JPS58501832A - Integrated intake/exhaust valve mechanism for internal combustion engines - Google Patents
Integrated intake/exhaust valve mechanism for internal combustion enginesInfo
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- JPS58501832A JPS58501832A JP82503423A JP50342382A JPS58501832A JP S58501832 A JPS58501832 A JP S58501832A JP 82503423 A JP82503423 A JP 82503423A JP 50342382 A JP50342382 A JP 50342382A JP S58501832 A JPS58501832 A JP S58501832A
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- valve
- cylinder
- suction
- intake
- exhaust
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
- F01L1/285—Coaxial intake and exhaust valves
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- 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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるため要約のデータは記録されません。 (57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】 発明の名称 内燃機関用の一’ ｆ４； ”＋’！吸入／′排出バルブ機構背景技術 この発明は内燃機関の改烏に関し、特に吸入排出時の単位時間当りチャージ容量 の増加を期待できる吸入排出バルブ機構に関４る。[Detailed description of the invention] name of invention 1'f4;'+'!Intake/'exhaust valve mechanism background technology for internal combustion engines This invention relates to the modification of internal combustion engines, particularly the charge capacity per unit time during intake and exhaust. Regarding the intake/exhaust valve mechanism, which can be expected to increase the
さらにエンジン効率の大きな増加と、総合燃焼工程の改善、および汚染の防ロー を図ることので′きる吸入排出バルブ機構に関する。Additionally, significant increases in engine efficiency, improvements in the overall combustion process and prevention of pollution This invention relates to an intake/exhaust valve mechanism that can achieve the following.
過去に一体吸排出バルブ機構に関する改良が多数行なわれている。Many improvements have been made to integrated intake and exhaust valve mechanisms in the past.
その−例はアメリカ特許第１，３５０．８００ （１つ２０任８月２４日）に開 示されているが、それは吸排出目により大きい面積を与える１個の吸排出バルブ 機構を示している。An example of this is published in U.S. Patent No. 1,350.800 (Aug. As shown, it has one suction and discharge valve which gives a larger area for the suction and discharge eyes. It shows the mechanism.
しかし実用化するｋめにはこの発明のカムはきわめて複雑１５構造をしている。However, in order to put it into practical use, the cam of this invention has an extremely complicated structure.
さらにこの装置の欠陥は、大変高価で複′ｍなカム機構が必要である事は別とし で単一集中バルブ部品の子指が弔過ぎる事である。A further drawback of this device is that it requires a very expensive and complex cam mechanism. The problem is that the little finger of the single central valve part is too weak.
この燃焼至にお（プる甲−集中バルブ機構の過剰表面積は燃焼１稈の次の排気Ｈ にもとずく過大ない荷の問題を発’）する、 とい゛）のはシリンダに、１３い て高いガス珪に対抗して排気バルブは開１］シなければならない！ζめＣ・ある 。At this point in combustion, the excess surface area of the central valve mechanism is This causes the problem of excessive loading based on the cylinder. The exhaust valve must be opened to counter the high gas pressure! ζme C・Yes .
単一排気バルブに、Ｊ、つ（’ ｈ ｋ、らされる極端に人さい表面積は結局こ の機構を非現実的なものとしてしま）。The extremely small surface area exposed to a single exhaust valve ends up being the mechanism of the system is unrealistic).
他の集中バルブについＣ米国特許１，９５０，９１１ （１９３４年３月１３日 ）に開示されている。U.S. Pat. No. 1,950,911 (March 13, 1934) for other centralizing valves. ) is disclosed.
その発明にａ３いてば排出バルブにおりる１）１刀ス１１の減少のためにスリー ブのような雫中吸排出機構を開示し−（いる。If the invention is a3, it will go to the discharge valve 1) Three to reduce the number of swords 11 Discloses a droplet suction and discharge mechanism like a droplet.
どころがこの発明のバルブの体積や′くＩ法はよ−）たく非現実的である。However, the volume of the valve of this invention and the I method are very unrealistic.
