JP4160708B2 - Structure of scavenging passage for air-leaded stratified scavenging two-cycle engine - Google Patents

Structure of scavenging passage for air-leaded stratified scavenging two-cycle engine Download PDF

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JP4160708B2
JP4160708B2 JP37168499A JP37168499A JP4160708B2 JP 4160708 B2 JP4160708 B2 JP 4160708B2 JP 37168499 A JP37168499 A JP 37168499A JP 37168499 A JP37168499 A JP 37168499A JP 4160708 B2 JP4160708 B2 JP 4160708B2
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scavenging
cylinder
air
port
passage
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JP2001182541A (en
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和之 上野山
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority to JP37168499A priority Critical patent/JP4160708B2/en
Priority to US09/558,596 priority patent/US6257179B1/en
Priority to DE60040765T priority patent/DE60040765D1/en
Priority to EP06015680A priority patent/EP1724450B1/en
Priority to DE60019187T priority patent/DE60019187T2/en
Priority to DE60042862T priority patent/DE60042862D1/en
Priority to EP04026486A priority patent/EP1508679B1/en
Priority to EP09001034A priority patent/EP2055409A1/en
Priority to EP06015681A priority patent/EP1726802A1/en
Priority to DE60035073T priority patent/DE60035073T2/en
Priority to EP06015682A priority patent/EP1739300B1/en
Priority to EP00108969A priority patent/EP1048831B1/en
Priority to US09/832,802 priority patent/US6408805B2/en
Publication of JP2001182541A publication Critical patent/JP2001182541A/en
Priority to US10/152,035 priority patent/US6564761B2/en
Priority to US10/338,727 priority patent/US6729276B2/en
Priority to US10/634,918 priority patent/US7225769B2/en
Priority to US11/700,036 priority patent/US7516725B2/en
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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
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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

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  • Supercharger (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、クランク室圧縮掃気式２サイクルエンジン、特に掃気用空気を用いて先行掃気を行なうようにした空気先導式層状掃気２サイクルエンジンにおける、掃気ポートに連なる掃気通路構造に関する。
【０００２】
【従来の技術】
クランク室圧縮式２サイクルエンジンにおいては、ピストンが上死点へ移動するときにクランクケース内に形成されたクランク室が負圧になることを利用して、吸気ポートからクランク室に混合気を吸い込み、ピストンが下死点方向に移動するときに該クランク室で圧縮された混合気が掃気ポート開口時にクランク室から掃気通路及び掃気ポートを通って燃焼室内に導入され、燃焼ガスを押し出しながら燃焼室内に充填される。かかる２サイクルエンジンにあっては、前記掃気行程では掃気ポートと排気ポートとの開いている区間が広範囲でオーバーラップしているため、燃焼ガスとともに混合気が吹き抜けられるのを防止するとともに、燃焼室内に均一に混合気を充填する手段が従来より種々提供されている。
【０００３】
かかる手段の１つに実公平１−４４７４０号の考案がある。
かかる考案においては、クランク室から立ち上がって、上端部がシリンダ中心方向へ湾曲してシリンダ内に開口する掃気通路を左右に１個ずつ備えた２サイクルエンジンであって、前記湾曲する掃気通路上端の上壁面がシリンダ内に開口する角度を、その一側から他側に向かって連続的に変化させている。
【０００４】
【発明が解決しようとする課題】
かかるクランク室圧縮掃気式２サイクルエンジンは、燃焼ガスとともに吹き抜ける混合気の量を減らし、過大なＴＨＣ（全炭化水素）の排出をなくし、燃料の浪費を抑制することが要求される。
【０００５】
