1244526 玖、發明說明： 【發明所屬之技術領域】 本發明係關於一種將節流閥體裝置通過進氣管連接到 汽缸頭上的進氣口的直喷引擎之進氣裝置，上述節流閥體 裝置包括具有進氣通路的閥體部；橫切上述進氣通路且能 夠轉動地支撐在上述閥體部上的節流閥軸；以調節上述進 氣通路開口面積的方式固定在上述節流閥軸上的節流閥； 及在上述閥體部的外部固定在上述節流閥軸的一端上，同 時，纏繞連接有節流閥纜線的節流閥鼓，在上述汽缸頭上 設有以對應上述節流閥的轉動量的燃料的量直接噴射到燃 燒室内的喷射器。 【先前技術】 迄今以來，設置在車輛上的直噴引擎，其對應車輛操作 者用之加速踏板或節流閥握把之操作量部份的燃料，是從 設置在汽缸頭上的噴射器直接喷射到燃燒室内，但在引擎 之低負荷、低速轉動區域，在進行引擎輸出控制以便通過 稀釋燃燒試圖降低燃料消耗時，加速踏板或節流閥握把之 操作量、即節流閥的轉動量與引擎的進氣量之間非線形對 應。 為了使節流閥的轉動量和引擎的進氣量之間出現非線 性對應關係，在日本專利文獻1所揭示的非直喷引擎的引擎 進氣裝置中，和節流閥不同在進氣系統内另外設有其他的 控制閥，並由E C U來控制該控制閥的開啟度。 (專利文獻1 ) 6 312/發明說明書(補件)/93-06/93107769 1244526 曰本專利特開平1 1 — 1 Ο 7 7 8 8號公報 【發明内容】 (發明所欲解決之問題） 通過將上述專利文獻1所揭示之技術應用在直喷引擎 上，使節流閥的轉動量和引擎的進氣量之間出現非線性對 應的關係，在引擎低負荷、低速轉動之區域，可以進行稀 釋燃燒來降低燃料消耗，但是除節流閥外還需要有由ECU 控制的控制閥，不僅零件數量增加，同時結構也變得複雜。 本發明係鑒於上述問題而提出者，其目的在於提供一種 直喷引擎之進氣裝置，可用簡單的結構使節流閥的轉動量 和引擎的進氣量之間成為非線性的關係，以使在引擎之低 負荷、低速轉動區域，能夠降低燃料消耗。 (解決問題之手段） 為了實現上述目的，申請專利範圍第1項所記載的發明 中，在將節流閥體裝置通過進氣管而連接到汽缸頭的進氣 口上的直喷引擎之進氣裝置中，上述節流閥體裝置包括具 有進氣通路的閥體部；橫切上述進氣通路且能夠轉動地支 撐在上述閥體部上的節流閥軸；以調節上述進氣通路開口 面積的方式固定在上述節流閥軸上的節流閥；及在上述閥 體部的外部固定在上述節流閥轴的一端上，同時，纏繞連 接有節流閥纜線的節流閥鼓；在上述汽缸頭上設有以對應 上述節流閥的轉動量的量將燃料直接喷射到燃燒室内的喷 嘴，其特徵在於：上述進氣口形成具有可以吸入引擎最大 輸出時所必需的空氣量的必要且足夠的開口面積，上述節 7 312/發明說明書(補件)/93-06/93107769 1244526 流閥體裝置的進氣通路形成必要的開口面積，即從全閉位 置向全開位置轉動的板狀節流閥在全閉位置和全開位置之 間的中間位置的狀態下，能夠吸入上述引擎最大輸出時所 必需的空氣量。 根據申請專利範圍第1項所記載發明的結構，在開啟側 最大限度地轉動節流閥之前，節流閥體裝置中進氣通路的 開口面積成為下述尺寸，即必須能使在引擎最大輸出時所 必需的空氣流通，從喷射器喷出的燃料量對應節流閥轉動 量而變化，以使節流閥的轉動量與節流閥體裝置中進氣通 路的開口面積能夠變成非線性的關係，利用通過價格低廉 的節流閥纜線的操作而使節流閥轉動的節流閥體裝置的簡 單結構，以使節流閥的轉動量與進氣量之間的關係成為非 線性，可以降低引擎低負荷、低速轉動區域的燃料消耗。 另外，申請專利範圍第2項所記載的發明，在上述申請專 利範圍第1項記載的發明之上，上述進氣管的内面形狀形成 為可以將上述節流閥體裝置的進氣通路和進氣口光滑地接 連的錐形。根據這種結構，從節流閥體裝置的進氣通路至 進氣口為止的進氣流速光滑地變化，可以更穩定地控制引 擎的輸出。 又，申請專利範圍第3項所記載的發明，在上述申請專 利範圍第1或2項記載的發明之上，喷射器係設置在汽缸體 上其以對應節流閥的轉動量之量將由燃料和空氣組成的混 合氣直接噴射到燃燒室内。根據這種結構，在微小流量下 312/發明說明書(補件)/93-06/93107769 1244526 燃料的霧化良好，結構簡化，可以進一步降低在低負荷、 低轉速下的燃料消耗。 【實施方式】 以下基於附圖所示的本發明一個實施例對本發明實施 形態進行說明。 圖1〜圖9顯示了本發明的一個實施例，圖1是引擎一部 分的縱剖面圖，圖2是顯示拆卸下頂蓋後的狀態的沿圖1中2 —2線看的圖，圖3是沿圖2中3 — 3線所做的剖面圖，圖4是 沿圖3中4 — 4線所做的咅ij面圖，圖5是沿圖2中5 — 5線所做的 剖面圖，圖6是沿圖5中6 — 6線所做的剖面圖，圖7是沿圖5 中7 — 7線所做的剖面圖，圖8是沿圖2中8 — 8線所做的剖面 圖，圖9是顯示節流閥轉動量和進氣量關係的圖。 首先在圖1中，頂置閥型4衝程水冷式即單缸直噴引擎本 體1 1包括曲柄箱1 2、結合在該曲柄箱1 2上的汽缸體1 3、與 曲柄箱1 2相對並結合在汽缸體1 3上的汽缸頭1 4以及與汽缸 體1 3相對並結合在汽缸頭1 4上的頂蓋1 5，並採用使汽缸頭 1 4稍微向上向前姿勢安裝在二輪機車等車輛上。 一併參照圖2〜圖4，可滑動地嵌合在設置在汽缸體1 3上 的汽缸内徑1 6内的活塞1 7通過連桿1 8和曲柄銷（圖中未示） 連接在曲柄軸1 0上（參照圖1 )，曲柄軸1 0可自由轉動地支 撐在曲柄箱1 2上。面臨活塞1 7頂部的燃燒室1 9形成在汽缸 體1 3和汽缸頭1 4之間。 在汽缸頭1 4上設置了分別向燃燒室1 9的頂壁1 9 a開口的 第一和第二進氣閥口 2 0和2 1 ;向上述頂壁1 9 a開口的排氣閥 9 312/發明說明書(補件)/93-06/93107769 1244526 口 22 ;與上述第一和第二進氣閥口 20和 缸頭1 4上部側面開口的進氣口 2 3 ;與上 向汽缸頭1 4下部側面開口的排氣口 2 4。 第一和第二進氣閥口 2 0和2 1向燃燒室 由第一和第二進氣閥2 7、2 8開閉。排氣 的開口端由排氣閥2 9開閉。第一和第二 可滑動地嵌合在固定在汽缸頭1 4上的導 3 2分別設置在分別固定在從導向筒3 0 ... 2 7、2 8上端的護圈3 1 ...和汽缸頭1 4之間 揮的彈力向關閉方向推兩個進氣閥27、 動地嵌合在固定在汽缸頭1 4上的導向筒 置在固定在從導向筒3 3突出的排氣閥2 9 3 4和汽缸頭1 4之間，由閥彈簧3 5發揮的 排氣閥29。 在沿兩個進氣閥口 2 0、2 1並列方向對 氣閥口 2 0的同時偏離燃燒室1 9的中心的 2 9並列位置，將面臨燃燒室1 9的火星塞 内。 由具有與汽缸内徑1 6的軸線即汽缸軸 在上述兩個進氣閥27、28和排氣閥29之 内的喷射器2 5，燃料和空氣的混合氣直 内，在該實施例中，與汽缸軸線C同軸的 缸頭1 4内。 312/發明說明書(補件)/93-06/93107769 2 1共通相連且向汽 述排氣口 2 2相連且 1 9的開口端分另|J 閥口 2 2向燃燒室1 9 進氣閥2 7、2 8分別 向筒3 0内，閥彈簧 突出的兩個進氣閥 。由閥彈簧32...發 28。排氣閥29可滑 3 3内，閥彈簧3 5設 的上端部上的護圈 彈力向關閉方向推 應一端側的第一進 位置，在與排氣閥 2 6安裝在汽缸頭1 4 線C平行的軸線且 間設置在汽缸頭1 4 接喷射到燃燒室1 9 噴射器2 5設置在汽 10 1244526 即噴射器2 5、一對進氣閥口 2 0和2 1、對應第二進氣閥口 2 1的排氣閥口 2 2、火星塞2 6採用下述方式設置在汽缸頭1 4 内，即兩個進氣閥口 2 0和2 1、排氣閥口 2 2和火星塞2 6圍繞 噴射器25 。 再一併參照圖5〜圖7，第一和第二進氣閥2 7、2 8和排氣 閥2 9由動閥裝置3 8開閉驅動。動閥裝置3 8包括具有進氣側 和排氣側凸輪3 9和4 0且轉動的凸輪軸4 1 ;從動於上述進氣 側凸輪3 9且擺動的進氣側第一搖臂4 2 ;從動於上述排氣側 凸輪4 0且擺動的排氣側第一搖臂4 3 ;在一端具有與第一和 第二進氣閥2 7和2 8接觸的一對推壓腕部4 4 a和4 4 b的進氣側 第二搖臂4 4 ;在一端具有與排氣閥2 9接觸的推壓腕部4 5 a 的排氣側第二搖臂4 5 ;將進氣侧第一搖臂4 2的擺動運動傳 遞到進氣側第二搖臂4 4而設置在進氣側第一和第二搖臂4 2 和4 4之間的進氣側驅動桿4 6 ;及將排氣側第一搖臂4 3的擺 動運動傳遞到排氣側第二搖臂4 5而設置在排氣側第一和第 二搖臂4 3和4 5之間的排氣側驅動桿4 7。 第一動閥室4 8形成在汽缸頭1 4和頂蓋1 5之間，用於收容 和配置上述動閥裝置3 8中進氣側和排氣側第二搖臂4 4和 4 5、擺動樞支上述進氣側和排氣側第二搖臂4 4和4 5的進氣 側和排氣側第二搖臂軸5 8和5 9、以及進氣側和排氣側驅動 桿4 6和4 7上部，用於收容動閥裝置3 8剩餘部分的第二動閥 室4 9在相對於汽缸軸線C在與上述火星塞2 6設置側相反側 上與汽缸軸線C平行延伸地形成在曲柄箱1 2、汽缸體1 3和汽 缸頭1 4内。 11 312/發明說明書(補件)/93-06/93107769 1244526 為了對上述動閥裝置3 8收容在第一動閥室4 8内的部分 進行潤滑，在頂蓋1 5内設置油噴出孔3 6，對收容在第一動 閥室4 8内的部分進行潤滑的油經過第二動閥室4 9返回形成 在曲柄箱1 2下部的油盤1 2 a内（參照圖1 )。 進氣側和排氣側第一搖臂4 2、4 3分別具有從汽缸頭1 4側 與進氣側和排氣側凸輪3 9和4 0滾動接觸的親5 4、5 5，被吸 氣側及排氣側第一搖臂5 6、5 7可搖動地支持，該吸氣側及 進氣側第一搖臂5 6、5 7設置在具有與上述凸輪軸4 1平行的 軸線的汽缸體1 3及蓋5 0之間。位於與上述親5 4、5 5相反側 上的杯形推壓部4 2 a、4 3 a分別採用在汽缸頭1 4側打開的方 式一體設置在進氣側和排氣側第一搖臂4 2、4 3上。 動閥裝置3 8中的凸輪軸4 1採用收容在第二動閥室4 9内 的方式設置在汽缸體1 3上，具有與曲柄軸1 0平行軸線的凸 輪軸4 1的兩端部通過滾珠軸承5 1、5 1可自由轉動地支撐在 汽缸體1 3上和以形成在第二動閥室4 9的外側面上的方式與 汽缸體1 3相連的蓋5 0上。 而且，用於向進氣側和排氣側凸輪3 9、4 0、進氣側第一 搖臂4 2和排氣側第一搖臂4 3的滑動接觸部提供潤滑油的供 油路3 7設置在凸輪軸4 1上。 為了將傳遞來自曲柄軸1 0的動力減速為一半，第一從動 鏈輪5 2、第一主動鏈輪6 0 (參照圖1 )和環形凸輪鏈5 3收容 在第二動閥室4 9内。第一從動鏈輪5 2不能相對轉動地結合 在凸輪軸4 1上，第一主動鏈輪6 0不能相對轉動地結合在曲 12 312/發明說明書(補件)/93-06/93107769 1244526 柄軸1 0上，凸輪鏈5 3捲掛在第一主動鏈輪6 0和第一從動鏈 輪5 2上。 進氣側和排氣側驅動桿4 6、4 7橫跨第一動閥室4 8向第二 動閥室4 9的一部分之間地延伸，與汽缸頭1 4側的相互間隔 變狹窄地設置驅動桿4 6、4 7。一端側球狀端部第一搖臂4 2、 4 3的推壓部4 2 a、4 3 a上，進氣側和排氣側驅動桿4 6、4 7的 另一端側球狀端部可以擺頭地嵌合在進氣側和排氣側的第 二搖臂44、45的受壓部44c、45b上。 在第一動閥室4 8内，具有與凸輪軸4 1平行的軸線的進氣 側和排氣側第二搖臂軸5 8和5 9設置在上述噴射器2 5兩側地 支撐和固定在汽缸體1 4上，在一端側具有與第一和第二進 氣閥2 8、2 9的上端接觸且與兩進氣閥2 8、2 9連動和連接且 分叉成兩股的一對推壓杯形部4 2 a、4 2 b的進氣側第二搖臂 4 4可自由擺動地支撐在進氣側第二搖臂軸5 8上。在一端側 具有與排氣闊2 9的上端接觸且與該排氣閥2 9連動和連接的 推壓杯形部4 5 a的排氣侧第二搖臂4 5可自由擺動地支撐在 排氣側第二搖臂軸5 9上。 而且，在進氣側第二搖臂軸5 8關閉的兩推壓杯形部 4 4 a、4 4 b的相反側上，在汽缸體1 3側敞開白勺杯形受壓部4 4 c 一體地設置在進氣側第二搖臂4 4的另一個端部上，在排氣 側第二搖臂軸5 9關閉的推壓杯形部4 5 a的相反側上，在汽缸 體1 3側敞開的碗狀的受壓部4 5 b —體地設置在排氣側第二 搖臂45上。 13 312/發明說明書(補件)/93-06/93107769 1244526 上述進氣側和排氣側第二搖臂4 4、4 5的另一個端部即受 壓部4 4 c、4 5 b設置在進氣側和排氣側第二搖臂軸5 8、5 9的 一端部之間，進氣側和排氣側驅動桿4 6、4 7在進氣側和排 氣側第二搖臂軸5 8、5 9的一端部之間與進氣側和排氣側第 二搖臂4 4、4 5的另一個端部連動連接起來。 在這種動閥裝置3 8内，對應從曲柄軸以1 / 2的減速比傳 遞轉動動力的凸輪軸4 1的轉動，由進氣側第一搖臂4 2和從 進氣側凸輪3 9的擺動，進氣側驅動桿4 6向其轴向作動，對 應於此，通過進氣側第二搖臂4 4擺動，第一和第二進氣閥 2 7、2 8被開閉驅動，由排氣側第一搖臂4 3跟從排氣側凸輪 4 0的擺動，排氣側驅動桿4 7向其軸向作動，對應於此，通 過排氣側第二搖臂4 5擺動，排氣閥2 9被開閉驅動。 因而，使活塞6 6沿與汽缸軸線C平行方向往復驅動的往 復式空氣泵6 1的壓縮空氣供應到喷射器2 5内。在對應設置 在汽缸頭1 4上的排氣口 2 4側，上述空氣泵6 1設置在汽缸體 1 3的下部。而且，在與汽缸軸線C垂直的平面内與第二動閥 室4 9大致成L字形連接配置在汽缸内腔1 6下方的作動室6 2 形成在汽缸體13内，上述空氣泵61在較第二動閥室49的下 方配設於第二動閥室及作動室6 2的建設部上。 一併參照圖8，空氣泵6 1的泵殼體6 3具有與汽缸軸線C平 行的軸線，同時是在汽缸頭1 4側敞開的有底的筒狀物，並 與汽缸體1 3 —體形成，氣密地關閉該泵殼體6 3的上述汽缸 頭1 4側開口部的蓋構件6 4連接到汽缸體1 3上。 14 312/發明說明書(補件)/93-06/93107769 1244526 活塞6 6可滑動地嵌合在泵殼體6 3内，活塞6 6的一端和蓋 構件6 4之間形成設置在汽缸頭1 4側的泵室6 5以使對應體積 收縮而生成壓縮空氣，設置在油盤1 2 a側的大氣壓室8 8形成 在活塞6 6的另一端和泵殼體6 3的閉塞端之間。 一方面，具有與凸輪軸4 1的軸線平行且通過上述活塞6 6 軸線的軸線的圓筒狀軸承構件6 9設置在作動室6 2内，該軸 承構件6 9通過螺栓7 1 ...分別連接到突設在汽缸體1 3上的多 個例如4個連接凸台7 0 ...上。而且，形成作動室6 2外部側面 的蓋7 2連接到汽缸體1 3上，在打開蓋7 2時，可以進行上述 螺栓7 1 ...的擰緊和鬆開作業。 泵驅動軸7 3同軸地插入上述軸承構件6 9，將滾柱軸承7 4 安裝在軸承構件6 9的一端和泵驅動軸7 3之間，將球軸承7 5 安裝在轴承構件6 9的另一端和果驅動轴7 3之間。即果驅動 軸7 3自由轉動地支撐在與汽缸體1 3相連的軸承構件6 9上。 利用從軸承構件6 9 —端部突出的部分内，來自凸輪軸4 1 的動力通過動力傳遞機構8 9傳遞到栗驅動軸7 3，動力傳遞 機構8 9由固定在泵驅動軸7 3上的第二從動鏈輪7 8、與結合 在凸輪軸41上的第一從動鏈輪52為一體的第二驅動鏈輪 7 9、纏繞在第二動和驅從動鏈輪7 8、7 9上的環形鏈條8 0組 成。 泵驅動軸7 3通過止轉棒輥式曲柄8 4與空氣果6 1的活塞 6 6相連，止轉棒軛式曲柄8 4就是使從泵驅動軸7 3 —端的偏 心位置突出的偏心軸7 3 a的前端連接到可滑動地嵌合在活 塞6 6上的滑動擋塊6 8上的構件。而且，泵驅動軸7 3利用從 15 312/發明說明書(補件)/93-06/93107769 1244526 凸輪軸4 1傳遞來的動力進行轉動，對應於此，偏心軸7 3 a 圍繞泵驅動軸7 3的軸線轉動。空氣泵6 1的活塞6 6可以增減 泵室6 5的體積地在泵殼體6 3内沿軸向往復驅動。 滑動孔6 7設置在活塞6 6上，滑動孔6 7的軸線設置在沿活 塞6 6的直徑線並在與凸輪軸4 1的軸線垂直的平面内，上述 滑動擋塊6 8可滑動地嵌合在滑動孔6 7内，此外，偏心軸7 3 a 一體地突設在泵驅動軸7 3的一端上。 而且，使泵驅動軸7 3的一端插入的開口部7 6設置在泵殼 體6 3内，活塞6 6上對應果驅動軸7 3的轉動允許偏心軸7 3 a 沿滑動孔6 7的軸線方向移動地插入該偏心軸7 3 a的插入孔 7 7，係設置為通過滑動孔6 7的縱向中央部。 在球軸承7 5和滾柱軸承7 4之間的中央部，通孔8 1、8 2分 別設置在軸承構件6 9的兩側部，在對應一個通孔8 1的位 置，用於將落到作動室6 2内的油的一部分引導到軸承構件 6 9和泵驅動軸7 3之間的油導體8 3 —體地設置在軸承構件6 9 上。即以引導積存在第一動閥室4 8内下部的油的一部分的 方式將設置在汽缸頭1 4内的通路1 3 4設置在汽缸頭1 4上，通 向上述通路1 3 4且向作動室6 2開口的通路1 3 5設置在汽缸體 1 3上，將從通路1 3 5落下的油通過通孔8 1引導的油導管8 3 一體地設置在軸承構件6 9上。而且，引導到軸承構件6 9和 泵驅動軸7 3之間的油的一部分係用於潤滑球軸承7 5和滾柱 軸承7 4，剩餘部分從通孔8 2落到作動室6 2内的下部，積存 在作動室6 2内下部的油從與作動室6 2内下部相通且設置在 汽缸體1 3上的返回通路1 3 6返回油盤1 2 a。 16 312/發明說明書(補件)/93-06/93107769 1244526 相對於上述軸承構件6 9在空氣泵6 1的相反側，具有與泵 驅動軸7 3同軸的轉動軸線的水泵9 0安裝在汽缸體1 3上。空 氣泵6 1和水泵9 0相對於包含汽缸軸線C且與泵驅動軸7 3垂 直的平面P L平面對稱地設置。 水泵9 0的泵殼體9 1由殼體主體9 2和封閉殼體主體9 2的 開放端的泵蓋9 3構成，碟狀部9 2 b —體地連設在於泵驅動軸 7 3側封閉的有底圓筒部9 2 a的開放端上而形成上述殼體主 體9 2，泵蓋9 3將殼體主體9 2的開放端外周部夾持在其與汽 缸體1 3之間，採用這種方式，與汽缸體1 3相連。 與泵驅動軸7 3同軸的泵軸9 4其兩端部被自由轉動地支 撐在有底圓筒部9 2 a的封閉端的中央部和泵蓋9 3的中央部 上，内磁鐵96固定在與上述泵軸94 一體轉動且插入有底圓 筒部9 2 a内的轉子9 5上。另一方面，具有同軸地圍繞上述殼 體主體9 2的有底圓筒部9 2 a的圓筒部9 7 a的轉動構件9 7固定 在從軸承構件6 9的另一端突出的泵驅動軸7 3的另一端上， 在上述圓筒部9 7 a的内面上固定有外磁鐵9 8。