201030229 六、發明說明： 【發明所屬之技術領域】 。本發明關於-種封閉系統的熱機引擎，尤指一種提供 -單向流動的jh作氣難且控難機引擎内的氣體壓力的 熱機引擎。 【先前技術】 外燃機heat如咖⑻跟多種循環相關，該些循 環從外部(例如太陽能或是銷爐的廢熱)將熱取出，並且將熱 傳遞至引擎(或發動機)的:L作流體中而產生出有用的功。史 特林循環(S削ng eye|es)以及愛利克生循環(EH_n 一叫 為上述該些循環中的其中一部分，其利用外部的熱源。雖 然史特林循是開放式循環，而愛利克生循環為封閉式循 環’然而兩個循環都使用了回熱器㈣⑽咖·）。如今，對 於一個簡單循環而言，史特林循環已達到最高的效率，因 為回熱器可將-個循環中正常要被排掉的熱回收，並且將 此熱能傳遞至下個循環的工作氣體中。 傳統上’史特林引擎是操作於高溫（攝氏75〇度）及 高速（30至50誠(Hei，tz))中，以達到高的功率重量比 (powertoweightmtios)。因為高的操作溫度及壓力，高溫的 史特林引擎會因騎變應力（ereep st·)而承受永久的損 褒即使史特林引擎使用了異金屬(ex〇ticmetal)，例如錄鉻 合金(I_d)。巾史特林引擎最近的發展已朝向利用低溫的 熱源(例如卫業廢熱、太陽能或是地熱）來轉換成電能。然 而，非常少量有成效的引擎被展示出，且只能用在小功率 輪出的範圍中。 傳統的史特林引擎的運作是藉由在一高低溫熱交換器 4/28 201030229 (hot and cold heat exchanger)及膨脹及壓縮活塞(expansion and compression piston)之間振蘯工作氣體來達成。這種振盪 氣體的引擎的主要缺失為：高低溫熱交換器的容積跟活塞 的工作容積(swept volume)—樣。在循環的其中一半之中， ' 必需將容積壓縮及膨脹。儘管在另外一半的循環中，閒置 空間(dead space)是被認為有負面效果的。壓縮活塞將氣體 壓縮至低溫熱交換器中，以達到等溫壓縮（isothermal compression)。壓縮活塞的進一步動作為：移動部分的低溫 φ 氣體通過回熱器而進入至高溫熱交換器。在高溫熱交換器 的氣體被加熱，而膨脹活塞開始膨脹。就其本身而言:，氣 脰攸南熱父換器的谷積中寺溫地膨服。.如此配置命缺失 為.當膨脹發生時，大量的工作氣體被遺留在低温潑交換 器的容積中。 在高溫的引擎中，因為熱交換器與活塞的工作容積的 谷積比值，使得遺留工作氣體在低溫熱交換器中是可以接 受的。在高溫㈣擎中’比值通常為1 : 3，而在低溫引擎 中，比值可低至US : i。如此可看出，在低溫引擎中，熱 交換器的容賴大於活塞玉作容積，且過多·體被遺留 在低溫熱交換財。事實上，較多的功被用在壓縮一氣體， 5亥氣體沒辦糾料擎的高溫區以產生有用的功。這就是 :何傳統=的史特林引擎通常無法有效地在攝氏· 度以下的> 皿度中運作的主要原因。 雖然現存的熱機引擎適合於各種對 時也能高效率地^ 在，咖丨擎溫度低 【發明内容】 5/28 201030229 依據本發明的一部份，一封閉循環式熱機引擎被提 ^該熱，引擎包括—第—膨脹活塞，第—膨脹活塞設置 於一第一汽缸中。一第二膨脹活塞設置於一第二汽缸中， 並且連動地連接該第—膨脹活塞，其中該第二汽虹連通 (m_ c_e)該第—汽叙。一壓縮活塞，設置於一第三汽 ^中’且連動地連接該第—膨脹活塞，其中該第三汽:被 連通用以接收來自於該第二汽缸的—卫作流體 該工作流體至該第一汽缸中。 及博圮 引擎明二Γ部份，一種具有—工作流體的熱機 引擎被k供。销機引擎包括—第―汽㈣， 活塞，該第-膨脹活塞連通及連動地連 ，一第-祕雜。