しかしながら、実公平１−４４７４０号にて提案されているクランク室圧縮掃気式２サイクルエンジンにあっては、シリンダ内に開口する掃気通路上端の上壁面の角度つまり吹上げ角を掃気ポートの一側から他側に向かって連続的に変化させているが、これの第３図に示されるように、該吹上げ角θは、第３図(ａ)に示す排気ポート寄りの部位(θａ)の方が、同図(ｃ)に示す吸気ポート寄りの部位(θｃ)よりも大きく形成されている。
【０００６】
従ってかかる従来技術にあっては、排気ポート寄りの部位の吹上げ角θを最大としているため、掃気通路の排気ポート寄りの部位から燃焼室内に吹き出された混合気は、燃焼室の上方に上がった後、排気ポートに向かって流れる燃焼ガスの流れに巻き込まれ易くなる。このため、該排気ポート寄りの部位から供給された混合気が燃焼ガス即ち排気ガスとともに排気ポートに吹き抜け易くなり、前記ＴＨＣ（全炭化水素）の排出量が多くなり、燃料の浪費が増大するとともに、掃気効率が低下して、燃焼室内に充填される混合気濃度が低くなり、エンジンの出力低下をもたらす。
【０００７】
本発明は、かかる従来技術の課題に鑑み、クランク室掃気圧縮式２サイクルエンジン、特に、混合気の排気ポートへの吹き抜けを回避して、ＴＨＣ（全炭化水素）の排出量を低減するとともに、掃気効率を上昇させて燃焼室内に充填される混合気濃度を高め、燃焼を改善してエンジン出力を上昇せしめることを目的とする。
【０００８】
【課題を解決するための手段】
本発明はかかる課題を解決するため、請求項１記載の発明として、シリンダ側部に設けられて該シリンダ内に開口する排気ポートと、シリンダ側部に前記排気ポートと周方向にずらして設けられ該シリンダ内に開口する掃気ポートと、ピストンの往復動により開口されてクランク室内に混合気を供給する吸気ポートと、前記クランク室と掃気ポートとを接続する掃気通路とを備え、前記掃気通路より掃気用空気を用いて先行掃気を行なうようにした空気先導式層状掃気２サイクルエンジンにおいて、
前記掃気通路は、前記掃気ポートに連なる上壁面とシリンダ中心に直角方向線とがなす吹上げ角(α)がシリンダの周方向において異なるように構成され、前記排気ポート寄りの部位における前記吹上げ角をα１、前記吸気ポート寄りの部位における前記吹上げ角をα２とすると、α１＜α２に構成するとともに、前記掃気通路の上壁面は、吸気ポート寄りの部位の吹上げ角 ( α ２ ) から排気ポート寄りの部位の吹上げ角 ( α １ ) に、１段または複数段の段差を有して変化するように形成したシリンダを備え、該シリンダは該段差部を境にして前記のような吹上げ角の異なる２つの型を組み合わされて鋳造されたシリンダであることを特徴とする空気先導式層状掃気２サイクルエンジンの掃気通路構造を提案する。
【０００９】
【００１０】
【００１１】
かかる発明によれば、ピストンの往復動により排気ポートが開かれ、次いで前記排気ポートと周方向にずらして設けられた掃気ポートが開かれると、クランク室から掃気通路に送られた混合気は該掃気ポートから燃焼室内に流入する。
【００１２】
この際において、前記掃気通路は、掃気ポートに連なる上壁面の吸気ポート寄りの部位における吹上げ角が排気ポート寄りの部位における吹上げ角よりも大きく構成されているので、排気ポート寄りの部位から流入した混合気はピストン頂面に沿って拡散せずに流れるため流速が速く、燃焼ガスとの混合が回避され、排気ポートへの吹き抜けが低減される。また、前記吸気ポート寄りの部位から、前記排気ポート寄りの部位よりも低い流速で流入した混合気は、燃焼室上部の点火プラグ周辺に送られることとなって効率良く着火燃焼に供される。
【００１３】
従ってかかる発明によれば、混合気の排気ポートへの吹き抜けが回避され、掃気効率が上昇せしめられて燃焼室内に充填される混合気濃度が高められる。これにより、燃焼が改善されてエンジン出力を上昇せしめることができる。また前記混合気吹き抜けの回避により、ＴＨＣ（全炭化水素）の排出量が低減される。
【００１４】
また、本発明によれば、前記掃気通路の上壁面を、吸気ポート寄りの部位の大きな吹上げ角(α２)から排気ポート寄りの部位の小さな吹上げ角(α１)に、段差を付けて変化するように形成したので、シリンダ鋳造の際には該段差部を境にして前記のような吹上げ角の異なる２つの型を組み合わせれば良く、型抜きが容易となって、シリンダの製造工数が低減される。
また、吹上げ角の異なる２つの型を組み合わせて掃気通路を構成するので、吹上げ角の管理を正確にかつ容易になすことができる。
【００１５】
【発明の実施の形態】
以下、本発明を図に示した実施例を用いて詳細に説明する。但し、この実施例に記載される構成部品の寸法、材質、形状、その相対配置などは特に特定的な記載が無い限り、この発明の範囲をそれのみに限定する趣旨ではなく単なる説明例に過ぎない。
【００１６】
図１は本発明の実施形態の参考例に係る層状掃気２サイクルエンジンのシリンダを示すシリンダ中心線に沿う断面図、図２は本発明の実施例を示す図１対応図である。図３は前記シリンダの掃気通路の断面図で、(Ａ)は図１及び図２のＡ−Ａ線断面図、(Ｂ)はＢ−Ｂ線断面図である。図４は前記第２実施例における掃気ポート部の斜視図、図５は本発明が適用される層状掃気２サイクルエンジンのシリンダ中心線に沿う断面図である。
【００１７】
本発明が適用される層状掃気２サイクルエンジンを示す図５において、２はシリンダ、４２はシリンダ内面、４はピストン、６はクランク軸、６ａは該クランク軸６を構成するクランクウェブ、５はクランクケース、３はピストン４とクランク軸６とを連結するコネクティングロッド、７はシリンダヘッド、８は点火プラグ、１１はエアクリーナ、１２は気化器である。
また、２５は燃焼室、５ａはクランクケース５の内部に形成されたクランク室、１５ｂ、１５は前記気化器１２とクランク室５ａとを接続する混合気通路である。１３はシリンダ２の側部に開口した排気ポートで、排気通路４１を経て排気管に接続される。
【００１８】
９はシリンダ２の排気ポート１３の周方向左右に該排気ポート１３とほぼ直角方向の部位に２個対向するように設けられた掃気ポートである。対をなす該掃気ポート９の夫々は、シリンダ２に斜め方向に設けられた対をなす掃気分岐通路１０９ｅ、クランクケース５の両側面の壁内に弧状に形成された対をなす掃気通路１０９ｄ及び対をなす掃気通路開口部１０９ｂ、１０９ｂを介して前記クランク室５ａと連通されている。
【００１９】
１０はシリンダ２の側部の内部に設けられた空気供給室で、上流側がインシュレータ３０内の空気通路１０ｂに接続され、下流側が対をなす空気分岐通路１０ａに接続されている。該空気分岐通路１０ａは、対をなす掃気分岐通路１０９ｅに連通している。