因而，對應於 轉動構件9 7與泵驅動軸7 3同時轉動，轉子9 5與泵軸9 4 一起 轉動。 因而，殼體主體9 2和泵蓋9 3之間形成渦室9 9，收容在渦 室9 9内的渦輪1 0 0設置在轉子9 5上。 在渦室9 7中央部開口的多個吸入口 1 0 1 ...設置在泵蓋9 3 上，從上述吸入口 1 0 1吸入上述渦室9 9内的冷卻水係由渦輪 1 0 0的轉動加壓。而從水泵9 0排出的冷卻水係供應到設置在 汽缸體1 3上的缸側水套1 0 2以及通向該塊側水套1 0 2設置在 17 312/發明說明書(補件)/93-06/93107769 1244526 汽缸頭1 4上的頂側水套1 Ο 3，相應於冷卻水的溫度，由恒溫 器1 0 4切換將從頂側水套1 0 3排出的冷卻水引導到圖中未示 的散熱器等處的狀態、及迂迴經過散熱器等返回吸入口 1 〇 1 的狀態，恒溫器1 0 4的恒溫器殼體1 0 5與上述水泵9 0的泵蓋 9 3 —體形成。 空氣泵6 1中，將流經第二動閥室4 9的一部分油作為潤滑 用導入泵殼體6 3内的油導入孔8 5通向第二動閥室4 9地設置 在泵殼體6 3的上部側壁上。根據第二動閥室4 9的轉動，凸 輪軸4 1的進氣側凸輪3 9和排氣側凸輪4 0係使流經第二動閥 室4 8的一 分油上揚，同時利用離心力的作用，使上述油 分離和飛散。此外，雖然從油供給路3 7供給的一部分油因 離心力作用而分離、飛散，採用將分離後的油飛沫引導到 油導入孔8 5内的方式設定凸輪軸4 1和油導入孔8 5的相對位 置。 對應第二動閥室中動閥裝置3 8的部分的寬度，形成的比 其他部分大，大致半圓形地圍繞對應凸輪軸4 1中進氣側凸 輪3 9和排氣側凸輪4 0的部分的突壁8 6與第二動閥室内油流 通方向137反向地一體設置在汽缸體13上，上述空氣泵61 的油返回孔8 5沿油流通方向1 3 7，設置在上述突壁8 6的正上 游位置。即突壁8 6能將在第二動閥室内流通過來的油引導 到油導入孔8 5内。 但是油返回孔8 5從安裝在活塞6 6外周上且與泵殼體6 3 内周滑動接觸的活塞環1 3 8在大氣壓室8 8側向泵殼體6 3的 内周開口地設置在泵殼體6 3上，與活塞6 6的軸向移動無關 18 312/發明說明書(補件)/93-06/93107769 1244526 的油返回孔8 5總是與設置在活塞6 6上的滑動孔6 7的一端連 通。而且，連接活塞6 6的大氣壓室8 8側的端部和連結滑動 孔6 7兩端的一對槽1 3 9 ...設置在活塞6 6的外周上，從油返回 孔8 5引導到泵殼體6 3内油的一部分用於在活塞6 6和泵殼體 6 3之間的潤滑，剩餘部分經上述槽1 3 9 ...在大氣壓室8 8側流 動。但是，上述槽1 3 9 ...放出滑動孔6 7内的油，也實現有效 地防止在止轉棒輛式曲柄8 4内產生滑動擋塊6 8的抽吸作 用。 在大氣壓室8 8側流動的油從開口部7 6流到作動室6 2 側，而且從返回通路1 3 6流到油盤1 2 a側。 特別注意圖7和8，噴射器2 5是第一喷射閥1 0 7和第二噴 射閥1 0 8同軸連接而構成，第一喷射閥1 0 7用於喷射燃料且 安裝在頂蓋1 5上；第二喷射閥1 0 8，將和壓縮空氣一起的燃 料直接喷射到燃燒室1 9内且安裝在汽缸頭1 4上，第二喷射 閥1 0 8具有突入燃燒室1 9内的喷嘴1 0 8 a。 用於氣密地嵌合上述喷嘴1 0 8 a的嵌合孔1 0 9、比嵌合孔 1 0 9的直徑大並與嵌合孔1 ϋ g同軸相連白勺插入筒1 1 0與汽缸 軸線C同軸地設置在汽缸頭1 4上，第二喷射閥1 0 8從頂蓋1 5 側插入上述插入筒1 1 0内，直至氣密地將上述喷嘴1 0 8 a嵌合 在上述嵌合孔1 0 9内同時通過波形彈簧墊圈1 2 3與形成在嵌 合孔1 0 9和插入筒1 1 0之間的環形臺階1 1 1接觸為止。 第二喷射閥1 〇 8在後部具有的導線連接部1 0 8 b配置在設 置在插入筒1 1 0後端上的切口 1 1 0 a上，在插入筒1 1 0外，從 19 3 12/發明說明書(補件)/93-06/93 ] 07769 1244526 導線連接部1 Ο 8 b引出的一對導線1 1 2 ...夾持在汽缸頭1 4和 頂蓋1 5的結合面之間並貫通汽缸體1 1 3引出到外部。 一方面，在嵌合、保持第一噴射閥1 0 7的同時，具有將 上述第二噴射閥1 0 8夾持在汽缸頭1 4之間的發揮定位夾持 功能的定位部的圓筒狀噴射器殼體Π 4 —體形成在頂蓋1 5 内，頂蓋1 5和汽缸體1 4結合時，喷射器殼體11 4的前端與第 二喷射閥1 0 8的後端接觸。此外，與喷射器殼體1 1 4 一起夾 持第一喷射閥1 0 7的後端部的夾持板1 1 5連接到喷射器殼體 1 1 4的後端。 第一喷射閥1 0 7包括在其後部配線用端子1 0 7 a，利用噴 射器殼體1 1 4和夾持板1 1 5夾持第一噴射閥1 0 7的後端，在第 一噴射閥1 0 7安裝在頂蓋1 5上時，上述配線用端子1 0 7 a面臨 頂蓋1 5外部地設置。 通向第一噴射閥1 0 7内的環形燃燒室1 1 6形成在喷射器 殼體1 1 4和第一喷射閥1 0 7之間，從兩側夾持上述燃燒室1 1 6 的一對密封構件1 1 7、1 1 8安裝在喷射器殼體11 4和第一噴射 閥1 0 7之間。 但是，通向上述燃燒室11 6的燃料供給通路1 1 9直接設置 在頂蓋1 5内，從圖中未示的燃料供給源引導燃料的軟管1 2 0 通過接頭1 2 1與燃料供給通路11 9相連。 此外，在第一噴射閥1 0 7的前端部和第二喷射閥1 0 8的後 端部之間，在噴射器殼體Π 4内，形成通向第二噴射閥1 0 8 的環形空氣室1 2 2，來自上述空氣泵6 1的壓縮空氣供應到該 空氣室1 2 2内。 20 312/發明說明書(補件)/93-06/93107769 1244526 與用於引導來自圖中未示空氣淨化器的空氣的軟管相 連的吸入管1 2 4 (參照圖2 )設置在空氣泵6 1中的蓋構件6 4 上，吸入管1 2 4通過内置在蓋構件6 4内的簧片閥（圖中未示） 與泵室6 5相連。 對應泵室6 5的壓力增加而打開閥的提升閥1 2 5内置在上 述蓋構件6 4内，從空氣泵6 1排出的壓縮空氣通過上述提升 閥1 2 5和壓縮空氣供給路1 2 6供應到空氣室1 2 2内。 壓縮空氣供給路1 2 6由管件1 2 7、與管件1 2 7相通地直接 設置在汽缸頭1 4上的通路1 2 8、與上述通路1 2 8相通同時通 向空氣室1 2 2地直接設置在頂蓋1 5上的通路1 2 9構成，上述 管件1 2 7的一端連接到與上述提升閥1 2 5相連的蓋構件6 4 上，同時另一端連接到汽缸頭1 4上。 此外，跨過汽缸頭1 4和頂蓋1 5的結合面的圓筒狀定位銷 1 3 0的兩端部插入汽缸頭1 4和頂蓋1 5内，構成壓縮空氣通路 1 2 6的一部分且直接設置在汽缸頭1 4和頂蓋1 5上的通路1 2 8 和1 2 9通過上述定位鎖1 3 0相連。但是，圍繞定位銷1 3 0的0 型環1 3 3夾持在汽缸頭1 4和頂蓋1 5的結合面之間。 此外，噴孔1 3 1形成在定位銷1 3 0内，從喷孔1 3 1連接到 上游側的上述通路1 2 8的安全閥1 3 2 (參照圖2 )安裝在汽缸 頭1 4上。 注意圖1和3，通過進氣管1 4 1，節流閥體裝置1 4 0連接到 汽缸頭1 4的進氣口 2 3上。上述節流閥體裝置1 4 0包括具有進 氣通路1 4 2的閥體部1 4 3、橫切上述進氣通路1 4 2並可轉動地 支撐在閥體部1 4 3上的節流閥軸1 4 4、從全閉位置到全開位 21 312/發明說明書(補件)/93-06/93107769 1244526 置轉動以便調節上述進氣通路1 4 2的開口面積並固定在節 流閥軸1 4 4上的板狀蝶形節流閥1 4 5、在上述閥體部1 4 3的外 部並固定在節流閥軸1 4 4的一端上的節流閥鼓1 4 6。由節流 閥握把等操作構件操作的節流閥纜線1 4 7纏繞和連接在節 流閥鼓1 4 6上。 閥體部1 4 3是通過連接皮帶1 4 9連接到進氣管1 4 1上的構 件以使進氣通路1 4 2通向進氣管1 4 1内，包含檢測上述節流 閥軸1 4 4和蝶形節流閥1 4 5的轉動量即節流閥纜線1 4 7操作 量的感應器的控制單元1 4 8安裝在閥體部1 4 3上，由上述噴 射器2 5噴出的燃料和空氣的混合氣噴射量由控制單元1 4 8 對應上述節流閥1 4 5的轉動量進行控制。 汽缸頭1 4的進氣口 2 3形成的具有在引擎最大輸出時吸 入必要空氣量所需的充分的開口面積。對應與此，節流閥 體裝置1 4 0的進氣通路1 4 2形成的具有這樣的開口面積，即 能夠從全閉位置轉動至全開位置為止的節流閥1 4 5在上述 全閉位置和全開位置之間的中間位置狀態下，能夠在上述 引擎最大輸出時吸入所必需的空氣量。 即如圖9所示，當節流閥1 4 5從全閉位置向全開位置轉動 操作時，流過進氣通路1 4 2的進氣量變成根據包含開口面積 設定的小於進氣通路1 4 2的進氣口 2 3的進氣系統全體的流 通阻力所確定的最大進氣量，一旦到達最大進氣量，即使 在全開位置側操作節流閥1 4 5，進氣量也不增力口。 進氣管1 4 1的内面形狀形成為將節流閥體裝置1 4 0的進 氣通路1 4 2和進氣口 1 2 3光滑地結合的錐形。 22 312/發明說明書(補件)/93-06/93107769 1244526 下文對該實施例的作用進行說明，具有與汽缸軸線C平 行的軸線的噴射器2 5設置在汽缸體1 4上，可以將由燃料和 空氣組成的混合氣直接喷射到燃燒室1 9内，可以將上述混 合氣集中在燃燒室1 9的中心附近，由於可以稀釋燃燒，因 而能降低燃燒消耗。而且，由於喷射器2 5是由壓縮空氣將 燃料微粒化並直接喷射到燃燒室内的構件，微小流量下燃 料的霧化良好，結構簡化，提高燃燒性，可以進一步降低 在低負荷、低轉速下的燃料消耗。 雖然從噴射器2 5喷射的混合氣量對應通過進氣管1 4 1連 接到汽缸頭1 4上進氣口 2 3上的節流閥體裝置1 4 0所具有的 節流閥1 4 5的轉動量而被控制，如圖9所示，通過節流閥體 裝置1 4 0和進氣管1 4 1引導到進氣口 2 3内的進氣量與節流閥 1 4 5的轉動量存在非線性關係。 即，由於汽缸頭1 4上的進氣口 2 3形成的具有可以吸入在 引擎最大輸出時所必需的空氣量的充分開口面積，節流閥 體裝置1 4 0的進氣通路1 4 2形成的具有這樣的開口面積，即 節流閥1 4 5在全閉位置和全開位置之間的中間位置狀態 下，能夠在上述引擎最大輸出時吸入所必需的空氣量，在 開啟側最大限度地轉動節流閥1 4 5之前，在節流閥體裝置 1 4 0中進氣通路1 4 2的開口面積必須能使在引擎最大輸出時 所必需的空氣流通，節流閥1 4 5的轉動量與節流閥體裝置 1 4 0中進氣通路1 4 2的開口面積可能也變成非線性。而且， 利用通過價格低廉的節流閥纜線1 4 7的操作而使節流閥1 4 5 轉動的節流閥體裝置1 4 0的簡單結構，節流閥1 4 5的轉動量 23 312/發明說明書(補件)/93-06/93107769 1244526 與進氣量之間的關係為非線性，可以降低引擎之低負荷， 減少低轉動域的燃料消耗。 由於進氣管1 4 1的内面形狀成為可以將節流閥體裝置 1 4 0的進氣通路1 4 2和進氣口 2 3光滑地接連的錐形，從節流 閥體裝置1 4 0的進氣通路1 4 2至進氣口 2 3為止的進氣流速光 滑地變化，可以更穩定地控制引擎的輸出。 上文對本發明的實施例進行了說明，但是本發明並不侷 限於上述實施例，只要為不脫離申請專利範圍所記載的範 圍，本發明即可以進行各種設計變更。 (發明效果） 根據申請專利範圍第1項所記載的發明，利用通過價格 低廉的節流閥纜線的操作而使節流閥轉動的節流閥體裝置 的簡單結構，以使節流閥的轉動量與進氣量之間的關係成 為非線性，可以降低引擎低負荷、低速轉動區域的燃料消 耗。 根據申請專利範圍第2項所記載的發明，從節流閥體裝 置的進氣通路至進氣口為止的進氣流速光滑地變化，可以 更穩定地控制引擎的輸出。 根據申請專利範圍第3項所記載的發明，在微小流量下 燃料的霧化良好，結構簡化，可以進一步降低在低負荷、 低轉速下的燃料消耗。 【圖式簡單說明】 圖1為引擎之一部分的縱剖面圖。 24 312/發明說明書(補件)/93-06/93 ] 07769 1244526 圖2為顯示拆卸下頂蓋後的狀態的沿圖1中2 — 2線看的 圖。 圖3為沿圖2中3 — 3線的咅面圖。 圖4為沿圖3中4 — 4線的剖面圖。 圖5為沿圖2中5 — 5線的咅面圖。 圖6為沿圖5中6 — 6線的剖面圖。 圖7為沿圖5中7 — 7線的咅面圖。 圖8為沿圖2中8 — 8線的咅面圖。 圖9為顯示節流閥轉動量和進氣量的關係圖。 (元件符號說明） 10 曲柄軸 11 直噴引擎本體 12 曲柄箱 1 2a 油盤 13 汽缸體 14 汽缸頭 15 頂蓋 16 汽缸内腔 17 活塞 18 連桿 19 燃燒室 19a 頂壁 2 0 第一進氣閥口 2 1 第二進氣閥口 251244526 发明 Description of the invention: [Technical field to which the invention belongs] The present invention relates to an air intake device of a direct injection engine that connects a throttle body device to an air inlet on a cylinder head through an intake pipe. The device includes a valve body portion having an intake passage; a throttle shaft that is rotatably supported on the valve body portion across the intake passage; and is fixed to the throttle valve so as to adjust an opening area of the intake passage A throttle valve on the shaft; and an outer end of the valve body portion is fixed on one end of the throttle valve shaft, and a throttle drum with a throttle cable is wound around the cylinder head, and the cylinder head is provided with a corresponding The amount of fuel of the rotation amount of the throttle valve is directly injected into the injector in the combustion chamber. [Prior art] Until now, the direct injection engine installed on vehicles has directly injected fuel from the injector provided on the cylinder head corresponding to the amount of fuel used by the accelerator pedal or throttle grip of the vehicle operator. Into the combustion chamber, but in the low-load, low-speed rotation area of the engine, when the engine output control is performed to reduce fuel consumption through dilution combustion, the amount of operation of the accelerator pedal or throttle grip, that is, the amount of rotation of the throttle valve and Non-linear correspondence between engine air intake. In order to make a non-linear correspondence between the amount of rotation of the throttle valve and the amount of intake air of the engine, the engine intake device of a non-direct injection engine disclosed in Japanese Patent Document 1 is different from the throttle valve in the intake system In addition, other control valves are provided, and the opening degree of the control valve is controlled by the ECU. (Patent Document 1) 6 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 Japanese Patent Laid-Open No. 1 1 — 1 0 7 7 8 8 [Summary of the Invention] (Problems to be Solved by the Invention) Adopted Applying the technology disclosed in the above Patent Document 1 to a direct injection engine, a non-linear correspondence relationship exists between the rotation amount of the throttle valve and the intake air