JP2736659B2 - Subchamber gas engine - Google Patents
Subchamber gas engineInfo
- Publication number
- JP2736659B2 JP2736659B2 JP63234599A JP23459988A JP2736659B2 JP 2736659 B2 JP2736659 B2 JP 2736659B2 JP 63234599 A JP63234599 A JP 63234599A JP 23459988 A JP23459988 A JP 23459988A JP 2736659 B2 JP2736659 B2 JP 2736659B2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- sub
- main combustion
- combustion chamber
- 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
Links
- 239000000446 fuel Substances 0.000 claims description 30
- 238000002485 combustion reaction Methods 0.000 claims description 27
- 239000000203 mixture Substances 0.000 claims description 27
- 210000000056 organ Anatomy 0.000 claims 1
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
Landscapes
- Combustion Methods 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、例えば発電機の駆動用に使用される副室式
ガス機関の副室の形状に関するものである。Description: TECHNICAL FIELD The present invention relates to the shape of a sub-chamber of a sub-chamber gas engine used for driving a generator, for example.
（従来技術及びその問題点） この種の副室式ガス機関は第５図に示すように、主燃
焼室10に連続して副室12を設け、主燃焼室10には吸気通
路14から流通する稀薄混合気を供給し、副室12にはガス
管18から供給されるガス燃料で濃厚混合気を形成し、点
火プラグ20でまず副室12内の濃厚混合気に点火して主燃
焼室10内の稀薄混合気をも燃焼し、低燃費と低公害を両
立するようにしている。(Prior art and its problems) In this type of sub-chamber gas engine, as shown in FIG. 5, a sub-chamber 12 is provided continuously with the main combustion chamber 10, and the main combustion chamber 10 circulates through an intake passage 14. A rich mixture is supplied to the sub-chamber 12 with the gas fuel supplied from the gas pipe 18, and the rich mixture in the sub-chamber 12 is first ignited by the ignition plug 20 to ignite the main combustion chamber. The lean mixture in the 10 is also burned to achieve both low fuel consumption and low pollution.
なお、15はガスレギュレーター、16はスロットル弁、
17はミキサー、19は点火装置、21は潤滑油パイプ、23は
ポンプ、25は吸気弁、26は排気弁である。ガス管18の途
中には副室12内の負圧で開弁し、正圧で閉弁するチェッ
ク弁24が介装されている。このチェック弁24については
本件出願人による特願昭62−37946号に詳しく記載して
ある。In addition, 15 is a gas regulator, 16 is a throttle valve,
17 is a mixer, 19 is an ignition device, 21 is a lubricating oil pipe, 23 is a pump, 25 is an intake valve, and 26 is an exhaust valve. In the middle of the gas pipe 18, a check valve 24 that opens with a negative pressure in the sub chamber 12 and closes with a positive pressure is provided. The check valve 24 is described in detail in Japanese Patent Application No. 62-37946 filed by the present applicant.
ところで、以上のような副室式ガス機関を大型化して
行くと、機関の大型化に伴って副室12内の混合気の流速
が速すぎて、副室12内の混合気に点火し難くなる。By the way, when the size of the sub-chamber gas engine as described above is increased, the flow rate of the air-fuel mixture in the sub-chamber 12 is too fast with the enlargement of the engine, and it is difficult to ignite the air-fuel mixture in the sub-chamber 12. Become.
本件に関連する先行技術としては、特公昭55−14749
号がある。Prior art related to this case is Japanese Patent Publication No. 55-14749.
There is a number.
（発明の目的） 本発明は、副室式ガス機関において、副室内の混合気
の点火性を改善できる副室式ガス機関の副室の形状を提
供することを目的としている。(Object of the Invention) It is an object of the present invention to provide a sub-chamber type gas engine having a sub-chamber type gas engine capable of improving the ignitability of an air-fuel mixture in the sub-chamber type gas engine.
