200424424 玖、發明說明： 【發明所屬之技術領域】 本發明係關於一種汽缸蓋上凸輪型引擎，其中，在 引擎主體的一部分的汽缸蓋上，以可開閉的方式配置 氣閥和排氣閥，使其順著以吸氣側和排氣側閥彈簧向 的方向逼迫，而在配置於吸氣側和排氣側閥彈簧之間 旋轉地支承於汽缸蓋的凸輪軸上，配置有第1凸輪和 凸輪，該第1凸輪用於驅動吸氣閥和排氣閥中的一個 第2凸輪用於驅動吸氣閥和排氣閥中的另一個。 【先前技術】 已知有例如專利文獻1等中的汽缸蓋上凸輪型引擎 中，為了確保配置火星塞的空間，配置於吸氣閥和排 之間的凸輪軸係從汽缸軸線上偏靠於吸氣閥和排氣閥 中一側。 (專利文獻1 ) 日本專利特公昭5 9 — 2 5 8 6 1號公報 【發明内容】 (發明所欲解決之問題） 但是，在上述習知技術中，由於吸氣閥和排氣閥的 所形成的閥夾角較大，故不利於燃燒室的節省空間化 致汽缸蓋的大型化。 本發明是針對上述問題而提出者，目的在於提供一 缸蓋上凸輪型引擎，其可使燃燒室節省空間，並且使 蓋小型化。 312/發明說明書(補件)/93-05/93105275 構成 有吸 閉閥 並可 第2 ，該 ，其 氣閥 的其 閥桿 ，導 種汽 汽缸 6 200424424 (解決問題之手段） 為了實現上述目的，申請 種汽缸蓋上凸輪型引擎，其 汽缸蓋上，以可開閉的方式 閥和排氣闊係以螺旋狀的吸 向逼迫，在配置於上述吸氣 間、並以可旋轉的方式支承 有第1凸輪和第2凸輪，該 排氣閥其中一者，該第2凸 其中另一者，該汽缸蓋上凸 輪軸係以其軸線大致配置於 汽缸蓋上，配置於上述吸氣 凸輪係形成為小於第1凸輪 述凸輪軸的軸線的方向自上 發生偏離的位置。 根據此種構造，可避免第 氣側閥彈簧之間的干擾，同 的夾角設定得較小，而可使 的壓縮比，同時可使具有凸 進而獲得汽缸蓋的小型化。 此外，申請專利範圍第2 利範圍第1項的發明之構造 軸的兩側，沿著該凸輪軸的 氣閥和排氣閥，係以可開閉 專利範圍第1項的發明係為一 係在構成引擎主體的一部分的 配置吸氣閥和排氣閥，該吸氣 氣側和排氣側閥彈簧向閉閥方 側閥彈簧和排氣側閥彈簧之 於上述汽缸蓋的凸輪軸上配置 第1凸輪係用以驅動吸氣閥和 輪係用以驅動吸氣閥和排氣閥 輪型引擎之特徵在於，上述凸 汽缸軸線上的方式支承於上述 側和排氣側閥彈簧之間的第2 ，第1凸輪係配置於在沿著上 述吸氣側和排氣側閥彈簧之間 1和第2凸輪、及吸氣側和排 時可將吸氣閥和排氣閥的閥桿 燃燒室節省空間化，獲得較高 輪軸的閥動裝置節省空間化， 項的發明，係除了上述申請專 外，尚有特徵為，在上述凸輪 軸線的方向並排的各一對的吸 的方式配置於上述汽缸蓋上； 312/發明說明書(補件)/93-05/93105275 7 200424424 根據該構造，於4閥的汽缸蓋上凸輪型引擎中，可達成燃 燒室的節省空間化，獲得較高的壓縮比，並可使具有凸輪 軸的閥動裝置節省空間化，進而獲得汽缸蓋的小型化。 申請專利範圍第3項的發明，係除了上述申請專利範圍 第1或2項的發明之構造外，尚有特徵為，包括上述汽缸 蓋的引擎主體係以使上述汽缸軸線朝向前上方傾斜、且曲 柄軸的軸線處於水平的姿勢，於小型車輛的前輪後方裝載 於車體框架上，連動於上述第1和第2凸輪其中一者的第 1搖臂係以可擺動的方式支承於具有平行於上述凸輪軸的 軸線的第1擺動軸上，連動於上述第1和第2凸輪其中另 一者的第2搖臂係以可擺動的方式支承於具有平行於上述 凸輪軸的轴線且設置於第1擺動軸之後方的第2擺動軸 上，第2擺動軸和上述曲柄軸之間的距離係設定為小於第 1擺動軸和上述曲柄軸之間的距離；根據該構造，即便汽 缸轴線朝向前上方傾斜，仍可儘量地縮短從曲柄軸到引擎 主體的前端下部的距離，可避免與前輪的干擾，同時使引 擎主體接近前輪側，有助於縮短小型車輛的軸距（w h e e 1 base)，或可將前輪的輪行程（wheel stroke)設定得較長。 申請專利範圍第4項的發明，係除了上述申請專利範圍 第3項的發明之構造外，尚有特徵為，在上述第1搖臂上， 以軸支承有與上述第1凸輪滾動接觸的滾子（roller)，在 上述第2搖臂上，設置有與上述第2凸輪滑動接觸的凸輪 滑塊；根據該構造，可避免使配置空間較小的凸輪滑塊與 配置於吸氣側和排氣側閥彈簧之間的第2凸輪滑動接觸而 8 312/發明說明書(補件)/93-05/93105275 200424424 使吸氣閥和排氣閥的閥桿的夾角增加，而可獲得汽缸蓋的 小型化，另外，由於配置於自吸氣側和排氣側閥彈簧之間 偏離的位置，故使配置空間較大的滾子在不對上述夾角造 成影響的第1凸輪上滾動接觸，藉此，可有助於閥動裝置 的摩擦損失的降低。 申請專利範圍第5及6項的發明，係除了上述申請專利 範圍第3或4項的發明之構造外，尚有特徵為，係由具有 朝向前上方傾斜的汽缸軸線的前部汽缸側體（f r ο n t b a n k )、與從側面看呈V字形地與上述汽缸軸線交叉的汽缸 軸線的後部汽缸側體（rear bank)之V型的上述引擎主體所 構成；根據該構造，可在避免與前輪的干擾之同時，使該 引擎主體所具有的前部汽缸蓋接近前輪側，藉此，可避免 小型車輛的軸距增加，或前輪的輪行程縮短，同時，將引 擎主體儘量地配置於下方位置，可在引擎主體的上方保有 較大的用於確保其他零件的空間，並可降低駕駛員用座的 南度。 【實施方式】 下面根據圖式所示的本發明的一個實施例，對本發明的 實施形態進行說明。 圖1〜1 1表示本發明的一個實施例，圖1為摩托車的側 視圖，圖2為從與圖1相同的方向所視之動力單元的切除 局部的側視圖，圖3為沿圖2中的3 — 3線的剖視圖，圖4 為沿圖3中的4 一 4線的剖視圖，圖5為沿圖4中的5 — 5 線的箭視圖，圖6為省略了搖臂的狀態之與圖5相對應的 9 312/發明說明書(補件)/93-05/93105275 200424424 圖，圖7為沿圖5中的7 — 7線的剖視圖，圖8為沿圖5 中的8 — 8線的剖視圖，圖9為沿圖4中的9 — 9線的剖視 圖，圖1 0為沿圖4中的1 0 — 1 0線的箭視圖，圖1 1為沿圖 9中的箭頭1 1的箭視圖。 首先，在圖1中，在屬於小型車輛的摩托車的車體框架 1 1上，裝載著配置於前輪W F和後輪W R之間的動力單元P， 該動力單元P係由4循環2缸筒的引擎E、與配置於該引 擎E和後輪W R的車軸1 8之間的動力傳送裝置T所構成。 一併參照圖2〜圖4，上述引擎E的引擎主體1 3為V形， 其包括：曲柄軸箱1 4，其以可旋轉的方式支承具有沿車架 1 1的左右方向延伸的水平軸線之曲柄軸1 2;前部汽缸側體 FB，其係使汽缸軸線CF朝向前上方傾斜並與上述曲柄軸箱 1 4連接；以及後部汽缸側體R B，其係從側面看為呈V字形 與上述汽缸軸線CF交叉，並使汽缸軸線CR朝向後上方傾 斜而與上述曲柄軸箱1 4連接；兩個汽缸側體F B、R B分別 構成為汽缸蓋上閥型。 前部汽缸側體F B包括與上述曲柄軸箱1 4連接之前部汽 缸體1 5 F、與上述前部汽缸體1 5 F連接之前部汽缸蓋1 6 F、 以及在與前部汽缸體1 5 F的相反側與前部汽缸蓋1 6 F連接 之前部頭蓋1 7 F，後部汽缸側體R B包括與上述曲柄軸箱1 4 連接之後部汽缸體1 5 R、與後部汽缸體1 5 R連接之後部汽 缸蓋1 6 R、以及在與後部汽缸體1 5 R的相反側與後部汽缸 蓋1 6R連接之後部頭蓋1 7R。 曲柄軸箱1 4係由殼體左半部1 9和殼體右半部2 0相互 10 312/發明說明書(補件)/93-05/93105275 200424424 連接而成，該殼體左半部1 9配置於朝向摩托車的行進方向 前方時之左側，該殼體右半部20配置於朝向摩托車的行進 方向前方時之右側，上述兩個殼體半部1 9、2 0藉由與上述 前部和後部汽缸側體FB、RB的汽缸軸線CF、CR平行的連 接面21而相互連接。 曲柄軸1 2的一端部貫穿設置於殼體左半部1 9的左側曲 柄軸頸部2 2，以可旋轉的方式支承於該曲柄軸頸部2 2上， 該曲柄軸1 2的另一端部貫穿設置於殼體右半部2 0的右側 曲柄軸頸部2 3，以可旋轉的方式支承於該曲柄軸頸部2 3 上。 曲柄軸1 2包括配置於左側曲柄軸頸部2 2的内方的第1 曲柄垂重部24及配置於右側曲柄軸頸部23的内方的第2 曲柄垂重部2 5，連桿2 8 F的大端部與連桿2 8 R的大端部以 可旋轉的方式與曲柄銷2 9連接，該連桿2 8 F與以可滑動的 方式與設置於前部汽缸體1 5 F的搪缸機2 6 F嵌合之活塞 2 7 F連接，該連桿2 8 R與以可滑動的方式與配置於後部汽 缸體1 5 R的搪缸機2 6 R嵌合之活塞2 7 R連接，該曲柄銷2 9 將第1和第2曲柄垂重24、25之間連接且配置於曲柄 軸1 2上。 後部汽缸體1 5 R係從前部汽缸體1 5 F偏靠到沿曲柄軸1 2 的軸線的一端側而配置，上述兩個連桿2 8 F、2 8 R的大端部 係以前部汽缸體1 5 F側的連桿2 8 F靠近第2曲柄垂重部2 5 而配置、且後部汽缸體1 5 R側的連桿2 8 R靠近第1曲柄垂 重部24而配置之方式，在第1和第2曲柄垂重部24、25 11 312/發明說明書(補件)/93-05/93丨05275 200424424 之間與曲柄銷2 9連接。 在從左側曲柄軸頸部2 2突出的曲柄軸1 2的一端部，安 裝有發電機3 0，該發電機3 0由固定於曲柄軸1 2的一端部 的轉子3 1與容納於該轉子3 1内的定子3 2構成。該發電機 3 0由與曲柄軸箱1 4的殼體左半部1 9連接的左引擎罩3 3 覆蓋，該定子32固定於左引擎罩33上。 在左曲柄軸頸部22和發電機30之間配置有從動齒輪 3 5，.該從動齒輪3 5以同軸的方式圍繞曲柄軸1 2，該被動 齒輪3 5係透過單向離合器3 4而連接於發電機3 0的轉子 3 1。另外，具有與曲柄軸1 2平行的旋轉軸線之起動馬達 3 6係位於前部和後部汽缸體1 5 F、1 5 R之間，支承於曲柄 軸箱1 4的頂部，在該起動馬達3 6的輸出軸設置有驅動小 齒輪3 7。另一方面，在曲柄軸箱1 4的殼體左半部1 9和左 引擎罩3 3之間，一體形成的第1和第2中間齒輪3 8、3 9 與第3中間齒輪4 0係以可繞與曲柄軸1 2平行的軸線旋轉 的方式支承，上述驅動小齒輪3 7與直徑大於該驅動小齒輪 3 7的第1中間齒輪3 8嚙合，直徑小於第1中間齒輪3 8的 第2中間齒輪3 9與第3中間齒輪4 0嚙合，該第3中間齒 輪4 0的直徑大於第2中間齒輪3 9且與從動齒輪3 5嚙合。 於是，藉由在引擎E起動時使起動馬達3 6動作，使來 自起動馬達3 6的驅動力減小並傳達給曲柄軸1 2，另外， 在引擎E起動後，不會有因為單向離合器34的作用而將曲 柄軸1 2的動力傳達至起動馬達3 6側之狀況。 在從右側曲柄軸頸部2 3突出的曲柄軸1 2的另一端部， 12 312/發明說明書(補件)/93-05/93105275 200424424 固定有一體形成的一對驅動鏈輪4 4 F、4 4 R，在其中一個驅 動鏈輪4 4 F上，捲繞有凸輪鏈條4 6 F，該凸輪鏈條4 6 F用 於驅動配置於前部汽缸蓋1 6 F的閥動裝置4 5 F，而在另一 個驅動鏈輪4 4 R上，捲繞有凸輪鏈條4 6 R，該凸輪鏈條4 6 R 用於驅動配置於後部汽缸蓋1 6 R的閥動裝置4 5 R。另外， 覆蓋曲柄軸1 2的另一端部的右引擎罩4 7係與曲柄軸箱1 4 的殼體右半部2 0連接。 又，於圖1中，配置於引擎E的前方斜上方的空氣清潔 器4 8裝載於車體框架1 1上，而配置於空氣清潔器4 8的上 方的燃料槽4 9裝載於車體框架1 1上，在前部和後部汽缸 蓋16F、16R上，透過各自的吸氣管50F、50R而連接於上 述空氣清潔器4 8。此外，對從前部和後部汽缸蓋1 6 F、1 6 R 排出的排氣進行導向的排氣管5 1 F、5 1 R係共通地與配置於 後輪WR右側的排氣消音器52連接。 動力傳達裝置T包括：皮帶式的連續變速機5 3，係自動 且無級地改變從曲柄軸1 2輸出的動力；減速齒輪組5 4， 係減小該連續變速機5 3的輸出；以及鏈條式傳動機構5 5， 係設置於減速齒輪列5 4和後輪W R的車軸1 8之間。 該動力傳達裝置T所具有的變速機箱5 6由外殼主體 5 7、右側殼體5 8和左側殼體5 9構成，該外殼主體5 7 —體 配置於曲柄軸箱1 4的殼體左半部1 9和殼體右半部2 0，前 部配置於向後方延伸的箱支承部1 4 a的右側、後部配置於 後輪WR的左侧而沿前後延伸，該右側殼體58覆蓋該外殼 主體5 7的前半部右側，與外殼主體5 7連接，該左側殼體 13 312/發明說明書(補件)/93-05/93105275 200424424 5 9覆蓋外殼主體5 7的後半部左側，與外殼主體5 Ί 外殼主體5 7的前部與曲柄軸箱1 4的箱支承部1 4 a 在外殼主體5 7的前半部和右側殼體5 8之間，形 速機室6 0，在外殼主體5 7的後半部和左側殼體5 £ 形成有齒輪室61。 連續變速機5 3收納於變速機室6 0内，其包括：： 輪軸6 2，係在與曲柄軸1 2的軸線相垂直的平面内 於與該曲柄軸1 2間隔開的位置，其軸線與曲柄軸 行；從動帶輪軸6 3，其軸線與該主動帶輪軸6 2平 動帶輪6 4，係安裝於主動帶輪軸6 2上；從動帶輪 安裝於從動帶輪軸6 3上；迴圈狀的V形皮帶6 6， 於從動帶輪6 4和從動帶輪6 5上。 主動帶輪軸6 2配置於曲柄軸1 2的後方，該主動 6 2的一端部以可旋轉的方式支承於設於曲柄軸箱1 體左半部1 9的一端側軸承部6 7上，主動帶輪軸6 2 部係以可旋轉的方式支承於設於曲柄軸箱1 4的殼骨 部2 0上的中間軸承部6 8上，該主動帶輪軸6 2的另 以可旋轉的方式支承於設於變速箱體5 6的右側殼骨 的另一端側軸承部6 9上。另夕卜，中間軸承部6 8呈 沿曲柄軸1 2的第2曲柄垂重部2 5的外周所形成的 跡的形狀，S己置於曲柄軸箱1 4的殼體右半部2 0上 在曲柄軸1 2和主動帶輪軸6 2之間設置有傳動齒 7 0，該傳動齒輪組7 0在第1曲柄垂重部2 4的外方 左側曲柄軸頸部2 2的内方，配置於左側曲柄軸頸奇 312/發明說明書(補件)/93-05/93105275 7連接， 緊固。 成有變 丨之間， t動帶 ，配置 1 2相平 行；主 6 5，係 係捲繞 帶輪軸 4的殼 的中間 I右半 一端部 ! 58上 其局部 旋轉軌 〇 輪組 ，位於 ^ 22的 14 200424424 外方的發電機3 0則配置於傳動齒輪組7 0的外方。 上述傳動齒輪組7 0由主動齒輪7 1和從動齒輪7 2構成， 該主動齒輪7 1固定於曲柄軸1 2上，該從動齒輪7 2固定於 主動帶輪軸6 2上並與主動齒輪7 1嚙合，其按照與主動相 互嚙合的輔助齒輪7 3可相對於主動齒輪7 2旋轉的方式安 裝於主動帶輪軸6 2上，以便抑制相互嚙合之主動齒輪7 1 和從動齒輪7 2的嚙合部的齒隙造成的異常聲音的發生，在 從動齒輪7 2和輔助齒輪7 3之間，設置有彈簧（圖中未示 出），該彈簧施加使兩個齒輪7 2、7 3相對旋轉的方向的彈 力。 在上述一端側軸承部6 7上，開設使主動帶輪軸6 2的一 端部以可旋轉的方式穿過之軸承孔74，在該軸承孔74的 内面和主動帶輪軸6 2的外面之間，夾設有球軸承7 5。另 外，在上述中間軸承部6 8上，以與上述軸承孔7 4同軸的 方式配置使主動帶輪軸62的軸向中間部可旋轉地穿過之 軸承孔7 6，在軸承孔7 6的内面和主動帶輪軸6 2的外面之 間，夾設有球軸承7 7和環狀的密封構件7 8。另外，在上 述另一端側軸承部6 9上，以與上述各軸承孔7 4、7 6同軸 的方式配置使主動帶輪轴6 2的另一端部插入之有底的車由 承孔7 9，球軸承8 0則介裝於軸承孔7 9的内面和主動帶輪 軸62的夕卜面之間。 像這樣，在傳動齒輪組70的兩側，以兩側懸臂的方式 支承主動帶輪軸6 2，藉此可減輕中間軸承部6 8的負荷， 並使中間軸承部6 8儘量小型化而從第2曲柄垂重部2 5側 15 312/發明說明書(補件)/93-05/93】05275 200424424 接近主動帶輪軸6 8，且更進一步地縮短動力單元P的前後 長度，可進一步縮短軸距。 主動帶輪6 4由主動側固定帶輪半體8 4和主動側活動帶 輪半部體85構成，該主動側固定帶輪半體84固定於主動 輪軸6 2的另一端部，而該主動側活動帶輪半體8 5可相對 於主動側固定帶輪半體84接近·離開，並以可滑動的方式 支承於主動帶輪軸6 2上，主動帶輪軸6 2配置於從側面看 時主動帶輪64的一部分與曲柄軸12的第1和第2曲柄垂 重部2 4、2 5的外周所形成的旋轉執跡重疊的位置。 此外，上述主動側活動帶輪半體8 5經由帶輪驅動機構 8 6沿著軸方向驅動，該帶輪驅動機構8 6在捲繞有上述凸 輪鏈條46F、46R的驅動鏈輪44F、44R上，配置於沿上述 曲柄軸1 2的軸線的方向相對應的位置而在主動側活動帶 輪半體8 5和上述中間軸承部6 8之間配置有上述帶輪驅動 機構8 6。 在球軸承7 7之内圈和主動側固定帶輪半體8 4之間，主 動帶輪軸62上安裝有圍繞該主動帶輪軸62的圓筒狀的套 筒8 7，而主動側活動帶輪半體8 5係以可於軸方向滑動的 方式支承於該套筒87上。 上述帶輪驅動機構8 6包括：螺桿8 8，係形成為呈圍繞上 述套筒87的圓筒狀，固定於變速箱體56的外殼主體57 上；螺帽8 9係與該螺桿8 8螺合；從動齒輪9 0，係一體形 成於螺帽8 9的外周；主動小齒輪9 2，係設置於支承在變 速箱體5 6的外殼主體5 7上的電動馬達9 1 (參照圖2 )的 16 312/發明說明書(補件)/93-05/93105275 200424424 輸出軸上；減速齒輪機構9 3，係減小電動馬達9 1的旋轉 動力，將其從主動小齒輪9 2傳達給從動齒輪9 0，並設置 於主動小齒輪9 2和從動齒輪9 0之間。 如果採用此種帶輪驅動機構8 6，便可對應於電動馬達 9 1的動作而使螺帽8 9於主動帶輪軸6 2的軸方向進退動 作。另外，螺帽8 9係透過球軸承9 4而與主動側活動帶輪 半體8 5連接，並對應於螺帽8 9的上述進退動作而使主動 側活動帶輪半體8 5於主動帶輪軸6 2的軸方向滑動。 如此，從側面看時配置於使主動帶輪6 4的一部分與發 電機3 0重疊的位置的主動帶輪軸6 2的中間部，係以可旋 轉的方式支承設置於曲柄軸箱1 4的中間軸承部6 8上，中 間軸承部6 8的一部分形成為沿曲柄軸1 2所具有的第1和 第2曲柄垂重部2 5的外周所形成的旋轉軌跡的形狀，沿著 從動帶輪軸6 3而以滑動方式驅動固定於主動帶輪軸6 2的 主動側固定帶輪軸84及構成主動帶輪64的主動側活動帶 輪8 5的帶輪驅動機構8 6 ’係沿曲柄轴1 2的轴方向配置於 與驅動鏈輪44F、44R相對應的位置，因此，主動帶輪64 可以其一部分從側面看為與發電機3 0重疊的方式接近曲 柄軸1 2側，其結果是，可縮短動力單元P的前後長度，進 而可縮短軸距。 從動帶輪軸6 3的一端部係以可旋轉的方式穿過外殼主 體5 7，並突入齒輪室6 1中，外殼主體5 7和從動帶輪軸6 3 之間則介裝有球軸承9 5。另外，從動帶輪軸6 3的另一端 部係透過球軸承9 6，以可旋轉的方式支承於右側殼體5 8 17 312/發明說明書(補件)/93-05/93105275 200424424 上。 從動帶輪6 5由從動側固定帶輪半體9 7和 輪半體9 8構成，該從動側固定帶輪半體9 7 位置是一定的方式而可相對旋轉地支承於從 上，該從動側活動帶輪半體9 8可相對於從動 體9 7接近·離開，以可滑動並且可相對旋轉 從動側固定帶輪半體9 7上，同時朝向從動側 9 7而彈性地逼迫。 在從動側固定帶輪半體9 7上，一體地配1 並同軸地圍繞從動帶輪軸6 3之圓筒狀的導ϊ 速箱體5 6中的右側殼體5 8側，與上述從動 體9 7面對的從動側活動帶輪半體9 8係以可 承於上述導向部97a。此外，在固定於上述 右側殼體5 8側的端部的彈簧接納構件9 9和 輪半體9 8之間，設置有彈簧1 0 0，該彈簧1 動帶輪半體9 8朝向從動側固定帶輪半體9 7 在上述從動側固定帶輪半體9 7的導向部 輪軸6 3之間，配置有離心離合器1 0 1，對應 固定帶輪半體9 7繞從動帶輪軸6 3的軸線而 的旋轉次數旋轉的情況，將從動帶輪6 5的旋 從動帶輪軸6 3。 減速齒輪組5 4係以使來自上述從動帶輪』 旋轉動力經過中間軸1 0 2而向輸出軸1 0 3減 方式構成，其收納於齒輪室6 1的内部，中間 312/發明說明書(補件)/93-05/93105275 從動侧活動帶 以軸線方向的 動帶輪軸6 3 側固定帶輪半 的方式支承於 固定帶輪半體 L可相對旋轉， 与部9 7 a，從變 側固定帶輪半 滑動的方式支 導向部97a的 從動側活動帶 0 0將從動側活 側逼迫。 9 7 a和從動帶 於上述從動側 以規定值以上 轉動力傳達給 降6 3的一端的 小同時傳達的 軸1 0 2和輸出 18 200424424 軸1 0 3以可旋轉的方式支承於外殼主體5 7和左侧殼體5 9 上，輸出軸1 0 3的一端從左側殼體5 9突出。 在鏈條式傳動機構5 5中，迴圈狀的鏈條1 0 7捲繞於驅 動鏈輪1 0 5和從動鏈輪1 0 6上，該驅動鏈輪1 0 5固定於與 上述輸出軸1 0 3以同軸並以無法相對旋轉的方式連接的驅 動軸1 0 4上，該從動鏈輪1 0 6固定於後輪W R的車軸1 8上， 該鏈條式傳動機構5 5收納於設於後輪W R的左側的鏈條外 殼1 0 8中。 在左側殼體5 9上，緊固有圓筒狀的支承軸1 0 9，該支承 軸1 0 9圍繞上述輸出軸1 0 3的左側殼體5 9的突出部，上述 鏈條外殼1 0 8的前部以可透過徑向軸承1 1 0而擺動的方式 支承。此外，驅動軸1 0 4以可透過球軸承1 1 1、1 1 1旋轉的 方式支承於鏈條外殼1 0 7上。 另一方面，在變速箱體5 6的外殼主體5 7上，以可透過 徑向軸承1 1 3而擺動的方式支承與上述輸出軸1 〇 3和驅動 軸1 0 4同軸之擺動軸1 1 2，並配置於後輪W R的右側，沿前 後延伸的臂1 1 4的前部係固定於上述擺動軸1 1 2上。另外， 後輪W R的車軸1 8以可擺動的方式支承於鏈條外殼1 〇 8的 後部和上述臂1 1 4的後部之間。 但是，由於在皮帶式連續變速機5 3的從動帶輪6 5上， 從動側活動帶輪半體9 8係從外方與從動側固定帶輪半體 9 7面對，並相對從動側固定帶輪半體9 7而接近·離開， 因此，屬於變速箱體5 6的外面側的右側殼體5 8形成為其 後部在前部的外側方突起的形狀。即，在右側殼體58中， 19 312/發明說明書(補件)/93-05/93105275 200424424 形成有低位部5 8 a，該低位部5 8 a覆蓋主動帶輪6 4 ;以及 高位部5 8 b，該高位部5 8 b覆蓋從動帶輪6 5，在低位部5 8 a 的外側方突起，同時與上述低位部5 8 a的後部連接。 在上述主動帶輪軸6 2的周圍，在上述低位部5 8 a設有 多個之與變速機室60連通之通孔115…，在主動帶輪64 中的主動側固定帶輪半體84中，一體形成有將空氣從上述 各通孔1 1 5…吸引到變速機室6 0内之多個葉片8 4 a…。即， 主動側固定帶輪半體8 4亦有作為風扇的功能。 在變速箱體5 6的右側殼體5 8上，安裝有覆蓋低位部5 8 a 的空氣導入罩116，空氣導入通路117形成於空氣導入罩 1 1 6和低位部5 8 a之間，該空氣導入通路1 1 7與上述各通 孔1 1 5…連通，並且面對上述高位部5 8 b的前端部側面而 開口。 此外，在高位部5 8 b的前部内，以與變速機室6 0的内 部連通的方式形成有空氣排氣通路118，該空氣排氣通路 118對應上述空氣導入通路117的開口端而形成為圓弧 狀，該空氣排氣通路118在上述空氣導入孔117的後方， 朝向下方而開放。 而且，藉由對應於主動側固定帶輪半體84的旋轉，從 空氣導入通路1 1 7經過通孔1 1 5…而導入到變速機室6 0中 的空氣，對無機變速機5 3進行冷卻，冷卻後的空氣從變速 機室6 0經過空氣排氣通路1 1 8，排到變速箱體5 6的外部。 