amount of the engine, and it can be diluted in the low-load and low-speed rotation area of the engine Combustion reduces fuel consumption, but in addition to the throttle valve, a control valve controlled by the ECU is required. Not only the number of parts increases, but the structure becomes complicated. The present invention has been made in view of the above-mentioned problems, and an object thereof is to provide an air intake device for a direct injection engine, which can use a simple structure to make a non-linear relationship between the amount of rotation of the throttle valve and the amount of air intake of the engine, so that The low-load and low-speed rotation of the engine can reduce fuel consumption. (Means for Solving the Problems) In order to achieve the above-mentioned object, in the invention described in claim 1 of the scope of patent application, the intake of a direct injection engine in which a throttle body device is connected to an intake port of a cylinder head through an intake pipe In the device, the throttle body device includes a valve body portion having an intake passage; a throttle shaft that is rotatably supported on the valve body portion across the intake passage; and adjusts an opening area of the intake passage A throttle valve fixed on the throttle valve shaft in a manner; and fixed on one end of the throttle valve shaft outside the valve body part, and at the same time, a throttle drum connected with a throttle cable is wound; The cylinder head is provided with a nozzle that directly injects fuel into the combustion chamber by an amount corresponding to the amount of rotation of the throttle valve, and the inlet is formed to have a necessary amount of air that can be sucked into the engine at the maximum output. And sufficient opening area, the above section 7 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 The intake passage of the valve body device forms the necessary opening area, that is, from the fully closed position to the fully open position The amount of air is set when the throttle plate is rotated in a state in an intermediate position between the fully closed position and a fully open position, the suction can be above the maximum engine output required. According to the structure of the invention described in the first patent application scope, before the throttle is turned to the maximum on the open side, the opening area of the intake passage in the throttle body device has the following dimensions, which must be able to maximize the output of the engine The amount of air circulation necessary at the time varies according to the amount of throttle valve rotation, so that the amount of rotation of the throttle valve and the opening area of the intake passage in the throttle body device can become a non-linear relationship. The simple structure of the throttle body device that rotates the throttle valve through the operation of the inexpensive throttle cable makes the relationship between the amount of rotation of the throttle valve and the intake air volume non-linear, which can reduce the engine Fuel consumption in low-load, low-speed turning areas. In addition, in the invention described in claim 2 of the patent application scope, on the invention described in claim 1 of the aforementioned patent application scope, the inner surface shape of the intake pipe is formed so that the intake passages and intake ports of the throttle body device can be formed. The ports are tapered smoothly in succession. According to this structure, the flow velocity of the intake air from the intake passage of the throttle body device to the intake port smoothly changes, and the output of the engine can be controlled more stably. In addition, in the invention described in claim 3, above the inventions described in claims 1 or 2, the injector is provided on the cylinder block, and the fuel is supplied by fuel in an amount corresponding to the amount of rotation of the throttle valve. The air-fuel mixture is injected directly into the combustion chamber. According to this structure, at a minute flow rate, the fuel is well atomized and the structure is simplified, which can further reduce the fuel consumption under low load and low speed at a minute flow rate (Supplement) / 93-06 / 93107769 1244526. [Embodiment] An embodiment of the present invention will be described below based on an embodiment of the present invention shown in the drawings. 1 to 9 show an embodiment of the present invention, FIG. 1 is a longitudinal sectional view of a part of the engine, and FIG. 2 is a view taken along line 2-2 in FIG. 1 showing a state after the top cover is removed, FIG. 3 2 is a cross-sectional view taken along line 3-3 in FIG. 2, FIG. 4 is a 咅 ij plane view taken along line 4-4 in FIG. 3, and FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 2. Fig. 6 is a sectional view taken along line 6-6 in Fig. 5, Fig. 7 is a sectional view taken along line 7-7 in Fig. 5, and Fig. 8 is a sectional view taken along line 8-8 in Fig. 2. FIG. 9 is a diagram showing the relationship between the amount of throttle rotation and the amount of intake air. First, in FIG. 1, the overhead valve type 4-stroke water-cooled single-cylinder direct-injection engine body 1 1 includes a crank case 1 2, a cylinder block 1 3 coupled to the crank case 1 2, and opposed to the crank case 1 2 The cylinder head 14 coupled to the cylinder block 13 and the top cover 15 opposed to the cylinder block 13 and coupled to the cylinder head 14 are mounted on the two-wheeled locomotive, etc., with the cylinder head 14 positioned slightly upward and forward. On the vehicle. Referring to FIGS. 2 to 4 together, a piston 1 7 slidably fitted in a cylinder inner diameter 16 provided on a cylinder block 13 is connected to a crank through a connecting rod 18 and a crank pin (not shown) On the shaft 10 (refer to FIG. 1), the crank shaft 10 is rotatably supported on the crank case 12. A combustion chamber 19 facing the top of the piston 17 is formed between the cylinder block 13 and the cylinder head 14. The cylinder head 14 is provided with first and second intake valve ports 20 and 21 respectively opening to the top wall 19 a of the combustion chamber 19 and an exhaust valve 9 opening to the above top wall 19 a. 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 Port 22; with the first and second intake valve ports 20 and the cylinder head 1 4 above, the intake port opening at the upper side 2 3; with the upward-facing cylinder head 1 4 Exhaust port 2 4 opening at the lower side. The first and second intake valve ports 20 and 21 are opened and closed toward the combustion chamber by the first and second intake valves 27 and 28. The open end of the exhaust is opened and closed by an exhaust valve 29. The first and second guides 3 2 slidably fitted to the cylinder head 14 are respectively provided on the slave guide cylinders 30 respectively. . . 