また、該空気供給室１０には、左右の空気分岐通路１０ａ、１０ａへの開口部に、空気分岐通路１０ａ、１０ａ側に向かう流れのみを許容する逆止弁１６が設けられている。
【００２０】
前記インシュレータ３０は、エンジン本体側と吸気系とを熱的に遮断するもので、シリンダ２の側面にボルト締めされている。該インシュレータ３０内部の上側には前記空気通路１０ｂ、下側には混合気通路１５ｂが形成されている。
該混合気通路１５ｂの上流側は、気化器１２内の混合気流量制御用の絞り弁１４に連通され、下流側は吸気ポート１５ａを介してシリンダ内（燃焼室２５）と連通されている。
１１０はエアクリーナ１１とインシュレータ３０を接続する気化器１２と一体の空気通路管で、該空気通路管１１０には空気通路面積を変化させる空気制御弁２０が設けられており、該空気制御弁２０は気化器１２の絞り弁１４と連動するようになっている。
【００２１】
本発明は、以上に示された層状掃気２サイクルエンジンの掃気通路構造の改良に関するものである。
即ち本発明の実施例を示す図２及び図３において、２はシリンダ、２５は該シリンダ内に形成された燃焼室、４３は前記点火プラグ８用の点火プラグ穴、１５は混合気通路、１５ａは該混合気通路１５の燃焼室２５への開口部である吸気ポート、１３は排気ポート、４１は該排気ポート１３に連通される排気通路である。４２はシリンダ内面を示す。
【００２２】
９は掃気ポートで、前記掃気通路１０９ｄの燃焼室２５への開口部を構成している。該掃気ポート９及び掃気通路１０９ｄは、図５と同様に対をなして２個設けられている。
前記掃気ポート９に連なる前記掃気通路１０９ｄは、図３示すように、前記掃気ポート９に連なる上壁面９ａ、９ｂと、シリンダ中心５０に直角方向線即ち水平方向線４５とがなす吹上げ角(α)がシリンダの周方向において異なるように構成されている。
【００２３】
図２に示される実施例においては、前記掃気通路１０９ｄは、図３に示されるように、前記排気ポート１３寄りの部位における前記上壁面９ｂの吹上げ角をα１(図３のＢ)、前記吸気ポート１５ａ寄りの部位における前記上壁面９ａの吹上げ角をα２(図３のＡ)とすると、α１＜α２に構成され、かつ該吹上げ角(α)は、吸気ポート１５ａ寄りの部位(α２)から排気ポート１３寄りの部位(α１)に向けて連続的に小さくなるように構成されている。
【００２４】
また、図２、４及び３に示される実施例においては、前記掃気通路１０９ｄは、その上壁面９ａ、９ｂが、吸気ポート１５ａ寄りの部位の所定長さａの範囲における吹上げ角α２から、排気ポート１３寄りの部位の所定長さｂの範囲の吹上げ角α１に、段差部４４を付けて変化するように形成されている。
この場合、前記所定長さａの範囲内では一定の吹上げ角α２、また所定長さｂの範囲では一定の吹上げ角α１に夫々構成する。また、前記段差部４４を２個以上設けて、吹上げ角を３段階以上変化させてもよい。
【００２５】
かかる構成からなる層状掃気２サイクルエンジンの運転時において、燃焼室２５内の燃焼圧力によりピストン４が下降し、排気ポート１３が開くと、該燃焼室２５内の燃焼ガス（排気ガス）は排気ポート１３及び排気通路４１を通って排気管へ排出され、マフラ（図示省略）を通って外気中へ放出される。
ピストン４がさらに下降すると、左右の掃気ポート９、９が開口し、掃気分岐通路１０９ｅに溜められていた空気が、燃焼室２５内に流入して燃焼ガスを排気ポート１３側へ押し出す。
【００２６】
次いで、クランク室５ａ内に溜められていた混合気がそれぞれ対をなす掃気通路開口部１０９ｂ及び１０９ｂ、掃気通路１０９ｄ及び１０９ｄ、掃気分岐通路１０９ｅ及び１０９ｅを経て、掃気ポート９、９から燃焼室２５内に流入する。
ピストン４が下降して下死点にある状態では、排気ポート１３、２つの掃気ポート９、９は開口していて、燃焼室２５内への空気及び混合気の供給は終了、あるいは終了しようとしている。そして、ピストン４が下死点から上昇すると、該ピストン４によって掃気ポート９、９が閉じられクランク室５ａ内が密閉空間となり、膨張即ち圧力の低下が始まる。
【００２７】
ピストン４がさらに上昇すると、排気ポート１３が閉じられ、燃焼室２５内の混合ガスの圧縮が始まる一方、ピストン４の上昇によるクランク室５ａの容積増大により該クランク室５ａ内の圧力はさらに低下する。ピストン４がさらに上昇するとシリンダ２側面に形成された吸気ポート１５ａが開口し、気化器１２で生成され、絞り弁１４で流量制御された混合気が混合気通路１５を経てクランク室５ａ内に供給される。
【００２８】
前記クランク室５ａ内の圧力の低下は、掃気通路開口部１０９ｂ、１０９ｂ、掃気通路１０９ｄ、１０９ｄ、及び掃気分岐通路１０９ｅ、１０９ｅを経て左右の空気分岐通路１０ａ、１０ａにも伝わるので、逆止弁１６が開弁し、該逆止弁１６を経て空気供給室１０内に供給された空気が掃気通路１０９ｄ、１０９ｄに充填される。
【００２９】
ピストン４が圧縮上死点近傍に達すると、点火プラグ８によって燃焼室２５内に火花放電され、圧縮された混合気に着火、燃焼が行なわれる。この燃焼により、発生する圧力でピストン４が押し下げられ、クランク軸６に回転トルクが生じる。
ピストン４が下降して排気ポート１３が開口すると、燃焼室２５内の燃焼ガスは排気ポート１３から排気管に流れ、次いでマフラ（図示省略）を経て外部に排出される。
【００３０】
前記掃気作用時において、前記掃気通路１０９ｄは、掃気ポート９に連なる上壁面９ａ、９ｂの吸気ポート１５ａ寄りの部位における吹上げ角α２が排気ポート１３寄りの部位における吹上げ角α１よりも大きく構成されているので、該排気ポート１３寄りの部位から流入した混合気はピストンの頂面に沿って拡散せずに流れるため流速が速く、これにより燃焼ガスとの混合が回避され、排気ポート１３への混合気の吹き抜けが低減される。
【００３１】
また、前記掃気通路１０９ｄの、前記吸気ポート１５ａ寄りの部位から、前記排気ポート１３寄りの部位よりも低い流速で流入した混合気は、燃焼室２５上部の点火プラグ８周辺に送られることとなって、効率良く着火燃焼に供される。
【００３２】
従って、かかる実施例によれば、燃焼室２５内に供給された混合気の排気ポート１３への吹き抜けが回避され、掃気効率が上昇せしめられて燃焼室２５内に充填される混合気濃度が高められる。
【００３３】