（発明の構成） （１）技術的手段 本発明は、主燃焼室に連続して副室を設け、主燃焼室
に稀薄混合気を供給する吸気通路を設け、副室にガス燃
料による濃厚混合気を形成するガス管を設け、点火プラ
グで先に副室内の濃厚混合気に点火した後に主燃焼室内
の稀薄混合気をも燃焼するようにした副室式ガス機関に
おいて、副室の断面積を主燃焼室側に向かって漸次狭め
るように形成し、副室の長さをＬ、副室の最大直径を
Ｄ、最小直径をｄとした時に、d/Dの値を略0.3に設定
し、且つL/Dの値を1.5〜2.0に設定し、副室の最小直径
部分より同径同芯の円形断面の通路を設け、その通路の
先端を傾斜した複数の孔を通して主燃焼室へ接続したこ
とを特徴とする副室式ガス機関である。(Constitution of the Invention) (1) Technical Means The present invention provides a sub-chamber continuous with the main combustion chamber, an intake passage for supplying a lean mixture to the main combustion chamber, and a rich mixture of gas fuel in the sub-chamber. In a sub-chamber gas engine in which a gas pipe for forming air is provided, and a rich air-fuel mixture in the sub-chamber is ignited first by a spark plug and then a lean air-fuel mixture in the main combustion chamber is also burned, the cross-sectional area of the sub-chamber Is formed so as to gradually narrow toward the main combustion chamber side, and when the length of the sub chamber is L, the maximum diameter of the sub chamber is D, and the minimum diameter is d, the value of d / D is set to approximately 0.3. The L / D value is set to 1.5 to 2.0, and a passage having a circular cross section of the same diameter and concentric from the minimum diameter portion of the sub chamber is provided, and the tip of the passage is connected to the main combustion chamber through a plurality of inclined holes. This is a sub-chamber gas engine characterized by the following.
（２）作用 副室の断面積が主燃焼室側に向かって漸次狭められる
ようになっているので、副室内の混合気の流れで循環域
が生じることによって、良好な混合気が形成され、点火
性が向上する。(2) Operation Since the cross-sectional area of the sub-chamber is gradually narrowed toward the main combustion chamber, a good air-fuel mixture is formed by the formation of a circulation region in the flow of the air-fuel mixture in the sub-chamber. The ignitability is improved.
（実施例） 本発明を採用したシリンダ径が100mm以上の大型副室
式ガス機関の要部を示す第１図において、第５図と同一
の符号で示した部分は同一または相当部分を示す。(Embodiment) In FIG. 1 showing a main part of a large sub-chamber gas engine having a cylinder diameter of 100 mm or more and employing the present invention, portions denoted by the same reference numerals as those in FIG. 5 indicate the same or corresponding portions.
第１図中で、シリンダヘッド30には副室本体31がパッ
キン32を介して螺合している。副室本体31の上端にはス
リーブ33が溶接してあり、スリーブ33には前記点火プラ
グ20、チェックバルブ24を設けてある。チェックバルブ
24で開閉されるガス通路18の下端部34は副室本体31の中
心線に対して傾斜して副室12に連通している。副室本体
31の周囲には冷却水通路35を形成してあり、冷却水通路
35は副室本体31の通路36に連通している。In FIG. 1, a sub-chamber main body 31 is screwed into a cylinder head 30 via a packing 32. A sleeve 33 is welded to the upper end of the sub-chamber main body 31. The sleeve 33 is provided with the ignition plug 20 and the check valve 24. Check valve
The lower end 34 of the gas passage 18 that is opened and closed by 24 is inclined with respect to the center line of the sub-chamber main body 31 and communicates with the sub-chamber 12. Sub chamber
A cooling water passage 35 is formed around the periphery of the cooling water passage 31.
Reference numeral 35 communicates with a passage 36 of the sub-chamber main body 31.
副室12を形成する副室本体31の内面40の形状は、円筒
面41、テーパー面42からなる略逆円錐形をなしている。
テーパー面42の下端は円形断面の通路43に連続し、通路
43は例えば３本の孔44に連通している。The shape of the inner surface 40 of the sub-chamber main body 31 forming the sub-chamber 12 has a substantially inverted conical shape including a cylindrical surface 41 and a tapered surface 42.
The lower end of the tapered surface 42 is continuous with the passage 43 having a circular cross section,
43 communicates with, for example, three holes 44.