こうした欠点をみると、従来の内燃機関に実際ト集中パル７機構が応用できない 問題点が明らかにされでいる。Considering these shortcomings, the concentrated pulse 7 mechanism cannot actually be applied to conventional internal combustion engines. The problems have been clarified.
イれに対して本発明は内燃機関のための複合環＋１１吸排出バルブ機構を採用り る事によって前記した問題点を改善したもので・ある。In response to this, the present invention adopts a composite ring + 11 intake and exhaust valve mechanism for internal combustion engines. The above-mentioned problems have been improved by
イーのため本発明の機構では中位時間当Ｖ〕のチ（？−ジ容早をきり／ｅつで増 加さυることかＣｃ′Ｘる−１また集中バルブ機構における排出圧を太き・く低 １′：さＩよ、渦Ｗ＋ｊ特性を増加さ０る１１ｈ１（ｚ＼る、本発明の層れ１． ：実施例どＬ Ｕ集中バルブ機構にはけと−）のシリンタ゛当り４絹のバルブが 用いられている。。Because of this, the mechanism of the present invention reduces the speed of the change (? In addition, the exhaust pressure in the central valve mechanism is increased and lowered. 1': Increase the vortex W+j characteristic by increasing the vortex W+j characteristic. : In the example, there are 4 silk valves per cylinder in the LU central valve mechanism. It is used. .
ぞの実施例（は吸入、排出流のための最適なバルブ面積を設定したシリンダにつ いで、４個の吸入バルブと４個の排出バルブを設置Ｊだしのである。This example shows a cylinder with optimal valve area for intake and exhaust flow. So I installed 4 intake valves and 4 exhaust valves.
その結果、改善され／ζζ吸入光速速度シリンダ内へ流入する甲１◇時間当りの 充填容φか増加するどう滑れた効果がらたらされる。As a result, the speed of light flowing into the cylinder is improved /ζζinhalation speed of light per hour As the filling volume φ increases, a slipping effect is produced.
また第二の効果としては吸入工程において燃焼室内の混合気は１分に均質なもの に改善されている。The second effect is that during the intake process, the air-fuel mixture in the combustion chamber becomes homogeneous every minute. has been improved.
その結果、Ｊ、り完全な燃焼および燃焼］−程にお【プるより強力２ｊエネルＶ −の発生という効果が得られる。As a result, more complete combustion and combustion] - more powerful than 2j energy V The effect of generating - can be obtained.
この機構の伯の利点はシリンダの−ｂから一つの燃料を供給した時に、他方から は他の種類の燃料を供給する事ができることである。The main advantage of this mechanism is that when one fuel is supplied from the -b of the cylinder, the other is that it can supply other types of fuel.
−ｆの結果、例えばガソリンとアルコールのような二種類の混合が可能である。As a result of -f, mixing of two types, such as gasoline and alcohol, is possible.
さらに重要な効果（、Ｌ流入部分の面積の増加は吸入と排出にと）−Ｃ有効であ って、単位時間当りの容量を大ぎく増加させるとともに、また一方では吸排出バ ルブの作動を強制・する機械的加速を減少りる点にある、。A more important effect (increasing the area of the L inflow area for suction and evacuation) -C is effective. Therefore, the capacity per unit time is greatly increased, and on the other hand, the suction and exhaust The purpose is to reduce the mechanical acceleration that forces the valve to operate.
より大きい円周を得たために、このバルブは単位時間当りの最適充■眞量を得る のにさほど大きく開［−１ηる必要がなくなった。Due to the larger circumference, this valve obtains the optimum amount of charge per unit time. It is no longer necessary to open it so wide [-1η].
またパルｆの開１−１状態を維持づるために力ｌ＼シレノ［−の条件によって制 限をシ（〕ることがなくなった。In addition, in order to maintain the open 1-1 state of the pulse f, the force is controlled by the condition of l\sireno[-. I no longer have to limit myself.
従来の４リイクル−［ンジンの問題点は、吸入ゴニ稈峙に充分な容量の充填が行 われにくい点にある。The problem with the conventional 4-recycle engine is that it does not fill enough volume to the suction culm. It's difficult to understand.
