の
吸気流路を形成し、かつ、シリンダヘツドの内部
で上記吸気流路より上方の部位に、該シリンダヘ
ツドを水平方向に貫通する第1排気流路を形成
し、また、シリンダヘツドの内部に、一端が一対
の排気口に連通し、他端側が上記第1排気流路に
連通して該シリンダヘツドの外部に連通する第2
排気流路を形成したものである。"Means for Solving the Problems" In order to achieve the above object, the intake and exhaust structure of the present invention has one end communicating with a pair of intake ports, and one end communicating with a pair of intake ports, and the other end communicating with a pair of intake ports. forming a pair of intake passages each opening at the lower surface of the cylinder head, and a first exhaust passage passing horizontally through the cylinder head at a portion inside the cylinder head above the intake passages. A second exhaust passage is formed inside the cylinder head, one end of which communicates with the pair of exhaust ports, the other end of which communicates with the first exhaust flow path and communicates with the outside of the cylinder head.
It has an exhaust flow path formed therein.
「作用」
そして、本考案の吸排気構造においては、吸気
は上記一対の吸気流路を通じてなされ、排気は上
方に延びる上記第2排気流路と水平方向に延びる
上記第1排気流路とによつてなされ、第1排気流
路は、従来はシリンダヘツドに接続される排気管
として機能する。"Operation" In the intake/exhaust structure of the present invention, air is taken in through the pair of intake passages, and exhaust is exhausted through the second exhaust passage extending upward and the first exhaust passage extending horizontally. The first exhaust flow path conventionally functions as an exhaust pipe connected to the cylinder head.
「実施例」
以下、本考案の一実施例を第1図ないし第3図
を参照して説明する。"Embodiment" Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 3.
図中10は、ボア径をDとすると約1.4Dの高
さを有する4弁式シリンダヘツドで、その下面に
は、一対の吸気口11a,11bと一対の排気口
12a,12bが並べて形成されている。このシ
リンダヘツド10の内部の下方部位には、各一端
が上記一対の吸気口11a,11bにそれぞれ連
通し、各他端が該シリンダヘツド10の側方下面
にそれぞれ開口する一対の吸気流路13a,13
bが形成され、また、シリンダヘツド10の内部
で上記一対の吸気流路13a,13bより上方の
部位には該シリンダヘツド10を水平方向に貫通
する第1排気流路14が形成され、さらに、シリ
ンダヘツド10の内部には、一端が上記一対の排
気口12a,12bに連通し、他端側が上記第1
排気流路14に連通する第2排気流路15が形成
されている。 In the figure, 10 is a four-valve type cylinder head having a height of approximately 1.4D when the bore diameter is D, and a pair of intake ports 11a, 11b and a pair of exhaust ports 12a, 12b are formed side by side on the lower surface. ing. In the lower part of the interior of the cylinder head 10, there is a pair of intake passages 13a, each of which has one end communicating with the pair of intake ports 11a and 11b, and the other end of which opens at the lower side surface of the cylinder head 10. ,13
A first exhaust flow path 14 is formed inside the cylinder head 10 above the pair of intake flow paths 13a and 13b and extends horizontally through the cylinder head 10. Inside the cylinder head 10, one end communicates with the pair of exhaust ports 12a, 12b, and the other end communicates with the first exhaust port 12a, 12b.
A second exhaust flow path 15 communicating with the exhaust flow path 14 is formed.
上記一対の吸気流路13a,13bは、互いに
略同一の流路断面積を有するもので、下方に向つ
て凹なる円弧状に、かつ、シリンダの円周方向に
沿つて延び、その各他端のシリンダヘツド10の
下面における開口部は、シリンダヘツド10の左
右方向(第2図の左右方向)において同一の位置
に並んでいる。そして、一方の吸気流路13aが
他方の吸気流路13bより長く、かつ、径の大き
な円弧状に延びている。 The pair of intake flow passages 13a and 13b have substantially the same cross-sectional area, and extend in a downwardly concave arc shape and along the circumferential direction of the cylinder. The openings on the lower surface of the cylinder head 10 are aligned at the same position in the left-right direction of the cylinder head 10 (left-right direction in FIG. 2). One intake passage 13a is longer than the other intake passage 13b and extends in an arcuate shape with a larger diameter.
また、上記第1排気流路14は、排気口12
a,12bより大きい所定の円形流路断面を有す
るもので、上記一対の吸気流路13a,13bの
各他端の上方部位に位置せしめられ、かつ、多シ
リンダ機関において複数のシリンダヘツド10を
並べて配設する際、該複数のシリンダヘツド10
が並ぶ方向(第2図における上下方向)に水平に
延びている。 Further, the first exhaust flow path 14 is connected to the exhaust port 12.
It has a predetermined circular flow passage cross section larger than that of intake flow passages 13a and 12b, and is located above each other end of the pair of intake passages 13a and 13b, and is used when a plurality of cylinder heads 10 are lined up in a multi-cylinder engine. When disposing, the plurality of cylinder heads 10
(vertical direction in FIG. 2).