副室12の高さ（長さ）をＬ、円筒面41の直径をＤ、テ
ーパー面42の下端の直径をｄとすると、内面40の形状
は、 d/D＝0.3 …（１） L/D＝1.5〜2.0 …（２） に設定してある。（１）式は圧縮行程時に副室12内のガ
スと主室10の稀薄混合気が良好に混合するための条件で
あり、（２）式は副室12内でのガス燃料と吸気との混合
および燃焼、火炎伝播を良好にするための条件である。Assuming that the height (length) of the sub chamber 12 is L, the diameter of the cylindrical surface 41 is D, and the diameter of the lower end of the tapered surface 42 is d, the shape of the inner surface 40 is d / D = 0.3 (1) L / D = 1.5 to 2.0 (2) Equation (1) is a condition for satisfactorily mixing the gas in the sub-chamber 12 and the lean air-fuel mixture in the main chamber 10 during the compression stroke, and the equation (2) is a relation between the gas fuel and the intake air in the sub-chamber 12. This is a condition for improving mixing, combustion, and flame propagation.
なお、本発明の副室12は第１図の場合に限らず、円筒
面41の高さは適宜に調整できるし、円筒面41を設けずに
副室12のＬにわたってテーパー面42を形成することもで
きる。In addition, the sub-chamber 12 of the present invention is not limited to the case of FIG. 1, the height of the cylindrical surface 41 can be appropriately adjusted, and the tapered surface 42 is formed over the L of the sub-chamber 12 without providing the cylindrical surface 41. You can also.
以上の構成によると、副室式ガス機関の吸入行程では
主室10の負圧で副室12内にガス管18からガス燃料が流れ
込む。次に圧縮行程に移ると、主室10内の稀薄混合気が
圧縮されて孔44、通路43を逆流して副室12へ流れ込み、
副室12内に充満しているガス燃料と稀薄混合気が混合す
る。稀薄混合気の流れは流速v m/sで通路43から副室12
へ流れ込む。According to the configuration described above, gas fuel flows from the gas pipe 18 into the sub-chamber 12 due to the negative pressure of the main chamber 10 during the suction stroke of the sub-chamber gas engine. Next, when moving to the compression stroke, the lean mixture in the main chamber 10 is compressed, flows backward through the holes 44 and the passages 43, and flows into the sub-chamber 12,
The gaseous fuel filling the sub chamber 12 and the lean mixture are mixed. The flow of the lean air-fuel mixture flows from passage 43
Flow into
この流速v m/sは燃焼状態に影響を与える。流速v m/s
に対する燃費f MJ/KWhの変化を示す第２図に示すよう
に、ｖ＝160m/s以上では吹き消えのために着火せず、ｖ
＝30m/s以下では燃焼変動が大きく燃焼が続かない。第
２図の特性X1からｖ＝90m/s程度の領域で燃費f MJ/KWh
が最もよくなる。This flow rate vm / s affects the combustion state. Flow rate vm / s
As shown in FIG. 2 showing the change in fuel efficiency f MJ / KWh with respect to
If it is less than 30 m / s, combustion fluctuations are large and combustion does not continue. Fuel consumption f MJ / KWh in the region of about v = 90 m / s from the characteristic X1 in FIG.
Is best.
以上のように通路43から流速v m/sで流れ込む圧縮行
程での稀薄混合気の流れは噴流と見なすことができ、こ
の噴流で副室12内に良好な濃厚混合気を形成し得るよう
に詳しくは後述する形状に副室12の内面40を形成してあ
る。As described above, the flow of the lean air-fuel mixture in the compression stroke flowing from the passage 43 at the flow velocity vm / s can be regarded as a jet, and is described in detail so that a good rich air-fuel mixture can be formed in the sub chamber 12 with this jet. Has an inner surface 40 of the sub-chamber 12 in a shape described later.