在曲柄軸箱1 4的内部，按照透過配置於曲柄軸箱1 4中 的間隔壁14b而相互分隔的方式’形成曲柄轴室124與油 20200424424 发明 Description of the invention: [Technical field to which the invention belongs] The present invention relates to a cam engine with a cylinder head, in which a gas valve and an exhaust valve are arranged on the cylinder head of a part of the engine body in an openable and closable manner. A first cam is arranged to be urged in a direction in which the intake-side and exhaust-side valve springs are rotatably supported on a cylinder head disposed between the intake-side and exhaust-side valve springs. And a cam, the first cam is used to drive one of the intake valve and the exhaust valve, and the second cam is used to drive the other of the intake valve and the exhaust valve. [Prior Art] For example, in a cam-type engine with a cylinder head described in Patent Document 1, etc., in order to secure a space for placing a spark plug, a cam shaft system disposed between an intake valve and a row is biased from the cylinder axis One side of the suction valve and the exhaust valve. (Patent Document 1) Japanese Patent Laid-Open Publication No. 5 9 — 2 5 8 6 1 [Summary of the Invention] (Problems to be Solved by the Invention) However, in the conventional technology described above, due to the necessity of the intake valve and the exhaust valve, The formed valve angle is large, which is not conducive to the space saving of the combustion chamber and the enlargement of the cylinder head. The present invention has been made in view of the above problems, and an object thereof is to provide a cam-type engine with a cylinder head, which can save space in a combustion chamber and reduce the size of a cover. 312 / Invention Manual (Supplement) / 93-05 / 93105275 It is equipped with a suction and closing valve and can be the second, the valve stem of its valve, the guide cylinder 6 200424424 (means for solving the problem) In order to achieve the above purpose In order to apply for a cam-type engine with a cylinder head, the cylinder head has an openable and closable valve and an exhaust system that are driven in a spiral suction direction. It is arranged in the suction room and is rotatably supported. The first cam and the second cam, one of the exhaust valve and the other of the second convex, the camshaft on the cylinder head is arranged approximately on the cylinder head with its axis, and is arranged on the intake cam system The position where the direction of the axis of the camshaft of the first cam is deviated from above. According to this structure, interference between the first valve side spring can be avoided, and the same included angle can be set to be small, so that the compression ratio can be made, and at the same time, the cylinder head can be made convex and the cylinder head can be miniaturized. In addition, the two sides of the structural shaft of the invention of the second patent scope and the first patent scope of the patent application, the air valve and the exhaust valve along the camshaft are the first invention of the patent scope which can be opened and closed as one An intake valve and an exhaust valve are disposed as a part of the engine body, and the intake and exhaust valve springs are arranged on a closed valve side valve spring and an exhaust valve spring on a camshaft of the cylinder head. 1 The cam system is used to drive the intake valve and the exhaust valve to drive the intake valve and the exhaust valve. The wheel-type engine is characterized in that the convex cylinder axis is supported on the first side between the above-mentioned side and the exhaust-side valve spring. 2. The first cam is arranged in the valve rod combustion chamber of the intake valve and the exhaust valve when the first cam and the second cam along the intake side and the exhaust valve spring are arranged between the intake and exhaust valve springs. Space-saving and space-saving valve actuator with higher axles. In addition to the above-mentioned application, the invention is also characterized in that a pair of suctions arranged side by side in the direction of the cam axis is arranged in the above. On the cylinder head; 312 / Invention Manual (Supplement) / 93-05 / 93105275 7 200424424 According to this structure, in a cam valve engine with a 4-valve cylinder head, space saving of the combustion chamber can be achieved, a high compression ratio can be obtained, and a valve operating device having a camshaft can be space-saving, further Obtained miniaturization of the cylinder head. The invention in the third scope of the patent application, in addition to the structure of the invention in the first or second scope of the patent application, is also characterized in that the main engine system including the cylinder head is such that the cylinder axis is inclined upward and forward, and The axis of the crankshaft is in a horizontal posture, and is mounted on the body frame behind the front wheels of the small vehicle. The first rocker arm, which is linked to one of the first and second cams, is rotatably supported parallel to the A second rocker arm linked to the other of the first and second cams on a first swing axis of the axis of the camshaft is swingably supported by an axis parallel to the camshaft and provided at On the second swing axis behind the first swing axis, the distance between the second swing axis and the crank shaft is set smaller than the distance between the first swing axis and the crank shaft; according to this structure, even the cylinder axis Inclined towards the front and forward, the distance from the crankshaft to the lower part of the front end of the engine body can still be minimized, interference with the front wheels can be avoided, and the engine body can be approached to the front wheel side, which helps to reduce the Wheelbase of the vehicle (w h e e 1 base), or front-wheel wheel travel (wheel stroke) can be set longer. The invention in the fourth scope of the patent application, in addition to the structure of the invention in the third scope of the patent application, is also characterized in that the first rocker arm is pivotally supported by a roller in rolling contact with the first cam. A roller is provided on the second rocker arm with a cam slider that is in sliding contact with the second cam. According to this structure, it is possible to avoid the cam slider with a small arrangement space and the cam slider from being arranged on the suction side and the exhaust side. The second cam sliding contact between the gas-side valve spring and 8 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 increases the angle between the valve stems of the intake valve and the exhaust valve to obtain the cylinder head. The miniaturization is arranged at a position deviated from the valve spring between the intake side and the exhaust side, so that the roller having a large arrangement space is brought into rolling contact with the first cam that does not affect the included angle. It can help reduce the friction loss of the valve device. The inventions in the scope of patent applications Nos. 5 and 6 are in addition to the structure of the inventions in the scope of patent applications No. 3 or 4 above. They are also characterized by a front cylinder side body with a cylinder axis inclined upward and forward ( fr ο ntbank), and a V-shaped engine main body of the rear cylinder side (rear bank) of the cylinder axis that crosses the cylinder axis in a V-shape as viewed from the side; according to this structure, it is possible to avoid At the same time of interference, the front cylinder head of the engine body is brought closer to the front wheel side, thereby avoiding an increase in the wheelbase of a small vehicle or a shortened wheel travel of the front wheels, and at the same time, placing the engine body in a lower position as much as possible. Large space for other parts can be kept above the engine body, and the south of the driver's seat can be reduced. [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 11 show an embodiment of the present invention, FIG. 1 is a side view of a motorcycle, FIG. 2 is a side view of a cutaway part of a power unit viewed from the same direction as FIG. 1, and FIG. 3 is a view taken along FIG. 2. 4 is a cross-sectional view taken along line 3—3 in FIG. 3, FIG. 4 is a cross-sectional view taken along line 4-4 in FIG. 3, FIG. 5 is an arrow view taken along line 5-5 in FIG. 4, and FIG. 6 is a state in which the swing arm is omitted. 9 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 corresponding to FIG. 5, FIG. 7 is a sectional view taken along line 7-7 in FIG. 5, and FIG. 8 is taken along 8-8 in FIG. 9 is a cross-sectional view taken along line 9-9 in FIG. 4, FIG. 10 is an arrow view taken along line 10-10 in FIG. 4, and FIG. 11 is taken along arrow 1 in FIG. Arrow view. First, in FIG. 1, a body frame 11 of a motorcycle belonging to a small vehicle is loaded with a power unit P disposed between a front wheel WF and a rear wheel WR. The power unit P is a 4-cycle 2-cylinder cylinder. Is composed of an engine E and a power transmission device T disposed between the engine E and the axle 18 of the rear wheel WR. Referring to FIG. 2 to FIG. 4 together, the engine body 13 of the above-mentioned engine E is V-shaped and includes a crankshaft box 14 which rotatably supports a horizontal axis extending in the left-right direction of the frame 11 Crank shaft 12; front cylinder side body FB, which tilts the cylinder axis CF toward the front and upwards, and is connected to the above crankshaft box 1 4; and rear cylinder side body RB, which is V-shaped when viewed from the side. The cylinder axis CF intersects, and the cylinder axis CR is inclined toward the rear and upward to be connected to the crank case 14; the two cylinder side bodies FB and RB are respectively configured as a valve with a cylinder head. The front cylinder side body FB includes a front cylinder block 1 5 F connected to the above crankshaft box 14, a front cylinder head 16 F connected to the front cylinder block 15 F, and a front cylinder block 1 5 The opposite side of F is connected to the front cylinder head 1 6 F and the front head cover 1 7 F. The rear cylinder side body RB includes the rear cylinder block 1 4 R and the rear cylinder block 1 5 R. The rear cylinder head 16 R and the rear head cover 17R are connected to the rear cylinder head 16R on the opposite side to the rear cylinder block 15R. The crank case 1 4 is formed by connecting the left half 19 of the housing and the right half 20 of the housing 10 to each other 10 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424, the left half of the housing 1 9 is arranged on the left when facing forward in the direction of travel of the motorcycle, and the right half portion 20 of the housing is arranged on the right when facing forward in the direction of travel of the motorcycle. The cylinder axes CF and CR of the front and rear cylinder side bodies FB and RB are connected to each other by parallel connection surfaces 21. One end portion of the crank shaft 12 penetrates the left crank shaft neck portion 