200417688 (1) 玖、發明說明 【發明所屬之技術領域】 本發明是關於壓縮供給空氣等的流體（主】 壓縮機，尤其是關於活塞式壓縮機。本發明尤 將壓縮空氣適合供給內燃機的燃料噴射裝置的 【先前技術】 壓縮供給空氣等流體的活塞式壓縮機爲以 ，例如，日本專利特公昭63 -54909號公報、 65 181號公報所揭示的冷凍裝置用的活塞式壓 ，在內燃機的燃料噴射裝置中使用空氣壓縮機 熟知，例如日本專利2820782號公報所揭示將 給2衝程引擎空氣燃料噴射裝置的活塞式空秦 〇 以上的活塞式壓縮機安裝有形成圓筒形汽 缸體上端面覆蓋該汽缸空間的汽缸頭，在汽缸 由滑動嵌合配設活塞，汽缸頭設置吸氣及排氣 此外’吸氣閥爲設置可自由開關連接流體供給 路，使流體形成僅容許流入汽缸空間內流動的 成’排氣閥是設置可自由開關連接流體供給源 ，使流體形成僅容許從汽缸空間流出流體的單 。該等吸氣.閥及排氣閥，具備有薄的撓性金屬 簧片閥式的閥，或者使閥體利用作用彈簧的作 通路而著位的提動閥式的閥。 ㊂爲氣體）的 其是關於可 S縮機。 往即已熟知 特開昭6 3 -縮機。並且 也爲一般所 壓縮空氣供 泵（壓縮機） 缸空間的汽 空間內可自 閥所構成。 源的流入通 單向閥所構 的流出通路 向閥所構成 板所構成的 用堵塞流出 -5- (2) (2)200417688 【發明內容】 〔發明所欲解決之課題〕 以上的壓縮機中，從流入及流出通路的單向閥連接汽 缸空間內的空間部分藉著活塞的往返運動壓縮汽缸空間內 的流體時形成死點空間，形成壓縮效率變小的一個原因等 課題。並且使用提動閥式的單向閥時’爲了防止關閉時提 動閥抵接著位面產生噪音的同時確保關閉時的密閉性’多 在提動閥的著位面黏貼薄的橡膠密封材（彈性密封材）’但 是會容易產生該橡膠密封材耐久性的問題。尤其是與橡膠 密封材的著位面內周圍緣部相對的部分，相對於著位面與 抵接部分的壓縮變形，由於內周圍部分不產生壓縮變形， 因此有造成與著位面內周圍緣部相對的部分的壓縮變形量 有大的變化等課題。 本發明有鑒於以上的問題，提供一種減小流入或流出 通路造成的死點空間產生量提高壓縮效率，並且可提高提 動閥的彈性密封材的耐久性所構成的壓縮機爲目的。 〔解決課題用的手段〕 爲了以上目的的達成，第1圖的本發明中，具備有圓 筒形汽缸空間的汽缸體（壓縮機汽缸體）；該汽缸體上覆蓋 汽缸空間安裝的汽缸頭（壓縮機汽缸頭）；在汽缸空間內可 自由滑動嵌合配設的活塞（壓縮機活塞）；汽缸頭上可自由 關閉地覆蓋連通汽缸空間形成流體穿通孔（例如，實施形 (3) (3)200417688 態的空氣穿通孔52b)的單向閥（例如實施形態的提動閥70 ，）所構成的壓縮機。並且，此一單向閥具有著位於直徑 大於流體穿通孔的著位面覆蓋流體穿通孔的閥體所構成， 與該閥體的著位面抵接的部分接合設有薄板狀的彈性密封 構件，此時，形成彈性密封構件使與彈性密封構件的著位 面抵接的部分的內周圍緣部（例如，實施形態的彈性密封 構件73的環形外圍面73b的內周圍緣部）位在較著位面 的流體穿通孔內周圍緣部的更外圍側。 以上構成的壓縮機中，雖然藉著活塞嵌合汽缸空間的 狀態下往返滑動使單向閥開啓動作進行流體的壓縮供給， 但是此時藉著設置在閥體的彈性密封構件的作用，降低閥 體抵接著位面產生的噪音，並且使閥體著位於著位面封閉 流體穿通孔時可確實將此部份密封。與進行上述作用的彈 性密封構件的著位面抵接的部分（實施形態的彈性密封構 件73的環形外圍面73b)，由於其內周圍面形成較著位面 的內周圍緣部更外側的位置，因此該抵接的部分不與內周 圍緣部抵接，而是形成與彈性密封構件的著位面抵接的部 分整體（環形外圍面73b整體）抵接著位面接受大致均勻壓 縮力的構成，可提高彈性密封構件的耐久性。 第2的本發明中，同樣具備有圓筒形汽缸空間的汽缸 體；覆蓋該汽缸體的汽缸空間安裝的汽缸頭；在該汽缸空 間內自由滑動嵌合配設的活塞；汽缸頭上可自由關閉地覆 蓋連通汽缸空間形成流體穿通孔的單向閥所構成的壓縮機 。此一壓縮機中，與活塞的汽缸頭相對的面上，活塞位於 -7- (4) 200417688 上死點附近時形成突出流體穿通孔內（例如，實 空氣穿通孔52b的內部空間）的凸部。以上構成 中’活塞從下死點移動至上死點壓縮汽缸空間內 ’凸部突出流體穿通孔內同樣壓縮該空間部分的 此可減小死點空間提高壓縮效率。 第3的本發明中，同樣具備有圓筒形汽缸空 體；該汽缸體上覆蓋汽缸空間安裝的汽缸頭；在 間內自由滑動嵌合配設的活塞；汽缸頭上可自由 蓋連通汽缸空間形成流體穿通孔的單向閥所構成 。此一壓縮機中，與活塞的汽缸頭相對的面上， 上死點附近時形成突出流體穿通孔內的凸部，構 位於直徑大於流體穿通孔的著位面而覆蓋流體穿 板狀閥體的單向閥，與該閥體的著位面抵接的側 置薄板狀彈性密封構件，彈性密封構件與著位面 通孔內周圍緣部相對的部分呈凹陷（例如，實施 狀凹槽73a)。 以上構成的壓縮機中，藉著設置在與閥體著 的側面的彈性密封構件，與第1發明的場合同樣 閥體與著位面抵接產生的噪音，並且閥體著位於 閉流體穿通孔時可確實將此部份密封。並且藉著 活塞的汽缸頭相對的面（活塞頭面）上的凸部，與 發明的場合同樣地，當活塞移動至上死點附近時 流體流通孔內同時壓縮該空間的流體提高壓縮效 ，彈性密封構件僅使得與著位面的流體穿通孔內 施形態的 的壓lis機 的流體時 流體，因 間的汽缸 該汽缸空 關閉地覆 的壓縮機 活塞位於 成具有著 通孔的平 面接合設 的流體穿 形態的環 位面抵接 ，可降低 著位面封 設置在與 第2之本 凸部突出 率。此外 周圍緣部 -8- (5) (5)200417688 相對的部分凹陷，與活塞頭面相對的部分同樣設置彈性密 封構件。藉此彈性密封構件可發揮緩衝吸收功能，因此當 活塞位在上死點位置附近時，可以設定使上述凸部前端極 爲接近設有閥體壇性密封構件的面上，更提高其壓縮效率 〇 第4的本發明中，具備有圓筒形汽缸空間的汽缸體； 該汽缸體上覆蓋汽缸空間安裝的汽缸頭；在該汽缸空間內 自由滑動嵌合配設的活塞；汽缸頭上可自由關閉地覆蓋連 通汽缸空間形成流體穿通孔的單向閥，與活塞的汽缸頭相 對的面（活塞頭面）上，位於上死點附近時形成突出流體穿 通孔內的凸部等所構成的壓縮機。此外，將此壓縮機安裝 在內燃機’受此內燃機之曲軸轉動驅動力使活塞在汽缸空 間內往返滑動，將壓縮空氣供給內燃機的燃料噴射裝置。 在此構成的壓縮機中同樣使形成在活塞頭面的凸部突出流 體穿通孔內同時壓縮此一部份的流體獲得高的壓縮效率， 以上述高的壓縮效率將所壓縮的空氣供給燃料噴射裝置， 進行良好的燃料噴射。 【實施方式】 以下’參閱圖示說明本發明的最佳實施形態。第1圖 〜第4圖表示具備運用本發明的壓縮機所構成的機車驅動 裝置，針對該驅動裝置構成首先說明如下。並且，第1圖 及第2圖在表示空間方便上，在截線部分上是以二分割表 示。兩圖是表示以截線部分連接成一個圖面。該驅動裝置 -9- (6) (6)200417688 具備單氣筒的引擎部E與變速機部TM，藉著變速機部 TM使該引擎部E的曲軸1 6的轉動驅動力變速’傳達至 輸出驅動鏈輪SP，同時從輸出驅動鏈輪SP經由位圖示的 鏈條傳達至後輪，構成可驅動後輪。 首先針對引擎部E說明如下。引擎部E，具備有圓筒 形汽缸內周圍面10a的引擎汽缸體10 ;覆蓋引擎汽缸體 10上面而安裝的引擎汽缸頭12;汽缸內周圍面10&上可 軸向滑動移動地嵌合配設在引擎汽缸體1 〇內的活塞1 3 ; 支撐汽缸體1 0的外罩H S G內朝著與汽缸軸正交方向延伸 的同時，藉著軸承17a、17b、17c可自由轉動支撐的曲軸 1 6 ;及前端部1 4 a經由活塞銷1 3 a樞接活塞1 3的同時， 基端部1 4 b經由曲軸銷1 5樞接在曲軸1 6的曲柄部1 6 a上 的連桿夾套1 4。 引擎汽缸頭12安裝點火塞21及燃料噴射裝置22， 引擎汽缸體1 0內藉著燃料噴射裝置22將壓縮空氣與燃料 的混合氣體噴射至包圍汽缸頭1 2與活塞1 3的燃燒室1 1 內，形成以點火塞12點火燃燒。引擎汽缸頭1 2如第3圖 所示藉著彈簧23a、24a安裝朝著封閉方向作用的吸氣閥 23及排氣閥24，吸氣閥23可以使形成在汽缸頭12的吸 氣通路12a開關，排氣閥24則可以開關排氣通路12b。 並且’吸氣通路12a連接吸氣歧管25，排氣通路12b的 出口端12c連接排氣歧管（未圖示）。 引擎部E爲4衝程式引擎所構成，活塞13在2往返 之間’進行吸氣、壓縮、燃燒、排氣行程，並配合此進行 -10- (7) (7)200417688 閥2 3、2 4的開關動作。由於該供排氣閥2 3、2 *的開關動 作，曲軸16的端部結合設置第1鏈輪3 1，自由轉動設置 在引擎汽缸體1 〇側部的凸輪軸3 4設有第2鏈輪3 3，第1 及第2鏈輪3 1 ' 3 3捲掛有第}鏈條3 ^設定第1及第2 鍵3 1、3 3的園數爲1 : 2，以曲軸1 ό的1 / 2的轉速轉動 驅動凸輪軸3 4。凸輪軸3 4上形成吸氣用凸輪部3 4 a與排 氣用凸輪部3 4 b，分別藉連結銷3 5 a、3 6 a將樞接引擎汽 缸體1 〇上的凸輪從動件3 5、3 6的滾子3 5 b、3 6 b抵接在 各凸輪部34a、34b上（參閱第4圖）。 另一方面，引擎汽缸頭1 2的上面藉樞接銷3 9 a、4 0 a 樞接供排氣閥動作用的鎖緊臂3 9、4 0形成可自由擺動地 安裝，連接該等鎖緊臂3 9、4 0 —端與上述凸輪從動件3 5 、3 6配設如圖所示的推桿3 7、3 8。鎖緊臂3 9、4 0的另外 端抵接上述供排氣閥23、24的前端，可藉著鎖緊臂39、 40的擺動使供排氣閥23、24抵抗彈簧23a、24a的作用 而下壓使其開放。 上述構成的機構中，以曲軸16的1/2轉速轉動驅動 凸輪軸3 4，並對應此使凸輪從動件3 5、3 6每轉動一次凸 輪軸3 4時即上下擺動一次（S卩’曲軸1 6每轉動二次爲一 次），對應此一擺動上下往返移動推桿3 7、3 8使鎖緊臂 3 9、4 0經由樞接銷3 9 a、4 0 a擺動，供排氣閥2 3、2 4抵 抗彈簧2 3 a、2 4 a的作用而下壓開放，使吸氣及排氣通路 12a、12b與燃燒室I1連通。並且’設定凸輪部34a、34b 使吸氣閥2 3在吸氣行程開放’排氣閥2 4在排氣行程開放 -11 - (8) (8)200417688 又，以預定的時間從燃料噴射裝置2 2將壓縮空氣與 燃料的混合氣體噴入燃燒室丨丨內，以點火塞2 1點火燃燒 該混合氣體進行燃燒行程。此時，從燃料噴射裝置22將 局濃度的混合氣體噴射點火塞2 1的前端點火部2 1 a的周 圍進行效率良好的燃燒，同時整體進行稀薄燃燒獲得燃燒 效率提昇的同時並可獲得排氣氣體的淸潔化。 如上述爲了進行氣動式燃料噴射，除了上述燃料噴射 裝置22之外，具有從燃料泵（未圖示）經由燃料供給管路 27a(參閱第6圖）將所供給的燃料供給混合室7內的燃料 供給裝置2 7，及將壓縮空氣供給混合室2 8內的壓縮機5 0 。在混合室2 8內混合燃料供給裝置2 7所供給的燃料與壓 縮機5 0所供給的壓縮空氣製造具有噴霧狀燃料的高濃度 混合氣體，該混合氣體利用本身的內部壓力從燃料噴射裝 置22的噴射部22a以預定的時間噴入燃燒室內。並且， 貫穿上下覆蓋引擎汽缸頭1 2上面安裝的頭罩2 6形成混合 室形成孔2 6 a，該混合室形成孔2 6 a內，從上下夾持分別 嵌入的燃料供給裝置27與燃料噴射裝置22形成混合室 28。 參閱第5圖〜第7圖說明上述壓縮機5 0的構造及驅動 此的機構如下。壓縮機5 0是與引擎汽缸頭1 〇 —體連接的 構成，具備有圓筒形汽缸內周圍面5 1 a的壓縮機汽缸體 5 1 ;覆蓋壓縮機汽缸體5 1的上面安裝的壓縮機汽缸頭5 2 ;汽缸內周圍面5 1 a上可軸向滑動移動嵌合配設在壓縮機 -12- (9) (9)200417688 汽缸體5 1內的壓縮機活塞5 3 ;及以壓縮機活塞5 3嵌合 汽缸內周圍面5 1 a的狀態滑接往返運動用的止轉棒軛機構 S Y所構成。止轉棒軛機構S Y具有與壓縮機活塞5 3 —體 連接的平板狀活塞桿5 4的前端所形成的滑動孔5 4 a內嵌 合，形成與汽缸軸直角自由滑動配設的滑動件5 5，在設 置引擎汽缸體1 〇側部的壓縮機驅動軸5 6前端偏心形成的 偏心軸5 7，偏心軸5 7可自由轉動嵌合連結在滑動件5 5 上。並且，壓縮機驅動軸56藉著軸承58a、58b利用引擎 汽缸體1 〇自由轉動地支撐。 以上的構成中，一旦轉動驅動壓縮機驅動軸5 6時， 藉著止轉棒軛機構S Y的作用可以使壓縮機活塞5 3在汽 缸內周圍面51a —邊滑動並形成往返運動。由於該壓縮驅 動軸5 6的轉動驅動，與結合配設在凸輪軸3 4的第2鏈輪 3 3 —體設置第3鏈輪6 0，壓縮驅動軸5 6結合配設第4鏈 輪61，第3及第4鏈輪60、61捲掛有第2鏈條62。第3 及第4鏈輪60，61具有相同齒數，兩者是與第2鏈輪33 相同的轉速轉動。因此，第4鏈輪6 1是以引擎曲軸1 6的 1 /2的轉速轉動，壓縮機驅動軸5 6是以此相同轉速轉動， 使壓縮機活塞5 3在引擎曲軸1 6轉動兩次時進行一往返運 動。 如上述對應壓縮機活塞53的往返運動，將空氣吸入 汽缸內周圍面5 1 a內的壓縮機汽缸頭5 2與壓縮機活塞5 3 所包圍的汽缸空間50a內壓縮，因此在壓縮機汽缸頭52 ’如第8圖擴大詳細表市設置吸氣簧片閥64及排氣提動 -13- (10) (10)200417688 閥70。 吸氣簧片閥64是將薄金屬板所成的閥片63沖壓加工 成第1 〇圖表示的形狀而形成舌片形。該閥片6 3是夾持壓 縮機汽缸體5 1的上端面與壓縮機汽缸頭5 2下端面之間安 裝’舌片形吸氣簧片閥64從下面側覆蓋形成在壓縮機汽 缸頭5 2的吸氣孔5 2 a。此時，閥片6 3是相對於內周圍面 5 1 a(以兩點虛線表示）配設形成圖示的位置關係，藉著插 入形成於閥板6 3之插入孔6 3 a的結合螺栓，結合壓縮機 汽缸體5 1與壓縮機汽缸頭5 2。並且，如圖示形成突入形 成在後述壓縮機活塞5 3的凸部用的圓形孔6 5。 該吸氣簧片閥6 4如第8圖如箭頭A所示，壓縮機活 塞5 3向下方移動時，受到汽缸空間5 0 a內產生的負壓如 圖中兩點虛線所示彈性變形撓曲，經吸氣孔52a吸入外部 空氣。另一方面，如箭頭B表示壓縮機活塞53向上方移 動時，受到本身的彈性變形恢復力及汽缸空間5 0a內產生 的空氣壓力使吸氣簧片閥64密接吸氣孔52a將其堵塞， 阻止汽缸空間50a內的壓縮空氣經由吸氣孔52a漏出外部 〇 另一方面，排氣提動閥70如第9圖擴大表示，爲配 設著位於壓縮機汽缸頭52所形成壓縮空氣穿通空間52d 內的著位面52c的圓板形閥體71，及將此閥體71朝著著 位面52c的著位方向作用的壓縮彈簧74所構成，從壓縮 空氣穿通空間52d的著位面52連通汽缸空間50a形成空 氣連通孔52b，閥體71在著位於著位面52c的狀態下藉 -14- (11) (11)200417688 著閥體7 1覆蓋空氣穿通孔5 2b而封閉。 該閥體7 1是如第1 1圖表示，在圓盤形金屬板72的 下面設置橡膠等薄層所成的彈性密封層73所構成。彈性 密封層7 3形成環形凹槽7 3 a的同時，在凹層7 3 a內的四 個位置形成凹部73d。並且，凹部73d在金屬板72下面 設置彈性密封層7 3時爲支撐金屬板7 2所產生的凹部。環 形凹部7 3 a可從第9圖得知，形成與著位面5 2 c的空氣穿 通孔5 2b的內周圍緣部p相對。即，藉著環形凹槽7 3 a將 彈性密封層7 3的表面分割爲環形外圍面7 3 b與圓形內周 圍面73c，但是環形外圍面73b的內周圍緣部位在較著位 面5 2c的空氣穿通孔52b的內周圍緣部P的外圍側，圓形 內周圍面73c的外圍緣部位在較著位面52c的空氣穿通孔 5 2b的內周圍緣部P的內周圍側位置。因此，閥體71著 位於著位面時，僅彈性密封層7 3的環形外圍面7 3 b與著 位面5 2 c抵接，圓形內周圍面7 3 c只與空氣穿通孔5 2 b相 對不致與著位面52c抵接。 上述構成的排氣提動閥7 0如第8圖箭頭A表示使壓 縮機活塞5 3向下方移動時，受到汽缸空間5 0a內產生的 負壓以著位於著位面52c的狀態保持閥體71堵塞空氣穿 通孔52b，防止壓縮空氣穿通空間52d內的壓縮空氣朝著 汽缸空間5 0a內逆流。此時，使橡膠等構成的彈性密封層 73(尤其是環形外圍面73b)與著位面52d密接，確保堵 塞時的密封性。另一方面，如箭頭B表示壓縮活塞5 3向 上方移動時，壓縮吸入汽缸空間5 0a內的空氣藉著產生的 -15- (12) (12)200417688 壓力，使閥體7 1抵抗壓縮彈簧74的作用力上升，使壓縮 後的空氣通過空氣穿通孔5 2b壓出壓縮空氣穿通空間52 內。 以上的說明可得知，一旦轉動曲軸1 6時，此一轉動 經第1及第2鏈條3 2、62傳達以曲軸1 6的1 /2轉速轉動 驅動壓縮機驅動軸5 6，壓縮機活塞5 3對應壓縮機驅動軸 5 6的轉動往返運動，使得壓縮機活塞5 3對應壓縮機驅動 軸5 6的轉動而往返運動。此一結果，曲軸1 6的每2次轉 動使壓縮機活塞5 3進行一次往返運動。如上述當壓縮機 活塞5 3往返運動時，在壓縮機活塞5 3的向下運動行程（ 箭頭A方向移動的行程）中開放吸氣簧片閥64從吸氣孔 5 2a將外部空氣吸入汽缸空間50a內，向上運動行程（箭頭 B方向移動的行程）中開放排氣提動閥7 0，將對應壓縮機 活塞5 3的向上運動被壓縮之汽缸空間5 0 a內的壓縮空氣 推出壓縮空氣穿通空間52d。並且，以上推出壓縮空氣的 時間是如上述與曲軸1 6的轉動同步，配合燃料噴射裝置 22的燃料噴射進行。 又，如圖示，在壓縮機活塞5 3的上端面形成圓筒形 凸部5 3 a。該凸部5 3 a具有稍微小於空氣穿通孔5 2 b小的 直徑，壓縮機活塞53向上運動至上死點附近爲止時，構 成凸部53a突入空氣穿通孔52b內。藉此，空氣穿通孔 52b內部空間的空氣爲凸部53a所壓縮形成推出壓縮空氣 穿通空間52d內，壓縮死點空間小時可形成高的壓縮效率 。其中，壓縮機活塞5 3位於上死點時，使凸部5 3 a的前 -16- (13) (13)200417688 端面儘可能地接近彈性密封層7 3的圓形內周圍面7 3 c構 成儘可能地提高壓縮效率。 如上述，將壓縮空氣推出壓縮空氣穿通空間5 2 d內， 使排氣提動閥7 0的閥體7 1上下運動時，可提高閥體7 1 與著位面5 2 c間的密接性，同時爲了降低閥體7 1抵接著 位面5 2 c時的噪音，同樣在環形外圍面7 3 b設置彈性密封 層7 3。