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JP3117349B2 - Combustion chamber of subchamber internal combustion engine - Google Patents

Combustion chamber of subchamber internal combustion engine

Info

Publication number
JP3117349B2
JP3117349B2 JP05348924A JP34892493A JP3117349B2 JP 3117349 B2 JP3117349 B2 JP 3117349B2 JP 05348924 A JP05348924 A JP 05348924A JP 34892493 A JP34892493 A JP 34892493A JP 3117349 B2 JP3117349 B2 JP 3117349B2
Authority
JP
Japan
Prior art keywords
chamber
sub
combustion chamber
main combustion
auxiliary passage
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 - Fee Related
Application number
JP05348924A
Other languages
Japanese (ja)
Other versions
JPH07119467A (en
Inventor
忠雄 大村
浩二 井元
洋一 片岡
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to JP05348924A priority Critical patent/JP3117349B2/en
Publication of JPH07119467A publication Critical patent/JPH07119467A/en
Application granted granted Critical
Publication of JP3117349B2 publication Critical patent/JP3117349B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【産業上の利用分野】本発明は、副室式内燃機関の燃焼
室に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combustion chamber of a sub-chamber internal combustion engine.

【0002】[0002]

【従来の技術】図には従来の副室式ディーゼル機関の
燃焼室近傍の断面図が示されている。図において4はシ
リンダヘッド、7はピストン、8はシリンダであり、該
ピストンの上面、シリンダヘッド4の下面及びシリンダ
8の内面により主燃焼室1が区画形成される。
2. Description of the Related Art FIG. 5 is a sectional view showing the vicinity of a combustion chamber of a conventional sub-chamber diesel engine. In the figure, reference numeral 4 denotes a cylinder head, 7 denotes a piston, and 8 denotes a cylinder. The main combustion chamber 1 is defined by an upper surface of the piston, a lower surface of the cylinder head 4 and an inner surface of the cylinder 8.

【0003】2は副室で、シリンダヘッド4の内部に、
該シリンダヘッド4とこれに圧入された副室口金9とに
より区画形成される。3は前記主燃焼室1と副室2とを
連通する副室噴口である。前記副室2は、シリンダ中心
線A−Aから一定距離を存した外周寄りに設けられる。
[0003] 2 is a sub-chamber, inside the cylinder head 4,
The cylinder head 4 and the sub-chamber base 9 press-fitted therein are defined. Reference numeral 3 denotes a sub chamber injection port for communicating the main combustion chamber 1 with the sub chamber 2. The sub-chamber 2 is provided near the outer periphery at a certain distance from the cylinder center line AA.

【0004】5は副室2内に向けて燃料を噴射する燃料
噴射弁、6は副室2内のガスを加熱するためのグロープ
ラグである。
[0004] Reference numeral 5 denotes a fuel injection valve for injecting fuel into the sub-chamber 2, and reference numeral 6 denotes a glow plug for heating gas in the sub-chamber 2.

【0005】前記のような従来の副室式ディーゼル機関
の作用について説明する。機関の圧縮行程において、ピ
ストン7により主燃焼室1内の空気が圧縮され、副室噴
口3を経て副室2へ流入して渦流Sを生成する。渦流S
の速度はピストン7が上死点近傍にくると増大する。渦
流Sの方向に沿って燃料噴射弁5より燃料を噴射すると
燃料は渦流Sと共に副室2内を旋回しながら空気との混
合気形成が行われグロープラグ6付近より着火し始めて
燃焼する。副室2内の燃焼ガス及び未燃ガスは主燃焼室
1と副室2の圧力差(主燃焼室の圧力<副室の圧力)と
ピストン7の下降運動によって副室噴口3を通って主燃
焼室1へ噴出する。噴出ガスはピストン7に仕事をする
と同時に主燃焼室1内の空気と混合しあって更に拡散燃
焼が進む。
The operation of the above-described conventional sub-chamber diesel engine will be described. In the compression stroke of the engine, the air in the main combustion chamber 1 is compressed by the piston 7 and flows into the sub-chamber 2 via the sub-chamber injection port 3 to generate a vortex S. Eddy current S
Increases when the piston 7 comes near the top dead center. When the fuel is injected from the fuel injection valve 5 in the direction of the vortex S, the fuel is swirled with the vortex S in the sub-chamber 2 to form an air-fuel mixture and ignites near the glow plug 6 to start burning. The combustion gas and unburned gas in the sub-chamber 2 pass through the sub-chamber injection port 3 by the pressure difference between the main combustion chamber 1 and the sub-chamber 2 (the pressure of the main combustion chamber <the pressure of the sub-chamber) and the downward movement of the piston 7. Spouts into the combustion chamber 1. The ejected gas works on the piston 7 and at the same time mixes with the air in the main combustion chamber 1 to further promote diffusion combustion.