まず、副室12内の全域にわたって通路43からの噴流で
良好な濃厚混合気が発生するための条件、すなわち前記
（１）式の根拠を説明する。文献TURBULENT JETS（N.Ra
jaratnam著,Elservier Scientific Publishing Compan
y,Amsterdam,1976年発行）によると、噴流の流量Ｗは、
噴流が円筒状の管路を流れると仮定すると、 となり、無次元パラメータＨは、 になり、係数Ctによって渦領域の大きさが決定すること
になる。なお、ｍは係数CtとともにCurted and Riconが
1964年に定義した係数で、無次元パラメータＨが（３）
式に変型されるように設定した係数である。この係数Ct
は噴流で生じる再循環域の大きさを決定する係数であ
る。前述の文献によると、Ct＝0.3で渦領域が管内一杯
になる。First, the conditions for generating a good rich air-fuel mixture by the jet from the passage 43 over the entire area in the sub-chamber 12, that is, the basis of the expression (1) will be described. Document TURBULENT JETS (N.Ra
jaratnam, Elservier Scientific Publishing Compan
y, Amsterdam, published in 1976), the flow rate W of the jet is
Assuming that the jet flows through a cylindrical pipe, And the dimensionless parameter H is And the size of the vortex region is determined by the coefficient Ct. Note that m is Curted and Ricon together with the coefficient Ct.
The coefficient defined in 1964, and the dimensionless parameter H is (3)
It is a coefficient set to be transformed into an expression. This coefficient Ct
Is a coefficient that determines the size of the recirculation zone generated by the jet. According to the aforementioned document, the vortex region becomes full in the tube when Ct = 0.3.
一方Ingersoll−Rand社が1984年ASME paperに発表し
た論文によると、無限長管における再循環に要する流量
Mrは、 で表現でき、（４）式で係数Ctは、 Ct＝［（D/d）２）−1/2］−1/2 として、簡略化して表現できる。したがって、Ct＝0.3
としてd/Dの値を求めると、 d/D≒0.3 を得る。On the other hand, according to a paper published by Ingersoll-Rand in ASME paper in 1984, the flow rate required for recirculation
Mr. In equation (4), the coefficient Ct can be simply expressed as Ct = [(D / d) 2 ) −1/2] −1/2 . Therefore, Ct = 0.3
When the value of d / D is obtained, d / D ≒ 0.3 is obtained.
第１図の副室式ガス機関（シリンダ径100mm以上）に
よる実験では、係数Ctに対する燃費f MJ/KWhのグラフで
ある第３図に示すように、特性X2のようにCt＝0.3で燃
費ｆが最小になる。In the experiment using the sub-chamber gas engine (cylinder diameter 100 mm or more) shown in FIG. 1, as shown in FIG. 3, which is a graph of fuel efficiency f MJ / KWh with respect to coefficient Ct, fuel efficiency f at Ct = 0.3 as shown by characteristic X2. Is minimized.
次に、（２）式の条件について説明する。文献TURBUL
ENT JETSによると第４図に示すように直径Ｄの円筒状管
路で軸対称管内流によって渦領域が発生する長さをＬと
すると、Becker et alの実験による特性X3、Curtet and
Barchilonによる特性X4、Hillによる特性X5の領域Ｒで
渦領域になることが解る。ここで、係数Ct＝0.3の場合
には、前記特性X3との交点P1のL/D＝1.5から特性X5との
交点P2のL/D＝2.0迄の範囲で渦領域が発生することにな
る。したがって、L/D＝1.5〜2.0の範囲で良好な混合気
が得られ、それ以外の範囲では混合不良になることが解
る。Next, the condition of the expression (2) will be described. Document TURBUL
According to ENT JETS, as shown in FIG. 4, if the length of the vortex region generated by the axisymmetric pipe flow in a cylindrical pipe having a diameter D is L, as shown in FIG.
It can be seen that a vortex region is formed in the region R of the characteristic X4 by Barchilon and the characteristic X5 by Hill. Here, when the coefficient Ct = 0.3, a vortex region is generated in a range from L / D = 1.5 at the intersection P1 with the characteristic X3 to L / D = 2.0 at the intersection P2 with the characteristic X5. . Therefore, it can be seen that a good air-fuel mixture is obtained in the range of L / D = 1.5 to 2.0, and poor mixing occurs in other ranges.