其中，如上述，環形外圍面7 3 b的內周圍緣部位 在著位面52c的空氣穿通孔52b內周圍緣部P更外圍側的 位置，因此當閥體71著位於著位面52c時，環形外圍面 73b的整體與著位面52c抵接，對於此一部份施以均勻壓 縮力的作用，因此可提高彈性密封層7 3的耐久性。 如上述供給壓縮空氣的壓縮空氣穿通空間52d連接有 壓縮空氣供給管75，該空氣供給管75是如第6圖表示， 與形成在引擎汽缸頭1 2的壓縮空氣供給通路7 6連接。壓 縮空氣供給通路7 6在混合室形成孔2 6 a形成開口，如上 述爲上下嵌入混合室形成孔2 6內的燃料供給裝置2 7 a與 燃料噴射裝置2 2所夾持形成的混合室2 8內供給壓縮空氣 並且’雖然形成連接混合室形成孔2 6 a上側的較大直徑 的燃料供給裝置配設孔2 6 b，在此配設燃料供給裝置2 7， 糸m燃料供給管路2 7 a供給的燃料經燃料供給裝置2 7供給 混合室28內。又，調整從壓縮機50供給混合室28內的 壓縮空氣之壓力的調壓裝置78是連接上述壓縮空氣供給 通路76設置（參閱第4圖）。 另一方面，如第7圖表示，連接與形成壓縮機驅動軸 -17- (14) (14)200417688 5 6的偏心軸5 7側的相反側端部設置電磁聯結方式水泵 WP。該水泵WP爲經由連結構件8 〇聯結壓縮機驅動軸5 6 的外磁鐵8 1 ;經隔離構件8 4相對配設在外磁鐵8 1內部 的內磁鐵8 2 ;與內磁鐵8 2結合的泵軸8 3 ;及安裝在泵軸 83前端的泵葉片85所構成。隔離構件84隔離出配設有 壓縮機驅動軸5 6的工作油流動空間，及配設有泵葉片8 5 的冷卻水流動的空間。外磁鐵8 1與內磁鐵8 2構成非接觸 式聯結器機構，雖是夾持隔離構件8 4使其遠離，但是也 可以藉著兩者間的磁力作用使一側轉動追隨另一側轉動。 上述的水泵WP中，如上述藉著曲軸1 6的轉動而轉 動壓縮機驅動軸5 6，使與此一起轉動驅動外磁鐵8 1時’ 藉著磁力聯結器作用連動轉動驅動內磁鐵，經泵軸8 3轉 動驅動泵葉片8 5。藉此，從水槽吸入引擎冷卻水’從吐 出口 8 7吐出。並且，吐出口 8 7連接冷卻水供給管（未圖 示），此一冷卻水供給管連接第4圖表示的冷卻水入口部 8 8，由此對形成引擎汽缸體1 〇及引擎汽缸頭1 2內的冷卻 水通路供給冷卻水’使該冷卻水通路循環進行引擎汽缸體 10及引擎汽缸頭12冷卻的冷卻水是從冷卻水出口部89( 參閱第1圖）經由未圖示的管送至散熱氣。此外，水泵WP 中，從泵葉片8 5至吐出□ 8 7通過冷卻水的部分設置恒溫 器閥門8 6。 啓動以上構成的引擎邰E用的起動馬達1是如弟4圖 表示安裝於外罩H S G上。該起動馬達1的驅動軸上安裝 有起動小齒輪（未圖示）’該起動小齒輪是與耢者單向離合 -18- (15) (15)200417688 器（未圖示）安裝在曲軸端部的起動齒輪2咬合。並且，在 曲軸1 6的端部安裝發電機G，藉曲軸1 6驅動進行發電， 但也可以將上述單向離合器定位在該發電機G內。 驅動起動引擎部E用的起動馬達丨時，經起動小齒輪 轉動驅動起動齒輪2，而轉動驅動曲軸1 6。藉此，如上述 驅動壓縮機5 0將壓縮空氣供給混合室2 8。與此的同時藉 著曲軸1 6的轉動驅動燃料泵（未圖示），並經由燃料供給 裝置2 7將燃料同時供給混合室2 8。在混合室2 8內混合 該等壓縮空氣與燃料製成高濃度的混合氣體，此係配合活 塞1 3的往返運動噴射至燃燒室1 1內的同時，藉點火塞 2 1點火燃燒，起動引擎部E。此時，如上述爲了提高壓縮 機5 0的效率，可以順暢地起動引擎部E。 如上述起動引擎部E後，針對使曲軸1 6的轉動驅動 力變速傳達至驅動鏈輪S P的變速機部TM，除了第2圖 以外並參閱擴大變速機部TM表示的第1 2圖說明如下。 變速機部TM具有設置在曲軸16端部的離心離合器CL1 ;與曲軸1 6平行配設的輸入軸9 1與輸出軸92 ;設置在 輸入軸9 1端部的濕式多板離合器CL2 ;及排列配設在輸 出入軸91、92之間的第1速〜第4速變速齒輪110〜140所 構成，輸出軸92的端部安裝有驅動鏈輪SP。 離心離合器CL 1是作爲可自由轉動配設在曲軸1 6上 的傳達驅動齒輪93與曲軸1 6之用，曲軸1 6的轉動形成 預定轉動以上時藉著離心力的動作，將傳動驅動齒輪93 結合在曲軸1 6上使兩者一體轉動。傳達驅動齒輪9 3是咬 -19- (16) (16)200417688 合在可自由轉動配設在輸入軸9 1上的傳達從動齒輪94上 ’將傳達驅動齒輪9 3的轉動傳達至傳達從動齒輪9 4。傳 達從動齒輪94是藉著濕式多板離合器CL2形成可自由卡 脫於輸入軸9 1，可以卡合濕式多板離合器c L 2使傳達從 動齒輪9 4與輸入軸9 1 一體轉動。 濕式多板離合器C L 2爲結合傳達從動齒輪9 4的離合 器鼓96;栓槽結合輸入軸91的離合器轂97;交替重疊連 結在離合器鼓9 6的離合器板及聯結在離合器轂9 7的摩擦 板配置的多板離合器部9 8 ;與多板離合器部9 8相對的活 塞構件99a ;將活塞構件99a緊貼多板離合器部98的彈 簧9 9b ;及使活塞構件99a朝著遠離多板離合器部98的 方向移動的球形凸輪機構9 5所構成。通常不使球形凸輪 機構95動作，彈簧99b將活塞構件99a緊貼多板離合器 部96卡合濕式多板離合器CL2，使傳達從動齒輪94與輸 入軸9 1 一體轉動。變速時球形凸輪機構9 5動作，使活塞 構件99a從多板離合器部96遠離解放濕式多板離合器 CL2，形成傳達從動齒輪94與輸入軸9 1不進行轉動傳達 的狀態。 第1速〜第4速齒輪列11〇〜140爲設置在輸入軸91上 的第1〜第4速驅動齒輪1 1 1〜1 4 1 ;及設置在輸出軸92上 分別與第1〜第4速驅動齒輪1 1 1〜141咬合的第1〜第4速 從動齒輪1 12〜142所構成。第1速驅動齒輪1 1 1是與輸入 軸91 一體形成，第2速驅動齒輪1 2 1是可相對自由轉動 配設在輸入軸上，同時形成第1合釘1 2 1 a，第3速驅動 -20- (17) (17)200417688 園輪131是栓槽結合在輸入軸91上，同時形成有第2合 釘131a、第1合釘卡合孔131及第1叉形槽131c，第4 速驅動齒輪1 4 1可相對自由轉動地配設在輸入軸9 1上的 同時形成桌2合釘卡合孔1 4 1 a。又，第1速從動齒輪u 2 可相對自由轉動地配設在輸出軸上的同時形成第3合釘卡 合孔1 1 2 a ’第2速從動齒輪1 2 2與輸出軸9 2栓槽結合的 同時，形成第3合釘122a、第4合釘122b及第2叉形槽 1 2 2 c ’第3速從動齒輪1 3 2可相對自由轉動地配設在輸出 軸9 2上的同時形成第4合釘卡合孔1 3 2 a，第4速從動齒 輪142栓槽結合在輸出軸92上。 該等第1速〜第4速變速齒輪列1 1 0〜1 4 0的側方設有 旋轉式變速機構1 5 0，構成此機構的第1及第2移位叉 151、152的前端叉形部是卡合在上述第1及第2叉形槽 131c、122c內。兩移位叉151、152可自由轉動且軸向自 由移動地安裝在移位鼓1 5 3上，同時將銷1 5 1 a、1 5 2 a卡 合在凸輪槽1 5 3 a、1 5 3 b內，因應移位鼓1 5 3的轉動構成 軸向移動。移位鼓1 5 3是藉著環機構1 5 4連接移位踏板（ 未圖示），操作移位踏板時對應此一操作轉動移位鼓1 5 3 ，使第1及第2移位叉151、152軸向移動。 其中，第2移位叉152在圖中朝著左方向移動時，第 2速從動齒輪122朝著左方向移動使第3合釘122a嵌入 第3合釘卡合孔U2a內，使第1速從動齒輪112與第2 速從動齒輪1 2 2結合。因此，輸入軸91的轉動是從第1 速齒輪列1 1 0 (第1速驅動齒輪1 1 1及第2速從動齒輪 -21 - (18) (18)200417688 1 1 2 )經由第2速從動齒輪1 2 2傳達至輸出軸9 2 ’進行對 應第1速齒輪列1 1 0的齒輪比變速。另一方面’第2移位 叉152朝著又方向移動時，第4合釘l22b嵌入第4合釘 卡合孔1 3 2 a內，使第2速從動齒輪1 2 2與第3速從動龜 輪1 3 2結合。因此，輸入軸9 1的轉動是從第3速齒輪列 13 0(第3速驅動齒輪131及第3速從動齒輪132)經由第2 速從動齒輪1 2 2傳達至輸出軸9 2，進行對應第3速齒輪 列1 3 0的齒輪比變速。 另外，第1移位叉151在圖中朝著左方向移動時，第 3速驅動齒輪131朝著左方向移動將第1合釘121a嵌入 第1合釘卡合孔1 1 3 b，使第2速驅動齒輪1 2 1與第3速 從動齒輪1 3 1結合。因此輸入軸9 1的轉動是從第3速驅 動齒輪1 3 1的狀態傳達至第2速驅動齒輪1 2 1 ’經由第2 速齒輪列1 2 0 (第2速驅動齒輪1 2 1及第2速從動齒輪 1 2 2 )傳達至輸出軸9 2，進行對應第2速齒輪列1 2 0齒輪 比的變速。另一方面，第1移位叉1 5 1朝著右方向移動時 ，將第2合釘131a嵌入第2合釘嵌合孔141a，使第3速 驅動齒輪1 3 2與第4速從動齒輪1 42結合。因此，輸入軸 9 1在轉動狀態下從第3速驅動齒輪1 3 1傳達至第4速驅 動齒輪141，經由第4速齒輪列14 0(第4速驅動齒輪141 及第4速從動齒輪142)傳達輸出軸92，進行對應第4速 齒輪列1 4 0齒輪比的變速。 如上述經由任意的第1速〜第4速齒輪列1 10〜140而 變速驅動的輸出軸92的轉動在其狀態下傳達至輸出驅動 -22- (19) (19)200417688 鏈輪SP，如上述，經由未圖示的鏈條傳達至後輪並驅動 後輪。 以上之中，運用本發明的壓縮機雖是爲了製造與燃料 混合的混合氣之用，當然也可以運用在除此以外的壓縮機 。並且，壓縮對象不限於空氣，也可以是其他的氣體。 〔發明效果〕 根據以上說明的第1的本發明，具備汽缸體、汽缸頭 、活塞及單向閥構成壓縮機，該單向閥具有著位在直徑大 於流體穿通孔的著位面覆蓋流體穿通孔的閥體所構成，與 該閥體的著位面抵接的部分接合設置薄板狀的彈性密封構 件，此時，與彈性密封構件的著位面抵接部分的內周圍緣 部形成有位在較著位面的流體穿通孔內周圍緣部外圍側的 彈性密封構件。以上構成的壓縮機中，活塞嵌合汽缸空間 的狀態下往返滑動，藉以使單向閥開關動作壓縮流體而供 給，但是此時，藉著設置在閥體的彈性密封構件的作用， 可以降低閥體抵接著位面產生的噪音，並且使閥體著位於 著位面封閉流體穿通孔時，可以確實使該部分密封。抵接 進行上述作用的彈性密封構件的著位面的部分，其內周圍 緣部是形成較著位面內周圍緣部外側的位置，因此該抵接 部分不會與內周圍緣部抵接，與彈性密封構件的著位面抵 接的部分整體抵接著位面，形成接受大致均勻壓縮力的構 成，可提高彈性密封構件的耐久性。 第2的本發明中，同樣具備汽缸體、汽缸頭、活塞及 -23- (20) (20)200417688 單向閥構成壓縮機，該壓縮機中，與活塞的汽缸頭相對的 面上’活塞位於上死點附近位置時形成突出流體穿通孔內 的凸部。以上構成的壓縮機中，活塞從下死點移動至下死 點壓縮汽缸空間內的流體時，凸部突出流穿通孔內同樣壓 縮此空間部分的流體，可形成小的死點空間提高壓縮效率 〇 第3的本發明中，同樣具備汽缸體、汽缸頭、活塞及 單向閥構成壓縮機，該壓縮機中，與活塞的汽缸頭相對的 面上，活塞位於上死點附近位置時形成突出流體穿通孔內 的凸部，此單向閥具有著位在直徑大於流體穿通孔的著位 面並覆蓋流體穿通孔的平板狀閥體所構成，與該閥體的著 位面抵接的側面接合設置薄板狀的彈性密封構件，彈性密 封構件與著位面的流體穿通孔內周圍緣部相對的部分形成 凹陷部。在該壓縮機中，藉著設置在與閥體的著位面抵接 的側面上的彈性密封構件，與第1的本發明的場合相同， 可降低閥體抵接著位面產生的噪音，並且使閥體著位於著 位面封閉流體穿通孔時，可確實將此部份密封。並且，藉 著設置在與活塞汽缸頭相對面（活塞頭面）上的凸部，與第 2的發明的場合相同，活塞移動至上死點附近時凸部突出 流體穿通孔內’同樣壓縮此空間部分的流體提高其壓縮效 率。另外，彈性密封構件與著位面的流體穿通孔內周圍緣 部相對的部分僅形成凹陷部，即可同樣在與活塞頭面相對 的部分設置彈性密封構件。藉此使彈性密封構件發揮緩衝 吸收功能，因此活塞位於上死點附近位置時設定盡可能使 -24- (21) (21)200417688 上述凸部的前端接近設有閥體的彈性密封構件的面，可更 提高其壓縮效率。 第4的本發明中，同樣具備汽缸體、汽缸頭、活塞及 單向閥構成壓縮機，與活塞的汽缸頭相對的面（活塞頭面） 上’活塞位於上死點附近位置時形成突出流體穿通孔內的 凸部構成壓縮機。並且將此壓縮機安裝在內燃機上，接受 該內燃機的曲軸轉動驅動力使活塞在汽缸空間內往返滑動 ，將壓縮空氣供給內燃機的燃料噴射裝置。以上構成的壓 縮機中形成在活塞頭面的凸部同樣突出流體穿通孔內壓縮 該部分的流體而可獲得高的壓縮效率，因此可以將高壓縮 效率壓縮的空氣供給燃料噴射裝置，進行良好的燃料噴射 【圖式簡單說明】 第1圖是表示將具有本發明涉及之壓縮機的機車驅動 裝置（尤其是引擎部），在通過引擎曲軸及引擎汽缸軸心的 平面上截斷的前視剖面圖。 第2圖是表示將具有本發明涉及之壓縮機的機車驅動 裝置（尤其是變速機部），在通過引擎曲軸及引擎汽缸軸心 的平面上截斷的正面剖視圖。 第3圖是表示在通過汽缸軸及供排氣閥中心的面上截 斷上述驅動裝置的引擎部的正面剖視圖。 第4圖是表示上述引擎部的正面前視側的部分剖視圖 -25- (22) (22)200417688 第5圖是表不配設在上述引擎部的壓縮機構成的正面 剖視圖。 第6圖是表示上述壓縮機構成的側面剖視圖。 第7圖是表示上述壓縮機及水泵構成的平面剖視圖。 第8圖是擴大表示上述壓縮機的汽缸頭部的正面剖視 圖。 第9圖是擴大表示上述壓縮機的排氣提動閥周圍的正 面剖視圖。 第1 〇圖是表示上述壓縮機所使用構成吸氣簧片閥之 閥板的平面圖。 第1 1圖是表示上述壓縮機所使用構成排氣提動閥之 閥體的剖視圖（表示沿著第Π (B)圖箭頭X-X的剖面）及底 面圖。 第1 2圖是表示上述驅動裝置的變速機部的構成剖試 圖。 〔符號說明〕 10 :引擎汽缸體 1 1 :燃燒室 12 :引擎汽缸頭 13 :活塞 5 〇 :壓縮機 5 1 :壓縮機汽缸體 5 2 :壓縮機汽缸頭 -26- (23) (23)200417688 5 2 a :吸氣孔 52b :空氣穿通孔 5 2 c :著位面 5 3 :壓縮機活塞 6 3 :閥板 64 :吸氣簧片閥 7 0 :排氣提動閥 7 1 :閥體 7 3 :彈性密封層 7 3 a :環形凹槽 74 :壓縮彈簧 S Y :止轉棒軛機構 E :引擎部 TM :變速機部200 417 688 (1) Nine, description of the invention [Field of the invention The present invention belongs is (main] air compressor supplying compressed fluid on the other, in particular on a piston compressor. The invention is particularly suitable for the compressed air of an internal combustion engine fuel supply as in, e.g., Japanese Patent Publication No. Sho 63 -54909 Publication, piston type pressure injection apparatus of the prior art] [piston compressor supplying compressed fluid such as air refrigeration apparatus disclosed in Publication No. 65181 is used in the internal combustion engine The use of air compressors in fuel injection devices is well known. For example, Japanese Patent No. 2820782 discloses that a piston-type compressor for a two-stroke engine air fuel injection device is mounted on a piston compressor having a cylindrical cylinder body to cover the upper end surface. The cylinder head of the cylinder space is equipped with a piston by sliding fitting in the cylinder. The cylinder head is provided with suction and exhaust. In addition, the suction valve is provided with a freely openable and connectable fluid supply path, so that the fluid can only flow into the cylinder space. The Cheng 'exhaust valve is set to be freely switchable to connect the fluid supply source, so that the fluid can only be formed. Single fluid flows from the cylinder space such suction. Valves and exhaust valves, Includes a thin flexible metal reed valve type valve, Alternatively, the