2 7、2 8 Upper retaining ring 3 1. . . The elastic force swinging between the cylinder head 1 and 4 pushes the two intake valves 27 in the closing direction, and a guide cylinder fixedly fitted to the cylinder head 1 4 is placed on an exhaust valve fixedly protruding from the guide cylinder 3 3 An exhaust valve 29 is exerted by the valve spring 35 between 2 9 3 4 and the cylinder head 14. When the two intake valve ports 20 and 21 are aligned side by side and the valve port 20 is offset from the center of the combustion chamber 19 at a parallel position of 29, it will face the inside of the Mars plug of the combustion chamber 19. From the injector 25 having the axis with the cylinder inner diameter 16 that is the cylinder shaft within the above-mentioned two intake valves 27, 28 and exhaust valve 29, the fuel and air mixture is straight in, in this embodiment , Inside the cylinder head 14 coaxial with the cylinder axis C. 312 / Invention Manual (Supplement) / 93-06 / 93107769 2 1 Commonly connected and connected to the steam exhaust port 2 2 and 1 9 Open end separately | J Valve port 2 2 Combustion chamber 1 9 Intake valve 2 7 and 2 8 are two intake valves that project into the cylinder 30 with a valve spring protruding. By valve spring 32. . . Hair 28. The exhaust valve 29 can slide inside 3 3, and the retainer on the upper end of the valve spring 3 5 pushes the first advance position of the one end side in the closing direction. The exhaust valve 2 6 is installed on the cylinder head 1 4 line. C Parallel axis is arranged in the cylinder head 1 4 and then injected into the combustion chamber 1 9 Injector 2 5 is arranged in the steam 10 1244526 That is, the injector 2 5, a pair of intake valve ports 2 0 and 21 1, corresponding to the second inlet Exhaust valve port 2 of gas port 2 1 2. Mars plug 2 6 is arranged in the cylinder head 1 4 in the following manner, that is, two intake valve ports 2 0 and 2 1. Exhaust valve port 2 2 and Mars The plug 2 6 surrounds the ejector 25. 5 to 7 together, the first and second intake valves 27, 28, and the exhaust valve 29 are opened and closed by a moving valve device 38. The moving valve device 38 includes a camshaft 41 which has an intake-side and exhaust-side cams 39 and 40 and is rotated; and an intake-side first rocker arm 4 2 which is driven by the aforementioned intake-side cam 39 and swings ; The exhaust-side first rocker arm 4 3 driven from the exhaust-side cam 40 and swinging; having a pair of pressing wrists 4 at one end in contact with the first and second intake valves 27 and 28 4 a and 4 4 b intake-side second rocker arm 4 4; at one end, there is an exhaust-side second rocker arm 45 that presses the wrist portion 4 5 a in contact with the exhaust valve 29; The swing motion of the first rocker arm 4 2 is transmitted to the intake-side second rocker arm 4 4 and the intake-side drive lever 4 6 provided between the intake-side first and second rocker arms 4 2 and 4 4; and An exhaust-side driving lever provided between the exhaust-side first rocker arm 4 3 and the exhaust-side second rocker arm 45 is transmitted to the exhaust-side second rocker arm 45 4 7. The first moving valve chamber 4 8 is formed between the cylinder head 14 and the top cover 15 for receiving and disposing the second rocker arms 4 4 and 4 5 on the intake side and the exhaust side of the moving valve device 3 8. The swing pivot supports the above-mentioned intake-side and exhaust-side second rocker arms 4 4 and 4 5 and the intake-side and exhaust-side second rocker arms 5 8 and 5 9 and the intake-side and exhaust-side drive levers 4 The upper part of 6 and 4 7 is a second moving valve chamber 4 8 for housing the remaining part of the moving valve device 3 9 and is formed to extend parallel to the cylinder axis C with respect to the cylinder axis C on the side opposite to the side where the spark plug 2 6 is provided. Inside the crankcase 12, the cylinder block 13 and the cylinder head 14. 11 312 / Invention Manual (Supplement) / 93-06 / 93107769 1244526 In order to lubricate the above-mentioned moving valve device 3 8 in the first moving valve chamber 4 8, an oil ejection hole 3 is provided in the top cover 15. 6. Lubricating the oil contained in the first moving valve chamber 48 is returned to the oil pan 12 a formed at the lower portion of the crank case 12 through the second moving valve chamber 49 (see FIG. 1). The first rocker arms 4 and 4 on the intake and exhaust sides respectively have pro- 5, 4 and 5 5 that are in rolling contact with the intake-side and exhaust-side cams 39 and 4 0 from the cylinder head 1 4 side. The gas-side and exhaust-side first rocker arms 5 6, 5 7 are swingably supported, and the suction-side and intake-side first rocker arms 5 6, 5 7 are provided on an axis having an axis parallel to the above-mentioned camshaft 41. Between the cylinder block 13 and the cover 50. The cup-shaped pressing portions 4 2 a and 4 3 a located on the opposite sides of the above-mentioned pro 5 4 and 5 5 are integrally provided on the intake side and the exhaust side of the first rocker arm by opening the cylinder head 1 4 side, respectively. 4 2, 4 3 on. The cam shaft 41 in the moving valve device 38 is installed on the cylinder block 13 so as to be accommodated in the second moving valve chamber 49, and both ends of the cam shaft 41 having an axis parallel to the crank shaft 10 pass through The ball bearings 51, 51 are rotatably supported on the cylinder block 13 and a cover 50 connected to the cylinder block 13 so as to be formed on the outer surface of the second moving valve chamber 49. Further, an oil supply path 3 for supplying lubricating oil to sliding contact portions of the intake-side and exhaust-side cams 39, 40, the intake-side first rocker arm 42, and the exhaust-side first rocker arm 4 3 is provided. 7 is provided on the camshaft 41. In order to reduce the power transmitted from the crankshaft 10 to half, the first driven sprocket 5 2, the first driving sprocket 60 (see FIG. 1), and the endless cam chain 5 3 are housed in the second moving valve chamber 4 9 Inside. The first driven sprocket 5 2 cannot be coupled to the camshaft 41 in a relative rotation, and the first driven sprocket 60 can not be coupled in a relative rotation to the curve 12 312 / Invention Manual (Supplement) / 93-06 / 93107769 1244526 On the arbor 10, the cam chain 53 is wound on the first driving sprocket 60 and the first driven sprocket 52. The intake-side and exhaust-side drive levers 4 6 and 4 7 extend across a portion of the first and second actuating valve chambers 4 8 and 9 and are narrowly spaced from each other at the cylinder head 14 and 4 sides. Set the drive levers 4 6, 4 7. One end of the spherical end of the first rocker arm 4 2, 4 3 on the pressing part 4 2 a, 4 3 a, the other side of the intake and exhaust side drive levers 4 6, 4 7 spherical end The pressure-receiving portions 44c and 45b of the second rocker arms 44 and 45 on the intake side and the exhaust side can be swung and fitted. In the first valve-operating chamber 4 8, the second rocker arm shafts 5 8 and 5 9, which have an axis parallel to the cam shaft 41, are supported and fixed on both sides of the injector 25. On the cylinder block 14, one end is provided on one end side in contact with the upper ends of the first and second intake valves 28 and 29 and is linked and connected with the two intake valves 28 and 29 and is branched into two branches. The second rocker arm 4 on the intake side for pressing the cup-shaped portions 4 2 a, 4 2 b is swingably supported on the second rocker arm 5 8 on the intake side. On one end side, an exhaust-side second rocker arm 45, which is in contact with the upper end of the exhaust valve 29, and which is linked and connected with the exhaust valve 29, is supported on the row by swinging freely. The air-side second rocker shaft 5 9 is on. Furthermore, on the opposite sides of the two push cup portions 4 4 a, 4 4 b with the second rocker arm shaft 58 closed on the intake side, the cup-shaped pressure receiving portion 4 4 c is opened on the cylinder block 1 3 side. It is integrally provided on the other end portion of the second rocker arm 4 on the intake side, on the opposite side of the pressing cup portion 4 5 a from which the second rocker arm shaft 5 9 on the exhaust side is closed, and on the cylinder block 1 A bowl-shaped pressure receiving portion 4 5 b opened on three sides is integrally provided on the exhaust-side second swing arm 45. 