22 provided in the left half portion 19 of the housing, and is rotatably supported on the crank shaft neck portion 22, and the other end of the crank shaft 12 The portion penetrates the right crank journal portion 23 provided on the right half portion 20 of the housing, and is rotatably supported on the crank journal portion 23. The crankshaft 12 includes a first crank weight portion 24 disposed inside the left crank journal portion 22 and a second crank weight portion 25 disposed inside the right crank journal portion 23, and the connecting rod 2 The large end of the 8 F is connected to the crank pin 2 9 in a rotatable manner with the large end of the connecting rod 2 8 F. The connecting rod 2 8 F is slidably connected to the front cylinder block 1 5 F 2 6 F is fitted with a piston 2 7 F fitted with a piston 2 7 F. The connecting rod 2 8 R is slidably fitted with a piston 2 6 R fitted with a cylinder 2 1 R arranged at the rear. 2 7 R R connection, the crank pin 2 9 connects the first and second crank weights 24 and 25 and is arranged on the crank shaft 12. The rear cylinder block 1 5 R is arranged from the front cylinder block 1 5 F to one end side along the axis of the crank shaft 12. The large ends of the two connecting rods 2 8 F and 2 8 R are the front cylinders. The link 2 8 F on the side of the body 1 5 F is arranged close to the second crank weight 2 5, and the link 2 8 R on the rear side of the cylinder block 1 5 R is arranged close to the first crank weight 24. The first and second crank weights 24, 25 11 312 / Invention Specification (Supplement) / 93-05 / 93 丨 05275 200424424 are connected to the crank pin 29. A generator shaft 30 is attached to one end of the crank shaft 12 protruding from the left crank shaft neck 22, and the generator 30 is composed of a rotor 31 fixed to one end of the crank shaft 12 and accommodated in the rotor. The stator 3 2 is composed of 31. The generator 30 is covered by a left hood 3 3 connected to the left half 19 of the housing of the crankcase 14, and the stator 32 is fixed to the left hood 33. A driven gear 35 is arranged between the left crank journal 22 and the generator 30. The driven gear 35 surrounds the crank shaft 12 in a coaxial manner, and the passive gear 3 5 passes through the one-way clutch 3 4 The rotor 31 is connected to the generator 30. In addition, a starter motor 3 6 having a rotation axis parallel to the crank shaft 12 is located between the front and rear cylinder blocks 1 5 F and 1 5 R, and is supported on the top of the crank case 14. The output shaft of 6 is provided with a driving pinion 3 7. On the other hand, between the left half 19 of the housing of the crankcase 14 and the left hood 33, the first and second intermediate gears 3 8, 3, 9 and the third intermediate gear 40 are integrally formed. The driving pinion 37 is supported so as to be rotatable about an axis parallel to the crank shaft 12. The above-mentioned driving pinion 37 is meshed with the first intermediate gear 38 having a diameter larger than the driving pinion 37, and the first The 2 intermediate gear 3 9 meshes with a third intermediate gear 40, and the diameter of the third intermediate gear 40 is larger than the second intermediate gear 39 and meshes with the driven gear 3 5. Therefore, by starting the starter motor 36 when the engine E is started, the driving force from the starter motor 36 is reduced and transmitted to the crankshaft 12. In addition, after the engine E is started, there is no one-way clutch. The role of 34 transmits the power of the crankshaft 12 to the starter motor 36 side. At the other end of the crank shaft 12 protruding from the right crank shaft neck 23, 12 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 is fixed to a pair of integrally formed drive sprocket 4 4 F, 4 4 R, a cam chain 4 6 F is wound on one of the driving sprocket 4 4 F, and the cam chain 4 6 F is used to drive a valve actuating device 4 5 F arranged in the front cylinder head 1 6 F, On the other driving sprocket 4 4 R, a cam chain 4 6 R is wound. The cam chain 4 6 R is used to drive a valve actuating device 4 5 R arranged at the rear cylinder head 16 R. In addition, a right hood 4 7 covering the other end portion of the crankshaft 12 is connected to a right half 20 of a housing of the crankcase 12. In FIG. 1, an air cleaner 4 8 disposed diagonally above the front of the engine E is mounted on the vehicle body frame 11, and a fuel tank 4 9 disposed above the air cleaner 4 8 is mounted on the vehicle body frame. At 11, the front and rear cylinder heads 16F and 16R are connected to the air cleaner 48 through the respective suction pipes 50F and 50R. In addition, the exhaust pipes 5 1 F and 5 1 R that guide the exhaust gas discharged from the front and rear cylinder heads 16 F and 16 R are connected in common to an exhaust muffler 52 disposed on the right side of the rear wheel WR. . The power transmission device T includes: a belt-type continuous transmission 5 3 that automatically and steplessly changes the power output from the crank shaft 12; a reduction gear set 54 that reduces the output of the continuous transmission 5 3; and The chain transmission mechanism 5 5 is arranged between the reduction gear train 54 and the axles 18 of the rear wheel WR. The transmission case 5 6 of the power transmission device T is composed of a case main body 5 7, a right case 5 8 and a left case 5 9. The case main body 5 7 is arranged in the left half of the case of the crank case 14. The front part 19 and the right half part 20 of the housing are arranged on the right side of the box support part 14a extending rearward, and the rear part is arranged on the left side of the rear wheel WR to extend forward and backward. The right housing 58 covers the The right side of the front half of the case main body 5 7 is connected to the case main body 5 7, and the left side case 13 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 5 9 covers the left side of the rear half of the case main body 5 7 and the case The main body 5 Ί The front part of the case main body 5 7 and the box support part 14 of the crank case 14 are located between the front half of the case main body 5 7 and the right case 5 8, and the speed machine room 60 is located in the case main body. The rear half of 5 7 and the left case 5 £ form a gear chamber 61. The continuous transmission 53 is housed in the transmission room 60, and includes: a wheel shaft 62, which is in a plane perpendicular to the axis of the crank shaft 12 at a position spaced from the crank shaft 12 and its axis Driven with the crank shaft; the driven pulley shaft 6 3, the axis of which is parallel to the driving pulley shaft 6 2 and the translation pulley 6 4 is mounted on the driving pulley shaft 6 2; the driven pulley is installed on the driven pulley shaft 6 3 The loop-shaped V-belt 6 6 is on the driven pulley 64 and the driven pulley 65. The driving pulley shaft 62 is arranged behind the crank shaft 12. One end of the driving pulley 62 is rotatably supported on an end-side bearing portion 6 7 provided on the left half 19 of the crank case 1 body. The pulley shaft 6 2 is rotatably supported by an intermediate bearing portion 6 8 provided on the shell bone portion 20 of the crank shaft box 14. The active pulley shaft 6 2 is rotatably supported by It is provided on the other end side bearing portion 69 of the right side shell of the transmission case 56. In addition, the intermediate bearing portion 68 has a shape formed along the periphery of the second crank weight portion 25 of the crankshaft 12, and S has been placed in the right half of the housing 20 of the crankshaft box 14. Transmission gears 70 are provided between the crankshaft 12 and the driving pulley shaft 62, and the transmission gear set 70 is inward of the left crankshaft neck 22 of the outer side of the first crank weight 24, It is arranged on the left crank journal 312 / Invention Manual (Supplement) / 93-05 / 93105275 7 connection and tightening. Between changes, t moving belts, configuration 1 and 2 are parallel; the main 65, 5 is the middle I right half of the shell of the winding wheel shaft 4! 58 on its local rotating track 0 wheel set, located at ^ 22 of 14 200424424 The generator 3 0 on the outside is arranged outside the transmission gear set 70. The above-mentioned transmission gear set 70 is composed of a driving gear 71 and a driven gear 72, the driving gear 71 is fixed on the crank shaft 12 and the driven gear 7 2 is fixed on the driving pulley shaft 62 and connected with the driving gear 7 1 meshes, and is mounted on the driving pulley shaft 6 2 in such a manner that the auxiliary gear 7 3 that is engaged with the driving gear can rotate relative to the driving gear 7 2 so as to suppress the meshing of the driving gear 7 1 and the driven gear 7 2 with each other. An abnormal sound caused by the backlash of the meshing portion occurs. Between the driven gear 72 and the auxiliary gear 73, a spring (not shown in the figure) is provided, and the spring is applied to make the two gears 7 2, 7 3 oppose each other. Elasticity in the direction of rotation. A bearing hole 74 through which one end portion of the driving pulley shaft 62 is rotatably passed is formed on the one end side bearing portion 67, between the inner surface of the bearing hole 74 and the outer surface of the driving pulley shaft 62, Clamped with ball bearings 7 5. Further, a bearing hole 76 is provided on the intermediate bearing portion 68 so as to be coaxial with the bearing hole 74, so that the axial middle portion of the driving pulley shaft 62 can be rotatably passed through the bearing hole 76. A ball bearing 7 7 and an annular sealing member 78 are interposed between the outer surface of the driving pulley shaft 62 and the outer surface of the driving pulley shaft 62. In addition, a bottomed car receiving hole 7 9 is disposed on the other end side bearing portion 6 9 so as to be coaxial with each of the bearing holes 7 4 and 7 6 and the other end portion of the driving pulley shaft 62 is inserted therein. The ball bearing 80 is interposed between the inner surface of the bearing hole 79 and the surface of the driving pulley shaft 62. In this way, the drive pulley shaft 62 is supported on both sides of the transmission gear set 70 in a cantilever manner on both sides, thereby reducing the load on the intermediate bearing portion 68 and miniaturizing the intermediate bearing portion 68 as much as possible. 