valve body is a poppet-type valve that is held in place by using a spring as a passage. ㊂ gas) which is available on S compressor. Laid-Open Publication already known to 63-- compressor. And also for the general air pump (compressor) within the vapor space of the valve from the cylinder space may be formed. Inflow and outflow through the check valve configuration outflow passage to a source constituted by the valve plate consisting of blocked 5- (2) (2) 200 417 688 SUMMARY OF THE INVENTION [Problem to be solved by the invention] In the above compressor , Dead space is formed connecting the space portion within the cylinder space of the check valve from the inflow and outflow of the fluid passage within the cylinder space by the reciprocating motion of the piston compression, A problem such as a cause of the reduction in compression efficiency is created. And use the poppet type check valve "in order to prevent the poppet valve to abut against the closed plane noise while ensuring tightness when closed 'more in the position of the poppet valve surface adhesive thin rubber sealing material ( (Elastic sealing material) 'However, the problem of durability of the rubber sealing material easily occurs. Especially the part of the inner surface of the rubber sealing member with the bit peripheral edge portions opposite, Relative to the compressive deformation of the seating surface and the abutting part, Since there is no compression deformation in the inner and surrounding parts, For this reason, there is a problem that the amount of compressive deformation of a portion facing the peripheral edge portion in the positioning plane is greatly changed. The present invention has been made in view of the above problems, Provide a method to reduce the amount of dead space generated by the inflow or outflow path and improve the compression efficiency. And the compressor can be improved durability of the elastic seal member of the poppet valve constituted for the purpose. The means to solve the problem [with] in order to reach the above purposes, In the present invention shown in FIG. 1, The cylinder space is provided with a circular cylindrical cylinder block (cylinder block of the compressor); A cylinder head cover (a cylinder head of the compressor) is mounted on the cylinder space of the cylinder block; In the cylinder space disposed slidably fitted with a piston (a piston compressor); The cylinder head can freely close to communicate with the cylinder space to form a fluid through hole (for example, The one-way valve (for example, the poppet valve 70 of the embodiment) of the embodiment (3) (3) 200417688 state air through hole 52b), ) Compressor. and, This one-way valve is composed of a valve body covering a fluid through hole at a seating surface having a diameter larger than a fluid through hole. And the plane of the valve body abutment portion engaging a sealing member is provided with an elastic thin plate-like, at this time, Elastic sealing member forming the inner peripheral edge portion (e.g., the plane portion and the elastic sealing member abuts, Elastic sealing member 73 of the embodiment of an annular peripheral edge portion of the inner peripheral surface 73b) of the peripheral side of the fluid located in a more forward position than the through hole of the surrounding surface of the edge portion. In the compressor configured as above, Although the state of the piston through the cylinder space fitted round the slide opening operation of the check valve supplying compressed fluid, However, at this time, due to the effect of the elastic sealing member provided on the valve body, Noise reduction valve member abuts against the plane produced, And the valve body is located on the seating surface to close the fluid through hole, which can surely seal this part. And the planes of the elastic sealing member abutting the above-described effect of a part (an annular elastomeric seal embodiment 73 of the peripheral surface of member 73b), Since the inner peripheral surface forms a position outside the inner peripheral edge portion of the landing surface, Thus the abutting peripheral edge portions does not abut the inner peripheral portion, But is formed with a plane portion elastic sealing member abuts the overall division (integrally annular peripheral surface 73b) abuts against the receiving plane compression force is substantially uniform configuration, The durability of the elastic sealing member can be improved. In the second invention, There also have a cylindrical cylinder block of the cylinder space; A cylinder head covering the cylinder space of the cylinder body is mounted; Freely sliding the fitted piston in the cylinder space; The head of the cylinder can freely close and cover a compressor constituted by a check valve that communicates with the cylinder space and forms a fluid through hole. In this compressor, The side opposite the cylinder head of the piston, When the piston is located near -7- (4) 200417688 top dead center, a protruding fluid passage hole is formed (for example, The inner space of the air passage hole 52b). In the above configuration 'of the piston compression top dead center from the bottom dead point of the movement of the cylinder space' projecting portions projecting fluid through the same hole to compress the space portion of this dead space can be reduced to improve the compression efficiency. In the third invention, Also includes a cylinder block with a cylindrical hollow body; The cylinder head cover on the cylinder block mounting of the cylinder space; Freely sliding the fitted piston in the room; A cylinder head cover can freely communicate with the cylinder space to form a unidirectional fluid valve through holes formed. This compressor, The side opposite the cylinder head of the piston, When the top dead center is formed, a convex part protruding from the fluid through hole is formed, Located in a plane configuration greater than the diameter of the fluid through holes and covers the fluid through the check valve of the plate-like body, A thin plate-shaped elastic sealing member is in contact with the seating surface of the valve body, Elastic sealing member and the peripheral edge of the through-hole of planes opposing portions form concave portion (e.g., Implement shaped groove 73a). The compressor of the above configuration, By elastic sealing member provided on the side surface of the valve body, To the case of the first invention and the same plane of the valve body comes into contact noise is generated, And the valve body portion of the seal at the closed fluid may indeed when this through hole. And by the convex part on the opposite side (piston head surface) of the cylinder head of the piston, As in the case of the invention, When the piston move to the vicinity of the top dead center while compressing the fluid flow bore of the fluid space to improve the compression efficiency, Such that only the elastic sealing member and the plane bore fluid through the fluid pressure applied to form lis machine fluid, Because of the cylinder, the compressor is closed on the ground, and the piston of the compressor is located on the annular surface abutting the fluid passing form of a plane joint with a through hole. Reduces the sealing surface disposed at a position projecting portions projecting the present rate of the second. Moreover peripheral edge portion of 8- (5) (5) 200 417 688 opposing the recess portion, An elastic sealing member is also provided at the portion facing the piston head surface. Whereby the elastic sealing member can absorb a buffering function, So when the piston is near the top dead center, The front end of the convex portion can be set to be close