さらに従来の一１ンシンＣは、中１＋’７１＋；’１間当りの吸入光１ａ吊（よ バルブ全問時のカムの回転速度によって制限され（いる。Furthermore, the conventional 11shin C has an inhalation light 1a suspension per 1+'71+; It is limited by the rotational speed of the cam when all valves are open.
それに：２Ｊ （］、この発明はＣはバルブの最適な開口時間を認めている。Also: 2J (), this invention recognizes that C is the optimum opening time of the valve.
図面の簡単な説明 第１図はこの発明を利用したエンジンの平面図であり、Ａ−ハーヘッドハルブヤ ）カムの配置、吸入？−ホール１〜等を一部想像線で示す。Brief description of the drawing FIG. 1 is a plan view of an engine using this invention. ) Cam placement, suction? -Hole 1 etc. are partially shown with imaginary lines.
第２△、２Ｌ３図はひとつの燃焼°仝に設【ブた４箇所のバルブのうちの２箇所 を、ｆｔｔｉ型的なシリングヘラ１〜の部分で切断した縦断面図を示ず。Figures 2△ and 2L3 are installed at one combustion point [two of the four valves]. A vertical cross-sectional view taken at the ftti type shilling spatula 1 is not shown.
第２Ａ図は集中吸入方式、第２Ｂ図は分散吸入方式を承り。Figure 2A is for the concentrated suction method, and Figure 2B is for the distributed suction method.
第３図をは第２図の実施例と同一であ−〕で吸入バルブの開口状態を示す３、 第４図は第３図の実施例と同一であってｕＦ Ｌｌ−：バルブが開口、吸入バル ブか閉［」シている状態を示す。FIG. 3 is the same as the embodiment shown in FIG. 2, and shows the opening state of the intake valve. FIG. 4 is the same as the embodiment shown in FIG. 3, with uF Ll-: valve open, suction valve Indicates a closed state.
第す図（よ吸入、排出ハルツ機構の分解図を示す。Figure 2 shows an exploded view of the intake and exhaust Hartz mechanism.
第６図は排出バルブの分解図を示す。FIG. 6 shows an exploded view of the exhaust valve.
発明を実施（ｆるための最良の形態 第１．図ｉｔＪお、いで、本発明の平面、図を示すと、エンジンのシリンダヘラ ・１〜１゛１の４に（３Ｌ、１絹のカムシ、ｔ・フト１０が配装置されている。Best mode for carrying out the invention 1st. Figure 1 shows a plan view of the present invention, showing an engine cylinder spatula. ・1~1゛1 4 (3L, 1 silk comb, T-foot 10 are arranged.
図面中ではさらにエンジンシリンダ１２は想像線で示しである。Furthermore, the engine cylinder 12 is shown in phantom lines in the drawing.
各のシリンダには、想像線Ｃ示づ−ように、４個の開口部１４を設（ノる。Each cylinder is provided with four openings 14, as shown by imaginary line C.
そしｒ −−一つの開１−１部１４には、−絹の吸入バルブど排気バルブどを設 ける。- One opening 1-1 section 14 is equipped with a silk intake valve, exhaust valve, etc. Let's go.
このようにしで、図面で示ｇ４シリンダ丁−ンジシー（゛は、各のシリンダこと に４個の吸入バルブと、４個の排気バルブとを有し、その吸入バルブは、同心固 状に排気ハバルブの中に位置しでいる６ ざらに力１１シ１１ノド１０には、３個を１１１１にりるカム群をシリンダの上 部毎に１組、合計４組設りる。In this way, the g4 cylinder alignment seam shown in the drawing (' is each cylinder) It has four intake valves and four exhaust valves, and the intake valves are concentric and rigid. The exhaust valve is located inside the valve. On the rough force 11 side 11 throat 10, put a group of 3 cams on 1111 on the cylinder. There will be one group for each department, 4 groups in total.