—第—壓縮活塞連通及連動地連接該 第-祕活塞及該第二膨脹活塞。其巾該第—汽缸岭置 成-第-封_環以提供該卫作流體的單向流動。 =，_又—部份’—種封閉循環式熱機引擎的 3方法被提供之。該方法包括加熱4作流體。膨 加熱的該X作流體進人―第—汽缸中的膨脹，以移動 塞至-第-位置。被加熱的該卫作流體流動至— 第二汽缸中而移動-第二膨脹活塞至—第二位置。該 流體從該第-汽缸中及該第二汽虹中流動至—第^汽缸 中。及工作流體在_二汽缸巾被—壓縮活塞壓縮。該工 作流體從該第三汽缸中流動至該第一汽缸中。 依據本發明的又一部份’提供一種熱機引擎被，該熱 機引擎包括互相連通的至少兩膨脹活塞，每一個該膨脹^ 塞設置於-舰汽缸巾。至少-壓輪塞連職至少兩膨 脹活塞，每一個該壓縮活塞設置於一壓縮汽缸中。一傳動 6/28 201030229 連捍連動地連接該至少兩膨脹活塞以及該至少一壓縮活 基亥傳動連桿設置於一曲轴箱中’其中該曲轴箱連通該 些膨脹汽缸及壓縮汽缸。一壓力槽也被提供來連通該曲軸 箱，其中該壓力槽用以將一加壓氣體加入至該曲軸箱中， 以反應該熱機引擎運作的變化。 依據本發明的又一部份提供一封閉循環式熱機引擎， 該熱機引擎包括一第一膨脹活塞，第一膨脹活塞設置於一 苐一汽缸中。一苐二膨服活塞設置於一第二汽缸中，並且 連動地連接該第一膨脹活塞，其中該第二汽缸連通該第一 汽缸。一壓縮活塞，其設置於一第三汽缸中且連動地連接 該第一膨脹活塞’其中該第三汽缸被連通用來接收來'自於. 該第二汽缸的一工作流體且傳送該工作流體至該第^汽缸 中。一傳動速桿連接該第一膨脹活塞、該第二膨脹活塞及 該壓縮活塞，其中該傳動連桿為一凸輪板（cam plate)或 一鉸接式曲軸（articulated C1’ankshaft)。一傳動箱連接該傳 動連桿，該傳動箱在一壓力下運作，該壓力小於或等於『該 封閉循環式熱機引擎運作的過程中，該工作流體在該第一 汽缸及該第二汽缸中的最小壓力』。從該第二汽缸流動至該 第三汽缸的工作流體的熱能藉由一回熱器傳遞至從該第三 汽缸流動至該弟一戍缸的工作流體中，其中該回熱器為一 逆流式熱交換器。一加熱器以可傳熱的方式連接於該回熱 器及該第一汽缸之間。一冷卻器以可傳熱的方式連接於該 第三汽缸及該面熱态之間。一第一閥連通該加熱器及該第 一汽缸之間。〆第二閥，連通該第二汽缸及該回熱器之間。 一第一單向間，連通該第三汽缸，以讓該工作流體流進該 第三汽缸令。/第二單向閥’連通該第三汽缸，以讓該工 7/28 201030229 作流體從該第三汽缸中流出。 參 依據本發明的又-部份提供一種具有一工作流體的執 機引擎。該熱機引擎包括-第-汽紅組，該第一汽虹組具 有-第-膨脹活塞與-第-壓縮活塞，該第一膨脹活塞連 通及連動地連接-第二膨脹活塞，—第—㈣活塞連通及 連動地連接第-膨脹汽缸及第二膨脹汽缸。其中該第—活 塞組設置成一第一封閉循環，以提供該工作流體的單向流 動。-第二汽缸組連動地連接該第一組汽缸，該第二 =有一第三膨脹活塞及―第二壓縮活塞，該第三膨脹活 連接—第四膨脹活塞，該第二壓縮活塞連 通及f動地連接第三膨脹故及第四膨脹汽缸，其中該第 組第二封閉循環，以提供該工作流體的單 Μ 一A缸組及該第二汽紅組彼此間隔90度。一 熱的方式連接該第—封閉循環及該第二封閉 ^活熱器設置於該第—封__位於該第二 ==_活塞之間的部分，並且該回熱器設 參 活夷之的位於該第_彡脹活塞域第二壓縮 封i循二分。一加熱器連接該第-封閉循環及該第二 1傳遞熱能至該工作流體。 ^ 能。一傳動箱、表^ f 從該工作流體中傳出熱 該傳動r t 連㈣f—汽缸組聽第二汽紅組， 機引擎』;乍的:m ’該運作壓力小於或等於『該熱 二汽缸組中的最^壓力二工作流體在該第—雜組及該第 / 。