to the surface on which the valve body altar-like sealing member is provided, Further improve the compression efficiency of the present invention square 4, It includes a cylindrical cylinder space of the cylinder block; The cylinder head cover on the cylinder block mounting of the cylinder space; Slidably fitted with a piston disposed in the cylinder space; A cylinder head cover can be free to close the cylinder space communicating fluid to form a unidirectional valve through-hole, On the side opposite the cylinder head of the piston (piston head surface), When located near the top dead center, a compressor is formed which is formed by protruding parts such as protruding through holes in the fluid. In addition, This compressor is installed in an internal combustion engine 'affected by the rotational driving force of the engine crank shaft and from the piston to slide within the space between the cylinders, The fuel injection device of an internal combustion engine supplied compressed air. In this configuration the compressor likewise forming a part of this fluid while compressing the projecting portions projecting in the fluid through-hole of a piston head surface to achieve high compression efficiency, The compressed air is supplied to the fuel injection device with the above-mentioned high compression efficiency, Good fuel injection. [Embodiment] Hereinafter, the best embodiment of the present invention will be described with reference to the drawings. 1 to 4 show a locomotive driving device including a compressor using the compressor of the present invention. The configuration of the driving device will be described first. and, Figures 1 and 2 are convenient for showing space. It is expressed in two on the cut line. The two figures show that the drawing parts are connected into a drawing surface. The drive unit -9- (6) (6) 200417688 is equipped with a single cylinder engine section E and a transmission section TM, Transmission of the rotational driving force of the crankshaft 16 of the engine section E by the transmission section TM is transmitted to the output drive sprocket SP, At the same time, it is transmitted from the output drive sprocket SP to the rear wheel through the chain shown in the figure. Constructed to drive the rear wheels. First, the engine section E will be described as follows. Engine Department E, An engine cylinder block 10 having a cylindrical cylinder inner peripheral surface 10a; Engine cylinder head 12 installed above engine cylinder block 10; 10 & The piston 1 3 which is arranged in the cylinder block 10 of the engine can be axially slidably fitted; While the inner cover H S G supporting the cylinder block 10 extends in a direction orthogonal to the cylinder axis, By bearing 17a, 17b, 17c freely supported crankshaft 16; And the front end portion 1 4 a is pivotally connected to the piston 1 3 through the piston pin 1 3 a, The connecting rod sleeve 14 of the base end portion 14b is pivotally connected to the crank portion 16a of the crankshaft 16 via a crankpin 15. The engine cylinder head 12 is equipped with an ignition plug 21 and a fuel injection device 22, The engine cylinder block 10 injects a mixture of compressed air and fuel into the combustion chamber 1 1 surrounding the cylinder head 12 and the piston 13 through a fuel injection device 22, The ignition plug 12 is formed to ignite and burn. As shown in FIG. 3, the cylinder head 12 of the engine is supported by a spring 23a, 24a installs the suction valve 23 and the exhaust valve 24 acting in a closed direction, The suction valve 23 can open and close the suction passage 12a formed in the cylinder head 12, The exhaust valve 24 can open and close the exhaust passage 12b. And the 'intake path 12a is connected to the inhalation manifold 25, An outlet end 12c of the exhaust passage 12b is connected to an exhaust manifold (not shown). The engine section E is a 4-stroke engine. The piston 13 inhales between 2 round trips' compression, combustion, Exhaust stroke, And cooperate with this -10- (7) (7) 200417688 valve 2 3, 2 4 switch action. Since the supply and exhaust valve 2 3, 2 * switching action, A first sprocket 31 is provided in combination with an end of the crankshaft 16, The camshaft 3 4 provided on the side of the engine cylinder block 10 is provided with free rotation. A second sprocket 3 3 is provided. 1st and 2nd sprocket 3 1 '3 3 The third chain is hung ^ Set the 1st and 2nd keys 3 1, The number of gardens of 3 3 is 1: 2, The camshaft 34 is driven to rotate at a speed of 1/2 of the crankshaft. The cam shaft 3 4 is formed with an intake cam portion 3 4 a and an exhaust cam portion 3 4 b. Borrow the link pins 3 5 a, 3 6 a Pivot the cam follower on the engine block 1 〇 3 5, 3 6 rollers 3 5 b, 3 6 b abuts on each cam portion 34a, 34b (see Figure 4). on the other hand, The top of the engine cylinder head 1 2 is pivoted by a pin 3 9 a. 4 0 a Pivot locking arm for the operation of the exhaust valve 3 9, 4 0 forms a freely swingable installation, Connect these locking arms 3 9, 4 0 —end with the above-mentioned cam follower 3 5 、 3 6 is equipped with a putter as shown in the figure 3 7, 3 8. Locking arm 3 9, The other end of 4 0 is in contact with the supply and exhaust valve 23, 24's front end, By locking the arm 39, The swing of 40 makes the supply and exhaust valve 23, 24 counter spring 23a, The action of 24a pushes it down to open it. In the above structure, The camshaft 3 4 is driven to rotate at a speed of 1/2 of the crankshaft 16. Corresponding to this make the cam follower 3 5, 3 6 each time the camshaft shaft 34 rotates, it swings up and down once (S 卩 ’crankshaft 16 rotates twice every time), Correspond to this swing up and down to move the putter 3 7, 3 8 Make the locking arm 3 9, 4 0 via pivot pin 3 9 a, 4 0 a swing, Supply and exhaust valve 2 3, 2 4 Resistance to spring 2 3 a, The action of 2 4 a is pushed down to open, Make the intake and exhaust passages 12a, 12b communicates with the combustion chamber I1. And the setting cam portion 34a, 34b Open the intake valve 2 3 during the intake stroke ’The exhaust valve 2 4 opens during the exhaust stroke -11-(8) (8) 200417688 Again, A mixture of compressed air and fuel is injected into the combustion chamber from the fuel injection device 22 at a predetermined time. The mixture is ignited by the ignition plug 21 to perform a combustion stroke. at this time, The fuel injection device 22 injects a mixed gas having a local concentration into the periphery of the front-end ignition portion 2 1 a of the ignition plug 21 to perform efficient combustion. At the same time, lean combustion is carried out as a whole to improve the combustion efficiency and clean the exhaust gas. For pneumatic fuel injection as described above, In addition to the fuel injection device 22 described above, A fuel supply device 27 for supplying the supplied fuel from a fuel pump (not shown) to the mixing chamber 7 via a fuel supply line 27a (see FIG. 6), And the compressed air is supplied to the compressor 50 in the mixing chamber 28. In the mixing chamber 28, the fuel supplied by the fuel supply device 27 and the compressed air supplied by the compressor 50 are mixed to produce a high-concentration mixed gas having a spray fuel, This mixed gas is injected into the combustion chamber from the injection portion 22a of the fuel injection device 22 at a predetermined time using its own internal pressure. and, A mixing chamber forming hole 2 6 a is formed through the head cover 2 6 installed above and covering the engine cylinder head 12. The mixing chamber forms a hole 2 6 a, The fuel supply device 27 and the fuel injection device 22, which are respectively inserted from above and below, form