2Crank weight 2 5 Side 15 312 / Invention Manual (Supplement) / 93-05 / 93] 05275 200424424 Close to the driving pulley shaft 6 8 and further shorten the front and rear length of the power unit P, which can further shorten the wheelbase . The active pulley 64 is composed of an active side fixed pulley half 84 and an active side movable pulley half 85. The active side fixed pulley half 84 is fixed to the other end of the active pulley shaft 62, and the active The side movable pulley half 8 5 can approach and leave relative to the active side fixed pulley half 84 and is slidably supported on the active pulley shaft 6 2. The active pulley shaft 6 2 is configured to be active when viewed from the side. A portion of the pulley 64 overlaps with the rotation track formed by the outer circumferences of the first and second crank weights 24 and 25 of the crank shaft 12. In addition, the active-side movable pulley half 85 is driven in the axial direction via a pulley drive mechanism 86, and the pulley drive mechanism 86 is provided on the drive sprocket 44F, 44R around which the cam chains 46F, 46R are wound. The pulley driving mechanism 86 is arranged at a position corresponding to the direction of the axis of the crankshaft 12 and between the driving-side movable pulley half 85 and the intermediate bearing portion 68. Between the inner ring of the ball bearing 7 7 and the driving-side fixed pulley half 8 4, a cylindrical sleeve 8 7 surrounding the driving pulley shaft 62 is mounted on the driving pulley shaft 62, and the active-side movable pulley The half body 85 is supported on the sleeve 87 so as to be slidable in the axial direction. The above-mentioned pulley driving mechanism 88 includes a screw 8 8 formed in a cylindrical shape surrounding the sleeve 87 and fixed to a housing body 57 of the transmission case 56; and a nut 8 9 is screwed with the screw 8 8 The driven gear 90 is integrally formed on the outer periphery of the nut 8 9; the driving pinion 9 2 is an electric motor 9 1 (see FIG. 2) supported on the housing body 5 7 of the transmission case 5 6 ) 16 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 on the output shaft; reduction gear mechanism 9 3, which reduces the rotating power of the electric motor 91 1 and transmits it from the driving pinion 9 2 to the slave The driving gear 90 is disposed between the driving pinion 92 and the driven gear 90. If such a pulley driving mechanism 8 6 is used, the nut 8 9 can be moved forward and backward in the axial direction of the active pulley shaft 62 in accordance with the operation of the electric motor 91. In addition, the nut 8 9 is connected to the active side movable pulley half 8 5 through a ball bearing 9 4, and corresponds to the above-mentioned forward and backward movement of the nut 8 9 to make the active side movable pulley half 8 5 on the active belt. The axle 62 slides in the axial direction. In this way, when viewed from the side, the middle portion of the drive pulley shaft 62 arranged at a position where a part of the drive pulley 64 overlaps with the generator 30 is rotatably supported in the middle of the crank shaft box 14 In the bearing portion 68, a part of the intermediate bearing portion 68 is formed in a shape along a rotation trajectory formed along the outer periphery of the first and second crank weight portions 25 of the crank shaft 12 and along the driven pulley shaft 6 3 The driving side fixed pulley shaft 84 which is driven and fixed to the driving pulley shaft 6 2 and the active side movable pulley 8 which constitutes the driving pulley 64 is driven in a sliding manner 8 6 ′ along the crank shaft 1 2 The shaft direction is arranged at a position corresponding to the drive sprocket 44F, 44R. Therefore, the drive pulley 64 can approach the crankshaft 12 side so that a part of the drive pulley 64 overlaps the generator 30 as viewed from the side. The front and rear length of the power unit P can further shorten the wheelbase. One end of the driven pulley shaft 6 3 is rotatably passed through the housing body 5 7 and protrudes into the gear chamber 61. A ball bearing 9 is interposed between the housing body 5 7 and the driven pulley shaft 6 3. 5. In addition, the other end portion of the driven pulley shaft 63 is rotatably supported on the right case 5 8 17 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 through a ball bearing 9 6. The driven pulley 65 is composed of a driven-side fixed pulley half 9 7 and a wheel half 9 8. The driven-side fixed pulley half 9 7 is fixed in position and is rotatably supported from above. The driven side movable pulley half 9 8 can approach and leave relative to the driven body 9 7, and can be slidably and relatively rotated to fix the pulley half 9 7 on the driven side while facing the driven side 9 7 And persecution elastically. On the driven side fixed pulley half body 9 7, a cylindrical guide member 1 is integrally arranged and coaxially surrounds the driven pulley shaft 63. The right housing 5 8 side of the speed box 5 6 is the same as the above. The driven-side movable pulley half body 98 facing the driven body 97 is supported by the guide portion 97a. In addition, a spring 100 is provided between the spring receiving member 9 9 and the wheel half 98 that are fixed to the end of the right-side case 58 side, and the spring 1 moves the pulley half 98 to the driven. Side fixed pulley half 9 7 A centrifugal clutch 1 0 1 is arranged between the guide shaft 6 6 of the driven side fixed pulley half 9 7, and the corresponding fixed pulley half 9 7 is wound around the driven pulley shaft. When the number of rotations of the axis of 63 is rotated, the rotation of the driven pulley 65 is driven by the driven pulley shaft 63. The reduction gear set 5 4 is configured to reduce the rotation power from the driven pulley ′ through the intermediate shaft 1 2 and reduce it to the output shaft 1 0 3. It is housed inside the gear chamber 61 and intermediate 312 / invention specification ( (Supplement) / 93-05 / 93105275 The driven side movable belt is supported on the fixed pulley half L by the moving pulley shaft 6 in the axial direction on the fixed pulley half, which can be relatively rotated, and the part 9 7 a, changing from The side fixed pulley supports the driven side movable belt 0 0 of the guide portion 97a in a semi-sliding manner to be forced on the driven side. 9 7 a and the driven belt on the driven side are transmitted to the lower side of the lower end of the lower 6 3 with a rotational force greater than a specified value. The shaft 1 0 2 and the output 18 200424424 shaft 1 0 3 are rotatably supported on the housing. On the main body 5 7 and the left case 5 9, one end of the output shaft 103 is protruded from the left case 5 9. In the chain transmission mechanism 5 5, a loop-shaped chain 1 7 is wound around a driving sprocket 105 and a driven sprocket 10 6. The driving sprocket 1 0 5 is fixed to the output shaft 1. 0 3 is coaxial with the drive shaft 1 0 4 which can not be relatively rotated, the driven sprocket 1 06 is fixed on the axle 18 of the rear wheel WR, and the chain transmission mechanism 5 5 is housed in The chain housing on the left side of the rear wheel WR is in 108. A cylindrical support shaft 1 0 9 is fastened to the left case 5 9, and the support shaft 10 9 surrounds the protrusion of the left case 5 9 of the output shaft 10 3, and the chain housing 1 0 8 The front portion is supported so as to be swingable by a radial bearing 110. In addition, the drive shaft 104 is supported on the chain housing 107 by a ball bearing 1 1 1 and 1 1 1 so as to be rotatable. On the other hand, a casing main body 57 of the transmission case 56 supports a swing shaft 1 1 coaxial with the output shaft 1 0 3 and the drive shaft 1 0 4 so as to be swingable through a radial bearing 1 1 3. 2, and is arranged on the right side of the rear wheel WR, and the front part of the arms 1 1 4 extending forward and backward is fixed on the swing shaft 1 1 2. The axle 18 of the rear wheel W R is swingably supported between the rear part of the chain housing 108 and the rear part of the arm 1 14. However, on the driven pulley 65 of the belt-type continuous transmission 5 3, the driven-side movable pulley half 9 8 faces the driven pulley-side fixed pulley half 9 7 from the outside and faces each other. On the driven side, the pulley half body 97 is fixed to approach and leave. Therefore, the right-side case 58, which belongs to the outer side of the transmission case 56, is formed into a shape in which the rear part protrudes outward from the front part. That is, in the right case 58, 19 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 is formed with a lower portion 5 8 a which covers the driving pulley 6 4; and a high portion 5 8 b, the high-level portion 5 8 b covers the driven pulley 65 and protrudes outside the low-level portion 5 8 a and is connected to the rear portion of the low-level portion 5 8 a. Around the driving pulley shaft 62, a plurality of through holes 115 ... which are communicated with the transmission chamber 60 are provided in the lower portion 5a, and the driving-side fixed pulley half 84 in the driving pulley 64 is provided. A plurality of blades 8 4 a... That draw air from the above-mentioned through holes 1 1 5... Into the transmission chamber 60 are integrally formed. That is, the driving-side fixed pulley half body 84 also functions as a fan. On the right case 5 8 of the transmission case 5 6, an air introduction cover 116 covering the lower portion 5 8 a is installed. An air introduction passage 117 is formed between the air introduction cover 1 1 6 and the lower portion 5 8 a. The air introduction passages 1 1 7 communicate with the respective through holes 1 1 5... And open toward the side surface of the front end portion of the upper portion 5 8 b. In addition, an air exhaust passage 118 is formed in the front portion of the upper portion 5 8 b so as to communicate with the inside of the transmission compartment 60. The air exhaust passage 118 is formed corresponding to the open end of the air introduction passage 117. The air exhaust passage 118 is formed in an arc shape, and opens downwards behind the air introduction hole 117. Further, the inorganic transmission 5 3 is subjected to the air introduced into the transmission chamber 60 from the air introduction path 1 1 7 through the through holes 1 1 5... According to the rotation of the driving-side fixed pulley half body 84. The cooled and cooled air passes from the transmission room 60 through the air exhaust passage 1 1 8 and is discharged to the outside of the transmission case 56. Inside the crank case 14, a crank shaft chamber 124 and oil 20 are formed so as to be separated from each other by a partition wall 14 b disposed in the crank case 14.