13 312 / Invention Manual (Supplement) / 93-06 / 93107769 1244526 The other ends of the second rocker arms 4 4 and 4 5 on the intake side and the exhaust side are pressure receiving parts 4 4 c and 4 5 b. Between the intake and exhaust side second rocker shafts 5 8 and 5 9, the intake and exhaust side drive levers 4 6 and 4 7 are on the intake and exhaust side second rocker arms. One ends of the shafts 5 8 and 5 9 are interlockedly connected with the other ends of the second rocker arms 4 4 and 4 5 on the intake side and the exhaust side. In such a moving valve device 38, the rotation of the cam shaft 41, which transmits the rotational power from the crank shaft at a reduction ratio of 1/2, is performed by the intake side first rocker arm 4 2 and the intake side cam 3 9 In response to the swing, the intake-side drive lever 46 is actuated in the axial direction. Correspondingly, when the intake-side second rocker arm 4 4 is swung, the first and second intake valves 2 7 and 2 8 are driven to open and close. The exhaust-side first rocker arm 4 3 follows the swing of the exhaust-side cam 40, and the exhaust-side drive lever 47 moves in the axial direction. In response to this, the exhaust-side second rocker arm 45 swings and exhausts. The valves 29 are driven by opening and closing. Therefore, the compressed air of the reciprocating air pump 61 which drives the piston 66 in a direction parallel to the cylinder axis C is supplied into the ejector 25. The air pump 61 is provided on the lower side of the cylinder block 13 on the side of the exhaust port 24 corresponding to the cylinder head 14. Further, an actuating chamber 6 2 disposed below the cylinder cavity 16 in a substantially L-shape in a plane perpendicular to the cylinder axis C is formed in the cylinder block 13, and the air pump 61 is relatively The second moving valve chamber 49 is disposed below the construction portion of the second moving valve chamber and the operating chamber 62. Referring to FIG. 8 together, the pump housing 63 of the air pump 61 has an axis parallel to the cylinder axis C, and is a bottomed cylinder opened at the cylinder head 14 side, and is integrated with the cylinder block 1 3 The cover member 64 of the above-mentioned opening portion of the cylinder head 14 side of the pump casing 63 is hermetically closed, and is connected to the cylinder block 13. 14 312 / Invention Manual (Supplement) / 93-06 / 93107769 1244526 The piston 6 6 is slidably fitted in the pump housing 6 3, and one end of the piston 6 6 and the cover member 6 4 are formed on the cylinder head 1. The pump chamber 65 on the four sides shrinks the corresponding volume to generate compressed air, and an atmospheric pressure chamber 8 8 provided on the oil pan 1 2 a side is formed between the other end of the piston 66 and the closed end of the pump housing 63. On the one hand, a cylindrical bearing member 6 9 having an axis parallel to the axis of the cam shaft 41 and passing through the axis of the above-mentioned axis of the piston 6 6 is disposed in the actuation chamber 6 2, and the bearing member 6 9 is passed through the bolt 7 1. . . Each is connected to a plurality of, for example, four connecting bosses 7 0 protruding on the cylinder block 13. . . on. Moreover, the cover 7 2 forming the outer side of the operating chamber 6 2 is connected to the cylinder block 13, and when the cover 7 2 is opened, the above-mentioned bolt 7 1 can be performed. . . Tightening and loosening operations. The pump drive shaft 7 3 is coaxially inserted into the above-mentioned bearing member 6 9, a roller bearing 7 4 is installed between one end of the bearing member 6 9 and the pump drive shaft 7 3, and a ball bearing 7 5 is installed at the other of the bearing member 6 9 Between one end and the fruit drive shaft 7 3. That is, the drive shaft 7 3 is rotatably supported on a bearing member 6 9 connected to the cylinder block 13. The power from the camshaft 4 1 is transmitted to the pump driving shaft 7 3 through the part protruding from the end of the bearing member 6 9 through the power transmission mechanism 8 9. The power transmission mechanism 8 9 is fixed by the pump driving shaft 7 3. Second driven sprocket 78, second driving sprocket 7 9 integrated with first driven sprocket 52 coupled to camshaft 41, wound around second driven and driven driven sprocket 7 8, 7 The endless chain on 9 is composed of 80. The pump drive shaft 7 3 is connected to the piston 6 6 of the air fruit 61 through a scotch roller crank 8 4, and the scotch yoke crank 8 4 is an eccentric shaft 7 protruding from the eccentric position of the pump drive shaft 7 3 -end. The front end of 3 a is connected to a member slidably fitted on a slide stop 68 of the piston 66. In addition, the pump drive shaft 7 3 is rotated by power transmitted from 15 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 camshaft 41, and accordingly, the eccentric shaft 7 3 a surrounds the pump drive shaft 7 3's axis turns. The piston 6 6 of the air pump 61 can be reciprocated in the pump housing 6 3 in the axial direction while increasing or decreasing the volume of the pump chamber 65. The sliding hole 67 is provided on the piston 66. The axis of the sliding hole 66 is provided along the diameter line of the piston 66 and in a plane perpendicular to the axis of the camshaft 41. The sliding stopper 6 8 is slidably fitted. Fit in the sliding hole 67, and the eccentric shaft 7 3 a is integrally protruded on one end of the pump driving shaft 7 3. Furthermore, an opening portion 7 6 at which one end of the pump drive shaft 7 3 is inserted is provided in the pump housing 6 3, and the rotation of the piston 66 corresponding to the drive shaft 7 3 allows the eccentric shaft 7 3 a along the axis of the slide hole 67 The insertion hole 7 7 inserted into the eccentric shaft 7 3 a so as to move in the direction is provided through the longitudinal central portion of the slide hole 67. In the central portion between the ball bearing 75 and the roller bearing 74, through-holes 8 1 and 8 2 are respectively provided on both sides of the bearing member 69 and at positions corresponding to one through-hole 8 1. A part of the oil in the operating chamber 62 is guided to an oil conductor 8 3 between the bearing member 69 and the pump drive shaft 73, and is integrally provided on the bearing member 69. That is, a passage 1 3 4 provided in the cylinder head 14 is provided on the cylinder head 14 so as to guide a part of the oil stored in the lower portion of the first valve chamber 48 to the passage 1 3 4 and to The passage 1 3 5 opened in the operating chamber 62 is provided on the cylinder block 13, and the oil conduit 8 3 that guides the oil that has fallen from the passage 1 35 through the through hole 8 1 is integrally provided on the bearing member 69. Further, a part of the oil guided between the bearing member 69 and the pump drive shaft 73 is used to lubricate the ball bearing 75 and the roller bearing 74, and the remaining part falls from the through hole 82 to the operating chamber 62. In the lower part, the oil stored in the lower part of the operating chamber 62 is returned to the oil pan 1 2 a from a return passage 1 3 6 which communicates with the lower part of the operating chamber 62 and is provided on the cylinder block 13. 