また、前記実施例のように構成すれば、前記掃気通路１０９ｄの上壁面９ａ、９ｂを、吸気ポート１５ａ寄りの部位の大きな吹上げ角(α２)から排気ポート１３寄りの部位の小さな吹上げ角(α１)に、段差部４４を付けて変化するように形成したので、シリンダ２鋳造の際には該段差部４４を境にして前記のような吹上げ角αの異なる２つの型を組み合わせれば良く、型抜きが容易となる。
また、吹上げ角の異なる２つの型を組み合わせて掃気通路１０９ｄを構成するので、吹上げ角の管理を正確にかつ容易になすことができる。
【００３４】
【発明の効果】
以上記載のごとく本発明によれば、掃気通路を、掃気ポートに連なる上壁面の吸気ポート寄りの部位における吹上げ角が排気ポート寄りの部位における吹上げ角よりも大きく構成しているので、排気ポート寄りの部位から流入した混合気はピストンの頂面に沿って拡散せずに流れるため流速が速く、これにより燃焼ガスとの混合が回避され、排気ポートへの吹き抜けが低減される。また、前記吸気ポート寄りの部位から低い流速で流入した混合気は点火プラグ周辺に送られることとなって効率良く着火燃焼に供されることとなり、これにより、掃気効率が上昇せしめられて燃焼室内に充填される混合気濃度が高められ、燃焼が改善されてエンジン出力を上昇せしめることができる。また前記混合気吹き抜けの回避により、ＴＨＣ（全炭化水素）の排出量を低減できる。
【００３５】
また、本発明によれば、前記掃気通路の上壁面を、吸気ポート寄りの部位の大きな吹上げ角から排気ポート寄りの部位の小さな吹上げ角に、段差を付けて変化するように形成したので、シリンダ鋳造の際には該段差部を境にして前記のような吹上げ角の異なる２つの型を組み合わせれば良く、型抜きが容易となって、シリンダの製造工数が低減される。
また、吹上げ角の異なる２つの型を組み合わせて掃気通路を構成するので、吹上げ角の管理を正確にかつ容易になすことができる。
【図面の簡単な説明】
【図１】 図１は本発明の参考例に係る層状掃気２サイクルエンジンのシリンダを示すシリンダ中心線に沿う断面図である。
【図２】 本発明の実施例を示す図１対応図である。
【図３】 前記シリンダの掃気通路の断面図で、(Ａ)は図１及び図２のＡ−Ａ線断面図、(Ｂ)はＢ−Ｂ線断面図である。
【図４】 前記実施例における掃気ポート部の斜視図である。
【図５】 本発明が適用される層状掃気２サイクルエンジンのシリンダ中心線に沿う断面図である。
【符号の説明】
２ シリンダ
３ コネクティングロッド
４ ピストン
５ クランクケース
５ａ クランク室
６ クランク軸
６ａ クランクウェブ
７ シリンダヘッド
８ 点火プラグ
９ 掃気ポート
９ａ 上壁面
１０ 空気供給室
１０ａ 空気分岐通路
１０ｅ 気体通路
１１ エアクリーナ
１２ 気化器
１３ 排気ポート
１４ 絞り弁
１５、１５ｂ 混合気通路
１５ａ 吸気ポート
１６ 逆止弁
２０ 空気制御弁
２５ 燃焼室
３０ インシュレータ
４１ 排気通路
４２ シリンダ内面
４５ 水平方向線
５０ シリンダ中心
６０ クランク軸心
１０９ｂ
掃気通路開口部
１０９ｄ
掃気通路
１０９ｅ
掃気分岐通路[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scavenging passage structure connected to a scavenging port in a crankcase compression scavenging two-cycle engine, particularly an air-leading stratified scavenging two-cycle engine configured to perform scavenging using scavenging air.
[0002]
[Prior art]
In a crankcase compression type two-cycle engine, the air-fuel mixture is sucked into the crankcase from the intake port by utilizing the negative pressure in the crankcase formed in the crankcase when the piston moves to the top dead center. When the piston moves in the direction of bottom dead center, the air-fuel mixture compressed in the crank chamber is introduced from the crank chamber through the scavenging passage and the scavenging port into the combustion chamber when the scavenging port is open, Filled. In such a two-cycle engine, since the open section of the scavenging port and the exhaust port overlaps in a wide range in the scavenging stroke, the mixture gas is prevented from being blown out together with the combustion gas, and the combustion chamber Various means for uniformly filling the air-fuel mixture have been provided.
[0003]
One such means is the idea of Japanese Utility Model Publication No. 1-444740.
In this device, a two-cycle engine is provided with one scavenging passage that rises from the crank chamber and has an upper end curved toward the center of the cylinder and opened into the cylinder. The angle at which the upper wall surface opens into the cylinder is continuously changed from one side to the other side.