a mixing chamber 28. The structure and driving mechanism of the compressor 50 will be described with reference to FIGS. 5 to 7 as follows. The compressor 50 is a body connected to the cylinder head 1 0 of the engine. A compressor cylinder block 5 1 provided with a cylindrical cylinder inner peripheral surface 5 1 a; Cover the compressor cylinder head 5 2 installed above the compressor cylinder block 51; The cylinder inner peripheral surface 5 1 a can be axially slidably fitted to the compressor piston 5 3 arranged in the compressor -12- (9) (9) 200417688 cylinder block 5 1; And the compressor piston 5 3 is fitted into the cylinder inner peripheral surface 5 1 a, and is constituted by sliding contact with a scotch yoke mechanism S Y for reciprocating movement. The scotch yoke mechanism S Y has a sliding hole 5 4 a formed in the front end of a flat piston rod 5 4 integrally connected to the compressor piston 5 3. Forming a slider 5 5 which is freely slid at right angles to the cylinder shaft, An eccentric shaft 5 7 formed at the front end of the compressor drive shaft 5 6 at the side of the engine cylinder block 10, The eccentric shaft 5 7 is rotatably fitted to the slider 5 5. and, The compressor drive shaft 56 is supported by a bearing 58a, 58b is supported by the engine cylinder block 10 for free rotation. In the above configuration, Once the compressor drive shaft 56 is rotated, By the action of the scotch yoke mechanism S Y, the compressor piston 53 can slide on the peripheral surface 51a of the cylinder to form a reciprocating motion. Due to the rotational drive of the compression drive shaft 56, And the second sprocket 3 3 arranged on the camshaft 3 4 in combination with the third sprocket 60, Compression drive shaft 5 6 is provided with a fourth sprocket 61, 3rd and 4th sprockets 60, 61rolls have a second chain 62. 3rd and 4th sprockets 60, 61 has the same number of teeth, Both are rotated at the same rotation speed as the second sprocket 33. therefore, The fourth sprocket 61 is rotated at 1/2 of the engine crankshaft 16, The compressor drive shaft 56 is rotated at the same speed, The compressor piston 5 3 is caused to perform a round trip when the engine crankshaft 16 rotates twice. Corresponding to the reciprocating movement of the compressor piston 53 as described above, Air is drawn into the cylinder space 50a surrounded by the compressor cylinder head 5 2 and the compressor piston 5 3 in the inner peripheral surface 5 1 a of the cylinder. Therefore, an intake reed valve 64 and an exhaust poppet valve -13- (10) (10) 200417688 valve 70 are provided in the compressor cylinder head 52 'as shown in FIG. The suction reed valve 64 is formed by pressing a valve plate 63 made of a thin metal plate into a shape shown in FIG. 10 to form a tongue shape. The valve plate 63 is a tongue-shaped suction reed valve 64 which is installed between the upper end surface of the compressor cylinder block 51 and the lower end surface of the compressor cylinder head 5 2 to form a cover on the compressor cylinder head 5 2 of the suction hole 5 2 a. at this time, The valve plate 63 is arranged relative to the inner peripheral surface 5 1 a (indicated by two dotted lines) to form a positional relationship as shown in the figure. By inserting the coupling bolt formed in the insertion hole 6 3 a of the valve plate 63, Combining the compressor cylinder block 51 with the compressor cylinder head 52. and, As shown in the figure, a circular hole 65 is formed so as to protrude into a convex portion of a compressor piston 5 3 to be described later. The suction reed valve 64 is shown as an arrow A in FIG. 8. When the compressor piston 5 3 moves downward, Under the negative pressure generated in the cylinder space 50a, the elastic deformation and deflection are shown as two dotted lines in the figure. External air is sucked in through the suction hole 52a. on the other hand, If arrow B indicates that the compressor piston 53 moves upward, Due to its elastic deformation recovery force and the air pressure generated in the cylinder space 50a, the suction reed valve 64 is in close contact with the suction hole 52a and blocked, Prevent the compressed air in the cylinder space 50a from leaking to the outside through the suction hole 52a. On the other hand, The exhaust poppet valve 70 is enlargedly shown in FIG. 9, For a disc-shaped valve body 71 provided with a seating surface 52c in a compressed air passage space 52d formed by the compressor cylinder head 52, And a compression spring 74 that acts on the valve body 71 in the seating direction of the seating surface 52c, An air communication hole 52b is formed by communicating with the cylinder space 50a from the seating surface 52 of the compressed air passage space 52d. The valve body 71 is closed by covering the air passage hole 5 2b with the valve body 71 while the valve body 71 is positioned on the seating surface 52c by -14- (11) (11) 200417688. The valve body 71 is shown in FIG. 11, An elastic sealing layer 73 made of a thin layer of rubber or the like is provided under the disc-shaped metal plate 72. At the same time that the elastic sealing layer 7 3 forms the annular groove 7 3 a, Recesses 73d are formed at four positions in the recessed layer 7 3a. and, The recessed portion 73d is a recessed portion formed by supporting the metal plate 72 when the elastic sealing layer 73 is provided under the metal plate 72. The ring-shaped recess 7 3 a can be seen from FIG. 9, The inner peripheral edge portion p is formed to be opposed to the air passage hole 5 2b of the seating surface 5 2 c. which is, The surface of the elastic sealing layer 7 3 is divided into an annular peripheral surface 7 3 b and a circular inner peripheral surface 73 c by the annular groove 7 3 a. However, the inner peripheral edge portion of the annular peripheral surface 73b is on the outer peripheral side of the inner peripheral edge portion P of the air passage hole 52b of the positioning surface 5 2c. The peripheral edge portion of the circular inner peripheral surface 73c is located on the inner peripheral side of the inner peripheral edge portion P of the air passage hole 5 2b of the facing surface 52c. therefore, When the valve body 71 is on the seating surface, Only the annular peripheral surface 7 3 b of the elastic sealing layer 7 3 is in contact with the seating surface 5 2 c. Circular inner peripheral surface 7 3 c and the air only through holes 5 2 b relative to the plane 52c without abutting. The exhaust poppet valve 70 configured as described above indicates that when the compressor piston 53 is moved downward as shown by arrow A in FIG. 8, Under the negative pressure generated in the cylinder space 50a, the valve body 71 is blocked by the air passage hole 52b while being located on the seating surface 52c. Prevent the compressed air in the compressed air through the inner space 52d backflow towards the cylinder space 5 0a. at this time, The elastic sealing layer 73 (especially the annular peripheral surface 73b) composed of rubber and the like is in close contact with the seating surface 52d Ensure tightness when blocked. on the other hand, The arrow B indicates the compression piston 53 moves upwardly, Compressing intake air in the cylinder space 5 0a 200417688 -15- generated by the pressure (12) (12), The valve body 71 is raised against the force of the compression spring 74, Compressed air through the air through-hole 5 2b pressed out through the air space 52. The above description shows that Once the crankshaft is turned 16 This rotation by a first and second chains 32, 62 to convey the crankshaft 16 1/2 rotational speed of the compressor drive shaft 56, The compressor piston 5 3 corresponds to