また、本件発明者による実験によると、L/Dの値が1.5
未満では混合不良になり、L/Dの値が2.0を越えると副室
12の火炎が主室10に到達する迄に時間がかかり過ぎ、燃
焼不良が発生する。したがって、シリンダ径が100mm以
上の大型機関でも前記（２）式の範囲で燃焼が良好にな
る。Further, according to an experiment by the present inventors, the value of L / D was 1.5
If the value is less than 2.0, the mixing will be poor.
It takes too long for the twelve flames to reach the main chamber 10, and poor combustion occurs. Therefore, even in a large engine having a cylinder diameter of 100 mm or more, good combustion can be achieved in the range of the expression (2).
（発明の効果） 以上説明したように本発明による副室式ガス機関では
次の効果を奏する。(Effects of the Invention) As described above, the sub-chamber gas engine according to the present invention has the following effects.
第１請求項では、副室12の断面積を主燃焼室側に向か
って漸次狭めるように形成したので、副室12内に流れ込
む噴流の流速が適当になり、シリンダ径が100mm以上の
大型機関でも、副室12の燃焼状態が良好になる。その理
由は、副室12を円筒形にすると、高速、大型機関では噴
流が流入するスロート部での流速が速くなり、吹き消え
が起こる。しかし、副室12の断面積を主燃焼室側に向か
って漸次狭めるように形成すると、副室容積が小さくな
って、スロート部の噴流速度が遅くなり、吹き消えが発
生しない。なお、副室12を主燃焼室側に向かって漸次狭
めるように形成しても、混合気の形成が良好であること
は本件発明者による実験で確認されている。In the first aspect, since the sectional area of the sub-chamber 12 is formed so as to gradually narrow toward the main combustion chamber side, the flow velocity of the jet flowing into the sub-chamber 12 becomes appropriate, and the large engine having a cylinder diameter of 100 mm or more is used. However, the combustion state of the sub chamber 12 is improved. The reason is that when the sub-chamber 12 is formed in a cylindrical shape, the flow velocity in the throat portion into which the jet flows in a high-speed, large engine becomes high, and the blow-out occurs. However, if the cross-sectional area of the sub-chamber 12 is formed so as to gradually narrow toward the main combustion chamber side, the sub-chamber volume becomes small, the jet velocity of the throat portion becomes slow, and blow-out does not occur. It has been confirmed by experiments by the present inventor that the formation of the air-fuel mixture is good even if the sub-chamber 12 is formed so as to gradually narrow toward the main combustion chamber side.
第１図に示すように、 d/D＝0.3 …（１） L/D＝1.5〜2.0 …（２） に設定したので、（１）式によって副室12内の濃厚混合
気と主室10の稀薄混合気を良好に混合することができ、
（２）式によって副室12内でのガス燃料と吸気との混合
および燃焼、火炎伝播を良好にすることができる。As shown in FIG. 1, since d / D = 0.3 (1) L / D = 1.5-2.0 (2), the rich air-fuel mixture in the sub-chamber 12 and the main chamber 10 are calculated by the equation (1). Can be mixed satisfactorily,
According to the equation (2), the mixing and combustion of the gas fuel and the intake air in the sub chamber 12 and the flame propagation can be improved.
副室12の最小直径ｄ部分より同径同芯の円形断面の通
路43を設け、その通路43の先端を傾斜した複数の孔44を
通して主燃焼室10へ接続したので、主燃焼室10から副室
12内へ稀薄混合気が乱れなく流入し、又副室12内の火炎
が主燃焼室10へ円滑に分配供給される。A passage 43 having a circular cross section of the same diameter and concentric from the minimum diameter d portion of the sub chamber 12 was provided, and the tip of the passage 43 was connected to the main combustion chamber 10 through a plurality of inclined holes 44. Room
The lean air-fuel mixture flows into the sub-chamber 12 without disturbance, and the flame in the sub-chamber 12 is smoothly distributed and supplied to the main combustion chamber 10.