[0004]
[Problems to be solved by the invention]
Such a crankcase compression scavenging two-cycle engine is required to reduce the amount of air-fuel mixture blown out with combustion gas, eliminate excessive THC (total hydrocarbons) emission, and suppress fuel waste.
[0005]
However, in the crank chamber compression scavenging two-cycle engine proposed in Japanese Utility Model Publication No. 1-4740, the angle of the upper wall surface of the scavenging passage opening in the cylinder, that is, the blowing angle is set to one side of the scavenging port. As shown in FIG. 3, the blow-up angle θ is changed in the region near the exhaust port (θa) shown in FIG. 3 (a). This is formed larger than the portion (θc) near the intake port shown in FIG.
[0006]
Therefore, in such a conventional technique, the blow-up angle θ at the portion near the exhaust port is maximized, so that the air-fuel mixture blown into the combustion chamber from the portion near the exhaust port of the scavenging passage rises above the combustion chamber. After that, it becomes easy to get involved in the flow of the combustion gas flowing toward the exhaust port. For this reason, the air-fuel mixture supplied from the portion near the exhaust port easily blows into the exhaust port together with the combustion gas, that is, the exhaust gas, the amount of THC (total hydrocarbons) discharged increases, and the waste of fuel increases. As a result, the scavenging efficiency is lowered, and the concentration of the air-fuel mixture filled in the combustion chamber is lowered, resulting in a decrease in engine output.
[0007]
In view of the problems of the prior art, the present invention avoids the blow-through of the air-fuel mixture to the exhaust port of the crankcase scavenging compression type two-cycle engine, and reduces the exhaust amount of THC (total hydrocarbons). The purpose is to increase the scavenging efficiency to increase the concentration of the air-fuel mixture filled in the combustion chamber, improve combustion, and increase engine output.
[0008]
[Means for Solving the Problems]
In order to solve such a problem, the present invention provides, as an invention according to claim 1, an exhaust port provided in a cylinder side portion and opening in the cylinder, and a cylinder side portion provided with a displacement in the circumferential direction from the exhaust port. comprising a scavenging port that opens into the cylinder, an intake port for supplying air-fuel mixture in the crank chamber is opened by reciprocating motion of the piston, and a transfer passage for connecting the crank chamber and the scavenging ports, from said transfer passage In an air-leading stratified scavenging two-cycle engine in which scavenging air is used for preceding scavenging ,
The scavenging passage is configured such that a blowing angle (α) formed by an upper wall surface connected to the scavenging port and a perpendicular line to the center of the cylinder is different in a circumferential direction of the cylinder, and the blowing at a portion near the exhaust port 1 corners alpha, when the upflow angle and alpha 2 at the site of the intake ports close, along with constituting the alpha 1 <alpha 2, the upper wall surface of the scavenging passages, upflow angle portion of the intake port closer ( a cylinder formed so as to change with a step of one or a plurality of steps at a blow-up angle ( α 1 ) near the exhaust port from α 2 ) , the cylinder having the step as a boundary The present invention proposes a scavenging passage structure for an air-leaded stratified scavenging two-cycle engine, characterized in that it is a cylinder cast by combining two types having different blowing angles as described above .
[0009]
[0010]
[0011]
According to this invention, when the exhaust port is opened by the reciprocating motion of the piston, and then the scavenging port provided to be shifted from the exhaust port in the circumferential direction is opened, the air-fuel mixture sent from the crank chamber to the scavenging passage is It flows into the combustion chamber from the scavenging port.
[0012]
In this case, the scavenging passage is configured such that the blowing angle at the portion near the intake port on the upper wall surface connected to the scavenging port is larger than the blowing angle at the portion near the exhaust port. Since the inflowing air-fuel mixture flows without diffusing along the top surface of the piston, the flow velocity is high, mixing with the combustion gas is avoided, and blow-through to the exhaust port is reduced. In addition, the air-fuel mixture that has flowed in from the portion close to the intake port at a lower flow rate than the portion close to the exhaust port is sent to the vicinity of the spark plug at the upper portion of the combustion chamber and is efficiently used for ignition and combustion.
[0013]
Therefore, according to this invention, the blow-through of the air-fuel mixture to the exhaust port is avoided, the scavenging efficiency is increased, and the air-fuel mixture concentration filled in the combustion chamber is increased. Thereby, combustion is improved and an engine output can be raised. Moreover, the amount of THC (total hydrocarbons) discharged is reduced by avoiding the air-fuel mixture blow-through.
[0014]
According to the present invention, the upper wall surface of the scavenging passage is changed with a step from a large blowing angle (α2) near the intake port to a small blowing angle (α1) near the exhaust port. Therefore, when casting a cylinder, it is only necessary to combine two molds having different blowing angles with the stepped portion as a boundary. Is reduced.
Moreover, since the scavenging passage is configured by combining two types having different blowing angles, the blowing angle can be managed accurately and easily.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are merely illustrative examples and not intended to limit the scope of the present invention unless otherwise specified. Absent.
[0016]
Figure 1 is a cross sectional view taken along the cylinder center line showing the cylinder stratified scavenging two-cycle engine according to the reference example embodiment of the present invention, FIG 2 is a diagram 1 corresponding view showing the actual施例of the present invention. FIG. 3 is a cross-sectional view of the scavenging passage of the cylinder, (A) is a cross-sectional view taken along the line AA in FIGS. 1 and 2, and (B) is a cross-sectional view taken along the line BB. FIG. 4 is a perspective view of the scavenging port portion in the second embodiment, and FIG. 5 is a sectional view taken along the cylinder center line of a stratified scavenging two-cycle engine to which the present invention is applied.