the reciprocating movement of the compressor drive shaft 5 6. So that the compressor piston 53 corresponds to rotation of the compressor drive shaft 56 is reciprocated. This result, 2 times per rotation of the crankshaft 16 causes the compressor piston 53 reciprocates once. As described above when the compressor 53 when the reciprocating motion of the piston, Downward movement of the piston stroke of the compressor 53 (the stroke movement direction of arrow A) and opening the intake valve reed 64 5 2a from the outside air into the air intake hole 50a of the cylinder space, Upward movement stroke (stroke direction of arrow B) of the open exhaust poppet valve 70, Corresponding to the upward movement of the piston compressor 53 is compressed by the compressed air in the cylinder space 50 of a compressed air introduced through the space 52d. and, Compressed air is introduced over time as described above with the crankshaft 16 is synchronized with the rotation, The fuel injection is performed in cooperation with the fuel injection device 22. also, As shown, A cylindrical convex portion 5 3 a is formed on the upper end surface of the compressor piston 5 3. 5 3 a convex portion having a small diameter slightly smaller than 5 2 b through the air holes, When the compressor piston 53 moves up to near the top dead center, The convex portion 53a is configured to protrude into the air passage hole 52b. With this, Air through the interior space of the air hole 52b is formed in the convex portion 53a of the compressed air introduced through the inner space 52d, Small compression dead point space can form high compression efficiency. among them, When the compressor piston 5 3 is at the top dead center, Circular inner peripheral surface of the projecting portion 5 3 a front-16- (13) (13) 200 417 688 end face as close as possible the elastic sealing layer 73 is 73 C constitute as much as possible to improve the compression efficiency. As above, The introduction of compressed air through the space 5 2 d, So that the exhaust poppet valve element 70 is moved up and down 71, The valve body 71 can be increased and the adhesion plane between 52 c, At the same time, in order to reduce the noise when the valve body 7 1 abuts the bit surface 5 2 c, An elastic sealing layer 73 is also provided on the annular peripheral surface 7 3b. among them, As above, The inner peripheral edge portion of the annular peripheral surface 7 3 b is located on the outer peripheral side of the inner peripheral edge portion P of the air passage hole 52 b of the seating surface 52 c. Therefore, when the valve body 71 is on the seating surface 52c, The entirety of the annular peripheral surface 73b is in contact with the seating surface 52c, The effect of applying a uniform compressive force to this part, Therefore, the durability of the elastic sealing layer 73 can be improved. A compressed air supply pipe 75 is connected to the compressed air passage space 52d for supplying compressed air as described above. This air supply pipe 75 is shown in FIG. 6, It is connected to a compressed air supply passage 76 formed in the cylinder head 12 of the engine. Compressed air supply passage 76 is formed in the mixing chamber 2 6 a hole forming an opening, As the fuel supply to the mixing chamber vertically fitted holes 26 are formed in the mixing chamber 2 7 a device with 22 sandwiched formed in the fuel injection device 28 and compressed air is supplied 'although the connection hole formed in the mixing chamber 26 is formed A the larger diameter side of the fuel supply apparatus provided with holes 2 6 b, A fuel supply device 27 is provided here, The fuel supplied from the 糸 m fuel supply line 27a is supplied to the mixing chamber 28 through the fuel supply device 27. also, Regulating device 50 is supplied to adjust the pressure of compressed air from the compressor 28 within the mixing chamber 78 is connected to said compressed air supply passage 76 is provided (see FIG. 4). on the other hand, As shown in Figure 7, A compressor connected to the drive shaft is formed 17- (14) (14) side end portion 57 side of the eccentric shaft 20041768856 embodiment of an electromagnetic coupling pump WP. The water pump WP coupled to the compressor via a coupling member 8 square outer magnets 56 of the drive shaft 81; The isolated member 84 relative to the outer magnet 81 is disposed within the interior of the magnet 82; Bonded magnet 82 and the inner shaft 83; And a pump blade 85 mounted on the front end of the pump shaft 83. Isolation member 84 is provided to isolate the compressor drive shaft 56 with the working oil flow space, And a space with the pump blades 85 of the cooling water flow. An outer magnet 81 and the magnet 82 constitute a non-contact coupling means, Although the spacer members 8 are held away from each other, However, it is also possible to make one side follow the other side by the magnetic force between the two. In the aforementioned water pump WP, As described above, the compressor drive shaft 5 6 is rotated by the rotation of the crankshaft 16, This rotary drive so that together with the outer magnets 8 1:00 'by magnetic coupling effect of the interlocking rotary drive magnet, The pump blade 85 is driven to rotate via the pump shaft 8 3. With this, The engine cooling water is sucked in from the water tank 'and is discharged from the discharge port 87. and, Discharge port 87 connected to a cooling water supply pipe (not shown), This connecting a cooling water supply pipe of FIG. 4 showing a cooling water inlet portion 88, Whereby a supply of cooling water in the cooling water and the engine cylinder head 1 billion passage engine cylinder block 12 'so that the cooling water passage for circulating the engine 10 and the cylinder head 12 cools the engine cooling water from the cylinder block cooling water outlet portion is 89 (see Figure 1) is sent to the heat sink through a tube (not shown). In addition, In the water pump WP, From the pump blade 85 is provided to discharge □ 8 7 through the thermostat valve 86 is part of the cooling water. Above the starter motor to start the engine Tai E configuration is used as a brother FIG. 4 showing the cover mounted on the H S G. Mounted on a drive shaft of the starter motor 1, the starter pinion (not shown) 'the starter pinion is by way clutch Lao 18- (15) (15) 200 417 688 (not shown) mounted on the crankshaft end The starting gear 2 of the part is engaged. and, An end portion of the crank shaft 16 is mounted in the generator G, Driven by crankshaft 16 to generate electricity, However, the one-way clutch may be positioned in the generator G. When driving the starter motor for starting engine section E, The starter gear 2 is driven via the starter pinion, And the rotation drives the crankshaft 16. With this, As described above drives the compressor 50 supplying compressed air to the mixing chamber 28. Simultaneously with this, by the rotation of the crankshaft drives the fuel pump (not shown) is 16, The fuel is simultaneously supplied to the mixing chamber 28 through the fuel supply device 27. Within the mixing chamber 28 a mixed gas of such compressed air with a high concentration of fuel is made, This is injected into the combustion chamber 1 1 with the reciprocating motion of the piston 1 3, By ignition plug 21 ignition combustion, Start the engine section E. at this time, As described above in order to improve the efficiency of the compressor 50, The engine section E can be started smoothly. After starting the engine section E as described above, In response to the speed change transmission of the rotational driving force of the crankshaft 16 to the transmission section TM of the drive sprocket SP, Except for the