さらに、上記第2排気流路15は、一端が上記
一対の排気口12a,12bに連通し、他端側が
上記第1排気流路14に側方から斜めに接続され
ると共に連通路16によつてシリンダヘツド10
の上面に開口せしめられたもので、なだらかに斜
方に向かつて延びており、また、第4図に示す従
来の排気流路5に比し、より大きな流路断面積を
有するものである。 Furthermore, one end of the second exhaust flow path 15 communicates with the pair of exhaust ports 12a and 12b, and the other end side is diagonally connected to the first exhaust flow path 14 from the side and is connected to the communication path 16. Cylinder head 10
The exhaust flow path 5 is opened at the upper surface of the exhaust flow path, and extends in a gentle oblique direction, and has a larger cross-sectional area than the conventional exhaust flow path 5 shown in FIG.
なお、図中17は吸気弁、18は弁ばねであ
る。また、19は弁押金具で、シリンダヘツド1
0の上方部位に鋳造により一体形成された案内部
20の案内孔に摺動自在に嵌入されている。 In addition, in the figure, 17 is an intake valve, and 18 is a valve spring. In addition, 19 is a valve pusher fitting, which is attached to the cylinder head 1.
The guide portion 20 is slidably fitted into a guide hole of a guide portion 20 that is integrally formed in the upper portion of the guide portion 20 by casting.
しかして、上記シリンダヘツド10は、例えば
立型直列8シリンダデイーゼル機関に使用される
場合は第3図に示すように8基が一列に並べられ
て配設される。そして、各吸気流路13a,13
bの開口端に吸気管(図示せず)が接続される一
方、例えば図示の如く2基毎にその各第1排気流
路14が連通され、かつ、その各2基の内一方の
シリンダヘツド10の連通路16の開口端に排気
管21が接続され、残りの各第1排気流路14と
連通路16の各開口端は閉塞部材により塞がれ
る。 When the cylinder heads 10 are used, for example, in a vertical in-line eight-cylinder diesel engine, eight cylinder heads 10 are arranged in a line as shown in FIG. And each intake flow path 13a, 13
While an intake pipe (not shown) is connected to the open end of b, for example, as shown in the figure, the first exhaust passages 14 of every two cylinders are communicated with each other, and one cylinder head of each of the two cylinders is connected to the The exhaust pipes 21 are connected to the open ends of the ten communicating passages 16, and the remaining first exhaust flow passages 14 and the open ends of the communicating passages 16 are closed by closing members.
この状態において、吸気は図示しない吸気管か
ら各一対の吸気流路13a,13b内に入り、吸
気弁17,17の作動に伴つて吸気口11a,1
1bからシリンダ内に噴出する。また、各シリン
ダ内の排気は排気弁の作動に伴つて排気口12
a,12bから第2排気流路15に入り、直接連
通路16から排気管21に流れ出るか、あるいは
第1排気流路14を通じて隣りのシリンダヘツド
10の第1排気流路14に入つて連通路16から
排気管21に流れ出る。 In this state, intake air enters the pair of intake channels 13a, 13b from an intake pipe (not shown), and as the intake valves 17, 17 operate, the intake ports 11a, 1
It is ejected from 1b into the cylinder. In addition, the exhaust inside each cylinder is discharged from the exhaust port 12 with the operation of the exhaust valve.
a, 12b into the second exhaust flow path 15 and directly flows out from the communication path 16 to the exhaust pipe 21, or enters the first exhaust flow path 14 of the adjacent cylinder head 10 through the first exhaust flow path 14 and enters the communication path. 16 and flows out into the exhaust pipe 21.
ここで、上記吸排気構造では、シリンダヘツド
10に2つの吸気流路13a,13bが形成され
ており、しかも、この吸気流路13a,13bは
なだらかな円弧状に延びているから、従来に比し
て流路面積が増大し、かつ、曲がり部分における
圧力損失が減少して、吸気抵抗が減少する。ま
た、上記各吸気流路13a,13bはシリンダの
円周方向に沿つて延びているから、吸気がシリン
ダの円周方向に流入して、強いスワールが発生す
る。またさらに、第2排気流路15は従来のもの
より流路断面積が大きく、しかも、ゆるやかに斜
めに傾斜しながら上方に延びているため排気抵抗
が少ない。さらに、従来は、上記のような立型直
列8シリンダデイーゼル機関においては、シリン
ダヘツドには長い排気管が接続されていたが、上
記シリンダヘツド10の内部には第1排気流路1
4が形成されており、この第1排気流路14が従
来の排気管の機能を果す。このため、排気管21
の長さが短くなり、全体の排気抵抗が大幅に低減
せしめられる。 Here, in the above intake and exhaust structure, two intake passages 13a and 13b are formed in the cylinder head 10, and these intake passages 13a and 13b extend in a gentle arc shape, compared to the conventional one. As a result, the flow path area increases, pressure loss at the bending portion decreases, and intake resistance decreases. Further, since each of the intake air passages 13a and 13b extends along the circumferential direction of the cylinder, the intake air flows in the circumferential direction of the cylinder, generating a strong swirl. Furthermore, the second exhaust flow path 15 has a larger cross-sectional area than the conventional one and extends upward while being gently inclined, so that the exhaust resistance is small. Furthermore, conventionally, in the above-mentioned vertical in-line 8 cylinder diesel engine, a long exhaust pipe was connected to the cylinder head.