【0006】[0006]

【発明か解決しようとする課題】副室式ディーゼル機関
の出力及び燃費の向上を図るには、副室噴口面積を拡大
して副室内の未燃、既燃ガスをすばやく主燃焼室へ噴出
させ主燃焼室での燃焼期間を短縮し等容度を向上させる
必要がある。しかしながら、副室噴口面積拡大には副
室、主燃焼室内の燃焼を確保する上で自ずと限界があ
り、従来の噴口面積もある一定のところまで拡げている
が、それ以上拡げると副室内の混合気形成エネルギが不
足(副室内渦流速度低下による)になり、副室内の燃焼
が悪化し、更には主燃焼室内の燃焼までが緩慢となって
性能(出力、燃費)の低下、排ガス(HC,CO)性能
の悪化を招く。
In order to improve the output and fuel efficiency of the sub-chamber type diesel engine, the area of the sub-chamber injection port is enlarged so that unburned and burned gas in the sub-chamber is quickly injected into the main combustion chamber. It is necessary to shorten the combustion period in the main combustion chamber and improve the isocapacity. However, there is a limit in securing the combustion in the sub-chamber and main combustion chamber, and the conventional spout area has been expanded to a certain level. Insufficient gas formation energy (due to reduced vortex flow velocity in the sub-chamber), combustion in the sub-chamber deteriorates, and even combustion in the main combustion chamber is slowed down, performance (output, fuel consumption) is reduced, and exhaust gas (HC, HC, CO) The performance is deteriorated.

【0007】本発明の目的は副室式内燃機関特に副室式
ディーゼル機関において、副室内の燃焼を促進させるこ
とにより主燃焼室内の燃焼を促進させ、機関サイクルの
等容度、燃焼効率を向上し、副室噴口を絞った状態下
(低速高負荷性能が良好)においても出力及び燃費の向
上が図られ、吐煙、HC等の排ガス性能が改善される副
室式内燃機関の燃焼室を提供することにある
SUMMARY OF THE INVENTION An object of the present invention is to promote combustion in a main combustion chamber by promoting combustion in a sub-chamber in a sub-chamber internal combustion engine, particularly in a sub-chamber diesel engine, thereby improving the isocapacity and combustion efficiency of an engine cycle. In addition, the combustion chamber of the sub-chamber internal combustion engine, in which the output and fuel efficiency are improved even under the condition where the sub-chamber injection port is narrowed (low speed and high load performance is good) and the performance of exhaust gas such as smoke and HC is improved. To provide .

【0008】[0008]