second figure, referring to the twelfth figure shown in the enlarged transmission section TM, the explanation is as follows. The transmission section TM has a centrifugal clutch CL1 provided at the end of the crankshaft 16; The input shaft 91 and the output shaft 92 are arranged in parallel with the crankshaft 16; 91 is provided in the wet end of the input shaft of the multi-plate clutch CL2 is; And arranged on the input / output shaft 91, The first to fourth speed gears between 92 and 110 to 140, A drive sprocket SP is attached to an end of the output shaft 92. The centrifugal clutch CL 1 is used to transfer the driving gear 93 and the crankshaft 16 that are freely rotatable on the crankshaft 16. The rotation of the crankshaft 16 is formed by a centrifugal force at a predetermined rotation or more. The drive gear 93 incorporated in the crankshaft 16 so that the two are integrally rotated. The transmission drive gear 9 3 is a bit. -19- (16) (16) 200417688 The transmission driven gear 94 which is rotatably provided on the input shaft 9 1 is used to communicate the rotation of the transmission drive gear 9 3 to the transmission slave. Moving gear 9 4. The transmission driven gear 94 is formed by a wet multi-plate clutch CL2 and can be freely engaged with the input shaft 9 1. The wet multi-plate clutch c L 2 can be engaged to rotate the transmission driven gear 9 4 and the input shaft 9 1 together. Wet multi-plate clutch C L 2 binds to convey the driven gear 94 of the clutch drum 96; Bolt groove combined with clutch hub 97 of input shaft 91; Even junction alternately overlap the clutch drum 96 and the clutch plate coupled multi-plate clutch of the clutch hub portion 97 of the friction plate 98 is arranged; A piston member 99a opposite the multi-plate clutch portion 98; The piston member 99a is in close contact with the spring 9 9b of the multi-plate clutch portion 98; And a spherical cam mechanism 95 that moves the piston member 99a in a direction away from the multi-plate clutch portion 98. Normally, the spherical cam mechanism 95 is not operated, The spring 99b engages the piston member 99a against the multi-plate clutch portion 96 and engages the wet multi-plate clutch CL2. Communicating with the driven gear 94 so that the input shaft 91 integrally rotate. The spherical cam mechanism 9 5 moves during shifting, Keeping the piston member 99a away from the multi-plate clutch portion 96 from the liberated wet multi-plate clutch CL2, The transmission driven gear 94 and the input shaft 91 are not rotated and transmitted. First speed to fourth speed gear train is disposed 11〇~140 1 ~ fourth speed of the input shaft drive gear 91 1~1 4 1 1 1; And the driving gear 11 is provided respectively engaging the first 1~141 1 ~ 4 1 12~142 driven gear formed on the output shaft 92 and the fourth speed of 1 ~. First speed drive gear 111 is integrally formed with the input shaft 91, Second speed drive gear 121 is relatively rotatably disposed on the input shaft, Simultaneously forming the first engagement nail 1 2 1 a, Third speed drive 20- (17) (17) 200 417 688 Park peg wheel 131 is incorporated in groove 91 on the input shaft, At the same time, a second staple 131a, The first staple engaging hole 131 and the first fork-shaped groove 131c, Fourth speed drive gear 141 are relatively rotatably disposed on the input shaft 91, while the table 2 is formed staple engaging engagement holes 1 4 1 a. also, Forming the third engagement nail engaging hole of the first driven gear u 2 relatively rotatably disposed on the output shaft while 1 1 2 a 'second speed driven gear 122 and the output shaft 92 pin grooves While combining, Forming the third dowel 122a, A fourth engagement nail groove 122b and the second fork 2 1 2 2 c 'third speed driven gear 132 relatively rotatably disposed on the output shaft 92 is simultaneously formed a fourth engagement nail engaging hole 13 2 a, The fourth speed driven gear 142 is bolted to the output shaft 92. Such first speed to fourth speed transmission gear 11 side 0~1 column 40 is provided with a rotary transmission mechanism 150, The first and second shift forks 151 constituting this mechanism The front fork portion of 152 is engaged with the first and second fork grooves 131c, Within 122c. Two shift forks 151, 152 may be rotatably and axially movably by a self-mounting on the shift drum 153, While the pin 1 5 1 a, 1 5 2 a is engaged with the cam groove 1 5 3 a, Within 1 5 3 b, In response to rotation of the shift drum 153 is configured to move axially. A shift drum 153 through the ring mechanism 154 is connected a shift pedal (not shown), When operating the shift pedal, rotate the shift drum 1 5 3 corresponding to this operation. Shift the first and second shift forks 151, 152 moves axially. among them, When the second shift fork 152 moves to the left in the figure, The second speed driven gear 122 moves in the left direction so that the third staple 122a fits into the third staple engaging hole U2a. The first driven gear 112 in conjunction with the second speed driven gear 122. therefore, Rotation of the input shaft 91 from the first speed gear train 110 (the first speed drive gear 111 and the second speed driven gear -21-- (18) (18) 200,417,688,112) through the second speed from gear 122 transmitted to the output shaft 92 'of the corresponding first-speed gear train 110 of the transmission gear ratio. On the other hand, when the second shift fork 152 moves in the other direction, 4 fitted engagement nail l22b fourth engagement nail engaging hole 1 3 2 a, The second speed driven gear 122 in conjunction with the third speed driven gear 132 Turtle. therefore, The rotation of the input shaft 91 is a column 13 0 from the third gear speed (the third speed drive gear 131 and the third speed driven gear 132) through the second driven gear 122 to the output shaft 92 to convey, For the third speed gear train corresponding to the gear ratio of the transmission 130. In addition, When the first shift fork 151 moves to the left in the figure, The third speed drive gear 131 moves the first engagement nail 121a fitted in the first engagement nail engaging hole toward the left direction 1 1 3 b, The second speed drive gear 121 in conjunction with the third speed driven gear 131. Thus rotation of the input shaft 91 is a drive gear from the third speed state 131 is transmitted to the second drive gear 121 'via the second-speed gear train 120 (the second speed drive gear 121 and the second second speed driven gear 122) transmitted to the output shaft 92, For the second-speed gear train corresponding to the gear ratio of the gear 120. on the other hand, When the first shift fork 151 is moved toward the right direction, Insert the second staple 131a into the second staple fitting hole 141a, 3 of the first speed drive gear 132 in conjunction with the fourth speed driven gear 142. therefore, The input shaft 91 is rotated in the state from the third speed drive gear 131 is communicated to the fourth speed drive gear 141, The output shaft 92 is transmitted via the fourth speed gear train 140 (the fourth speed drive gear 141 and the fourth speed driven gear 142), The gear shift is performed in accordance with the fourth speed gear train of 1 to 40 gear ratios. Output shaft speed as described above via any of the first to fourth speed gear train and variable speed drive 1 10~140 92 is rotated in its state communicated to output drive -22- (19) (19) 200 417 688 a sprocket SP, As above, It is transmitted to the rear wheels via a chain (not shown) and drives the rear wheels. Among the above, Although the compressor of the present invention is used for producing a mixed gas mixed with fuel, Of course, it can also be used in