4 is formed, and this first exhaust flow path 14 functions as a conventional exhaust pipe. For this reason, the exhaust pipe 21
The length of the exhaust gas is shortened, and the overall exhaust resistance is significantly reduced.
「考案の効果」
以上説明したように、本考案の4弁式シリンダ
ヘツドにおける吸排気構造は、シリンダヘツドの
高さを従来のものより高くすることにより、吸気
流路を一対にし、かつ、第2排気流路を上方に延
びるように設けると共に、従来の排気管の機能を
果す第1排気流路を一体に設けたものであるか
ら、吸気抵抗、排気抵抗が一段と低減されて、機
関性能が向上し、しかも、排気管の配管が容易と
なる等の効果を奏する。"Effects of the Invention" As explained above, the intake and exhaust structure of the four-valve cylinder head of the present invention makes the height of the cylinder head higher than that of the conventional one, thereby forming a pair of intake passages, and Since the two exhaust channels are provided to extend upward and the first exhaust channel is integrated, which functions as a conventional exhaust pipe, intake resistance and exhaust resistance are further reduced, improving engine performance. Moreover, it has the effect of making the exhaust pipe easier to install.
第1図ないし第3図は本考案の一実施例を示す
もので、第1図は側方からの断面図、第2図は下
方からの断面図、第3図は8シリンダ機関に適用
した場合の略図、また、第4図ないし第6図は従
来例を示すもので、第4図は下方からの断面図、
第5図は排気流路を示す側断面図、第6図は吸気
流路を示す側断面図である。
10……4弁式シリンダヘツド、11a,11
b……吸気口、12a,12b……排気口、13
a,13b……吸気流路、14……第1排気流
路、15……第2排気流路。
Figures 1 to 3 show an embodiment of the present invention, in which Figure 1 is a sectional view from the side, Figure 2 is a sectional view from below, and Figure 3 is an embodiment of the present invention applied to an 8-cylinder engine. In addition, FIGS. 4 to 6 show conventional examples, and FIG. 4 is a sectional view from below.
FIG. 5 is a side sectional view showing the exhaust flow path, and FIG. 6 is a side sectional view showing the intake flow path. 10...4-valve cylinder head, 11a, 11
b...Intake port, 12a, 12b...Exhaust port, 13
a, 13b...Intake flow path, 14...First exhaust flow path, 15...Second exhaust flow path.
Claims (1)
た4弁式シリンダヘツドにおいて、上記シリンダ
ヘツドの内部の下方部位には、各一端が上記一対
の吸気口にそれぞれ連通し、各他端が該シリンダ
ヘツドの下面にそれぞれ開口する一対の吸気流路
が形成され、かつ、上記シリンダヘツドの内部で
上記吸気流路より上方の部位には、該シリンダヘ
ツドを水平方向に貫通する第1排気流路が形成さ
れ、また、上記シリンダヘツドの内部には、一端
が上記一対の排気口に連通し、他端側が上記第1
排気流路に連通して該シリンダヘツドの外部に連
通する第2排気流路が形成されて成ることを特徴
とする4弁式シリンダヘツドにおける吸排気構
造。 In a four-valve cylinder head in which a pair of intake ports and a pair of exhaust ports are formed on the lower surface, each one end communicates with the pair of intake ports, and each other end communicates with the pair of intake ports in the lower part of the interior of the cylinder head. A pair of intake passages are formed on the lower surface of the cylinder head, and a first exhaust passage is provided inside the cylinder head above the intake passages, and a first exhaust passage passes through the cylinder head in a horizontal direction. A passage is formed inside the cylinder head, and one end communicates with the pair of exhaust ports, and the other end communicates with the first exhaust port.
An intake and exhaust structure for a four-valve cylinder head, characterized in that a second exhaust flow path is formed which communicates with the exhaust flow path and communicates with the outside of the cylinder head.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4694985U JPH0221570Y2 (en) | 1985-03-30 | 1985-03-30 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4694985U JPH0221570Y2 (en) | 1985-03-30 | 1985-03-30 |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS61164448U JPS61164448U (en) | 1986-10-13 |
JPH0221570Y2 true JPH0221570Y2 (en) | 1990-06-11 |
Family
ID=30561822
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4694985U Expired JPH0221570Y2 (en) | 1985-03-30 | 1985-03-30 |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0221570Y2 (en) |
-
1985
- 1985-03-30 JP JP4694985U patent/JPH0221570Y2/ja not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS61164448U (en) | 1986-10-13 |
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