16 312 / Invention specification (Supplement) / 93-06 / 93107769 1244526 With respect to the bearing member 6 9 on the opposite side of the air pump 6 1, a water pump 90 having a rotation axis coaxial with the pump drive shaft 7 3 is installed in the cylinder Body 1 3 on. The air pump 61 and the water pump 90 are disposed symmetrically with respect to a plane PL that includes the cylinder axis C and is perpendicular to the pump drive shaft 73. The pump casing 9 1 of the water pump 90 is composed of a casing main body 92 and a pump cover 9 3 which closes the open end of the casing main body 92. The dish-like portion 9 2b is integrally connected to the pump driving shaft 7 and is closed on the 3 side. The bottomed cylindrical portion 9 2 a is formed on the open end of the bottom body to form the above-mentioned housing body 92. The pump cover 9 3 clamps the outer peripheral portion of the open end of the housing body 92 between the cylinder body 13 and the cylinder body 13. In this way, it is connected to the cylinder block 13. The pump shaft 9 4 which is coaxial with the pump drive shaft 7 3 is rotatably supported at both ends of the central portion of the closed end of the bottomed cylindrical portion 9 2 a and the central portion of the pump cover 9 3. The inner magnet 96 is fixed to The rotor 95, which rotates integrally with the pump shaft 94 and is inserted into the bottomed cylindrical portion 92a, is inserted. On the other hand, a rotating member 9 7 having a cylindrical portion 9 7 a that coaxially surrounds the bottomed cylindrical portion 9 2 a of the housing body 92 is fixed to a pump drive shaft protruding from the other end of the bearing member 69. An outer magnet 98 is fixed to the inner surface of the cylindrical portion 9 7 a at the other end of the 7 3. Accordingly, corresponding to the rotation member 97 and the pump drive shaft 7 3 being rotated simultaneously, the rotor 95 and the pump shaft 9 4 are rotated together. Therefore, a volute chamber 9 9 is formed between the casing body 92 and the pump cover 93, and the turbine 100 accommodated in the volute chamber 9 9 is provided on the rotor 95. A plurality of suction ports 1 0 1 opened at the center of the vortex chamber 9 7. . . The cooling water installed in the pump cover 9 3 and sucked into the vortex chamber 9 9 from the suction port 101 is pressurized by the rotation of the turbine 100. The cooling water discharged from the water pump 90 is supplied to the cylinder-side water jacket 1 0 2 provided on the cylinder block 13 and the side-water jacket 1 102 leading to the block is provided at 17 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 The top water jacket 1 0 3 on the cylinder head 1 4 corresponds to the temperature of the cooling water. The thermostat 1 0 4 is switched to guide the cooling water discharged from the top water jacket 1 0 3 to the figure. The state of the radiator, etc., not shown, and the state of returning to the suction port 1 〇1 through the radiator, etc., the thermostat housing 104 of the thermostat 104, and the pump cover 9 3 of the water pump 90 above.体 形成。 Body formation. In the air pump 61, a part of the oil flowing through the second moving valve chamber 49 is introduced into the pump housing 63 as an oil introduction hole 8 5 for lubrication, and is provided in the pump housing to the second moving valve chamber 49. 6 3 on the upper side wall. According to the rotation of the second moving valve chamber 49, the intake-side cam 39 and the exhaust-side cam 40 of the camshaft 41 cause a portion of the oil flowing through the second moving valve chamber 48 to rise, while using the centrifugal force. Function to separate and scatter the oil. In addition, although a part of the oil supplied from the oil supply path 37 is separated and scattered due to centrifugal force, the camshaft 41 and the oil introduction hole 85 are set to guide the separated oil droplets into the oil introduction hole 85. relative position. The width of the portion corresponding to the moving valve device 38 in the second moving valve chamber is larger than that of the other portions, and approximately semicircularly surrounds the corresponding side of the intake-side cam 39 and the exhaust-side cam 40 in the camshaft 41. A part of the protruding wall 86 is integrally provided on the cylinder block 13 in an opposite direction to the oil flow direction 137 in the second moving valve chamber. The oil return hole 8 5 of the air pump 61 is provided in the protruding wall along the oil flow direction 1 3 7. 8 6 directly upstream position. That is, the protruding wall 86 can guide the oil flowing through the second valve valve chamber into the oil introduction hole 85. However, the oil return hole 8 5 is provided from the piston ring 1 3 8 which is installed on the outer periphery of the piston 6 6 and which is in sliding contact with the inner periphery of the pump housing 6 3. The atmospheric pressure chamber 8 8 is open to the inner periphery of the pump housing 63. The pump housing 6 3 has nothing to do with the axial movement of the piston 6 6 18 312 / Instruction Manual (Supplement) / 93-06 / 93107769 1244526 The oil return hole 8 5 is always the same as the sliding hole provided on the piston 6 6 6 7 is connected at one end. Furthermore, a pair of grooves 1 3 9 connecting the end of the atmospheric pressure chamber 8 8 side of the piston 6 6 and the ends of the sliding hole 6 7 are connected. . . It is arranged on the outer periphery of the piston 6 6 and is guided from the oil return hole 8 5 to the pump housing 6 3. A part of the oil is used for lubrication between the piston 6 6 and the pump housing 6 3. The remaining part passes through the groove 1 3. 9 . . . It flows on the 8-8 side of the atmospheric pressure chamber. However, the above slot 1 3 9. . . Draining the oil in the sliding holes 6 7 also effectively prevents the suction of the sliding stops 68 from occurring in the scotch-type crank 8 4. The oil flowing on the atmospheric pressure chamber 88 side flows from the opening portion 76 to the operation chamber 62 side, and also flows from the return passage 1 36 to the oil pan 12a side. Pay particular attention to FIGS. 7 and 8. The injector 25 is a coaxial connection between the first injection valve 107 and the second injection valve 108. The first injection valve 107 is used to inject fuel and is mounted on the top cover 15 The second injection valve 108, which directly injects the fuel together with compressed air into the combustion chamber 19 and is mounted on the cylinder head 14; the second injection valve 108 has a nozzle protruding into the combustion chamber 19 1 0 8 a. A fitting hole 1 0 9 for hermetically fitting the above-mentioned nozzle 1 0 8 a, a diameter larger than the fitting hole 1 0 9 and being coaxially connected with the fitting hole 1 ϋ g, a white spoon inserting cylinder 1 1 0 and a cylinder The axis C is coaxially provided on the cylinder head 14 and the second injection valve 108 is inserted into the insertion cylinder 1 10 from the top cover 15 side until the nozzle 1 0 8 a is air-tightly fitted into the insert. The wave-shaped spring washer 1 2 3 and the ring-shaped step 1 1 1 formed between the fitting hole 10 9 and the insertion tube 1 10 are simultaneously contacted in the closing hole 10 9 at the same time. The second injection valve 1 008 has a wire connecting portion 1 0 8 b at the rear portion, and is arranged on a cutout 1 1 0 a provided at the rear end of the insertion tube 1 1 0, and outside the insertion tube 1 1 0, from 19 3 12 / Invention Manual (Supplements) / 93-06 / 93] 07769 1244526 A pair of wires 1 1 2 led by the wire connecting portion 1 0 8 b. . . It is clamped between the joint surface of the cylinder head 14 and the top cover 15 and penetrates the cylinder block 1 1 3 and is led out to the outside. On the one hand, the first injection valve 107 is fitted and held, and a cylindrical shape having a positioning portion that functions to hold and clamp the second injection valve 108 between the cylinder heads 14 is provided. The injector housing Π 4 is integrally formed in the top cover 15. When the top cover 15 and the cylinder block 14 are combined, the front end of the injector housing 114 is in contact with the rear end of the second injection valve 108. Further, a clamping plate 1 1 5 that holds a rear end portion of the first injection valve 10 7 together with the injector housing 1 1 4 is connected to the rear end of the injector housing 1 1 4. The first injection valve 1 7 includes a wiring terminal 10 7 a at a rear portion thereof, and the rear end of the first injection valve 1 0 7 is held by the injector housing 1 1 4 and the holding plate 1 1 5. When the injection valve 10 7 is mounted on the top cover 15, the wiring terminal 10 7 a is provided facing the top cover 15 externally. An annular combustion chamber 1 1 6 that opens into the first injection valve 1 0 7 is formed between the injector housing 1 1 4 and the first injection valve 10 7. One of the combustion chambers 1 1 6 is held from both sides. The pair of sealing members 1 1 7 and 1 1 8 are installed between the injector housing 114 and the first injection valve 107. However, the fuel supply path 1 1 9 to the combustion chamber 116 is directly provided in the top cover 15 and a hose 1 2 0 for guiding fuel from a fuel supply source (not shown) is connected to the fuel supply through a joint 1 2 1 Paths 11 9 are connected. Further, between the front end portion of the first injection valve 107 and the rear end portion of the second injection valve 108, an annular air is formed in the injector housing Π 4 to the second injection valve 108. In the chamber 1 2 2, the compressed air from the air pump 61 is supplied into the air chamber 1 2 2. 