other compressors. and, The object of compression is not limited to air, Other gases can also be used. [Effects of the Invention] According to the first aspect of the present invention described above, With cylinder block, Cylinder head 、 The piston and check valve constitute a compressor, The non-return valve has a valve body covering a fluid through hole at a seating surface having a diameter larger than a fluid through hole. A thin plate-shaped elastic sealing member is connected to a portion abutting the seating surface of the valve body, at this time, The inner peripheral edge portion of the abutting surface of the elastic sealing member is formed with an elastic sealing member located on the peripheral side of the inner peripheral edge portion of the fluid through-hole in the upper surface. In the compressor configured as above, The piston slides back and forth with the cylinder space fitted, The check valve is operated to compress and supply fluid, But at this time, By the function of the elastic sealing member provided in the valve body, Can reduce the noise generated by the valve body abutting the surface, And when the valve body is closed at the seating surface to close the fluid through hole, This part can be surely sealed. The part of the abutment surface of the elastic sealing member that performs the above-mentioned action, The inner peripheral edge portion is formed at a position outside the inner peripheral edge portion of the landing plane. Therefore, the abutting portion will not abut against the inner peripheral edge, The portion abutting the seating surface of the elastic sealing member abuts the seating surface as a whole. Formed into a structure that receives a substantially uniform compressive force, The durability of the elastic sealing member can be improved. In the second invention, It also has a cylinder block, Cylinder head, The piston and -23- (20) (20) 200417688 check valve constitute the compressor, In the compressor, When the piston is positioned near the top dead center on the surface opposite to the cylinder head of the piston, a convex portion protruding from the fluid passage hole is formed. In the compressor configured as above, When the piston moves from BDC to BDC to compress the fluid in the cylinder space, The convex part protrudes the fluid in the through hole that also compresses this space part, Small dead space can be formed to improve compression efficiency. In the third invention, It also has a cylinder block, Cylinder head, The piston and check valve constitute a compressor, In the compressor, On the side opposite the cylinder head of the piston, When the piston is located near the top dead center, a convex portion protruding from the fluid through hole is formed, This non-return valve has a flat valve body that is located on the seating surface with a diameter larger than the fluid passage hole and covers the fluid passage hole. A thin plate-shaped elastic sealing member is provided in contact with the side surface abutting the seating surface of the valve body. The recessed portion is formed at a portion of the elastic sealing member that is opposite to the peripheral edge portion of the fluid through hole of the positioning surface. In this compressor, By the elastic sealing member provided on the side abutting the seating surface of the valve body, As in the case of the first invention, Can reduce the noise generated by the valve body abutting the surface, When the valve body is closed on the seating surface and the fluid passage hole is closed, This part can be surely sealed. and, By the convex portion provided on the surface opposite to the piston cylinder head (piston head surface), As in the case of the second invention, When the piston moves to the vicinity of the top dead center, the convex portion protrudes. Inside the fluid penetrating hole 'also compresses the fluid in this space to improve its compression efficiency. In addition, The portion of the elastic sealing member opposite to the inner peripheral edge portion of the fluid through hole of the positioning surface forms only a recessed portion, In other words, an elastic seal member may be provided in a portion facing the piston head surface. This allows the elastic sealing member to perform a cushioning and absorbing function, Therefore, when the piston is located near the top dead center, set the front end of the convex portion as close as possible to -24- (21) (21) 200417688. Can further improve its compression efficiency. In the fourth invention, It also has a cylinder block, Cylinder head, The piston and check valve constitute a compressor, On the surface (piston head surface) opposite to the cylinder head of the piston, when the piston is positioned near the top dead center, a convex portion protruding from the fluid through hole is formed to constitute the compressor. And install this compressor on the internal combustion engine, Receiving the crankshaft rotational driving force of the internal combustion engine to cause the piston to slide back and forth in the cylinder space, The fuel injection device of an internal combustion engine supplied compressed air. In the compressor configured as described above, the convex portion formed on the piston head surface also protrudes from the fluid through-hole to compress the fluid in this portion, thereby achieving high compression efficiency. Therefore, it is possible to supply compressed air with high compression efficiency to the fuel injection device. Good fuel injection [Brief description of the drawings] Fig. 1 shows a locomotive driving device (especially an engine section) having a compressor according to the present invention. Front sectional view cut through the plane through the engine crankshaft and engine cylinder axis. Fig. 2 shows a locomotive driving device (particularly a transmission section) having a compressor according to the present invention. Front sectional view taken in a plane passing through the engine crankshaft and the engine cylinder axis. Fig. 3 is a front cross-sectional view showing the engine portion of the driving device cut on a plane passing through the cylinder shaft and the center of the air supply and exhaust valve. Fig. 4 is a partial cross-sectional view showing the front-view side of the engine section. -25- (22) (22) 200417688 Fig. 5 is a front cross-sectional view showing the structure of a compressor not provided in the engine section. Fig. 6 is a side sectional view showing the structure of the compressor. Fig. 7 is a plan sectional view showing the configuration of the compressor and the water pump. Fig. 8 is an enlarged front sectional view showing a cylinder head of the compressor. Fig. 9 is an enlarged front sectional view showing the periphery of the exhaust poppet valve of the compressor. Fig. 10 is a plan view showing a valve plate constituting the suction reed valve used in the compressor. Fig. 11 is a cross-sectional view (showing a cross section taken along the arrow X-X of Fig. (B)) of a valve body constituting an exhaust poppet valve used in the compressor and a bottom view thereof. Fig. 12 is a cross-sectional view showing the configuration of a transmission section of the drive device. 〔Explanation of symbols〕 10: Engine block 1 1: Combustion chamber 12: Engine Cylinder Head 13: Piston 5 〇: Compressor 5 1: Compressor cylinder block 5 2: Compressor cylinder head -26- (23) (23) 200417688 5 2 a: Suction hole 52b: Air through hole 5 2 c: Seat 5 3: Compressor piston 6 3: Valve plate 64: Suction reed valve 7 0: Exhaust poppet valve 7 1: Body 7 3: Elastic sealing layer 7 3 a: Circular groove 74: Compression spring S Y: Scotch yoke mechanism E: Engine Department TM: Transmission Department