[0017]
In FIG. 5 showing a stratified scavenging two-cycle engine to which the present invention is applied, 2 is a cylinder, 42 is a cylinder inner surface, 4 is a piston, 6 is a crankshaft, 6a is a crank web constituting the crankshaft 6, and 5 is a crank. The case 3 is a connecting rod for connecting the piston 4 and the crankshaft 6, 7 is a cylinder head, 8 is a spark plug, 11 is an air cleaner, and 12 is a carburetor.
Reference numeral 25 denotes a combustion chamber, 5a denotes a crank chamber formed inside the crankcase 5, and 15b and 15 denote air-fuel mixture passages connecting the carburetor 12 and the crank chamber 5a. Reference numeral 13 denotes an exhaust port that opens at the side of the cylinder 2 and is connected to an exhaust pipe through an exhaust passage 41.
[0018]
Reference numeral 9 denotes scavenging ports provided on the left and right sides of the exhaust port 13 of the cylinder 2 so as to face two portions substantially perpendicular to the exhaust port 13. Each of the pair of scavenging ports 9 includes a pair of scavenging branch passages 109e provided in the cylinder 2 in an oblique direction, a pair of scavenging passages 109d formed in an arc shape in the walls on both sides of the crankcase 5, and It communicates with the crank chamber 5a through a pair of scavenging passage openings 109b and 109b.
[0019]
Reference numeral 10 denotes an air supply chamber provided inside the side portion of the cylinder 2. The upstream side is connected to the air passage 10b in the insulator 30, and the downstream side is connected to a pair of air branch passages 10a. The air branch passage 10a communicates with a pair of scavenging branch passages 109e.
The air supply chamber 10 is provided with a check valve 16 that allows only the flow toward the air branch passages 10a and 10a at the openings to the left and right air branch passages 10a and 10a.
[0020]
The insulator 30 thermally shuts off the engine main body side and the intake system, and is bolted to the side surface of the cylinder 2. The air passage 10b is formed on the upper side of the insulator 30, and the air-fuel mixture passage 15b is formed on the lower side.
The upstream side of the mixture passage 15b communicates with a throttle valve 14 for controlling the mixture flow rate in the carburetor 12, and the downstream side communicates with the inside of the cylinder (combustion chamber 25) via an intake port 15a.
Reference numeral 110 denotes an air passage pipe integrated with the carburetor 12 that connects the air cleaner 11 and the insulator 30. The air passage pipe 110 is provided with an air control valve 20 that changes the air passage area. The throttle valve 14 of the vaporizer 12 is interlocked with the throttle valve 14.
[0021]
The present invention relates to an improvement in the scavenging passage structure of the stratified scavenging two-cycle engine shown above.
That is, in FIG. 2 and FIG. 3 shows the actual施例of the present invention, 2 a cylinder, 25 is a combustion chamber formed in the cylinder, the spark plug hole for the spark plug 8 43, 15 mixture passage, Reference numeral 15 a denotes an intake port that is an opening of the mixture passage 15 to the combustion chamber 25, 13 denotes an exhaust port, and 41 denotes an exhaust passage that communicates with the exhaust port 13. Reference numeral 42 denotes an inner surface of the cylinder.
[0022]
Reference numeral 9 denotes a scavenging port, which constitutes an opening to the combustion chamber 25 of the scavenging passage 109d. The scavenging port 9 and the scavenging passage 109d are provided in pairs as in FIG.
As shown in FIG. 3, the scavenging passage 109 d connected to the scavenging port 9 has a blowing angle formed by upper wall surfaces 9 a and 9 b connected to the scavenging port 9 and a perpendicular line, that is, a horizontal line 45, to the cylinder center 50. α) is configured to be different in the circumferential direction of the cylinder.
[0023]
In actual施例that shown in Figure 2, the scavenging passage 109d, as shown in FIG. 3, the upflow angle of the upper wall 9b at the site of the exhaust port 13 toward [alpha] 1 (B in FIG. 3) Assuming that the blowing angle of the upper wall surface 9a in the portion near the intake port 15a is α2 (A in FIG. 3), α1 <α2 is established, and the blowing angle (α) is close to the intake port 15a. It is configured to continuously decrease from the portion (α2) toward the portion (α1) near the exhaust port 13.
[0024]
In the actual施例that shown in FIGS. 2, 4 and 3, wherein the scavenging passage 109d, the upper wall surface 9a, 9b is, upflow angle in the range of a predetermined length a portion of the intake port 15a toward α2 To a blowing angle α1 in a range of a predetermined length b near the exhaust port 13 so as to change with a stepped portion 44.
In this case, a constant blowing angle α2 is formed within the range of the predetermined length a, and a constant blowing angle α1 is formed within the range of the predetermined length b. Further, two or more stepped portions 44 may be provided, and the blowing angle may be changed in three or more steps.
[0025]
When the stratified scavenging two-cycle engine having such a configuration is operated, when the piston 4 is lowered by the combustion pressure in the combustion chamber 25 and the exhaust port 13 is opened, the combustion gas (exhaust gas) in the combustion chamber 25 is discharged from the exhaust port. 13 and the exhaust passage 41, the exhaust pipe is discharged, and the exhaust gas is discharged into the outside air through a muffler (not shown).
When the piston 4 is further lowered, the left and right scavenging ports 9 and 9 are opened, and the air stored in the scavenging branch passage 109e flows into the combustion chamber 25 and pushes the combustion gas to the exhaust port 13 side.
[0026]
Next, the air-fuel mixture accumulated in the crank chamber 5a is paired with the scavenging passage openings 109b and 109b, the scavenging passages 109d and 109d, and the scavenging branch passages 109e and 109e, and then from the scavenging ports 9 and 9 to the combustion chamber 25. Flows in.