20 312 / Invention (Supplement) / 93-06 / 93107769 1244526 A suction pipe connected to a hose for guiding air from an air cleaner not shown in the figure 1 2 4 (refer to FIG. 2) is provided at the air pump 6 On the cover member 6 4 in 1, the suction pipe 1 2 4 is connected to the pump chamber 65 through a reed valve (not shown) built in the cover member 6 4. A poppet valve 1 2 5 that opens the valve in response to an increase in the pressure of the pump chamber 65 is built in the cover member 64, and the compressed air discharged from the air pump 61 passes through the poppet valve 1 2 5 and the compressed air supply path 1 2 6 Supply into the air chamber 1 2 2. The compressed air supply path 1 2 6 is composed of a pipe fitting 1 2 7, a passage 1 2 8 directly connected to the cylinder head 1 4 communicating with the pipe fitting 1 2 7, and communicating with the passage 1 2 8 and simultaneously leading to the air chamber 1 2 2 ground. The passage 1 2 9 is directly provided on the top cover 15. One end of the pipe fitting 1 2 7 is connected to the cover member 6 4 connected to the poppet valve 1 2 5, and the other end is connected to the cylinder head 14. In addition, both ends of a cylindrical positioning pin 1 30 that crosses the joint surface of the cylinder head 14 and the head cover 15 are inserted into the cylinder head 14 and the head cover 15 to form a part of the compressed air passage 1 2 6 And the passages 1 2 8 and 1 2 9 which are directly provided on the cylinder head 14 and the top cover 15 are connected through the positioning lock 1 3 0 described above. However, the O-ring 1 3 3 surrounding the positioning pin 1 3 0 is sandwiched between the joint surface of the cylinder head 14 and the top cover 15. In addition, a nozzle hole 1 31 is formed in the positioning pin 1 30, and a safety valve 1 3 2 (see FIG. 2) connected from the nozzle hole 1 31 to the above-mentioned passage 1 2 8 on the upstream side is mounted on the cylinder head 14 . Note that in FIGS. 1 and 3, the throttle body device 140 is connected to the intake port 2 3 of the cylinder head 14 through the intake pipe 1 41. The above-mentioned throttle valve body device 1 40 includes a valve body portion 1 4 having an intake passage 1 4 2 and a throttle that rotatably supports the valve body portion 1 4 3 across the above-mentioned intake passage 1 4 2. Valve shaft 1 4 4. From fully closed position to fully open position 21 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 Turn to adjust the opening area of the intake passage 1 4 2 and fix it on the throttle shaft The plate-shaped butterfly throttle valve 1 4 5 on 1 4 4, and the throttle drum 1 4 6 which is fixed to one end of the throttle valve shaft 1 4 4 outside the valve body portion 1 4 3. A throttle cable 1 4 7 operated by an operating member such as a throttle grip is wound and connected to a throttle drum 1 4 6. The valve body portion 1 4 3 is a member connected to the intake pipe 1 4 1 through a connecting belt 1 4 9 so that the intake passage 1 4 2 opens into the intake pipe 1 4 1 and includes detection of the throttle valve shaft 1 described above. The amount of rotation of the 4 and butterfly throttle valve 1 4 5 is the throttle cable 1 4 7 The control unit of the sensor 1 4 8 is installed on the valve body 1 4 3, and the ejector 2 5 The injection amount of the mixed fuel and air is controlled by the control unit 1 4 8 corresponding to the rotation amount of the throttle valve 1 4 5. The air inlets 2 3 of the cylinder head 14 are formed to have a sufficient opening area required to suck in a necessary amount of air at the maximum output of the engine. Corresponding to this, the intake passage 1 4 2 of the throttle body device 1 40 has an opening area such that the throttle valve 1 4 5 that can be turned from the fully closed position to the fully open position is in the fully closed position. In the intermediate position between the full-open position and the full-open position, the required amount of air can be taken in at the maximum output of the engine. That is, as shown in FIG. 9, when the throttle valve 1 4 5 is rotated from the fully closed position to the fully open position, the amount of intake air flowing through the intake passage 1 4 2 becomes smaller than the intake passage 1 4 set according to the area including the opening. 2 intake port 2 3 The maximum intake air volume determined by the flow resistance of the entire intake system. Once the maximum intake air volume is reached, even if the throttle valve 1 4 5 is operated at the fully open side, the intake air volume does not increase. mouth. The inner shape of the intake pipe 1 4 1 is formed into a tapered shape that smoothly joins the intake passage 1 4 2 and the intake port 1 2 3 of the throttle body device 140. 22 312 / Invention Specification (Supplement) / 93-06 / 93107769 1244526 The function of this embodiment will be described below. The injector 25 having an axis parallel to the axis C of the cylinder is provided on the cylinder block 14. The mixture of air and air is directly injected into the combustion chamber 19, and the above-mentioned mixture can be concentrated near the center of the combustion chamber 19. Since the combustion can be diluted, the combustion consumption can be reduced. In addition, since the injector 25 is a component that atomizes fuel by compressed air and directly injects it into the combustion chamber, the atomization of the fuel is fine at a small flow rate, the structure is simplified, and the combustion is improved, which can further reduce the low load and low speed Fuel consumption. Although the amount of the mixture injected from the injector 2 5 corresponds to the throttle valve 1 4 5 of the throttle body device 1 4 0 connected to the intake port 2 3 on the cylinder head 1 4 1 through the intake pipe 1 4 1 The amount of rotation is controlled. As shown in FIG. 9, the amount of intake air guided into the intake port 2 3 by the throttle body device 1 40 and the intake pipe 1 4 1 and the amount of rotation of the throttle valve 1 4 5 There is a non-linear relationship. That is, since the air inlet 23 on the cylinder head 14 has a sufficient opening area that can absorb the amount of air necessary for the maximum output of the engine, the intake passage 1 4 2 of the throttle body device 1 40 is formed Has such an opening area that the throttle valve 1 4 5 can inhale the necessary amount of air at the maximum output of the engine in the intermediate position between the fully closed position and the fully open position, and rotates as much as possible on the open side Before the throttle valve 1 4 5, the opening area of the intake passage 1 4 2 in the throttle body device 1 40 must be able to circulate the air necessary for the maximum output of the engine. The rotation amount of the throttle valve 1 4 5 The opening area of the intake passage 1 42 in the throttle body device 140 may also become non-linear. Furthermore, the simple structure of the throttle body device 1 4 0 that rotates the