遠方法包括加熱一工作流體。膨脹被加熱之 8/28 201030229 該工作流體進入一第一汽紅中，以移動一第一膨脹活塞至 一第一位置。被加熱的該工作流體流動至一第二汽缸中， 以移動一第二膨脹活塞至一第二位置。該工作流體從該第 一汽缸中及該第二汽缸中流動至一第三汽缸中。該工作流 體在該第三汽缸中被一壓縮活塞壓縮。該工作流體從該第 三汽缸中流動至該第一汽紅中。在加熱該工作流體的步驟 之前，從該第二汽缸流動至該第三汽缸的該工作流體的熱 能傳遞至從該第三汽缸流動至該第一汽缸的該工作流體 中。在被加熱的該工作流體流動至該第二汽缸的步驟之中 的工作流體被壓縮前’冷卻該工作流體。於該工作流體從 該第一汽缸流動至該第三汽缸的過程中，讓該第二膨脹活 塞停留在該第二位置中。最後，當該第二膨脹活塞在5該第 二位置時，一傳動箱被加壓至一第一壓力，該第一壓力小 於或等於位在該第一汽缸及該第二汽缸中的該工作流體的 壓力。 τ 藉由以下的詳細說明及關連的圖示，本發明的優:點及 特色將更明確地說明，然而所附圖式僅供參考與說明用， 並非用來對本發明加以限制者。 【實施方式】 請參閱第一至五圖，顯示出一外燃機(external heat engine)20的一實施例，或稱為熱機引擎(heatengine)2〇。該 熱機引擎20利用一外部熱源22來對熱機引擎20中的一‘丁 作氣體(working gas)傳遞熱能。該熱機引擎2〇為一封閉系 統’其包括一高溫熱交換器(hot heat exchanger)24 (或稱加 熱器24 )、一低溫熱父換器(c〇id heat exchanger)26(或稱冷卻 器26)及一回熱器(regenerator)28。該熱機引擎20更包括一 9/28 201030229 殼體(housing)30,該殼體30包含有至少三個汽缸（cyHnder) 34、36、38。該第一或壓縮汽虹34包含一壓縮活塞 (compression piston) 32，用以壓縮低溫工作氣體。該壓縮活 塞32連接兩個膨脹活塞（eXpansi〇n pist〇n) ，其分別 - 容置於兩膨脹汽缸36、38中。每一個活塞都連接至一傳動 連桿(drivelinkage)44。該熱機引擎20並且包含多個閥46、 48、50、52，以控制通過熱機引擎20的工作氣體的流動。 該熱機引擎20利用工作氣體的一單向流動 (imidirectional flow)，工作氣體從壓縮汽缸34通過回熱器 28然後進入到高溫熱交換器24及膨脹汽缸36、38中，之 _ 後再返回。以下更清楚地說明之，藉由讓全部的被壓縮的 工作流體貫質地通過高溫熱交換器24，該氣體的單向流動 可產生些優點，因為全部的工作氣體沿著一方向在熱機引 奪20中傳播。藉由利用在咼溫熱交換器24的等壓加熱步 驟後的絕熱壓縮，該熱機引擎2〇也可產生些優點。 δ月參閱第一圖，該第一膨脹活塞4〇具有一進氣閥 (intake valve) 46，當第一膨脹活塞4〇移動時，進氣閥46 開啟並且谷許尚壓(pmax)及高溫(Tmax)的工作氣體流進第❹ 一膨脹汽缸36中。因為壓縮活塞32和第一膨脹活塞40同 時移動，第一次膨脹的工作氣體的總容積會有少量的變 .化。這樣的效果為：工作氣體的壓力及溫度實質地維持相 同，就像是一個等壓（1^^) /等溫（isotherman膨脹。 如第一圖所示，一旦第一膨脹活塞4〇到達下死點位置(dead center position) ’進氣閥46關閉’並且停蛰在上死點位置的 第^膨脹活塞42可允許移動。