312/發明說明書(補件)/93-05/93105275 200424424 儲存室1 2 5，該曲柄軸室1 2 4收納曲柄軸1 2的大 動帶輪軸62的一端部，該油貯存室125配置於ΐ 的後方側，上述油儲存室1 2 5在主動帶輪軸6 2 ί 伸，並連接於左引擎罩3 3的内部。 然而，油儲存室1 2 5内的油通過圖中未顯示出 泵，供給到引擎Ε的各部潤滑部，在潤滑後，返 軸室124内部的油通過圖中未顯示出的返回泵， 儲存室1 2 5。 在圖5〜圖9中，在前部汽缸側體F Β的前部3 上，控制面對於活塞2 7 F頂部之從向前部汽缸體 部汽缸蓋1 6 F之間形成的燃燒室1 2 6的吸氣管5 0 一對吸氣閥1 2 7…，和其沿著曲柄軸1 2之軸線的 且開閉自在地配置，與控制由上述燃燒室1 2 6朝 5 1 F的排氣之一對排氣閥1 2 8，上述吸氣閥1 2 7… 列且開閉自在的配置其兩吸氣闊1 2 7…係為由裝 汽缸蓋1 6 F之間的螺旋狀吸氣側閥彈簧1 2 9…逼 方向，兩排氣閥1 2 8…係為由裝入與前部汽缸蓋 的螺旋狀排氣側閥彈簧1 3 0…，逼迫在閉闊方向 以開閉驅動上述兩個吸氣閥1 2 7…和兩個排氣 的闊動裝置4 5 F係指收容於在前部汽缸蓋1 6 F和 1 7 F之間形成之閥動室1 2 3 F，透過定時傳動裝置 曲柄軸1 2而減小1 / 2的旋轉動力而旋轉驅動的： 承旋轉自在之前部汽缸蓋1 6 F的凸輪軸1 3 1及與 1 3 1平行且支承前部汽缸蓋1 6 F之第1和第2擺 312/發明說明書(補件)/93-05/93105275 部分和主 &柄軸1 2 泠左側延 的供給 回到曲柄 返回到油 :缸蓋1 6F 1 5 F和前 之吸氣的 方向排列 向排氣管 被平行排 入與前部 迫在閉閥 1 6 F之間 〇 閥1 2 8… 前部頭蓋 4 3 F，經 衣式，可支 該凸輪軸 動軸1 3 2， 21 200424424 1 3 3 ;及支承搖動可能的第1和第2搖軸1 3 2，1 3 3，之第1 和第2搖臂1 3 4，1 3 5。 上述凸輪軸1 3 1係其軸線以配置略於汽缸軸線C F上的 方式，在吸氣側閥彈簧1 2 9…和排氣側閥彈簧1 3 0…之間， 由前部汽缸蓋1 6 F旋轉自在地支承。在前部汽缸蓋1 6 F上， 沿凸輪軸1 3 1的軸方向隔著間隔一體配置，一對支承部 136，137，在這些支承部136，137上，設置有為旋轉自在 支承凸輪軸1 3 1之軸承孔1 3 8，1 3 9。然而，在支承部1 3 6 中的，軸承孔1 3 8的内面和凸輪軸1 31的外圍之間，裝設 有球軸承1 4 0，在支承部1 3 7中的軸承孔1 3 9的内面和凸 輪軸1 3 1的外圍之間，裝設有球軸承1 4 1。 在上述兩個支承部1 3 6，1 3 7之間，在凸輪軸1 3 1上， 吸氣閥1 2 7…和排氣閥1 2 8…中的其中一個，在本實施例的 情況下，為驅動吸氣閥1 2 7…的第一凸輪1 4 2與吸氣閥 1 2 7…和排氣閥1 2 8…中的另一個，在本實施例的情況下， 為驅動吸氣閥1 2 8…的第2凸輪1 4 3而設成一體。此外， 第2凸輪1 4 3形成為小於第1凸輪1 4 2，相對於配置在沿 凸輪軸1 3 1的軸線方向分別排列的吸氣側和排氣側闊彈簧 12 9··· ，1 3 0…之中的，軸方向一側（圖5和圖6的左側） 的吸氣側和排氣側閥彈簧1 2 9，1 3 0之間的情況，第1凸輪 1 4 2係配置於從上述軸方向一側的吸氣側和排氣側閥彈簧 1 2 9，1 3 0，進一步沿上述軸方向一側錯開的位置。 第1和第2擺動軸1 3 2，1 3 3係在從沿汽缸軸線C F的方 向看時，為從上下夾住凸輪軸1 3 1的位置，支承前部汽缸 22 312/發明說明書(補件)/93-05/93105275 200424424 蓋1 6 F，第2擺動軸1 3 3配置於第1擺動軸1 3 2 另外，第2擺動軸1 3 3和曲柄軸1 2之間的距離被 第1擺動軸1 3 2和曲柄軸1 2之間的距離。即，第 1 3 3僅較第1擺動軸1 3 2近△ L的距離被配置接ϋ 12° 在第1擺動軸1 3 2上，支承有使搖動可能之具 一對吸氣閥127···接觸的接觸臂134a，134b之第 1 3 4，此第1搖臂1 3 4上，被滾動接觸於凸輪軸1 凸輪1 4 2之滾子1 4 4軸支承者。另外，在第2擺 上，支承有使搖動可能之具有分別與一對排氣閥 觸的接觸臂135a，135b之第2搖臂135，該第2 上，配置有與凸輪軸131的第2凸輪143相接之 146° 定時動力傳送裝置4 3 F係收容於從曲柄軸箱 汽缸體1 5 F、前部汽缸蓋1 6 F和前部頭蓋1 7 F之 凸輪鏈條室148F中，其具備有固定於曲柄軸12 鏈輪4 4 F ;上述汽缸蓋1 6 F中，固定於從支承部 的凸輪軸1 3 1的一端部上之從動鏈輪1 4 9 F ;捲繞 輪44F和從動鏈輪149F上之凸輪鏈條46F;應給 條4 6 F的鬆弛側一定張力之摺接於凸輪鏈條4 6 F 條拉伸器1 5 0 F;如同施予一定物重之壓於鏈條拉 的長方向中間部之靠著前部汽缸體1 5 F上之拉伸 151F(tensioner lifter);如同摺接於凸輪鏈條 張側之靠著上述前部汽缸體1 5 F上之鏈條導向器 312/發明說明書(補件)/93-〇5/93105275 的下方。 設定小於 2擺動軸 ί曲柄軸 有分別與 1搖臂 31的第1 動軸1 3 4 1 2 8…接 搖臂1 3 5 凸輪滑塊 4，到前部 間形成之 上之驅動 136突出 於驅動鍵 予凸輪鏈 的弓形鏈 伸器1 5 0 F 支撐器 4 6F的緊 152F ° 23 200424424 但是，曲柄軸1 2係沿圖4中箭頭1 5 3所示方向旋轉， 在定時動力傳送裝置4 3 F中，凸輪鏈條4 6 F係較汽缸軸線 C F前側，亦即因汽缸軸線C F朝向前上方傾斜，故較汽缸 軸線C F下側處構成鬆弛侧，鏈條拉伸器1 5 0 F和拉伸支撐 器1 5 1 F均配置較汽缸軸線C F前側。 上述從動鏈輪1 4 9 F係透過複數個，例如一對螺栓1 5 5， 1 5 5固定於在前部汽缸蓋1 6 F中，由從支承部1 3 6突出的 凸輪軸1 3 1的一端部壓入等方式而固定之支承部份材料 處。 在圖1 0中，後部汽缸側體R B側的閥動裝置4 5 R係收容 於由後部汽缸蓋1 6 R和後部頭蓋1 7 R之間形成的閥動室 1 2 3 R，透過同步動力傳送裝置4 3 R，經曲柄軸1 2減小1 / 2 的旋轉動力而旋轉驅動的方式，可支承旋轉自在之後部汽 缸蓋1 6 R的凸輪軸1 3 1及與上述凸輪軸1 3 1平行，該軸 1 3 2，1 3 3且支承後部汽缸蓋1 6 R之第1和第2擺動軸1 3 2， 1 3 3 ;及支承搖動可能的第1和第2搖臂1 3 2，1 3 3之第1 和第2搖臂1 3 4，1 3 5。與前部汽缸側體F B側的閥動裝置 4 5F以相同的方式構成。 然而，關於閥動裝置4 5 R的結構，僅圖示與前部汽缸側 體F B側的閥動裝置4 5 F相對應的部分用同一參考符號，而 省略詳細之說明。 特別注意圖4，定時動力傳送裝置4 3 R係收容於從曲柄 軸箱1 4到後部汽缸體1 5 R、後部汽缸蓋1 6 R和後部頭蓋1 7 R 之間形成之凸輪鏈條室1 4 8 R中，其具備有固定於曲柄軸 24 312/發明說明書(補件)/93-05/93105275 200424424 12上之驅動鏈輪44R;固定於凸輪軸131的一端部上之從 動鏈輪149R;捲繞於驅動鏈輪44R和從動鏈輪149R上之 凸輪鏈條4 6 R ;應給予凸輪鏈條4 6 R的鬆弛側一定張力之 摺接於凸輪鏈條4 6 R之弓形鏈條拉伸器1 5 0 R ;如同施予以 一定物重之壓於鏈條拉伸器150R的長方向中間部之靠著 前部汽缸體1 5 R上之拉伸支撐器1 5 1 R ;如同摺接於凸輪鏈 條4 6 R的緊張側之靠著上述後部汽缸體1 5 R上之鏈條導向 器 1 52R。 此外，伴隨沿箭頭1 5 3所示的方向，使曲柄軸1 2旋轉 的情況，定時動力傳送裝置4 3 R的凸輪鏈條4 6 R係較後部 汽缸側體RB的汽缸軸線CR前側處構成鬆弛側，鏈條拉伸 器1 5 0 R和拉伸支撐器1 5 1 R係配置於較向後上方傾斜的汽 缸軸線CR之前方。 上述從動鏈輪1 4 9 R係透過例如，一對螺栓1 5 7，1 5 7於 凸輪軸131之一端以壓入等方式而固定於凸輪脈衝器（cam p u 1 s a r ) 1 5 6上，該凸輪脈衝器1 5 6係，在沿其周向間隔開 的3個地方，突設有突出於半徑方向外方之突部1 56a…， 在後部汽缸蓋1 6 R上，安裝有因可檢測上述各突部1 5 6 a… 而為，檢測活塞2 7 R的壓縮上死點之壓縮上死點檢測感測 器 158b。 但在檢測壓縮上死點之基準汽筒，在本實施例中，可檢 測後部汽缸側體RB的壓縮上死點而未圖示出的曲柄軸角 感測器，在本實施例中，由判斷前部汽缸側體FB的相位， 雖可檢測前部汽缸側體F B的壓縮上死點，但在凸輪脈衝器 25 312/發明說明書(補件)/93-05/93105275 200424424 僅有單一突部之時，當因噪音（η 〇 i s e )使信.號混亂時，會 無法判斷凸輪軸1 3 1之一次回轉量的壓縮上死點。於是經 由設置上述之3個突部1 5 6 a…於凸輪脈衝器1 5 6上，即使 在混入噪音（η 〇 i s e )的情況下，仍可透過凸輪軸 1 3 1的半 回轉（曲柄軸1 2的1回轉）而恢復。 在前部汽缸側體FB和後部汽缸側體RB中，在汽缸蓋 1 6 F，1 6 R上，將先端部相對於燃燒室1 2 6，雖分別安裝有 火星塞1 5 8 a…，但在吸氣閥1 2 7…和排氣閥1 2 8…之間， 配置有曲柄軸1 31…，所以在包括汽缸軸線CF，CR，並且 與凸輪軸1 3 1…的軸線平行之平面（圖9所示平面）的投 影圖上，與從動鏈輪14 9 F，1 4 9 R相反側的凸輪轴1 3 1…軸 線的延長線形成角度而相交之軸線，火星塞1 5 8由斜側方 向安裝於汽缸蓋16F，16R上。 即，關於汽缸軸線C F，C R，在與凸輪鏈條室1 4 8 F，1 4 8 R 的相反側，靠近汽缸蓋1 6 F，1 6 R的頭蓋1 7 F，1 7 R的外側 面，為安裝火星塞158…配置有在内方側凹陷的安裝用凹 部1 5 9…，於面對燃燒室1 2 6設置於汽缸蓋1 6 F，1 6 R上的 安裝孔1 6 0…中，從上述安裝用凹部1 5 9…塞進火星塞 15 8a."。 關於像這樣的火星塞1 5 8 a…的安裝結構中，必須防止用 於將火星塞1 5 8 a…安裝於汽缸蓋1 6 F，1 6 R上的工具對汽 缸蓋16F，16R和頭蓋17F，17R的連接部造成干擾的情況， 從此觀點而言，於應連接頭蓋1 7 F，1 7 R之汽缸蓋1 6 F，1 6 R 上設置的頭蓋連接面1 6 1 F，1 6 1 R係沿凸輪軸1 3卜.·的軸 26 312/發明說明書(補件)/93-05/93105275 200424424 線，向著上述從動鏈輪1 4 9 F，1 4 9 R側與汽缸體1 5 F，1 5 R 之間的距離變小，形成和與汽缸軸線C F，C R垂直相交的平 面斜交之傾斜面。 但是，與第1和第2凸輪1 4 2，1 4 3 —體的凸輪軸1 3 1… 係安裝在介於支承部1 3 6，1 3 7間的球軸承1 4 0，1 4 1的狀 態，將上述球軸承1 4 0，1 4 1的外輪壓入支承部1 3 6，1 3 7 的軸承孔1 3 8，1 3 9中所組成，與上述火星塞1 5 8 a…相反 側之上述汽缸蓋1 6 F，1 6 R的側壁上，如圖1 1所示般，向 上述各軸承孔1 3 8，1 3 9安裝凸輪軸1 3 1時，將可能插通凸 輪軸131之半圓狀的凹部162F、162R設置於連接上述頭蓋 連接面161F、161R兩端處。 此外，於上述頭蓋連接面1 6 1 F，1 6 1 R之間，夾有密封 墊片164…，與汽缸蓋16F，16R連接的頭蓋17F，17R上， 為對應於該頭蓋17F，17R與上述汽缸蓋16F，16R之連接 將上述凹部1 6 2 F，1 6 2 R於閉塞之圓形蓋部1 6 3設成一體。 但是，在將凸輪軸1 3 1…安裝於支承部1 3 6，1 3 7的軸承 孔1 3 8，1 3 9上時，具備凸輪軸1 3 1…的第1和第2凸輪1 4 2， 143之中，較大的第1凸輪142為了插通支承部136的軸 承孔1 3 8，上述軸承孔1 3 8並非為完全的圓形，，而是形成 為可通過第1凸輪142的高位部142a且一部份向外膨脹的 形狀。 下面對本實施例的作用進行說明，在V形的引擎E中的 前部和後部汽缸側體F B，R B的閥動裝置4 5 F，4 5 R中，分 別配置有第1和第2凸輪1 4 2，1 4 3的凸輪軸1 3 …其軸線 27 312/發明說明書(補件)/93-05/93105275 200424424 大致配置於汽缸軸線C F，C R上之處，且由汽缸蓋.1 6 F，1 6 R 支承，配置於吸氣側和排氣側閥彈簧1 2 9，1 3 0之間的第2 凸輪1 4 3…被做成小於第1凸輪1 4 2，第1凸輪1 4 2配置於 沿凸輪軸1 3 1…軸線的方向，與吸氣側和排氣側閥彈簧 1 2 9，1 3 0之間偏離的位置。 於是，在避免第1和第2凸輪1 4 2，1 4 3，與吸氣側和排 氣側閥彈簧1 2 9，1 3 0之間干擾的同時，將吸氣閥1 2 7和排 氣閥1 2 8的閥桿的夾角設定得較小，在預期得到燃燒室 1 2 6…的節省空間化及獲得高壓縮比的同時，亦希望得到含 有凸輪軸1 3卜··的閥動裝置4 5 F，4 5 R的節省空間化，進而 使汽缸蓋1 6 F，1 6 R小型化。 此外，在凸輪軸131的兩側，沿該凸輪軸1 31的軸線的 方向並排的一對吸氣閥1 2 7…和排氣閥1 2 8…因汽缸蓋 1 6 F，1 6 R開閉自在地配置於前部和後部汽缸側體F R，R B 中，所以，關於4汽門汽缸蓋上凸輪型引擎中，在預期得 到燃燒室1 2 6…的節省空間化及獲得高壓縮比的同時，亦 希望得到含有凸輪軸1 3卜··的閥動裝置4 5 F，4 5 R的節省空 間化，進而使汽缸蓋1 6 F，1 6 R小型化。 又，以曲柄軸1 2軸線於水平狀態的姿勢，在較摩托車 前輪WF的後方，搭載於車體框架11上的引擎主體13的前 部汽缸側體F B上，於第1凸輪1 4 2處，從動的第1搖臂 1 3 4支承於，於與第1擺動軸1 3 2有平行軸線之凸輪軸 1 3 1，於第2凸輪1 4 3處，從動的第2搖臂1 3 5係搖動可能 地支承著第1擺動軸1 3 2有平行軸線之凸輪軸1 3 1下方之 28 312/發明說明書(補件)/93-05/93105275 200424424 第2擺動軸1 3 3，第2擺動軸1 3 3和曲柄軸1 2之間的距離 小於第1擺動軸1 3 2和曲柄軸1 2之間的距離。， 為此，在前部汽缸側體F B中，即使汽缸軸線C F朝向前 方上傾斜，可能極力縮短從曲柄軸1 2到引擎1 3的前端底 部之間的距離，與接近為避免前輪WF間的干擾之引擎主體 1 3，有助於摩托車的軸距的縮小，或可將前輪WF的輪行程 設定得較長。 而且引擎E為V形，在避免前部汽缸頭1 6F對前輪WF 的妨礙的同時，可使前部汽缸蓋1 6F接近前輪WF側，設置 引擎本體13於極下方位置，可使引擎本體13的上方，確 保為了確保其它零件的空間較大，或可降低駕駛員用的座 墊（sheet)的高度。 又，在第1搖臂1 3 4上，軸支承滚動接觸之滚子1 4 4的 第1凸輪142，在第2搖臂135上，因配置有與第2凸輪 1 4 3摺接的凸輪滑塊1 4 6，在配置於吸氣側和排氣側閥彈簧 1 2 9，1 3 0之間的第2凸輪1 4 3上配置空間相對較小，可避 免摺接凸輪滑塊1 4 6之吸氣閥1 2 7和排氣閥1 2 8的閥桿的 夾角增加，而可期待汽缸蓋1 6 F，1 6 R的小型化，又，配置 於與吸氣側和排氣側閥彈簧1 2 9，1 3 0之間偏離的位置處， 所以不會被上述夾角影響的第1凸輪1 4 2上，配置空間相 對變大且依滚子144滚動接觸，而有助於使閥動裝置45F， 4 5 R的摩擦損耗的降低。312 / Invention (Supplement) / 93-05 / 93105275 200424424 The storage chamber 1 2 5 is a crank shaft chamber 1 2 4 which houses one end of the large movable pulley shaft 62 of the crank shaft 12, and the oil storage chamber 125 is disposed at On the rear side of ΐ, the above oil storage chamber 1 2 5 extends on the driving pulley shaft 6 2 and is connected to the inside of the left hood 3 3. However, the oil in the oil storage chamber 1 2 5 is supplied to the lubrication portions of the engine E through a pump not shown in the figure, and after lubrication, the oil in the return shaft chamber 124 is stored by a return pump not shown in the figure. Room 1 2 5. In FIGS. 5 to 9, on the front part 3 of the front cylinder side body F B, the combustion chamber 1 formed between the control surface and the top of the piston 2 7 F from the front cylinder body part cylinder head 1 6 F 2 6 suction pipe 5 0 A pair of suction valves 1 2 7... And its opening and closing arrangement along the axis of the crank shaft 12 are freely opened and closed, and control the discharge from the combustion chamber 1 2 6 to 5 1 F. One pair of exhaust valves 1 2 8 and the above-mentioned suction valves 1 2 7… are arranged in a row and open and close freely. The two suction widths 1 2 7… are spirally sucked by the cylinder head 1 6 F. The side valve springs 1 2 9 ... push the direction, and the two exhaust valves 1 2 8 ... are driven by the spiral exhaust side valve springs 1 3 0 ... installed in the front cylinder head, forcing them to open and close in the closing direction to drive the above. Two suction valves 1 2 7 ... and two exhaust wide actuating devices 4 5 F refer to the valve actuating chamber 1 2 3 F formed between the front cylinder heads 1 6 F and 1 7 F. Timing transmission crankshaft 12 reduces rotational power by 1/2 and is rotationally driven: the camshaft 1 3 1 that supports rotation from the front cylinder head 1 6 F and parallel to 1 3 1 and supports the front cylinder head 1 6 F 1st and 2nd swing 312 / round Instruction (Supplement) / 93-05 / 93105275 Part and main & shank 1 2 Ling left extended supply back to the crank Return to the oil: cylinder head 1 6F 1 5 F and the direction of the suction in front are aligned to exhaust The tube is discharged in parallel with the front closed valve 16 F. Valve 1 2 8 ... Front head cover 4 3 F, warp type, can support the camshaft moving shaft 1 3 2, 21 200424424 1 3 3 ; And support the first and second rocking shafts 1 2 3, 1 3 3, the first and second rocking arms 1 3 4, 1 3 5. The above-mentioned camshaft 1 3 1 is arranged so that its axis is slightly above the cylinder axis CF, between the intake-side valve spring 1 2 9... And the exhaust-side valve spring 1 3 0... F rotates and supports freely. The front cylinder head 16 F is integrally arranged at intervals along the axial direction of the cam shaft 1 31, and a pair of support portions 136 and 137 are provided on these support portions 136 and 137 to support the cam shaft in a rotatable manner. 1 3 1 bearing holes 1 3 8, 1 3 9. However, between the inner surface of the bearing hole 1 3 8 and the outer periphery of the cam shaft 1 31 in the bearing portion 1 3 6, a ball bearing 1 4 0 is installed, and the bearing hole 1 3 9 in the bearing portion 1 3 7 A ball bearing 1 4 1 is installed between the inner surface of the inner surface and the outer periphery of the cam shaft 1 3 1. Between the above-mentioned two supporting portions 1 3 6, 1 3 7, on the camshaft 1 31, one of the suction valve 1 2 7 ... and the exhaust valve 1 2 8 ..., in the case of this embodiment Next, it is the other of the first cam 1 4 2 that drives the intake valves 1 2 7... And the exhaust valves 1 2 8... And the exhaust valves 1 2 8... The second cams 1 4 3 of the air valves 1 2 8 ... are integrally formed. In addition, the second cam 1 4 3 is formed smaller than the first cam 1 4 2 and is arranged on the suction side and exhaust side wide springs 12 9 arranged in the axial direction of the cam shaft 1 3 1, 1 In the case of 3 0…, between the suction side and exhaust side valve springs 1 2 9, 1 3 0 on one side in the axial direction (left side of Figs. 5 and 6), the first cam 1 4 2 is arranged The valve springs 1 2 9 and 1 3 0 on the suction side and the exhaust side from the axial direction side are further shifted from each other along the axial direction side. The first and second swinging shafts 1 3 2 and 1 3 3 support the front cylinder 22 312 / Invention Specification (Supplementary Note) to hold the camshaft 1 3 1 from above and below when viewed from the direction along the cylinder axis CF. Pieces) / 93-05 / 93105275 200424424 Cover 1 6 F, the second swing shaft 1 3 3 is arranged on the first swing shaft 1 3 2 In addition, the distance between the second swing shaft 1 3 3 and the crank shaft 12 is 1 The distance between the swing shaft 1 3 2 and the crank shaft 12. That is, the first 1 3 3 is arranged at a distance of ΔL which is closer to ΔL than the first swing shaft 1 3 2. The first swing shaft 1 3 2 is supported by a pair of suction valves 127 that enable swinging. The contact arms 134a and 134b are in contact with each other, and the first rocker arm 1 3 4 is in rolling contact with the cam shaft 1 cam 1 4 2 roller 1 4 4 shaft support. In addition, on the second pendulum, a second rocker arm 135 having contact arms 135a and 135b that are capable of contacting a pair of exhaust valves, respectively, is supported on the second pendulum, and a second rocker arm 135 is disposed on the second rocker arm. The 146 ° timing power transmission device 4 3 F connected to the cam 143 is housed in a cam chain chamber 148F from the crankcase cylinder block 1 5 F, the front cylinder head 1 6 F, and the front head cover 1 7 F. Sprocket 4 4 F fixed to crankshaft 12; driven sprocket 1 4 9 F fixed to one end of cam shaft 1 3 1 of the supporting part among the above-mentioned cylinder head 16 F; winding wheel 44F and The cam chain 46F on the driven sprocket 149F; the loose side of the strip 4 6 F should be folded to a certain tension to the cam chain 4 6 F stretcher 1 50 0 F; as if a certain weight is applied to the chain 151F (tensioner lifter) against the front cylinder block 1 5 F in the middle of the long direction of pulling; like the chain guide on the front cylinder block 1 5 F that