【課題を解決するための手段】本発明に係る副室式内燃
機関の燃焼室は、シリンダヘッドの内壁と該シリンダヘ
ッドに圧入される副室口金とにより区画形成された副室
を、副室口金に突設された副室噴口を介して主燃焼室に
連通するように構成された副室式内燃機関において、前
記副室(2)の中心線(B−B)とシリンダ中心線(A
−A)との間の副室噴口(3)に隣接した位置に、主燃
焼室(1)と副室(2)とを連通する補助通路(33)
を設けるとともに、当該補助通路(33)内にはばね
(11)により前記主燃焼室(1)から副室(2)への
ガス流のみを許容するように付勢された逆止弁(20
0、300)を設け、逆止弁は、弁体(13、11
2)と一体でリフトする軸部(112a、212a)
有し、前記補助通路(33)に前記軸部(112a、2
12a)が進入したときのガス流路を、主燃焼(1)側
から副室(2)側に向けて流路の面積が縮小されるよう
に形成してなることを特徴とする。
A combustion chamber of a sub-chamber internal combustion engine according to the present invention comprises a sub-chamber defined by an inner wall of a cylinder head and a sub-chamber base pressed into the cylinder head. In a sub-chamber internal combustion engine configured to communicate with a main combustion chamber via a sub-chamber injection port protruding from a base, a center line (BB) of the sub-chamber (2) and a cylinder center line (A) are provided.
-A), an auxiliary passage (33) communicating the main combustion chamber (1) and the sub chamber (2) at a position adjacent to the sub chamber injection port (3).
And a check valve (20) urged by a spring (11) in the auxiliary passage (33) so as to allow only the gas flow from the main combustion chamber (1) to the sub chamber (2).
0,300) is provided, said check valve, the valve element (13,11
2) a shaft which lifts integrally has (112a, 212a), wherein the shaft portion in the auxiliary passage (33) (112a, 2
The gas flow path when 12a) enters the main combustion (1) side
So that the area of the flow path is reduced from
It is characterized by being formed in .

【0009】[0009]

【作用】副室式内燃機関の圧縮行程において、圧縮され
た主燃焼室の空気が副室噴口を通って副室に流入し副室
内に渦流を生成する。渦流の速度はピストンが上死点近
傍にくると大きくなる。主燃焼室と副室との差圧が逆止
弁のばねの力を超えると、逆止弁を押し開き補助通路を
通って副室内へ前記渦流に対向する向きに流入する。前
記逆止弁の開く時期は前記ばね力を変えることにより変
られる。ピストンが上死点付近になると、前記渦流の速
度は増大しその方向へ燃料が燃料噴射弁から噴射され、
燃料は空気と混合したグロープラグ付近で着火し燃焼が
始まる。
In the compression stroke of the sub-chamber internal combustion engine, the compressed air in the main combustion chamber flows into the sub-chamber through the sub-chamber injection port to generate a vortex in the sub-chamber. The velocity of the vortex increases as the piston approaches the top dead center. When the pressure difference between the main combustion chamber and the sub chamber exceeds the force of the spring of the check valve, the check valve is pushed open and flows through the auxiliary passage into the sub chamber in a direction opposite to the vortex. The opening timing of the check valve is changed by changing the spring force. When the piston is near top dead center, the speed of the vortex increases and fuel is injected from the fuel injector in that direction,
The fuel ignites near the glow plug mixed with air and starts burning.

【0010】前記の着火した混合ガスは補助通路から流
入した空気と衝突し、撹乱されながら速度が減衰する。
このため副室内の燃焼による圧力が高くなり、副室内の
未燃、既燃ガスが副室噴口から主燃焼室へ噴出されやす
くなる。前記補助通路は逆止弁が閉じ主燃焼室向きに流
れないで、未燃、既燃ガスは分散せずに噴流ペネトレー
シインを低下させることなく、まとまって副室噴口から
主燃焼室へ噴出される。
The ignited mixed gas collides with the air flowing from the auxiliary passage, and its velocity is attenuated while being disturbed.
For this reason, the pressure due to the combustion in the sub-chamber increases, and the unburned and burned gas in the sub-chamber is easily ejected from the sub-chamber injection port to the main combustion chamber. In the auxiliary passage, the check valve closes and does not flow toward the main combustion chamber, the unburned and burned gas is not dispersed, and the jet is discharged from the sub chamber injection port into the main combustion chamber without lowering the jet penetration. Is done.