３個のカムは、吸入バルブを駆動４゛る２個の内ノ〕ム゛１Ｇと、・ぞの外側に 設【ノた、排気バルブ駆動のための２個の外カム１８によｅ）構成１する。The three cams drive the intake valve, with two inner cams, 1G and 4, on the outside. (e) Configuration 1 with two outer cams 18 for driving the exhaust valve.
この力１１シＶフ）・１０（Ｊ玉ン；ンのＥ部に設（プ７，７ Ａ−バー／＼ツ １〜型であるか、駆動ｈ ？ｈは従来と同様て（（リリ、説明（、Ｌ省略する。This force is set in the E section of the Is it type 1 or drive h? h is the same as before ((Lili, explanation (, L omitted.
さらに仙のｒンジン部品（Ｊつい（ｂ、本ブｚ明の構成と直１ｇ関係の無い部分 にｆ・］いては、その説明を省略する。In addition, there are parts that are unrelated to the configuration of this book. f.], the explanation thereof will be omitted.
・第２図にＪ＞いて、吸入Ｕ１気ハルツの縦面面をホす。・Standing in Figure 2, look at the vertical surface of the inhaler U1.
各バルブの機能は同し／ρので、〜つのバルブについてた・（ｊ詳細に説明づる か、ハルツ機構の中心軸は、シリンダの中心軸にたいしである程度傾いて構成し てあり、バルブ機構相互には、約３０度のｍ石を右する、。The function of each valve is the same/ρ, so I have chosen ~ (j) for a detailed explanation. Or, the center axis of the Hartz mechanism is configured to be inclined to some extent with respect to the center axis of the cylinder. The valve mechanisms are oriented approximately 30 degrees from each other.
第２Ａ Ｉ”ｌ ４．Ｔ示す実施例の吸入用マ二ホール１〜２０は中央に位置し ており、ギ１７グレタからの流体を２箇所の吸入バルブ２２に分流させて供給で きる。2nd A I''l 4.TThe suction manifolds 1 to 20 of the embodiment shown are located in the center. The fluid from Gi 17 Greta can be divided and supplied to two intake valves 22. Wear.
−））第２［３図の実施例の構成であれば、各々シリンタ毎に独存した吸入系統 を猫λでいるから、Ｗなった種類の燃料を一つのシリンダに供給できる。。-)) Second [If the configuration of the embodiment shown in Figure 3 is used, each cylinder has its own suction system. Since λ is a cat, W types of fuel can be supplied to one cylinder. .
２− Ｌ Ｕ両図面（２△、２「３）において、吸入パルｆ２２、排気バルブ２ ４共に閉した状態にある。。2- In both L and U drawings (2△, 2"3), intake pulse f22, exhaust valve 2 4 are both closed. .
第３図において吸入バルブ作動用のカム１Ｇは、ハネの／Ｊに′１．」抗しＣ吸 入バルー１２２４最も押出した状態にある１、この時吸入ハル１２２は、吸入工 程にＪ５いて最適な距離だ（）開］］［２ているように、カム受１．−、） ２ ６の・１法を定める７、 この時、排気ハルｆ２・１は、ｉｌ＋気ハルＪのための戻りハネ５０によって、 閉［１状態にある。１吸入バルブ２２１（Ｌ、バルジヘラ［へ、バルブ軸２２、 閉口状態を確保する為のハネの弾力を妥・（〕る受けｌＩ１１２８等を有する９ 吸入バルブ用のカム１６の力を受・けるカム受け２６は、バルブ軸２２の先端に 固定している。In FIG. 3, the cam 1G for actuating the intake valve has a spring /J of '1. ”Resisting C-sucking Inlet balloon 1224 is in the most pushed out state 1, at this time the suction hull 122 is in the suction It's about J5 and the optimal distance is () open]] [As shown in 2, cam receiver 1. -, ) 2 6.1 Law 7 established; At this time, the exhaust hull f2.1 is moved by the return spring 50 for il + air hull J. Closed [in state 1. 1 Intake valve 221 (L, bulge spatula [to, valve shaft 22, 9 with a receiver lI1128 etc. that compensates for the elasticity of the spring to ensure the closed state. A cam receiver 26 that receives the force of the cam 16 for the intake valve is located at the tip of the valve shaft 22. Fixed.