以下麟楚地說明之，:活塞 ' 32、40、42的運動是由該傳動連桿44定義丨之。;在實施例中， 10/28 201030229 該傳動連桿44為至少具有一截面(profile)的一凸輪板(cam plate)。 該第一膨脹活塞36的容積決定了該第二膨脹汽缸38 的初始膨脹容積。工作氣體在第二膨脹汽缸38中的膨脹為 實質地絕熱。第三圖顯示出當第二膨脹活塞42移動時，第 一膨脹活塞40停留在下死點位置。在第二膨脹活塞42到 達了下死點位置後，該工作氣體膨脹至熱機引擎20的最小 壓力(Pmin)。 在第二膨脹活塞42到達了下死點位置後，該排氣閥 (exhaust valve)48開啟並且允許工作氣體移動至低溫熱交換 器26中。如第四圖所示應該知道的是，藉由傳動連粹44 的配置，熱機引擎20可被設置成從膨脹汽缸36、3於一起 或是先後地移出該工作氣體。當工作氣體從膨脹汽缸36、 38移出時，該工作氣體仍然含有大量的熱能。該工作氣體 先穿過該回熱器28’朝向低溫熱交換器26流動的工作流體 被回熱器28取出熱能。在實施例中，回熱器28為一個逆 流式熱交換器（counter flow heat exchanger)，其可為多個板 體或是管式交換器的管體，其中於管式交換器中，高溫氣 體朝一方向流過一腔室而低溫氣體朝一相反方向流過一相 鄰的腔室。回熱器28的主要功能為：在工作氣體到達低溫 熱交換器26之前，從排出的工作氣體（意指流向低溫熱交 換器26的工作氣體）中擷取熱能，並且在從壓縮汽缸34 流出的被壓縮及低溫的工作氣體到達高溫熱交換器24之 前，將熱能傳遞給該工作氣體。 當工作氣體通過回熱器28後，工作氣體來到低溫熱交 換器26中，在此全部的不可回復的熱能實質上會被擷取出 11/28 201030229 並藉由一散熱器(radiator)54排放至大氣中。低溫工作氣體 離開低溫熱交換器26然後進入到壓縮汽缸34中，於壓縮 汽缸34内，壓縮活塞32絕熱地壓縮工作氣體’如第五圖 所示。一旦壓縮汽缸34的壓力達到最大值(pmax)，一單向 閥(check valve)50開啟並且允許被壓縮的工作氣體從壓縮 汽缸34移動到回熱器28。一第二單向閥52設置在鄰近該 壓縮汽缸34的入口處，以防止氣體回流到低溫熱交換器 26。低溫工作氣體流經回熱器28時’會被反向流過的被排 放出的工作氣體加熱，如先前所說明，工作氣體以低於最 大運作溫度(Tmax)的溫度離開回熱器28。工作氣體之後通 ® 過高溫熱交換器24,其中於高溫熱交換器24中，外部的熱 源再次被利用來將該工作氣體加熱至最大溫度(Tmax)，並 且重複該熱力循環。 配合第六圖所示的一壓力容積圖（pressure_v〇〗ume (“PV”）diagram) ’以另-種方式來描述該熱機引擎2〇的運 作方式。壓力容積圖通常被用來描述熱力循環。藉由將壓 力對容積積分’該壓力容積圖可用來計算出該熱機引擎 所產生的功(丽k)。藉由計算壓力容積圖的循環所包圍的面 φ 積，該功可快速地被計算出。通常，當熱機引擎以壓力容 積圖所示的順時針方向運作時，可產生出正功 work) 〇 該循環從點102開始 共對應第一圖所示的熱機引擎 的位置。在此點，熱機引擎20_力及容積為最小 ^溫工作«被容料過進_ 46而進人轉脹汽缸36: 該熱機引擎細的壓力上升，而容積實質地維持獅啊 旦達到最大壓力時’該進氣閥46 _且該循環位在點 12/28 201030229 104，其對應第二圖。 该傳動連桿44設置成允許第二膨脹活塞42爾後移 動，藉此工作氣體膨脹進入第二膨脹汽缸38中。如此讓熱 機引擎20的容積增加，同時讓壓力獨，而如同循環從點 104移動到點1〇6。