第１図は本発明を採用した副室式ガス機関の要部を示す
縦断面部分図、第２図は噴流の流速−燃費のグラフ、第
３図は係数Ct−燃費のグラフ、第４図は係数Ct−係数L/
Dのグラフ、第５図は従来例の構造略図である。10……
主室、12……副室、14……吸気通路、18……ガス管、20
……点火プラグ、40……内面、41……円筒面、42……テ
ーパー面FIG. 1 is a partial longitudinal sectional view showing a main part of a sub-chamber type gas engine employing the present invention, FIG. 2 is a graph of jet flow velocity-fuel consumption, FIG. 3 is a graph of coefficient Ct-fuel consumption, FIG. Is the coefficient Ct-coefficient L /
FIG. 5 is a schematic diagram of a conventional example. Ten……
Main room, 12… Sub room, 14… Intake passage, 18… Gas pipe, 20
…… Spark plug, 40 …… Inner surface, 41 …… Cylinder surface, 42 …… Tapered surface
Claims (1)
に稀薄混合気を供給する吸気通路を設け、副室にガス燃
料による濃厚混合気を形成するガス管を設け、点火プラ
グで先に副室内の濃厚混合気に点火した後に主燃焼室内
の稀薄混合気をも燃焼するようにした副室式ガス機関に
おいて、副室の断面積を主燃焼室側に向かって漸次狭め
るように形成し、副室の長さをＬ、副室の最大直径を
Ｄ、最小直径をｄとした時に、d/Dの値を略0.3に設定
し、且つL/Dの値を1.5〜2.0に設定し、副室の最小直径
部分より同径同芯の円形断面の通路を設け、その通路の
先端を傾斜した複数の孔を通して主燃焼室へ接続したこ
とを特徴とする副室式ガス機関。1. An auxiliary chamber is provided continuously in the main combustion chamber, an intake passage for supplying a lean mixture is provided in the main combustion chamber, and a gas pipe for forming a rich mixture of gas fuel is provided in the auxiliary chamber. In a subchamber gas engine in which a rich mixture in the subchamber is first ignited by a plug and then the lean mixture in the main combustion chamber is also burned, the sectional area of the subchamber is gradually narrowed toward the main combustion chamber. When the length of the sub-chamber is L, the maximum diameter of the sub-chamber is D, and the minimum diameter is d, the value of d / D is set to approximately 0.3, and the value of L / D is 1.5 to Sub-chamber type gas, characterized in that it is set to 2.0, and a passage having a circular cross section of the same diameter and concentric from the minimum diameter portion of the sub-chamber is provided, and the tip of the passage is connected to the main combustion chamber through a plurality of inclined holes. organ.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63234599A JP2736659B2 (en) | 1988-09-19 | 1988-09-19 | Subchamber gas engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63234599A JP2736659B2 (en) | 1988-09-19 | 1988-09-19 | Subchamber gas engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0281925A JPH0281925A (en) | 1990-03-22 |
| JP2736659B2 true JP2736659B2 (en) | 1998-04-02 |
Family
ID=16973559
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63234599A Expired - Fee Related JP2736659B2 (en) | 1988-09-19 | 1988-09-19 | Subchamber gas engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2736659B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2577381Y2 (en) * | 1990-04-24 | 1998-07-23 | 三菱重工業株式会社 | Torch ignition gas engine |
| JPWO2004099584A1 (en) * | 2003-05-09 | 2006-07-13 | ヤンマー株式会社 | Subchamber gas engine combustion chamber structure and subchamber gas engine |
| JP2005090381A (en) * | 2003-09-18 | 2005-04-07 | Niigata Power Systems Co Ltd | Pilot oil ignition gas engine |
| AT514813B1 (en) * | 2013-09-25 | 2015-04-15 | Ge Jenbacher Gmbh & Co Og | Arrangement of a cylinder head and a Vorkammersystem |
| JP7347308B2 (en) * | 2020-01-29 | 2023-09-20 | 株式会社デンソー | ignition system |
| EP4098857A4 (en) * | 2020-01-29 | 2023-11-29 | Denso Corporation | Ignition system |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4738227A (en) * | 1986-02-21 | 1988-04-19 | Adiabatics, Inc. | Thermal ignition combustion system |
| JPH07116991B2 (en) * | 1986-12-24 | 1995-12-18 | ヤンマーディーゼル株式会社 | Subchamber type gas chamber subchamber structure |
-
1988
- 1988-09-19 JP JP63234599A patent/JP2736659B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0281925A (en) | 1990-03-22 |
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| LAPS | Cancellation because of no payment of annual fees |