一方バルブ軸の細端のカムヘッドは、円筒状の排気バルブ２４の開放部の端面を 弁座どして使用する状態でその中に位置（７て°いる。On the other hand, the cam head at the narrow end of the valve shaft touches the end face of the open part of the cylindrical exhaust valve 24. The valve seat is in the position (7°) when in use.
その結果カム受け２６を加圧することによって、吸入バルブ２２のカムヘッドは 排気バルブ２４の内部から離れて、マニホールドに連絡する吸入用の通路３０を 開口することになる、。As a result, by pressurizing the cam receiver 26, the cam head of the intake valve 22 is A suction passage 30 that is separated from the inside of the exhaust valve 24 and communicates with the manifold is provided. It will be opened.
そしてこの吸入用の通路３０は、排気用バルブ２４の内部を通過して開設し−（ ある。This suction passage 30 is opened by passing through the inside of the exhaust valve 24. be.
なお第３図においては、両吸入バルブとも同時に開［１（〕ている状態を示１． ているが、実際には、各シリンダの吸入バルブ２２４よ吸入サイクルに従って開 閉するものである。Note that FIG. 3 shows a state in which both intake valves are open [1 (]) at the same time. However, in reality, the intake valve 224 of each cylinder opens according to the intake cycle. It is to be closed.
さらに実際には吸入ハルツ２２はその弁座から必要最小隔離れれば良いのであっ て、図面（パは解りやすいように誇張しで描い−Ｃある１゜ そして各燃焼室３２内に（、Ｌ、第３図に示すように開孔ｉする吸入ハルツ２２ が４二］存西゛するのである。Furthermore, in reality, the suction HARTZ 22 only needs to be separated from the valve seat by the minimum distance necessary. , the drawing (P is exaggerated to make it easier to understand - C is 1゜ Then, in each combustion chamber 32 (, L, as shown in FIG. 42] will continue to exist.
このように一つのシリンダについて４箇所のバルブから吸入することができるの Ｃ１本発明のシリンダは常に中位時間あたりＲ適の容量の燃料の供給を行うこと がでさ、しか・ｂこの吸入ハルツ２２の体積す寸法も従来のバルブ」、りら小さ −いしのてＷりる。In this way, one cylinder can inhale from four valves. C1 The cylinder of the present invention always supplies R suitable capacity of fuel per medium time. However, the volume of this intake Harutsu 22 is also smaller than that of a conventional valve. -Ishinote W Riruru.
第４図面では燃焼の後の排気工程において、ｌＪ１ｇ気バルブ２４が開孔しＣい る状態を承りが、この時吸入バルブ２２は円筒状の排気バルブ２４の内部にあっ て、吸入通路は閉口した状態にある。In the fourth drawing, in the exhaust process after combustion, the lJ1g air valve 24 opens and C. However, at this time, the intake valve 22 is inside the cylindrical exhaust valve 24. Therefore, the suction passage is in a closed state.
また排気バルブ２４１よ排気：２二ホールド３８に直結した排気ポート３６の内 部に位置し”Ｃいる。In addition, the exhaust valve 241 exhausts the exhaust port 36 directly connected to the second hold 38. It is located in the "C" section.
各排気バルブ２４は、排気用カム１８によって開閉されるか、このカム１８の加 几力は、カム受け４０をバネ４２の弾力に対抗して加圧し、ガイド板４６内を貫 通する４本のビン４４ 、Ｊｉよび受り板４８を介して排気バルブ２４を燃焼室 ３２の内部に押出すものである、。Each exhaust valve 24 is opened and closed by the exhaust cam 18, or is operated by the exhaust cam 18. The force pressurizes the cam receiver 40 against the elasticity of the spring 42 and penetrates the inside of the guide plate 46. The exhaust valve 24 is connected to the combustion chamber through the four bottles 44, Ji and the receiving plate 48. It is extruded into the inside of 32.