is folded to the side of the cam chain 312 / Invention Specification (Supplement) / 93-〇5 / 93105275. Set less than 2 swing shafts, the crank shaft has the first moving shaft 1 of the rocker arm 31, 1 3 4 1 2 8 ..., then the rocker arm 1 3 5 cam slider 4, and the drive 136 formed above the front part protrudes from Drive key to the cam chain of the bow-shaped chain extender 1 5 0 F support 4 6F tight 152F ° 23 200424424 However, the crank shaft 1 2 is rotated in the direction shown by the arrow 1 5 3 in FIG. 4, and the timing power transmission device 4 In 3 F, the cam chain 4 6 F is more forward than the cylinder axis CF, that is, because the cylinder axis CF is inclined forward and upward, it forms a loose side than the lower side of the cylinder axis CF. The chain tensioner 1 50 F and the stretch The supporters 1 5 1 F are arranged on the front side of the cylinder axis CF. The above-mentioned driven sprocket 1 4 9 F is fixed to the front cylinder head 1 6 F through a plurality of bolts, such as a pair of bolts 1 5 5 and 1 5 5. The cam shaft 1 3 protrudes from the support portion 1 3 6. One end of the support part is fixed by pressing into the material. In FIG. 10, the valve actuating device 4 5 R on the rear cylinder side body RB side is housed in a valve actuating chamber 1 2 3 R formed between the rear cylinder head 16 R and the rear head cover 1 7 R, and transmits synchronous power The conveying device 4 3 R can be driven by reducing the rotational power of the crank shaft 12 by 1/2, and can be driven by the cam shaft 1 3 1 which can rotate freely at the rear cylinder head 1 6 R and the cam shaft 1 3 1 Parallel, the shafts 1 3 2, 1 3 3 and support the first and second swing shafts 1 3 2, 1 3 3 of the rear cylinder head 1 6 R; and the first and second rocker arms 1 3 2 that support swinging , 1 3 3 of the first and second rocker arms 1 3 4, 1 3 5. It is configured in the same manner as the valve actuating device 4 5F on the front cylinder side body F B side. However, regarding the structure of the valve actuating device 4 5 R, only parts corresponding to the valve actuating device 4 5 F on the front cylinder side body F B side are shown with the same reference numerals, and detailed description is omitted. Pay particular attention to FIG. 4. The timing power transmission device 4 3 R is a cam chain chamber 1 4 formed between the crankcase 14 to the rear cylinder block 1 5 R, the rear cylinder head 1 6 R, and the rear head cover 1 7 R. In 8 R, it is provided with a driving sprocket 44R fixed on the crank shaft 24 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 12; a driven sprocket 149R fixed on one end of the cam shaft 131 ; Cam chain 4 6 R wound around drive sprocket 44R and driven sprocket 149R; The loose side of cam chain 4 6 R should be given a certain tension and folded to cam chain 4 6 R bow chain tensioner 1 5 0 R; as if a certain weight is applied to the middle of the longitudinal direction of the chain stretcher 150R, the stretch support 1 5 1 R against the front cylinder block 1 5 R; as if folded to the cam chain The tension side of 4 6 R rests on the chain guide 1 52R on the rear cylinder block 1 5 R described above. In addition, when the crank shaft 12 is rotated in the direction shown by the arrow 153, the cam chain 4 6 R of the timing power transmission device 4 3 R is loosened from the front side of the cylinder axis CR of the rear cylinder side body RB. On the side, the chain stretcher 15 0 R and the stretch supporter 15 1 R are arranged in front of the cylinder axis CR inclined rearward and upward. The above-mentioned driven sprocket 1 4 9 R is fixed to the cam pulsator (cam pu 1 sar) 1 5 6 through a pair of bolts 1 5 7 and 1 5 7 at one end of the cam shaft 131 and the like, for example. The cam pulsator 1 5 6 series is provided with protrusions 1 56a protruding outward in the radial direction at three places spaced apart in the circumferential direction. The rear cylinder head 1 6 R is provided with a cause Each of the protrusions 1 5 6 a can be detected, and the compression top dead center detection sensor 158 b that detects the compression top dead center of the piston 2 7 R can be detected. However, in the reference cylinder for detecting the compression top dead point, in this embodiment, a crank shaft angle sensor (not shown) that can detect the compression top dead point of the rear cylinder side body RB is not shown. Although the phase of the front cylinder side body FB can detect the compression top dead center of the front cylinder side body FB, there is only a single protrusion in the cam pulser 25 312 / Invention Manual (Supplement) / 93-05 / 93105275 200424424 At this time, when the signal No. is chaotic due to noise (η 〇ise), it is impossible to determine the compression top dead center of one revolution of the camshaft 1 3 1. Therefore, by setting the three protrusions 1 5 6 a… on the cam pulsator 1 56, the semi-rotation (crank shaft) of the cam shaft 1 3 1 can be transmitted through the cam shaft 1 3 1 even if noise (η 〇ise) is mixed. 1 2 1 turn) while recovering. In the front cylinder side body FB and the rear cylinder side body RB, on the cylinder heads 1 6 F, 16 R, the tip end is opposite to the combustion chamber 1 2 6, although a spark plug 1 5 8 a is installed, ..., However, between the suction valves 1 2 7 ... and the exhaust valves 1 2 8 ..., the crank shafts 1 31 ... are arranged, so in a plane including the cylinder axes CF, CR and parallel to the axes of the cam shafts 1 3 1 ... (Plane shown in Fig. 9) In the projection view, the axis that intersects with the extension of the camshaft 1 3 1 ... axis on the opposite side of the driven sprocket 14 9 F, 1 4 9 R, the Mars plug 1 5 8 It is mounted on the cylinder heads 16F and 16R from the oblique side. That is, regarding the cylinder axes CF, CR, on the opposite sides of the cam chain chambers 1 4 8 F, 1 4 8 R, the outer sides of the head covers 1 7 F, 1 7 R of the cylinder heads 1 6 F, 1 6 R, For the installation of the Mars plug 158, a recess 1 5 9..., Which is recessed on the inner side, is provided, and a mounting hole 1 6 0... Is provided in the cylinder head 1 6 F, 1 6 R facing the combustion chamber 1 2 6. From the above-mentioned mounting recesses 1 5 9 ... into the Mars plug 15 8a. &Quot;. With regard to the mounting structure of the Mars plug 1 5 8 a ..., it is necessary to prevent the tools for mounting the Mars plug 1 5 8 a ... on the cylinder heads 16 F, 16 R and the cylinder heads 16F, 16R and the head cover. In the case where the connecting parts of 17F and 17R cause interference, from this point of view, the head covers 1 7 F, 1 7 R should be connected to the cylinder heads 1 6 F, 1 6 R and the head cover connecting surfaces 1 6 1 F, 1 6 should be connected. 1 R is along the axis of camshaft 1 3 Bu .. 26 26312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 line, towards the above driven sprocket 1 4 9 F, 1 4 9 R side and cylinder block The distance between 1 5 F and 1 5 R becomes smaller, forming an inclined plane that intersects obliquely with the plane perpendicular to the cylinder axis CF, CR. However, the camshafts 1 3 1 which are integral with the first and second cams 1 4 2, 1 4 3 are ball bearings 1 4 0, 1 4 1 mounted between the support portions 1 3 6, 1 3 7. In the state, the outer ring of the ball bearing 1 4 0, 1 4 1 is pressed into the bearing holes 1 3 8, 1 3 7 of the support portion 1 3 6, 1 3 7 and the above-mentioned spark plug 1 5 8 a ... On the side walls of the cylinder heads 1 6 F and 1 6 R on the opposite side, as shown in FIG. 11, when the camshafts 1 3 1 are installed in the above bearing holes 1 3, 1 3 9, it is possible to insert the cams. The semicircular recesses 162F and 162R of the shaft 131 are provided at both ends of the head cover connection surfaces 161F and 161R. In addition, between the above-mentioned head cover connecting surfaces 1 6 1 F, 16 1 R, a gasket 164 ... is sandwiched, and the head covers 17F, 17R connected to the cylinder heads 16F, 16R correspond to the head covers 17F, 17R and The connection of the cylinder heads 16F and 16R integrates the recessed portions 16 2 F and 16 2 R with the closed circular cap portion 16 3. However, when the camshafts 1 3 1 ... are mounted in the bearing holes 1 3 8, 1 3 9 of the support portions 1 3 6, 1 3 7, the first and second cams 1 4 of the cam shafts 1 3 1 ... are provided. Among the 143, the larger first cam 142 is inserted into the bearing hole 1 3 8 of the support portion 136. The bearing hole 1 3 8 is not completely circular, but is formed so as to pass through the first cam 142. The shape of the upper portion 142a is partially expanded outward. The function of this embodiment will be described below. In the front and rear cylinder side bodies FB and RB of the V-shaped engine E, first and second cams 1 and 5 are disposed in the valve actuation devices 4 5 F and 4 5 R, respectively. 4 2, 1 4 3 camshaft 1 3… its axis 27 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 Approximately arranged on the cylinder axis CF, CR, and by the cylinder head. 1 6 F ， 1 6 R support ， the second cam 1 4 3 placed between the intake side and exhaust side valve spring 1 2 9，1 3 0 is made smaller than the first cam 1 4 2 and the first cam 1 4 2 is arranged in a position along the axis of the camshaft 1 3 1... And is deviated from the intake-side and exhaust-side valve springs 1 29, 130. Therefore, while avoiding interference between the first and second cams 1 2 4 and 1 4 3 and the intake and exhaust side valve springs 1 2 9 and 1 3 0, the intake valve 1 2 7 and the exhaust The included angle of the valve stem of the air valve 1 2 8 is set to be small, and while it is expected to save space and obtain a high compression ratio of the combustion chamber 1 2 6... The space saving of the devices 4 5 F and 4 5 R further reduces the size of the cylinder heads 16 F and 16 R. In addition, on both sides of the camshaft 131, a pair of suction valves 1 2 7 ... and exhaust valves 1 2 8 ... side by side in the direction of the axis of the cam shaft 1 31 are opened and closed by the cylinder heads 1 6 F, 1 6 R It is freely arranged in the front and rear cylinder side bodies FR, RB. Therefore, in the 4-cylinder head cam engine, space saving and high compression ratio of the combustion chamber 1 2 6 are expected at the same time It is also desired to obtain space-saving valve actuation devices 4 5 F, 4 5 R including camshafts 13 and so on, and further reduce the size of the cylinder heads 16 F, 1 6 R. In a posture where the crankshaft 12 axis is horizontal, the rear side of the motorcycle front wheel WF is mounted on the front cylinder side body FB of the engine main body 13 on the vehicle body frame 11 on the first cam 1 4 2 The driven first rocker arm 1 3 4 is supported by the cam shaft 1 3 1 having a parallel axis to the first swing axis 1 3 2 at the second cam 1 4 3 and the driven second rocker arm 1 3 5 series of swings may support the first swing shaft 1 3 2 cam shafts with parallel axes 1 3 28 under 28 1 / Invention Manual (Supplement) / 93-05 / 93105275 200424424 2nd swing shaft 1 3 3 The distance between the second swing axis 1 3 3 and the crank shaft 12 is smaller than the distance between the first swing axis 1 3 2 and the crank shaft 12. For this reason, in the front cylinder side body FB, even if the cylinder axis CF is inclined upward, it may be possible to shorten the distance from the crankshaft 12 to the front bottom of the engine 13 as much as possible, and to avoid the distance between the front wheels WF. The disturbing engine body 1 3 helps to reduce the wheelbase of the motorcycle, or the wheel stroke of the front wheel WF can be set longer. Moreover, the engine E is V-shaped. While avoiding the front cylinder head 16F obstructing the front wheel WF, the front cylinder head 16F can be approached to the front wheel WF side, and the engine body 13 is arranged at the extremely lower position, so that the engine body 13 To ensure that the space for other parts is large, or the height of the sheet for the driver can be reduced. In addition, on the first rocker arm 1 3 4, the first cam 142 of the roller 1 4 4 which is in rolling contact with the shaft is supported, and the second rocker arm 135 is provided with a second cam 1 4 3 which is folded in contact with the second cam 1 4 3. The cam slider 1 4 6 has a relatively small arrangement space on the second cam 1 4 3 disposed between the intake side and the exhaust side valve springs 1 2 9 and 1 3 0, which can avoid the cam slider 1 from being folded. The angle between the valve stem of the intake valve 1 2 7 and exhaust valve 1 2 8 of 4 6 increases, and the size reduction of the cylinder head 1 6 F, 1 6 R can be expected, and it is arranged on the side of the intake and exhaust The position of the side valve spring 1 2 9 and 1 3 0 is shifted, so the first cam 1 4 2 which is not affected by the included angle, has a relatively large arrangement space and makes rolling contact with the roller 144, which helps In order to reduce the friction loss of the valve actuation device 45F, 4 5 R.