【0011】さらに、逆止弁の円形状あるいはテーパ状
軸部が補助通路のテーパ状あるいは円形状通路部内に進
入することにより補助通路の面積が主燃焼室側から副室
側に向けて絞られ、これにより副室内渦流への対向流の
流速が増大し、渦流への衝突エネルギがさらに増大し
て、副室内での撹拌混合作用を促進する。
Further, when the circular or tapered shaft portion of the check valve enters the tapered or circular passage portion of the auxiliary passage, the area of the auxiliary passage is changed from the main combustion chamber side to the sub chamber.
Squeezed toward the side, thereby the flow rate of the counter flow is increased to the secondary chamber vortex, further increasing the collision energy to the vortex, to promote stirring and mixing action of the sub chamber.

【0012】[0012]

【実施例】本発明に係る実施例を図1〜図に基づき説
明する。第1実施例を示す図1〜2において、8はシ
リンダ、4はシリンダヘッド、7はピストン、1は該ピ
ストン7の上部、シリンダヘッド4及びシリンダ8に区
画構成された主燃焼室である。2は副室でシリンダヘッ
ド4、及び該シリンダヘッド4に圧入された副室口金9
により区画形成され、シリンダヘッド4側の上部が半球
状、副室口金9側の下部が円錐台形状に形成されてい
る。
The embodiment according to the embodiment of the present invention will be described with reference to FIGS. In Fig. 1 to FIG. 2 showing the first embodiment, 8 cylinder, the cylinder head 4, 7 piston, 1 main combustion chamber partitioned configured upper portion of the piston 7, the cylinder head 4 and the cylinder 8 It is. Reference numeral 2 denotes a sub-chamber, a cylinder head 4 and a sub-chamber base 9 press-fitted into the cylinder head 4.
The upper part on the cylinder head 4 side is formed in a hemispherical shape, and the lower part on the sub chamber base 9 side is formed in a truncated cone shape.

【0013】3は前記主燃焼室1と副室2とを連通する
副室噴口で、ピストン7の圧縮行程時主燃焼室1から副
室2内に流入する空気流が副室2内で渦流Sを効果的に
形成するよう、斜め方向に穿設されている。A−Aはシ
リンダ中心線、B−Bは副室中心線である。前記シリン
ダヘッド4には、副室2内へ対向して燃焼噴射弁5及び
グロープラグ6が装着されている。
Reference numeral 3 denotes a sub-chamber injection port for communicating the main combustion chamber 1 with the sub-chamber 2. The air flow flowing from the main combustion chamber 1 into the sub-chamber 2 during the compression stroke of the piston 7 is swirled in the sub-chamber 2. It is drilled in an oblique direction so as to form S effectively. AA is a cylinder center line, and BB is a sub-chamber center line. A combustion injection valve 5 and a glow plug 6 are mounted on the cylinder head 4 so as to face into the sub chamber 2.

【0014】33は副室口金9の底部に穿設された補助
通路で、前記副室噴口3とシリンダ中心線A−Aとの間
の部位に副室2と主燃焼室1とを連通して設けられる。
前記補助通路33は、後述するように、その形状を円筒
状孔あるいはテーパ状孔とされるとともに、その向きを
該補助通路中心と副室の内側底面とのなす角θが45°
〜110°に設定される。
Reference numeral 33 denotes an auxiliary passage formed in the bottom of the sub-chamber base 9, which communicates the sub-chamber 2 and the main combustion chamber 1 with a portion between the sub-chamber injection port 3 and the cylinder center line AA. Provided.
The auxiliary passage 33, as described later, while being the shape of a cylindrical hole or Te over path shaped holes, the orientation angle θ of the inner bottom surface of the auxiliary passage center and the auxiliary chamber 45 °
It is set to 110110 °.

【0015】また、前記補助通路33は副室噴口3とシ
リンダ中心線A−Aとの間の部位に、主燃焼室1と副室
2とを連通して設けられ、その向きを、該補助通路33
と副室2の内側底面とのなす角θが45°〜110°に
なるように設定される。
[0015] Also, the a portion between the auxiliary passage 33 is subchamber injection port 3 and the cylinder center line A-A, provided to communicate with the main combustion chamber 1 and subchamber 2, its orientation, the Auxiliary passage 33
Is set so that the angle θ formed between the sub-chamber 2 and the inner bottom surface of the sub-chamber 2 is 45 ° to 110 °.