在到達點1〇6後，該排氣閥48開啟， 讓工作氣體從該些雜狂36、38巾流出，贿流過回熱 器28及低溫熱交換器26，在進入壓縮汽缸34。應該知道 的是’雖然第四及五圖顯示該些膨脹活塞4〇、42依序移動， 參 傳動連桿44也可設置成讓兩個膨脹活塞40、42同時移動。 因為工作氣體從該些膨脹汽缸36、37流動到壓縮汽缸Μ， 壓力下降而容積增加，直到循環到達點1〇8，其對應第五圖 所示的熱機引擎20的位置。 _ ° 要結束熱力循環時，低溫工作氣體從壓縮汽缸流 回，從回熱态28及尚溫熱交換器24吸收熱。當熱機引擎 20回到第-圖所示的位置時’該容積下降而壓力保持在幾 乎相同的狀態。如先前所討論之，因為第六圖所示的循環 是朝向順時針方向移動，該熱機引擎20產生出正功或是有 用的功。 另一個實施例的熱機引擎200顯示於第七至十圖中。 該本實施例中’該熱機引擎包括四個活塞組㈣〇f pistons)202。每一活塞組2〇2包含—壓縮活塞32、一第一 膨脹活塞40及-第二膨脹活塞a每一活塞組逝分別如 同第一至五圖所描述的相同熱力學循環來運作。該些活塞 組202以引擎殻體(engine h〇using)2〇6的中心轴2〇4為參考 軸，設置成放射狀，使得該些活塞組2〇2間隔9〇度。 如第八及九圖所示，該熱機引擎200包含一傳動連桿 13/28 201030229 208 (例如凸輪板），其具有至少一第—凸輪截面（cam profilepiO以及一第二凸輪戴面2丨2。在本實施例中，與第 一凸輪戴面210銜接的從動件2丨4、216影響第一膨脹活塞 40及壓細活塞32的運動。類似地，第二膨脹活塞42有一 個與第二凸輪截面212銜接的從動件218。該些凸輪截面 ' 210、212設置成具有適合的幾何形狀’其可提供成有利於 第六圖所示的熱力循環的活塞32、4〇、42的時序(timing) 及動作。在本實施例中，該些從動件2M、2〗6、2]8包含 有一連接桿及滾輪。本領域已知的其它元件（圖未示)也可用 來讓從動件214、216、218與傳動連桿2〇8保持銜接。應_ 該知道的是，在其他實施例中，該熱機引擎2〇〇具有一用 於壓縮活塞32的第二凸輪截面，使得該壓縮活塞32與該 些膨脹活塞40、42位在不同階段(或稱相位(phase)p更應 該知道的S ’傳動連桿施也可以是一凸輪軸(議也姐)的 形式，以取代凸輪板。 請參閱第九圖，可以看出每一個活塞組2〇2分別位在 第六圖的熱力循環的不同階段(或稱相位）中。此舉讓熱機引 擎200以-實質相同的每分轉數!她，❹ RPM)平順地運作。每一個該膨脹活塞4〇、42連通先前敘 述的該些閥46、48。相對地，每一個膨脹活塞4〇及進氣閥 46藉由一岐管一起連接至單一個導管(c〇nduit)22〇，使得該 些膨脹活塞40連接至單個高溫熱交換器24。類似地，相對 的每一個第二膨脹活塞42及排氣閥48藉由㊉妓管士起連 接至一導管222，如此只需一條連接管連接回熱器.28。 …回熱,器微連接至一導管224，導管224逮接回激暴28 - 及低溫熱交換器26。該低溫熱交換器26;.藉通分破；聲連接至 14/28 201030229 單一個導管226 ’分配該工作氣體通過第二單向閥52到達 該些壓縮汽缸34中。當壓縮完工作氣體後，每一個壓縮汽 紅34藉由單向閥5〇連接至一岐管228。一導管230連接該 岐管228及該回熱器28。該回熱器28相應地藉由導管232 連接至高溫熱交換器24而完成此流體迴路(fluid circuit)。 如第十圖所示，為一熱機引擎300的另一實施例。類 似先前所述的該些實施例，該熱機引擎300包含有一個或 多個活塞組302 ’活塞組302包含一第一膨脹活塞40、一 φ 第二膨脹活塞42及一壓縮活塞32。