このように、４筒所の排気バルブ２４が同時に作動するので、本発明の排気バル ブの２４の容積や半径は従来の中−一一一体型バルブシステムに比較して極めて 小型のものでたりる。In this way, since the exhaust valves 24 at four cylinder locations operate simultaneously, the exhaust valves 24 of the present invention operate at the same time. The volume and radius of the 24 valves are extremely large compared to conventional central-to-one integrated valve systems. There are small ones.
排気ハルツ２４が押出される時、円筒状の排気バルブ２４内（、位置りる吸入バ ルブ２２は、同時に押出されることになる。。When the exhaust valve 24 is pushed out, the intake valve located inside the cylindrical exhaust valve 24 Lube 22 will be extruded at the same time. .
この排気ハルツ２４は、高温のυ［気カスか吸入マーホールド側に流入するのべ 完全に■上する事を要し、そのために円ね状の排気ハルツの外周には、シールリ ンク２５を取りト１リ−（ある、。This exhaust gas 24 has a high temperature υ [gas gas flowing into the intake marhold side It is necessary to raise the exhaust completely, and for this purpose a sealing ring is installed around the outer circumference of the circular exhaust hart. Take the link 25 and remove the tree.
カム軸１０おＪ、び力１１１８か回転を縦組）することにＪ、つ−（、戻りバネ ５０の弾力によって、排気バルブ２４はシリンダヘットの元の位置に戻る。各シ リンダは４箇所の排気バルブ２４ど４箇所の排気ポート３６を備えてＪ５す、排 気をエンジン両側の排気マニールド３８へ排出する。When the camshaft 10 and the force 1118 are vertically assembled), the return spring The elastic force of 50 causes the exhaust valve 24 to return to its original position in the cylinder head. Each scene The cylinder is equipped with four exhaust valves 24 and four exhaust ports 36. The air is discharged to exhaust manifolds 38 on both sides of the engine.
第５図には実施例の分解図を示す。FIG. 5 shows an exploded view of the embodiment.
主ハネ４２と、排気バルブの戻りバネ５０との弾力を適当（Ｊ調整することに１ よって、高速回転に囚って生・ｌ−るバルブ相方間の分離運動や、その結果ｑじ る不必並な振動や同調運動の発生を防止できる。Adjust the elasticity of the main spring 42 and the return spring 50 of the exhaust valve appropriately (J adjustment Therefore, the separation movement between the valve partners caused by high-speed rotation, and the resulting It is possible to prevent the occurrence of unnecessary vibrations and synchronized movements.
第１図に戻って説明すると、各シリンダ１２はその半径におおＵた最適な中位時 間当り充瞑醋を確保する為に、最適なバルブ円周と、最適なバルブ聞［−１部と を設定するしのである。Returning to FIG. 1, each cylinder 12 has an optimal intermediate position within its radius. In order to ensure a full and concentrated drink, the optimum valve circumference and optimum valve height [-1 part and This is the setting.
ぞの結果このエンジンにｔｒ３い−（−は中位時間当りのチせ−ジ卒を大幅に増 加させることができ上記したように、総合的４゛効宋を向１−（＼μることがで きる。１まＩ、二、第１図に見られるよ゛）に、傾斜間口部に関する力ｌ、の角 度を適当にｊバ択す−ることによって、各吸入工程にＪ５いて、吸入バルブに時 間差を）（ＪＴ連続開口状態どすることもできる。As a result, this engine has a tr3 - (- means a significant increase in the number of chiseges per medium time. As mentioned above, the comprehensive 4゛effects of the Song Dynasty can be Wear. 1, I, 2) As seen in Fig. 1, the angle of the force l with respect to the inclined frontage is By appropriately selecting the degree of (difference) (JT continuous opening state).
ぞの結果、吸入１１の増加に加えて均一な混合状態を確保て゛きる。As a result, in addition to increasing suction 11, a uniform mixing state can be ensured.
この様な充填助にａ３１）る燃料と酸素分子の均ｖ１’；ｈ分散、およびハロ圧 ］７程における燃焼室での均質な分散が行われる結果、燃焼効宋４高める事がＣ ′きる、。This kind of filling is facilitated by a31) equal v1';h dispersion of fuel and oxygen molecules, and halo pressure. ] As a result of homogeneous dispersion in the combustion chamber at about 7, the combustion efficiency can be increased. 'Wear,.