【0016】助通路近傍の詳細を示す図において、
200は逆止弁で、ばね受112、球状の弁体13、弁
用のばね11とより成り、主燃焼室1側から副室2側へ
向かうガスの流れのみを許容するように構成される。
[0016] In FIG. 2 showing details of auxiliary passages vicinity,
Reference numeral 200 denotes a check valve which includes a spring receiver 112, a spherical valve body 13, and a valve spring 11, and is configured to allow only a gas flow from the main combustion chamber 1 side to the sub chamber 2 side. .

【0017】前記逆止弁200のばね受け112の上部
には円柱状の軸部112aが設されるとともに、前記
補助通路33の副室2側開口部は前記弁体13とともに
ばね受112がリフトしたとき該軸部112aが進入し
て可変スロートを形成するようなテーパ状通路331に
形成される。
[0017] with cylindrical shaft portion 112a is set cut in the upper part of the spring bearing 112 of the check valve 200, subchamber 2 side opening of the auxiliary channel 33 has the valve element 13 the spring receiver 112 with The shaft portion 112a is formed in a tapered passage 331 that enters and forms a variable throat when lifted.

【0018】図には本発明の第実施例を示す。この
実施例の場合は、逆止弁300のばね受212の上部に
突設される軸部212aを上端部が細くなるようなテー
パ状に形成するとともに、該軸部212aが進入する補
助通路33を円形状通路332に形成している。
FIG. 3 shows a second embodiment of the present invention. In the case of this embodiment, the shaft portion 212a projecting above the spring receiver 212 of the check valve 300 is formed in a tapered shape such that the upper end portion becomes thinner, and the auxiliary passage 33 into which the shaft portion 212a enters. Are formed in the circular passage 332.

【0019】次に前記第1、第2実施例の作用を説明す
る。機関の圧縮行程中、ピストン7の上昇により主燃焼
室1内の空気が圧縮され、副室噴口3を通って副室2内
へ流入し渦流Sが生成される。渦流Sの速度はピストン
7が上死点近傍にくると増大する。また主燃焼室1内の
空気は、副室噴口3に隣接した補助通路33を通って副
室2への流入が可能であるが、補助通路33中に設けた
逆止弁200、300のばね11の力が主燃焼室1と副
室2との間の圧力差を超えた時に逆止弁200、300
が開弁すると、渦流Sに対向する形で流入し、対向流を
発生させる。前記ばね11の取付力を変えることによっ
て開弁タイミングが変化し、副室2へのガスの流入時期
を変えることができる。
Next , the operation of the first and second embodiments will be described. During the compression stroke of the engine, the air in the main combustion chamber 1 is compressed by the rise of the piston 7, flows into the sub-chamber 2 through the sub-chamber injection port 3, and the vortex S is generated. The velocity of the vortex S increases when the piston 7 comes near the top dead center. The air in the main combustion chamber 1 can flow into the sub-chamber 2 through the auxiliary passage 33 adjacent to the sub-chamber injection port 3, and the springs of the check valves 200 and 300 provided in the auxiliary passage 33 are provided. check valve 200 and 300 when a force of 11 exceeds the pressure differential between the main combustion chamber 1 and subchamber 2
When the valve is opened, it flows in a form opposite to the vortex S to generate a counter flow. By changing the mounting force of the spring 11, the valve opening timing changes, and the timing of the gas flowing into the sub chamber 2 can be changed.