In the state where the piston 4 descends and is at the bottom dead center, the exhaust port 13 and the two scavenging ports 9 and 9 are open, and the supply of air and air-fuel mixture into the combustion chamber 25 ends or is about to end. Yes. When the piston 4 rises from the bottom dead center, the scavenging ports 9 and 9 are closed by the piston 4, the inside of the crank chamber 5a becomes a sealed space, and expansion, that is, pressure reduction starts.
[0027]
When the piston 4 further rises, the exhaust port 13 is closed, and the compression of the mixed gas in the combustion chamber 25 starts, while the pressure in the crank chamber 5a further decreases due to the increase in the volume of the crank chamber 5a due to the rise of the piston 4. . When the piston 4 further rises, an intake port 15a formed on the side surface of the cylinder 2 opens, and an air-fuel mixture generated by the carburetor 12 and controlled in flow rate by the throttle valve 14 is supplied into the crank chamber 5a through the air-fuel mixture passage 15. Is done.
[0028]
The pressure drop in the crank chamber 5a is also transmitted to the left and right air branch passages 10a and 10a via the scavenging passage openings 109b and 109b, the scavenging passages 109d and 109d, and the scavenging branch passages 109e and 109e. 16 is opened, and the air supplied into the air supply chamber 10 through the check valve 16 is filled in the scavenging passages 109d and 109d.
[0029]
When the piston 4 reaches the vicinity of the compression top dead center, a spark is discharged into the combustion chamber 25 by the spark plug 8, and the compressed air-fuel mixture is ignited and burned. Due to this combustion, the piston 4 is pushed down by the generated pressure, and rotational torque is generated in the crankshaft 6.
When the piston 4 descends and the exhaust port 13 opens, the combustion gas in the combustion chamber 25 flows from the exhaust port 13 to the exhaust pipe, and then is discharged to the outside through a muffler (not shown).
[0030]
At the time of the scavenging action, the scavenging passage 109d is configured such that the blowing angle α2 at the portion near the intake port 15a of the upper wall surfaces 9a, 9b connected to the scavenging port 9 is larger than the blowing angle α1 at the portion near the exhaust port 13. As a result, the air-fuel mixture flowing in from the portion near the exhaust port 13 flows without diffusing along the top surface of the piston, so that the flow velocity is high, thereby avoiding mixing with the combustion gas and to the exhaust port 13. Blow-through of the air-fuel mixture is reduced.
[0031]
In addition, the air-fuel mixture that has flowed from the portion near the intake port 15a in the scavenging passage 109d at a lower flow rate than the portion near the exhaust port 13 is sent to the vicinity of the spark plug 8 above the combustion chamber 25. Therefore, it is used for ignition and combustion efficiently.
[0032]
Therefore, according to this embodiment, the air-fuel mixture supplied into the combustion chamber 25 is prevented from being blown through the exhaust port 13, the scavenging efficiency is increased, and the concentration of the air-fuel mixture filled in the combustion chamber 25 is increased. It is done.
[0033]
The front be configured as you施例, upper wall surface 9a of the scavenging passages 109d, 9b a small spray sites of the exhaust port 13 toward the large upflow angle portions of the intake ports 15a toward ([alpha] 2) Since the rising angle (α1) is formed so as to change with the stepped portion 44, when casting the cylinder 2, two molds having different blowing angles α as described above are formed with the stepped portion 44 as a boundary. What is necessary is just to combine, and die cutting becomes easy.
Further, since the scavenging passage 109d is configured by combining two types having different blowing angles, the blowing angle can be managed accurately and easily.
[0034]
【The invention's effect】
As described above, according to the present invention, the scavenging passage is configured so that the blowing angle at the portion near the intake port on the upper wall surface connected to the scavenging port is larger than the blowing angle at the portion near the exhaust port. Since the air-fuel mixture flowing in from the portion near the port flows without diffusing along the top surface of the piston, the flow velocity is high, thereby avoiding mixing with the combustion gas and reducing blow-through to the exhaust port. Further, the air-fuel mixture flowing at a low flow rate from the portion close to the intake port is sent to the vicinity of the spark plug and is efficiently used for ignition and combustion, thereby increasing scavenging efficiency and increasing the combustion chamber. Thus, the concentration of the air-fuel mixture charged in the engine can be increased, the combustion can be improved, and the engine output can be increased. Further, the amount of THC (total hydrocarbons) discharged can be reduced by avoiding the air-fuel mixture blow-through.
[0035]
Further , according to the present invention, the upper wall surface of the scavenging passage is formed to change with a step from a large blowing angle near the intake port to a small blowing angle near the exhaust port. When casting the cylinder, it is only necessary to combine the two dies having different blowing angles as described above with the stepped portion as a boundary, which facilitates die cutting and reduces the number of manufacturing steps of the cylinder.
Further, since the scavenging passage is configured by combining two types having different blowing angles, the blowing angle can be managed accurately and easily.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view along a cylinder center line showing a cylinder of a stratified scavenging two-cycle engine according to a reference example of the present invention.
FIG. 2 is a diagram corresponding to FIG. 1 showing an embodiment of the present invention .
3A and 3B are cross-sectional views of the scavenging passage of the cylinder, wherein FIG. 3A is a cross-sectional view taken along line AA in FIGS. 1 and 2, and FIG. 3B is a cross-sectional view taken along line BB.
4 is a perspective view of a scavenging port portion before you施例.
FIG. 5 is a sectional view taken along a cylinder center line of a stratified scavenging two-cycle engine to which the present invention is applied.