浄書（内容に変更なし） 第１図 第３図 手続補正書 昭和５８年 ８月２４日 特許庁長官 若 杉 和 夫 殿 １、事件の表示 ＰＣＴ／１Ｊｓ８２１０１４１７ ２、発明の名称 内燃機関用の一体型吸入／排出バルブ機構３、補正をする者 事件との関係 特許出願人 住 所 アメリカ合衆国 ４６２２０ インディアナ州インディアナポリス カ ロールトン アベニュー２２８ 名 称 アルタネイテブ コンパスチョンエンジニアリング インク 代表者 ウィルコックス 士ル ダニエル １ル（国籍） アメリカ合衆国 ４、代理人 〒１０５ 住 所 東京都港区新橋三丁目１番１０号 丸腰ビル９Ｆ６、補正の対象 （１）特許法第１８４条の５第１項の規定による書面の「代表者」の欄 （２）委任状およびその訳文 （３）以五の書面、翻訳文、および図面の浄書（内容に変更なし）特許法第１８ ４条女の５第１項の規定による書面、願書翻訳文、 明細書翻訳文、 請求の範囲翻訳文、 図面翻訳文 ７、補正の内容 別紙の通りEngraving (no changes to the content) Figure 1 Figure 3 Procedural amendment August 24, 1982 Mr. Kazuo Wakasugi, Commissioner of the Patent Office 1.Display of the incident PCT/1Js82101417 2. Name of the invention Integrated intake/exhaust valve mechanism 3 for internal combustion engines, corrector Relationship to the incident: Patent applicant Address: Indianapolis, Indiana, 46220, USA Rollton Avenue 228 Name: Alternative Compassion Engineering, Inc. Representative: Daniel Wilcox (nationality) United States of America 4. Agent〒105 Address: 9F6 Marukoshi Building, 3-1-10 Shinbashi, Minato-ku, Tokyo, subject to correction (1) “Representative” column in the document pursuant to Article 184-5, Paragraph 1 of the Patent Law (2) Power of attorney and its translation (3) Engraving of the following documents, translations, and drawings (no change in content) Patent Law No. 18 Documents pursuant to the provisions of Article 4, Section 5, Paragraph 1, translation of the application, Specification translation, claims translation, Drawing translation 7. Contents of correction As per attached sheet
Claims (1)
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US31287181A | 1981-10-19 | 1981-10-19 | |
| US312871DEEDK | 1981-10-19 | ||
| PCT/US1982/001417 WO1983001485A1 (en) | 1981-10-19 | 1982-10-15 | Multiple concentric intake/exhaust valve system for an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58501832A true JPS58501832A (en) | 1983-10-27 |
Family
ID=23213376
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP82503423A Pending JPS58501832A (en) | 1981-10-19 | 1982-10-15 | Integrated intake/exhaust valve mechanism for internal combustion engines |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0091944B1 (en) |
| JP (1) | JPS58501832A (en) |
| DE (1) | DE3278215D1 (en) |
| WO (1) | WO1983001485A1 (en) |
Families Citing this family (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2300026B (en) * | 1995-04-22 | 1998-12-23 | Peter Harrod | Internal combustion engine valve gear |
| PL314748A1 (en) * | 1996-06-12 | 1997-12-22 | Marek Hoepfler | Vavle-gear for four-stroke internal combustion engine and method of scavenging the cylinders of such engine |
| GB2315519A (en) * | 1996-07-22 | 1998-02-04 | Martyn Shane Finney | Coaxial lift valves, eg for i.c.engines |
| DE19718710C2 (en) * | 1997-05-02 | 2001-02-15 | Lazar Lazic | Internal combustion engine with double valve |
| CN101963100A (en) * | 2009-07-21 | 2011-02-02 | 贾尔·J·Y·帕克 | Air/fuel double pre-mix self-supercharging internal combustion engine with one freewheeling mechanism |
| US10753308B2 (en) | 2017-03-30 | 2020-08-25 | Quest Engines, LLC | Internal combustion engine |