【0020】ピストン7が上死点付近になると渦流Sの
速度は増大し、その方向に沿って燃焼噴射弁5から燃料
を噴射すると、この燃料が空気と混合し、渦流Sの下流
側に設置されたグロープラグ6付近で着火し燃焼が始ま
る。この未燃、既燃ガスはほぼ同時に、ある任意の時期
に逆止弁200、300が開き補助通路33から流入し
た空気の対向流と衝突し乱れながら減衰する。
When the piston 7 is near the top dead center, the velocity of the vortex S increases, and when fuel is injected from the combustion injection valve 5 along the direction, the fuel mixes with air and is installed downstream of the vortex S. Ignition occurs near the glow plug 6 and combustion starts. At approximately the same time, the unburned gas and the burned gas are attenuated while the check valves 200 and 300 are opened at an arbitrary time and collide with the counterflow of the air flowing from the auxiliary passage 33 and are disturbed.

【0021】このため副室2内の未燃、既燃ガスは主燃
焼室1へ噴出しやすくなるとともに、副室2内の燃焼圧
力によって逆止弁200、300は閉じられて、未燃、
既燃ガスは分散せずに噴流ペネトレーションを低下させ
ることなく、まとまって副室噴口3を通って速やかに主
燃焼室1へ噴出する。主燃焼室1へ噴出された噴流ガス
は、主燃焼室1内の空気と混合しながら再燃し、ピスト
ン7を下方へ押し下げて仕事をする
As a result, the unburned and burned gas in the sub-chamber 2 is easily discharged into the main combustion chamber 1, and the check valves 200 and 300 are closed by the combustion pressure in the sub-chamber 2, and
The burned gas is quickly dispersed into the main combustion chamber 1 through the sub chamber injection port 3 without dispersing and lowering the jet penetration. The jet gas ejected to the main combustion chamber 1 re-combustes while mixing with the air in the main combustion chamber 1, and pushes down the piston 7 to perform work .

【0022】また、逆止弁200,300が開弁する
と、ばね受112,212の軸部112a,212aが
上昇して補助通路33内に進入し、ガス通路が絞られ
る。この通路面積は、軸部又は補助通路の何れか一方が
テーパ状となっているので、ピストン7の上昇に伴う弁
体13及びばね受112,212の上昇とともに縮小さ
れる。このため補助通路33を通って副室2内に、副室
噴口3から流入する渦流Sに対向して噴出されるガスの
流速が増大し、副室2内の副室噴口3からの渦流Sの対
向流としてのエネルギは、図6に示すように、ピストン
上死点近傍で最大となる。
When the check valves 200 and 300 are opened, the shaft portions 112a and 212a of the spring supports 112 and 212 rise and enter the auxiliary passage 33, and the gas passage is narrowed. Since either the shaft portion or the auxiliary passage has a tapered shape, this passage area is reduced as the valve body 13 and the spring receivers 112 and 212 rise as the piston 7 rises. Therefore, the flow velocity of the gas ejected through the auxiliary passage 33 into the sub-chamber 2 in opposition to the vortex S flowing from the sub-chamber outlet 3 increases, and the vortex S from the sub-chamber outlet 3 in the sub-chamber 2 increases. As shown in FIG. 6, the energy of the counterflow becomes maximum near the top dead center of the piston.

【0023】即ち、図には補助通路33から副室2内
に噴出される渦流Sへの対向流の運動エネルギが示され
ており、図から明らかなように、補助通路面積が可変と
なっている本発明の運動エネルギAの方が補助通路面積
が一定のものの運動エネルギよりも大きくなる。
That is, FIG. 4 shows the kinetic energy of the counterflow to the vortex S ejected from the auxiliary passage 33 into the sub-chamber 2 and, as is apparent from the figure, the area of the auxiliary passage becomes variable. The kinetic energy A of the present invention is larger than the kinetic energy of the one having a fixed auxiliary passage area.

【0024】前記のようにして形成された補助通路33
からの対向流は副室2内で渦流Sに沿って噴射された燃
料と空気との混合気にブロープラグ6の下流領域におい
て衝突し混合気が撹乱されて混合、燃焼が促進される。
The auxiliary passage 33 formed as described above
The counter flow from the air collides with a mixture of fuel and air injected along the vortex S in the sub-chamber 2 in the downstream region of the blow plug 6, and the mixture is disturbed to promote mixing and combustion.