[Explanation of symbols]
2 cylinder 3 connecting rod 4 piston 5 crankcase 5a crank chamber 6 crankshaft 6a crank web 7 cylinder head 8 spark plug 9 scavenging port 9a upper wall surface 10 air supply chamber 10a air branch passage 10e gas passage 11 air cleaner 12 carburetor 13 exhaust port 14 Throttle valves 15, 15b Mixture passage 15a Intake port 16 Check valve 20 Air control valve 25 Combustion chamber 30 Insulator 41 Exhaust passage 42 Cylinder inner surface 45 Horizontal line 50 Cylinder center 60 Crank shaft center 109b
Scavenging passage opening 109d
Scavenging passage 109e
Scavenging branch passage

Claims (1)

シリンダ側部に設けられて該シリンダ内に開口する排気ポートと、シリンダ側部に前記排気ポートと周方向にずらして設けられ該シリンダ内に開口する掃気ポートと、ピストンの往復動により開口されてクランク室内に混合気を供給する吸気ポートと、前記クランク室と掃気ポートとを接続する掃気通路とを備え、前記掃気通路より掃気用空気を用いて先行掃気を行なうようにした空気先導式層状掃気２サイクルエンジンにおいて、
前記掃気通路は、前記掃気ポートに連なる上壁面とシリンダ中心に直角方向線とがなす吹上げ角(α)がシリンダの周方向において異なるように構成され、前記排気ポート寄りの部位における前記吹上げ角をα１、前記吸気ポート寄りの部位における前記吹上げ角をα２とすると、α１＜α２に構成するとともに、前記掃気通路の上壁面は、吸気ポート寄りの部位の吹上げ角 ( α ２ ) から排気ポート寄りの部位の吹上げ角 ( α １ ) に、１段または複数段の段差を有して変化するように形成したシリンダを備え、該シリンダは該段差部を境にして前記のような吹上げ角の異なる２つの型を組み合わされて鋳造されたシリンダであることを特徴とする空気先導式層状掃気２サイクルエンジンの掃気通路構造。An exhaust port provided in the cylinder side and opened in the cylinder, a scavenging port provided in the cylinder side portion shifted in the circumferential direction from the exhaust port and opened in the cylinder, and opened by reciprocation of the piston. An air-leading stratified scavenging comprising an intake port for supplying an air-fuel mixture into the crank chamber and a scavenging passage connecting the crank chamber and the scavenging port, and performing pre-scavenging using scavenging air from the scavenging passage In a two-cycle engine,
The scavenging passage is configured such that a blowing angle (α) formed by an upper wall surface connected to the scavenging port and a perpendicular line to the center of the cylinder is different in a circumferential direction of the cylinder, and the blowing at a portion near the exhaust port 1 corners alpha, when the upflow angle and alpha 2 at the site of the intake ports close, along with constituting the alpha 1 <alpha 2, the upper wall surface of the scavenging passages, upflow angle portion of the intake port closer ( a cylinder formed so as to change with a step of one or a plurality of steps at a blow-up angle ( α 1 ) near the exhaust port from α 2 ) , the cylinder having the step as a boundary A scavenging passage structure of an air-leading layered scavenging two-cycle engine, characterized in that it is a cylinder cast by combining two types having different blowing angles as described above .
JP37168499A 1999-04-28 1999-12-27 Structure of scavenging passage for air-leaded stratified scavenging two-cycle engine Expired - Lifetime JP4160708B2 (en)

Priority Applications (17)

Application Number Priority Date Filing Date Title
JP37168499A JP4160708B2 (en) 1999-12-27 1999-12-27 Structure of scavenging passage for air-leaded stratified scavenging two-cycle engine
US09/558,596 US6257179B1 (en) 1999-04-28 2000-04-26 Two-stroke cycle engine
EP00108969A EP1048831B1 (en) 1999-04-28 2000-04-27 Two-stroke cycle engine
DE60019187T DE60019187T2 (en) 1999-04-28 2000-04-27 Two-stroke internal combustion engine
DE60042862T DE60042862D1 (en) 1999-04-28 2000-04-27 Two-stroke engine
EP04026486A EP1508679B1 (en) 1999-04-28 2000-04-27 Two-stroke cycle engine
EP09001034A EP2055409A1 (en) 1999-04-28 2000-04-27 Method of casting a cylinder for a two-stroke engine
EP06015681A EP1726802A1 (en) 1999-04-28 2000-04-27 Two-stroke cycle engine
DE60040765T DE60040765D1 (en) 1999-04-28 2000-04-27 Two-stroke engine
EP06015682A EP1739300B1 (en) 1999-04-28 2000-04-27 Two-stroke cycle engine
EP06015680A EP1724450B1 (en) 1999-04-28 2000-04-27 Two-stroke cycle engine
DE60035073T DE60035073T2 (en) 1999-04-28 2000-04-27 Two-stroke internal combustion engine
US09/832,802 US6408805B2 (en) 1999-04-28 2001-04-12 Two-stroke cycle engine
US10/152,035 US6564761B2 (en) 1999-04-28 2002-05-22 Two-stroke cycle engine
US10/338,727 US6729276B2 (en) 1999-04-28 2003-01-09 Two-stroke cycle engine
US10/634,918 US7225769B2 (en) 1999-04-28 2003-08-06 Two-stroke cycle engine
US11/700,036 US7516725B2 (en) 1999-04-28 2007-01-31 Two-stroke cycle engine

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Application Number Priority Date Filing Date Title
JP37168499A JP4160708B2 (en) 1999-12-27 1999-12-27 Structure of scavenging passage for air-leaded stratified scavenging two-cycle engine

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JP4878265B2 (en) * 2006-11-09 2012-02-15 ハスクバーナ・ゼノア株式会社 2-cycle engine
JP5381871B2 (en) * 2010-03-31 2014-01-08 日立工機株式会社 Two-cycle engine and engine working machine equipped with the same

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