| US10590834B2 (en) | 2017-03-30 | 2020-03-17 | Quest Engines, LLC | Internal combustion engine |
| US10989138B2 (en) | 2017-03-30 | 2021-04-27 | Quest Engines, LLC | Internal combustion engine |
| US11041456B2 (en) | 2017-03-30 | 2021-06-22 | Quest Engines, LLC | Internal combustion engine |
| US10590813B2 (en) | 2017-03-30 | 2020-03-17 | Quest Engines, LLC | Internal combustion engine |
| US10465629B2 (en) | 2017-03-30 | 2019-11-05 | Quest Engines, LLC | Internal combustion engine having piston with deflector channels and complementary cylinder head |
| US10598285B2 (en) | 2017-03-30 | 2020-03-24 | Quest Engines, LLC | Piston sealing system |
| WO2018183682A1 (en) * | 2017-03-30 | 2018-10-04 | Quest Engines, LLC | Internal combustion engine |
| US10526953B2 (en) | 2017-03-30 | 2020-01-07 | Quest Engines, LLC | Internal combustion engine |
| US10724428B2 (en) | 2017-04-28 | 2020-07-28 | Quest Engines, LLC | Variable volume chamber device |
| WO2018204684A1 (en) | 2017-05-04 | 2018-11-08 | Quest Engines, LLC | Variable volume chamber for interaction with a fluid |
| US11060636B2 (en) | 2017-09-29 | 2021-07-13 | Quest Engines, LLC | Engines and pumps with motionless one-way valve |
| WO2019147963A1 (en) | 2018-01-26 | 2019-08-01 | Quest Engines, LLC | Method and apparatus for producing stratified streams |
| US11134335B2 (en) | 2018-01-26 | 2021-09-28 | Quest Engines, LLC | Audio source waveguide |
| CN111997775B (en) * | 2020-08-07 | 2022-04-05 | 中国北方发动机研究所(天津) | Rapid oil injection and efficient collaborative ventilation system for diesel engine |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2213202A (en) * | 1937-07-11 | 1940-09-03 | Buchi Alfred | Internal combustion engine |
| GB589642A (en) * | 1944-07-11 | 1947-06-25 | Nat Gas And Oil Engine Company | Improvements in or relating to valves and valve gear of 4-stroke internal combustionengines |
| FR68584E (en) * | 1955-12-01 | 1958-05-02 | Engine and four-stroke cycle improvements | |
| US2958316A (en) * | 1957-06-19 | 1960-11-01 | Buchi Alfred | Valve actuating gear for four-stroke internal combustion engines |
| GB895554A (en) * | 1961-02-23 | 1962-05-02 | Alfred Johann Buchi | Improvements in or relating to gas engines |
| FR2293601A1 (en) * | 1974-12-03 | 1976-07-02 | Duvant | INTERNAL COMBUSTION ENGINE OF THE TYPE CONTAINING TWO INTAKE VALVES PER CYLINDER CONTROLLED BY A SINGLE ROCKER |
| JPS5347807A (en) * | 1976-10-13 | 1978-04-28 | Shigeo Tsukagoshi | Loop endless tape continuous reproducer and device therefor with cassette |
| US4323046A (en) * | 1977-05-05 | 1982-04-06 | Stanley Barber | Dual fuel system for automobiles |
-
1982
- 1982-10-15 WO PCT/US1982/001417 patent/WO1983001485A1/en active IP Right Grant
- 1982-10-15 JP JP82503423A patent/JPS58501832A/en active Pending
- 1982-10-15 EP EP19820903405 patent/EP0091944B1/en not_active Expired
- 1982-10-15 DE DE8282903405T patent/DE3278215D1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| EP0091944A1 (en) | 1983-10-26 |
| WO1983001485A1 (en) | 1983-04-28 |
| DE3278215D1 (en) | 1988-04-14 |
| EP0091944B1 (en) | 1988-03-09 |
| EP0091944A4 (en) | 1985-04-11 |
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