【0025】[0025]

【発明の効果】本発明によれば、最適な時期に逆止弁を
介して補助通路から流入した空気の対向流と、副室噴口
から流入した渦流に沿った未燃、既燃ガスが、グロープ
ラグ側の副室口金の底部付近で衝突し、旋回中の噴流ガ
スが減衰され副室から副室噴口を通って速やかに流出さ
れる。また前記衝突による乱れにより副室内の燃焼が促
進される。前記両作用により主燃焼室内での燃焼が促進
され、且つ短期間に燃焼が終了するため、燃焼効率が向
上する。即ちある程度副室噴口を絞った状態下(低速高
負荷性能良好)においても出力及び燃費の向上が図ら
れ、HC,CO等の排ガス性能も改善される。
According to the present invention, the opposing flow of the air flowing from the auxiliary passage through the check valve at the optimum time and the unburned and burned gas along the vortex flowing from the sub-chamber injection port are obtained. The collision occurs near the bottom of the sub-chamber mouthpiece on the glow plug side, and the jet gas being swirled is attenuated and quickly flows out of the sub-chamber through the sub-chamber nozzle. Further, the combustion in the sub-chamber is promoted by the turbulence due to the collision. The combustion in the main combustion chamber is promoted by the above two actions, and the combustion is completed in a short time, so that the combustion efficiency is improved. That is, the output and the fuel efficiency are improved even under the condition that the injection port of the sub chamber is narrowed to some extent (low speed and high load performance is good), and the performance of exhaust gas such as HC and CO is also improved.

【0026】さらに、逆止弁の軸部が補助通路内に進入
することにより補助通路が絞られ、補助通路からの副室
内渦流への対向流の流速が増大し、渦流への衝突エネル
ギが増大して副室内の撹拌、混合作用がさらに促進さ
れ、燃焼効率のさらなる向上が得られる。
Further, when the shaft portion of the check valve enters the auxiliary passage, the auxiliary passage is narrowed, the flow velocity of the counterflow from the auxiliary passage to the sub-chamber vortex increases, and the collision energy with the vortex increases. As a result, the stirring and mixing actions in the sub chamber are further promoted, and the combustion efficiency is further improved.

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

【図1】本発明に係る実施例の燃焼室断面図。FIG. 1 is a sectional view of a combustion chamber according to an embodiment of the present invention.

【図2】第1実施例を示す図1におけるD部拡大断面
図。
FIG. 2 is an enlarged sectional view of a portion D in FIG. 1 showing the first embodiment .

【図3】本発明に係る第2実施例の図応当図。FIG. 3 is a diagram corresponding to FIG. 2 of a second embodiment according to the present invention.

【図4】本発明の作用効果を示す線図。 FIG. 4 is a diagram showing the operation and effect of the present invention.

【図5】従来例の燃焼室の断面図。 FIG. 5 is a sectional view of a conventional combustion chamber.

【符号の説明】[Explanation of symbols]

1…主燃焼室、2…副室、3…副室噴口、4…シリンダ
ヘッド、5…燃料噴射弁、6…グロープラグ、7…ピス
トン、8…シリンダ、9…副室口金、10…ピストン頂
面、00、300…逆止弁、11…ばね、12、11
2、212…ばね受、112a、212a…軸部、13
…弁体、33…補助通路、331…テーパ状通路、33
2…円形状通路、θ…補助通路中心線が副室底面となす
角、A−A…シリンダ中心線、B−B…副室中心線。
DESCRIPTION OF SYMBOLS 1 ... Main combustion chamber, 2 ... Subchamber, 3 ... Subchamber injection port, 4 ... Cylinder head, 5 ... Fuel injection valve, 6 ... Glow plug, 7 ... Piston, 8 ... Cylinder, 9 ... Subchamber base, 10 ... Piston Top surface, 200, 300 ... check valve, 11 ... spring, 12, 11
2, 212... Spring supports, 112a, 212a.
... Valve, 33 ... Auxiliary passage, 331 ... Tapered passage, 33
2 ... Circular passage, θ: Angle formed by the auxiliary passage center line with the sub-chamber bottom surface, AA: Cylinder center line, BB: Sub-chamber center line.