throttle valve 1 4 5 by the operation of the inexpensive throttle cable 1 4 7 makes the rotation amount of the throttle valve 1 4 5 23 312 / The relationship between the description of the invention (Supplement) / 93-06 / 93107769 1244526 and the intake air volume is nonlinear, which can reduce the low load of the engine and the fuel consumption in the low rotation range. The shape of the inner surface of the intake pipe 1 4 1 is a tapered shape that can smoothly connect the intake passage 1 4 2 and the intake port 2 3 of the throttle body device 1 40 from the throttle body device 1 4 0 The intake air flow rate from the intake passage 1 2 2 to the intake port 2 3 changes smoothly, and the output of the engine can be controlled more stably. The embodiments of the present invention have been described above, but the present invention is not limited to the above-mentioned embodiments, and various design changes can be made to the present invention as long as they do not depart from the scope described in the scope of patent application. (Effects of Invention) According to the invention described in the first item of the patent application scope, a simple structure of a throttle body device that rotates a throttle valve by operating an inexpensive throttle cable is used to make the amount of rotation of the throttle valve The relationship with the intake air volume is non-linear, and the fuel consumption in the low-load and low-speed rotation region of the engine can be reduced. According to the invention described in the second patent application range, the intake air flow rate from the intake passage of the throttle body device to the intake port changes smoothly, and the output of the engine can be controlled more stably. According to the invention described in claim 3 of the scope of patent application, the fuel is atomized well at a small flow rate, the structure is simplified, and the fuel consumption at a low load and a low speed can be further reduced. [Brief description of the drawings] FIG. 1 is a longitudinal sectional view of a part of the engine. 24 312 / Invention Manual (Supplement) / 93-06 / 93] 07769 1244526 Figure 2 is a view taken along line 2-2 in Figure 1 to show the state after the top cover is removed. Fig. 3 is a plan view taken along line 3-3 in Fig. 2. FIG. 4 is a sectional view taken along line 4-4 in FIG. 3. FIG. Fig. 5 is a plan view taken along line 5-5 in Fig. 2; FIG. 6 is a sectional view taken along line 6-6 in FIG. 5. FIG. FIG. 7 is a plan view taken along line 7-7 in FIG. 5. FIG. FIG. 8 is a plan view taken along line 8-8 in FIG. 2. FIG. FIG. 9 is a graph showing the relationship between the amount of throttle rotation and the amount of intake air. (Description of component symbols) 10 Crankshaft 11 Direct injection engine body 12 Crankcase 1 2a Oil pan 13 Cylinder block 14 Cylinder head 15 Top cover 16 Cylinder cavity 17 Piston 18 Connecting rod 19 Combustion chamber 19a Top wall 2 0 First intake Port 2 1 Second intake valve port 25
3 12/發明說明書(補件)/93-06/93107769 1244526 22 排 氣 閥 口 2 23 進 氣 口 24 排 氣 口 25 噴 射 器 26 火 星 塞 27 第 一 進 氣 閥 28 第 二 進 氣 閥 29 排 氣 閥 30 導 向 筒 3 1 護 圈 32 閥 彈 簧 33 導 向 筒 34 護 圈 35 閥 彈 簧 36 油 喷 出 孔 37 供 油 路 38 動 閥 裝 置 39 進 氣 側 凸 輪 40 排 氣 側 凸 輪 4 1 凸 輪 軸 42 進 氣 側 第 一搖 臂 42a 杯 形 推 壓 部 4 3 排 氣 側 第 一搖 臂 4 3a 杯 形 推 壓 部 312/發明說明書(補件)/93-06/931077693 12 / Instruction of the Invention (Supplement) / 93-06 / 93107769 1244526 22 Exhaust valve port 2 23 Intake port 24 Exhaust port 25 Injector 26 Mars plug 27 First intake valve 28 Second intake valve 29 Row Air valve 30 Guide cylinder 3 1 Guard ring 32 Valve spring 33 Guide cylinder 34 Guard ring 35 Valve spring 36 Oil ejection hole 37 Oil supply path 38 Actuating valve device 39 Intake side cam 40 Exhaust side cam 4 1 Camshaft 42 In Air side first rocker arm 42a cup-shaped pressing part 4 3 Air side first rocker arm 4 3a cup-shaped pressing part 312 / Invention Manual (Supplement) / 93-06 / 93107769
26 1244526 44 進 氣 側 第 二 搖 臂 44a 、44b 推壓月 宛部 45 排 氣 側 第 二 搖 臂 45a 推 壓 腕 部 46 進 氣 側 驅 動 桿 47 排 氣 側 馬區 動 桿 48 第 一 動 閥 室 49 第 二 動 閥 室 50 蓋 5 1 滾 珠 軸 承 52 第 一 從 動 鏈 輪 53 環 形 凸 輪 鏈 54、 55 1 56 吸 氣 側 第 一 搖 臂 57 排 氣 側 第 一 搖 臂 58 進 氣 側 第 二 搖 臂 軸 59 排 氣 側 第 二 搖 臂 軸 60 第 一 主 動 鏈 輪 6 1 往 復 式 空 氣 泵 62 作 動 室 63 泵 殼 體 64 蓋 構 件 65 泵 室 66 活 塞 312/發明說明書(補件)/93-06/93107769 1244526 67 滑 動 孔 68 滑 動 擋 塊 69 圓 筒 狀 軸 承 構 70 凸 台 7 1 螺 栓 72 蓋 73 泵 驅 動 轴 73a 偏 心 軸 74 滾 柱 轴 承 75 滾 珠 軸 承 76 開 P 部 77 插 入 孔 78 第 二 從 動 鏈 輪 79 第 二 驅 動 鏈 輪 80 環 形 鏈 條 81、 82 通孔 83 油 導 體 84 止 轉 棒 .厄 式 曲 85 油 導 入 孔 86 突 壁 88 大 氣 壓 室 89 動 力 傳 遞 機 構 90 水 泵 9 1 泵 殼 體 312/發明說明書(補件)/93-06/93107769 1244526 92 殼 體 主 體 92a 有 底 圓 筒 部 92b 碟 狀 部 93 泵 蓋 94 泵 軸 95 轉 子 97 轉 動 構 件 97a 圓 筒 部 98 外 磁 鐵 99 /1¾ 室 100 輪 10 1 吸 入 口 102 缸 側 水 套 103 頂 側 水 套 104 恒 溫 器 105 恒 溫 器 殼 體 107 第 一 噴 射 閥 107a 後 部 配 線 用端子 108 第 二 喷 射 閥 1 08a 噴 嘴 108b 導 線 連 接 部 109 欲 合 孔 110 插 入 筒 110a 切 口 312/發明說明書(補件)/93-06/93107769 29 1244526 111 環形臺階 113 汽缸體 114 圓筒狀喷射器殼體 115 夾持板 116 環形燃燒室 117 密封構件 119 燃料供給通路 1 20 軟管 12 1 接頭 1 22 環形空氣室 12 3 進氣口 1 24 吸入管 1 25 提升閥 1 26 壓縮空氣供給路 1 27 管件 1 28 通路 1 29 通路 13 0 圓筒狀定位銷 13 1 噴孔 1 32 安全閥 1 3 3 0型環 1 34 通路 13 5 通路 13 6 返回通路 3026 1244526 44 The second rocker arm 44a, 44b on the intake side pushes the moon 45. The second rocker arm 45a on the exhaust side pushes the wrist 46. The drive lever on the intake side 47 The lever on the exhaust side 48 First action valve Chamber 49 Second valve chamber 50 Cover 5 1 Ball bearing 52 First driven sprocket 53 Ring cam chain 54, 55 1 56 First rocker arm on the suction side 57 First rocker arm on the exhaust side 58 Second on the intake side Rocker shaft 59 Exhaust side Second rocker shaft 60 First drive sprocket 6 1 Reciprocating air pump 62 Operating chamber 63 Pump housing 64 Cover member 65 Pump chamber 66 Piston 312 / Instruction manual (Supplement) / 93- 06/93107769 1244526 67 Slide hole 68 Slide stop 69 Cylindrical bearing structure 70 Boss 7 1 Bolt 72 Cover 73 Pump drive shaft 73a Eccentric shaft 74 Roller bearing 75 Ball bearing 76 Open P section 77 Insertion hole 78 Second from Moving sprocket 79 second drive chain Wheel 80 endless chain 81, 82 through-hole 83 oil conductor 84 anti-rotating rod. Ursula 85 oil inlet hole 86 protruding wall 88 atmospheric pressure chamber 89 power transmission mechanism 90 water pump 9 1 pump housing 312 / invention specification (supply) / 93-06 / 93107769 1244526 92 Case body 92a Bottom cylindrical portion 92b Dish portion 93 Pump cover 94 Pump shaft 95 Rotor 97 Rotating member 97a Cylinder portion 98 External magnet 99 / 1¾ Chamber 100 Wheel 10 1 Suction port 102 Cylinder Side water jacket 103 Top water jacket 104 Thermostat 105 Thermostat housing 107 First injection valve 107a Terminal for rear wiring 108 Second injection valve 1 08a Nozzle 108b Wire connection part 109 Fitting hole 110 Inserting barrel 110a Cutout 312 / Invention Instructions (Supplements) / 93-06 / 93107769 29 1244526 111 Annular step 113 Cylinder block 114 Cylindrical injector housing 115 Clamping plate 116 Annular combustion chamber 117 Seal member 119 Fuel supply path 1 20 Hose 12 1 Connector 1 22 annular air chamber 12 3 air inlet 1 24 Suction pipe 1 25 Poppet valve 1 26 Compressed air supply line 1 27 Pipe fitting 1 28 Passage 1 29 Passage 13 0 Cylindrical positioning pin 13 1 Nozzle 1 32 Safety valve 1 3 3 0-ring 1 34 Passage 13 5 Passage 13 6 Return path 30
312/發明說明書(補件)/93-06/93107769 1244526 13 7 第二動閥室内油流通方向 1 39 槽 1 40 節流閥體裝置 14 1 進氣管 1 42 進氣通路 1 43 閥體部 1 44 節流閥軸 1 45 板狀蝶形節流閥312 / Invention Manual (Supplement) / 93-06 / 93107769 1244526 13 7 Direction of oil flow in the second valve chamber 1 39 Slot 1 40 Throttle body device 14 1 Intake pipe 1 42 Intake passage 1 43 Valve body 1 44 Throttle shaft 1 45 Plate butterfly throttle
1 46 節流閥滚筒 147 節流閥纜線 148 控制單元 149 皮帶1 46 Throttle drum 147 Throttle cable 148 Control unit 149 Belt
312/發明說明書(補件)/93-06/93107769 31312 / Invention Specification (Supplement) / 93-06 / 93107769 31