又，後上方使汽缸軸線CR傾斜的後部汽缸側體RB上， 在曲柄軸1 2和凸輪軸1 3 1之間，配置具有鏈條拉伸器1 5 0 R 29 312/發明說明書(補件)/93-05/93105275 200424424 的定時動力傳送裝置4、3R，將由曲柄軸1 2的動力變速，'傳 達到後輪W R上之變速機5 3的變速箱體5 6從曲柄軸箱1 4， 延伸到後方，而上述鏈條拉伸器1 5 0 R配置於上述汽缸軸線 CR的前方。 因此，透過鏈條拉伸器1 5 0 R的配置，後部汽缸體1 5 R 不向後方側膨脹，即使設定為上述汽缸軸線CR後方側的傾 斜角度較大，亦可避免變速箱體5 6的容量變小之後部汽缸 體15R的變速箱體56之妨礙，亦可能降低引擎E的高度。 又，引擎E係由使汽缸軸線CF朝向前上方傾斜之前部 汽缸側體FB，及使汽缸軸線CR朝向後上方傾斜之後部汽 缸側體RB所形成之V型，可使V形的引擎E在後方側以相 對較大程度傾斜，而降低引擎E的高度。 另外，具有前部汽缸側體F B之前部汽缸蓋1 6 F的側壁 下部，以及具有後部汽缸側體R B之後部汽缸蓋1 6 R的側壁 後部上，分別連接有排氣管5 1 F，5 1 R，於後方側以相對較 大程度傾斜的V形的引擎E中產生於前部汽缸侧體F B下方 的空間中，可良好地取回前部汽缸側體F B的排氣管5 1 F， 抑制從動力單元P朝向排氣管5 1 F之下方突出，容易確保 最低地上高度。又，在後部汽缸側體RB中，因為沒有與鏈 條拉伸器1 5 0 R有關的零件，即，拉伸支撐器1 5 1 R從後部 汽缸側體RB，朝向後方突出之事，故可不考慮對該零件的 干擾回避下，容易佈置後部汽缸側體R B的排氣管1 5 1 R。 但是，在前部和後部汽缸側體FB，RB中，其閥動裝置 45F，45R中的凸輪軸131…的一端部處，固定有從動鍵輪 30 312/發明說明書(補件)/93-05/93105275 200424424 149F，149R，在有與從動鏈輪149F，149R的相反側之凸輪 軸1 3 1的軸線的延長線成角度地交差之火星塞丨5 8 a，安裝 於前部和後部汽缸蓋1 6 F，1 6 R上，應與頭蓋1 7 F，1 7 R連 接之各汽缸蓋16F，16R上設置之頭蓋連接面161F，161R， 係向著沿凸輪軸1 3卜··的軸線的上述從動鏈輪1 4 9 F，1 4 9 R 側，使汽缸體1 5 F，1 5 R之間的距離變小。形成與各汽缸軸 線CF，CR垂直相交的平面斜交之傾斜面。 如此般，頭蓋連接面1 6 1 F，1 6 1 R係向著沿凸輪軸1 3 1… 的軸線的從動鏈輪149F，149R側，使接近汽缸體15F，15R 而傾斜，與火星塞1 5 8 a…相對應的部分，上述頭蓋連接面 1 6 1 F，1 6 1 R係位於距汽缸體1 5 F，1 5 R最遠的位置。因此， 如面對燃燒室1 2 6…的中間部般將火星塞1 5 8 a…的安裝姿 勢弄直，可避免因汽缸蓋16F，16R的大型化，以及頭蓋 1 7 F，1 7 R的小型化造成的岡彳性降低，火星塞用工具可避免 干擾汽缸蓋1 6 F，1 6 R和頭蓋1 7 F，1 7 R的連接部，亦可增 加火星塞158…的安裝自由度。 此外，在前部和後部汽缸蓋1 6 F，1 6 R上，配置有一體 之分別有可回轉自在地支承凸輪軸1 3 1…的軸承孔1 3 8， 1 3 9之一對支承部1 3 6，1 3 7，在與火星塞1 5 8 a…的相反側， 汽缸蓋1 6 F，1 6 R的側壁上，在將上述凸輪軸1 3 1…安裝於 各軸承孔1 3 8，1 3 9中時，為使該凹部1 62 F，1 6 2 R插通上 述凸輪軸1 3 1…，半圓狀的凹部1 6 2 F，1 6 2 R被配置成可使 上述頭蓋連接面1 6 1 F，1 6 1 R兩端相連。 為此，從凹部1 6 2 F，1 6 2 R處插入切削工具，使各支承 31 312/發明說明書(補件)/93-05/93105275 200424424 部1 3 6，1 3 7之軸承孔1 3 8，1 3 9可能切削加工，為確保良 好加工性之同時，可用汽缸蓋1 6 F，1 6 R支承零件數持續減 少之凸輪軸1 3 1。 又，在頭蓋17F，17R上，為對應於該頭蓋17F，17R與 上述汽缸蓋16F，16R之連接，將上述凹部162F，162R於 閉塞之圓形蓋部1 6 3設成一體。 為將凹部1 6 2 F，1 6 2 R封閉，無需頭蓋1 7 F，1 7 R以外的 零件，透過配置凹部1 6 2 F，1 6 2 R，可防止零件數增加的情 況。 以上，雖對本發明的實施例進行了說明，本發明不限於 上述實施例，可在不脫離專利申請範圍所記載的本發明的 情況下，進行各種設計變更。 例如，本發明亦適用於摩托車以外的三輪摩托車等的小 型車輛。 (發明效果） 依照如上述般之申請專利範圍第1項之發明，可相對較 小地設定吸氣閥和排氣閥的閥桿的夾角，在預期燃燒室的 節省空間化及獲得高壓縮比之同時，可預期包括凸輪軸的 閥動裝置的節省空間化及汽缸蓋之小型化。 又，依照申請專利範圍第2項之發明，針對4汽門頂置 凸輪型引擎，在預期燃燒室的節省空間化及獲得高壓縮比 之同時，可預期包括凸輪軸的閥動裝置的節省空間化及汽 缸蓋小型化。 依照申請專利範圍第3項之發明，儘管汽缸軸線朝向前 32 312/發明說明書(補件)/93-05/93105275 200424424 上方傾斜，仍可極力地縮短從曲柄軸到引擎主體的 部的距離，與接近為避免前輪間的干擾之引擎主體 於小型車輛的軸距的縮小，或可將前輪的輪行程設 長。 依照申請專利範圍第4項之發明，因避免吸氣閥 閥的閥桿的夾角增大，可預期汽缸蓋小型化及有助 閥動裝置的摩擦損失。 且，依照申請專利範圍第5及6項之發明，可在 前輪的妨礙的同時，使V形的引擎主體的前部汽缸 前輪側，因此避免加長小型車輛的軸距，或前輪輪 短，將引擎主體配置於極下方位置，可在引擎主體存 確保為其它零件之空間增大，亦可降低駕駛員用座 (sheet)的高度。 【圖式簡單說明】 圖1為摩托車的側視圖。 圖2為從與圖1相同的方向所視之動力單元的切 的側視圖。 圖3為沿圖2中的3 — 3線的剖視圖。 圖4為沿圖3中的4 — 4線的剖視圖。 圖5為沿圖4中的5 — 5線的箭視圖。 圖6為省略了搖臂的狀態之與圖5相對應的圖。 圖7為沿圖5中的7— 7線的剖視圖。 圖8為沿圖5中的8 — 8線的剖視圖。 圖9為沿圖4中的9 一 9線的剖視圖。 312/發明說明書(補件)/93-05/93105275 前端下 ，有助 定得較 和排氣 於減小 避免對 蓋接近 行程變 上方， 墊 除局部 33 200424424 圖1 0為沿圖4中，的10— 1 0線的箭視圖。 圖1 1為沿圖9中的箭頭1 1的箭視圖。 (元件符號說明） 11 車體框架 12 曲柄軸 13 引擎主體 14 曲柄軸箱 1 4 a 箱支承部 14b 間隔壁 1 5 F 前部汽缸體 1 5 R 後部汽缸體 1 6 F 前部汽缸蓋 1 6 R 後部汽缸蓋 1 7 F 前部頭蓋 1 7 R 後部頭蓋 18 車軸 19 殼體左半部 20 殼體右半部 2 1 連接面 2 2 左側曲柄軸頸 23 右侧曲柄軸頸 2 4 第1曲柄軸垂重部 2 5 第2曲柄軸垂重部 2 6 F 搪缸機 34In addition, a chain stretcher 1 50 0 R 29 312 / Invention Manual (Supplement) is arranged on the rear cylinder side body RB that tilts the cylinder axis CR upward and rearward between the crankshaft 12 and the camshaft 1 31. / 93-05 / 93105275 200424424's timing power transmission devices 4, 3R will shift the power from the crankshaft 12 to 'transmit the transmission 5 to the rear wheel WR 5 3 the gearbox 5 6 from the crankshaft box 1 4 Extending to the rear, the chain stretcher 150 R is arranged in front of the cylinder axis CR. Therefore, through the arrangement of the chain stretcher 150 R, the rear cylinder block 15 R does not expand to the rear side, and even if the inclination angle of the rear side of the cylinder axis CR is set to be large, the transmission body 56 can be avoided. The reduction of the capacity of the transmission body 56 of the rear cylinder block 15R may also reduce the height of the engine E. In addition, the engine E is a V-shape formed by tilting the cylinder axis CF toward the front and the front cylinder side body FB and tilting the cylinder axis CR toward the rear and the upper cylinder side body RB. The rear side is inclined to a relatively large extent, and the height of the engine E is reduced. In addition, an exhaust pipe 5 1 F, 5 is connected to the lower part of the side wall having the front cylinder head 16 F of the front cylinder side body FB and the rear part of the side wall having the rear cylinder head 16 R of the rear cylinder side body RB. 1 R, which is generated in the space below the front cylinder side body FB in the V-shaped engine E which is relatively inclined at the rear side, and the exhaust pipe of the front cylinder side body FB can be retrieved well 5 1 F It is suppressed from protruding from the power unit P toward the lower side of the exhaust pipe 5 1 F, and it is easy to ensure a minimum ground height. The rear cylinder side body RB does not include parts related to the chain stretcher 150 R, that is, the stretch support 15 1 R projects from the rear cylinder side body RB toward the rear. Considering interference avoidance of this part, it is easy to arrange the exhaust pipe 1 5 1 R of the rear cylinder side body RB. However, in the front and rear cylinder side bodies FB and RB, at one end of the camshaft 131 in the valve actuating devices 45F, 45R, a driven key wheel 30 312 / Invention Specification (Supplement) / 93 is fixed -05/93105275 200424424 149F, 149R, a Mars plug that intersects at an angle to the extension of the axis of the camshaft 1 3 1 on the opposite side of the driven sprocket 149F, 149R 丨 5 8 a, installed at the front and On the rear cylinder heads 1 6 F and 16 R, the head cover connection surfaces 161F and 161R provided on the cylinder heads 16F and 16R to be connected to the head covers 1 7 F and 1 7 R are oriented along the camshaft. The above-mentioned driven sprocket 1 4 9 F, 1 4 9 R side of the axis of the axis makes the distance between the cylinder blocks 1 5 F, 1 5 R smaller. An inclined plane is formed obliquely to a plane perpendicularly intersecting each of the cylinder axis lines CF and CR. In this way, the head cover connecting surfaces 1 6 1 F, 1 6 1 R are oriented toward the driven sprocket 149F, 149R along the axis of the camshaft 1 3 1…, so that they approach the cylinder block 15F, 15R and incline with the spark plug 1 5 8 a ... Corresponding part, the above-mentioned head cover connecting surface 1 6 1 F, 1 6 1 R is located at the farthest position from the cylinder block 1 5 F, 1 5 R. Therefore, straightening the installation position of the spark plugs 1 5 8 a ... as if facing the middle part of the combustion chambers 1 2 6 ... can avoid the enlargement of the cylinder heads 16F, 16R and the head covers 1 7 F, 1 7 R The miniaturization caused by the miniaturization is reduced, and the Mars plug tool can avoid interference with the connection parts of the cylinder heads 1 6 F, 16 R and the head cover 1 7 F, 1 7 R, and can increase the installation freedom of the Mars plug 158 ... . In addition, on the front and rear cylinder heads 16 F, 1 6 R, a pair of bearing portions 1 3 8 and 1 3 9 are integrally provided with bearing holes 1 3 1... 1 3 6, 1 3 7, on the side of the cylinder heads 1 6 F, 1 6 R on the side opposite to the spark plug 1 5 8 a ..., the above-mentioned camshafts 1 3 1 ... are installed in each bearing hole 1 3 In the case of 8, 1 3 9, in order to insert the recessed portion 1 62 F, 1 6 2 R through the camshaft 1 3 1 ..., the semi-circular recessed portion 1 6 2 F, 1 6 2 R is arranged so that the head cover can be used. The connecting surfaces 1 6 1 F and 1 6 1 R are connected at both ends. For this purpose, insert the cutting tool from the recesses 1 6 2 F, 1 6 2 R so that each support 31 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424 Parts 1 3 6, 1 3 7 bearing holes 1 3 8, 1 3 9 may be cut. To ensure good workability, the cylinder head 1 6 F, 1 6 R can be used to support the cam shaft 1 3 1 which continues to reduce the number of parts. The head covers 17F and 17R are integrally provided with the recessed portions 162F and 162R in the closed circular cover portions 16 to correspond to the connection between the head covers 17F and 17R and the cylinder heads 16F and 16R. In order to close the recesses 16 2 F and 16 2 R, parts other than the head covers 1 7 F and 17 R are not needed. By arranging the recesses 16 2 F and 16 2 R, the number of parts can be prevented from increasing. Although the embodiments of the present invention have been described above, the present invention is not limited to the above-mentioned embodiments, and various design changes can be made without departing from the present invention described in the scope of the patent application. For example, the present invention is also applicable to small vehicles such as tricycles other than motorcycles. (Effects