───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭58−65930(JP,A) 実開 昭52−170903(JP,U) 実開 昭49−56304(JP,U) 実開 昭63−140133(JP,U) 実開 昭57−172121(JP,U) 実開 昭57−33223(JP,U) (58)調査した分野(Int.Cl.7,DB名) F02B 19/00 - 19/18 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-58-65930 (JP, A) JP-A-52-170903 (JP, U) JP-A-49-56304 (JP, U) JP-A-63 140133 (JP, U) Japanese Utility Model Showa 57-172121 (JP, U) Japanese Utility Model Showa 57-33223 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F02B 19/00-19 / 18

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項1】 シリンダヘッドの内壁と該シリンダヘッ
ドに圧入される副室口金とにより区画形成された副室
を、副室口金に穿設された副室噴口を介して主燃焼室に
連通するように構成された副室式内燃機関において、前
記副室(2)の中心線(B−B)とシリンダ中心線(A
−A)との間の副室噴口(3)に隣接した位置に、主燃
焼室(1)と副室(2)とを連通する補助通路(33)
を設けるとともに、当該補助通路(33)内にはばね
(11)により前記主燃焼室(1)から副室(2)への
ガス流のみを許容するように付勢された逆止弁(20
0、300)を設け、逆止弁は、弁体(13、11
2)と一体でリフトする軸部(112a、212a)
有し、前記補助通路(33)に前記軸部(112a、2
12a)が進入したときのガス流路を、主燃焼(1)側
から副室(2)側に向けて流路の面積が縮小されるよう
に形成してなることを特徴とする副室式内燃機関の燃焼
室。
1. A sub-chamber defined by an inner wall of a cylinder head and a sub-chamber base press-fitted into the cylinder head communicates with a main combustion chamber via a sub-chamber injection hole formed in the sub-chamber base. In the sub-chamber internal combustion engine configured as described above, the center line (BB) of the sub-chamber (2) and the cylinder center line (A
-A), an auxiliary passage (33) communicating the main combustion chamber (1) and the sub chamber (2) at a position adjacent to the sub chamber injection port (3).
And a check valve (20) urged by a spring (11) in the auxiliary passage (33) so as to allow only the gas flow from the main combustion chamber (1) to the sub chamber (2).
0,300) is provided, said check valve, the valve element (13,11
2) a shaft which lifts integrally has (112a, 212a), wherein the shaft portion in the auxiliary passage (33) (112a, 2
The gas flow path when 12a) enters the main combustion (1) side
So that the area of the flow path is reduced from
A combustion chamber for a sub-chamber internal combustion engine, wherein the combustion chamber is formed as follows .
JP05348924A 1993-08-31 1993-12-28 Combustion chamber of subchamber internal combustion engine Expired - Fee Related JP3117349B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP05348924A JP3117349B2 (en) 1993-08-31 1993-12-28 Combustion chamber of subchamber internal combustion engine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP5-239044 1993-08-31
JP23904493 1993-08-31
JP05348924A JP3117349B2 (en) 1993-08-31 1993-12-28 Combustion chamber of subchamber internal combustion engine

Publications (2)

Publication Number Publication Date
JPH07119467A JPH07119467A (en) 1995-05-09
JP3117349B2 true JP3117349B2 (en) 2000-12-11

Family

ID=26534051

Family Applications (1)

Application Number Title Priority Date Filing Date
JP05348924A Expired - Fee Related JP3117349B2 (en) 1993-08-31 1993-12-28 Combustion chamber of subchamber internal combustion engine

Country Status (1)

Country Link
JP (1) JP3117349B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3061743B1 (en) * 2017-01-12 2019-08-16 Vianney Rabhi PRE-CLAMP CHAMBER

Also Published As

Publication number Publication date
JPH07119467A (en) 1995-05-09

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