of the Invention) According to the invention of the first scope of the patent application as described above, the angle between the valve stems of the intake valve and the exhaust valve can be set relatively small, which can save space in the combustion chamber and obtain a high compression ratio. At the same time, space saving of the valve operating device including the camshaft and miniaturization of the cylinder head are expected. In addition, according to the invention in the scope of patent application No. 2, for a 4-valve overhead cam engine, while saving space in the combustion chamber and obtaining a high compression ratio, it is expected that space saving of a valve operating device including a camshaft may be expected. And cylinder heads. According to the invention in the third scope of the patent application, although the cylinder axis is inclined toward the front 32 312 / Invention Specification (Supplement) / 93-05 / 93105275 200424424, the distance from the crank shaft to the part of the engine body can be shortened as much as possible. It is possible to reduce the wheelbase of the small vehicle by approaching the engine body to avoid interference between the front wheels, or the wheel travel of the front wheels can be set longer. According to the invention in the scope of patent application No. 4, since the angle of the valve stem of the intake valve is prevented from increasing, the cylinder head can be miniaturized and the friction loss of the valve driving device can be expected. In addition, according to the inventions of claims 5 and 6, the front cylinder side of the V-shaped engine body can be prevented while the front wheels are obstructed. Therefore, avoiding lengthening of the wheelbase of small vehicles or short front wheels, The engine main body is arranged at a very lower position, which can increase the space for the engine main body to be other parts, and also reduce the height of the driver's sheet. [Brief description of the drawings] Fig. 1 is a side view of a motorcycle. Fig. 2 is a cut-away side view of the power unit viewed from the same direction as Fig. 1. FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 2. FIG. 4 is a sectional view taken along line 4-4 in FIG. 3. FIG. 5 is an arrow view taken along line 5-5 in FIG. 4. FIG. FIG. 6 is a view corresponding to FIG. 5 in a state where the swing arm is omitted. Fig. 7 is a sectional view taken along line 7-7 in Fig. 5. FIG. 8 is a sectional view taken along line 8-8 in FIG. 5. FIG. Fig. 9 is a sectional view taken along line 9-9 in Fig. 4. 312 / Invention Manual (Supplement) / 93-05 / 93105275 Under the front end, it helps to set the airflow and reduce the airflow. It avoids the upper stroke of the cover. The part is removed. 2004200424 Fig. 10 is along Fig. 4. 10—10 line arrow view. FIG. 11 is an arrow view taken along the arrow 11 in FIG. 9. (Description of component symbols) 11 Body frame 12 Crankshaft 13 Engine body 14 Crankshaft box 1 4 a Box support 14b Partition wall 1 5 F Front cylinder block 1 5 R Rear cylinder block 1 6 F Front cylinder head 1 6 R Rear cylinder head 1 7 F Front head cover 1 7 R Rear head cover 18 Axle 19 Case left half 20 Case right half 2 1 Connecting surface 2 2 Left crank journal 23 Right crank journal 2 4 1st crank Shaft weight 2 5 2nd crank shaft weight 2 6 F Cylinder machine 34
312/發明說明書(補件)/93-05/93105275 200424424 27F 活 塞 27R 活 塞 28F 連 桿 28R 連 桿 29 曲 柄 銷 30 發 電 機 3 1 轉 子 32 定 子 33 左 引 擎 罩 34 離 合 器 35 從 動 齒 輪 36 起 動 馬 達 3 7 驅 動 小 齒 輪 38 第 1 中 間 齒 輪 39 第 2 中 間 齒 輪 40 第 3 中 間 齒 輪 43F 定 時 傳 動 裝 置 43R 定 時 傳 動 裝 置 44F 馬區 動 鏈 輪 44R 驅 動 鏈 輪 45F 閥 動 裝 置 45R 閥 動 裝 置 46F 凸 輪 鏈 條 46R 凸 輪 鏈 條 312/發明說明書(補件)/93-05/93105275312 / Invention Manual (Supplement) / 93-05 / 93105275 200424424 27F Piston 27R Piston 28F Connecting rod 28R Connecting rod 29 Crank pin 30 Generator 3 1 Rotor 32 Stator 33 Left hood 34 Clutch 35 Drive gear 36 Start motor 3 7 Drive pinion 38 1st intermediate gear 39 2nd intermediate gear 40 3rd intermediate gear 43F timing gear 43R timing gear 44F horse sprocket 44R driving sprocket 45F valve actuating device 45R valve actuating device 46F cam chain 46R cam Chain 312 / Invention Manual (Supplement) / 93-05 / 93105275
35 200424424 4 7 右引擎罩 48 空氣清潔器 4 9 燃料槽 5 OF 吸氣管 5 OR 吸氣管 5 1 F 排氣管 5 1 R 排氣管 5 2 排氣消音器 5 3 變速機 5 4 減速齒輪組 5 5 鏈條式傳動機構 5 6 變速機箱 5 7 外殼主體 58 右側殼體 5 8a 低位部 5 8b 高位部 5 9 左側殼體 60 變速機室 6 1 齒輪室 6 2 主動帶輪軸 6 3 從動帶輪軸 6 4 主動帶輪 65 從動帶輪 66 V型皮帶 3635 200424424 4 7 Right hood 48 Air cleaner 4 9 Fuel tank 5 OF Suction pipe 5 OR Suction pipe 5 1 F Exhaust pipe 5 1 R Exhaust pipe 5 2 Exhaust muffler 5 3 Gearbox 5 4 Deceleration Gear set 5 5 Chain drive mechanism 5 6 Gearbox 5 7 Housing body 58 Right case 5 8a Low section 5 8b High section 5 9 Left case 60 Gearbox 6 1 Gear chamber 6 2 Driven pulley shaft 6 3 Driven Pulley shaft 6 4 Drive pulley 65 Driven pulley 66 V-belt 36
312/發明說明書(補件)/93-05/93105275 200424424 6 7 側軸承部 68 中間軸承部 6 9 側軸承部 7 0 傳動齒輪組 7 1 主動齒輪 72 從動齒輪 73 輔助齒輪 7 4 軸承孔 7 5 球軸承 7 6 軸承孑L* 7 7 球轴承 78 環狀的密封構件 7 9 軸承孔 8 0 球轴承 84 主動側固定帶輪半體 84a 葉片 85 主動側活動帶輪半體 8 6 帶輪驅動機構 87 套筒 88 螺桿 8 9 螺帽 9 0 從動齒輪 9 1 電動馬達 9 2 主動小齒輪 312/發明說明書(補件)/93-05/93105275 200424424 93 減速齒輪機構 9 4 球軸承 9 5 球軸承 9 6 球軸承 9 7 從動側固定帶輪半體 97a 導向部 98 從動側活動帶輪半體 99 彈簀接納構件 1 00 彈簣 10 1 離心離合器 1 02 中間軸 1 03 輸出軸 10 4 驅動軸 10 5 驅動鏈輪 10 6 從動鏈輪 10 7 鏈條 1 08 鏈條外殼 10 9 支承轴 110 徑向軸承 111 球轴承 1 1 2 搖動軸 113 徑向軸承 114 延伸臂 1 1 5 透孔 38312 / Invention Manual (Supplement) / 93-05 / 93105275 200424424 6 7 Side bearing section 68 Intermediate bearing section 6 9 Side bearing section 7 0 Drive gear set 7 1 Drive gear 72 Drive gear 73 Auxiliary gear 7 4 Bearing hole 7 5 Ball bearing 7 6 Bearing 孑 L * 7 7 Ball bearing 78 Ring-shaped seal member 7 9 Bearing hole 8 0 Ball bearing 84 Active side fixed pulley half 84a Blade 85 Active side movable pulley half 8 6 Belt drive Mechanism 87 Sleeve 88 Screw 8 9 Nut 9 0 Driven gear 9 1 Electric motor 9 2 Drive pinion 312 / Invention manual (Supplement) / 93-05 / 93105275 200424424 93 Reduction gear mechanism 9 4 Ball bearing 9 5 ball Bearing 9 6 Ball bearing 9 7 Driven side fixed pulley half 97a Guide 98 Driven side movable pulley half 99 Impeachment receiving member 1 00 Impeachment 10 1 Centrifugal clutch 1 02 Intermediate shaft 1 03 Output shaft 10 4 Drive shaft 10 5 Drive sprocket 10 6 Driven sprocket 10 7 Chain 1 08 Chain housing 10 9 Support shaft 110 Radial bearing 111 Ball bearing 1 1 2 Swing shaft 113 Radial bearing 114 Extension arm 1 1 5 Through hole 38
3〗2/發明說明書(補件)/93-05/93105275 200424424 116 空氣導入罩 117 空氣導入通路 118 空氣排出通路 1 2 3 F 閥動室 1 24 曲軸室 1 25 油儲存室 1 26 燃燒室 1 27 吸氣閥 1 28 排氣閥 1 29 吸氣側閥彈簧 1 30 排氣側閥彈簧 13 1 凸輪軸 1 32 第1搖軸 13 3 第2搖軸 1 34 第1搖臂 1 3 4 a 接觸臂 1 3 4 b 接觸臂 135 第2搖臂 1 3 5 a 接觸臂 1 3 5 b 接觸臂 1 36 支承部 1 37 支承部 1 38 軸承孔 1 39 軸承孔 312/發明說明書(補件)/93-05/93105275 200424424 140 球 軸 承 141 球 轴 承 142 第 1 凸 輪 143 第 2 凸 輪 144 滾 子 145 滾 子 軸 承 146 凸 輪 滑 塊 148F 凸 輪 鏈 條 室 148R 凸 輪 鏈 條 室 149F 從 動 鏈 輪 1 49R 從 動 鏈 輪 1 50F 鏈 條 拉 伸 器 1 50R 鏈 條 拉 伸 器 151F 拉 伸 支 撐 器 151R 拉 伸 支 撐 器 1 52F 鏈 條 導 向 器 1 52R 鏈 條 導 向 器 153 箭 頭 154 支 承 部 分 材料 155 螺 栓 156 凸 輪 脈 衝 器 1 56a 突 部 157 螺 栓 158a 火 星 塞 312/發明說明書(補件)/93-05/93105275 200424424 1 5 8 b壓縮上死點檢測感測器 15 9 安裝用凹部 160 安裝孔 1 6 1 F 頭蓋連接面 1 6 1 R 頭蓋連接面 1 6 2 F 凹部 1 6 2 R 凹部 163 蓋部 164 密封墊片 CF 汽缸軸線 CR 汽缸軸線 E 引擎 FB 前部汽缸侧體 P 動力單元 RB 後部汽缸側體 T 動力傳送裝置 WF 前輪 WR 後輪 413 〖2 / Invention specification (Supplement) / 93-05 / 93105275 200424424 116 Air introduction cover 117 Air introduction passage 118 Air exhaust passage 1 2 3 F Valve actuating chamber 1 24 Crankshaft chamber 1 25 Oil storage chamber 1 26 Combustion chamber 1 27 Intake valve 1 28 Exhaust valve 1 29 Intake-side valve spring 1 30 Exhaust-side valve spring 13 1 Camshaft 1 32 First rocker shaft 13 3 Second rocker shaft 1 34 First rocker arm 1 3 4 a Contact Arm 1 3 4 b Contact arm 135 2nd rocker arm 1 3 5 a Contact arm 1 3 5 b Contact arm 1 36 Support part 1 37 Support part 1 38 Bearing hole 1 39 Bearing hole 312 / Instruction manual (Supplement) / 93 -05/93105275 200424424 140 Ball bearing 141 Ball bearing 142 1st cam 143 2nd cam 144 Roller 145 Roller bearing 146 Cam slider 148F Cam chain chamber 148R Cam chain chamber 149F Driven sprocket 1 49R Driven sprocket 1 50F chain stretcher 1 50R chain stretcher 151F stretch support 151R stretch support 1 52F chain guide 1 52R chain guide 153 arrow 154 support part material 155 bolt 156 cam vein Puncher 1 56a Projection 157 Bolt 158a Mars plug 312 / Invention manual (Supplement) / 93-05 / 93105275 200424424 1 5 8 b Compression top dead center detection sensor 15 9 Mounting recess 160 Mounting hole 1 6 1 F Head cover connection surface 1 6 1 R Head cover connection surface 1 6 2 F Recess 1 6 2 R Recess 163 Cover 164 Gasket CF Cylinder axis CR Cylinder axis E Engine FB Front cylinder side body P Power unit RB Rear cylinder side body T Power transmission WF front wheel WR rear wheel 41
312/發明說明書(補件)/93-05/93105275312 / Invention Specification (Supplement) / 93-05 / 93105275