該熱機引擎300並且含 有一高溫熱交換器24、一低溫熱交換器26及一回熱器28， 如同先前所述。 該些膨脹活塞40、42以及該壓縮活塞32連動地連接 至位在一曲轴箱(crankcase)306中的一傳動連桿304。連通 (fluidly couple)至曲軸箱3〇6的是一第一高壓力容器或壓力 槽 308(例如 2000 碎每平方英对(p〇und per SqUare inch，〇r psi))以及一第二低壓力容器或壓力槽31〇(例如1〇〇psi)。該 φ 些槽308、31〇依據所需的運作速度來對熱機引擎300增加 或減少氣體。應該知道的是’該些槽308、310可包含有一 個或多個元件（圖未示）’例如閥312、泵浦314以及感測器 316等，以幫助氣體的流動《在一實施例中，曲軸箱3〇6的 壓力被維持在一壓力，該壓力等於或小於熱力循環中的熱 機引擎所產生的最小壓力，例如第六圖所示的壓力容積圖 上的點102、108的壓力。在一實施例中，該壓力感測器316 量測位在低溫熱交換器26及壓縮汽缸34之間的導管318 的壓力。在這個層面下，藉由調整曲軸箱3〇6的壓力，任 何從汽缸洩漏出的工作氣體將流動至曲軸箱3〇6中，而再 15/28 201030229 度被利用。維持曲軸箱306的壓力也會產生些優點，因為 活塞密封件(piston sea』)（圖未示）之間的壓力差可被最小 化，如此施加在傳動連桿304上的力可被減少。 該些槽308、310也連接至位於回熱器28及壓縮活塞 32之間的導管320。一個泵浦314連接在該些槽308、31〇 之間，以從低壓槽3】0傳送工作氣體至高壓槽3〇8。應該知 道的是，將該些槽308、310連接至曲軸箱306及導管320 的該些導管被描述成分別地連接該些槽308、310，然而其 它的配置也可以被考量使用之。 在運作過程中，當功率需要降低時，該些槽3〇8、31〇 Φ 設置成將導管320的工作氣體移除至低壓槽31〇中。一旦 連接低壓槽310及導管320的閥關閉，泵浦314將工作氣 體傳送至高壓槽308中。當需要提高功率時，工作氣體從 尚壓槽308流回至導管320。此舉提供一優點：在不同功率 輸出下，熱機引擎仍可維持相同的轉速。此舉還提供些優 點：在任何時間上，平衡熱機引擎3〇〇中的工作氣體的量。 如第十一圖及第十二圖所示，為另一個實施利的熱機 引擎350。類似先前所述的該些實施例，該熱機引擎具有多 參 數個設置在殼體30的汽缸。應該知道的是，該熱機引擎350 也包含有先前敘述的一回熱器28、熱交換器24、26及多個 閥46、48、50、52，然而為了簡潔，該些元件沒繪製在第 ^ 十一至十二圖。此外，該熱機引擎350也可包含敘述過的 …:… 4 : l槽308、310。該熱機引擎350進一步包含有一活塞組，.其擎31 包含有第一膨脹活塞40、第二膨脹活塞42及壓縮活塞52 m ¥ •、丨r:」:::母一個活塞32、40、4Z各有:一:個相連的連接桿(connector丨2各 A 1¾ rod)352。不像先前所述的該些實施例本實施例中該壓縮此的沒匕 16/28 201030229 活塞32及第二膨脹活塞42連揍至一第一拉桿（办吗 link)354。該第一拉桿樞接於一軸356上。第二膨脹活 塞42與壓縮活塞32的連接提供些優點：讓一傳動連桿44 能使用，該傳動連桿44包含有一曲軸總成（cmnk aSSembly)362，第二膨脹活塞42能停留在上死點位置，而 壓縮活塞32能停留在下賴位置。該第—舰活塞4〇連 接至一第二拉桿358，第二拉桿358樞接在一軸36〇上。 傳動連桿44包含有一上連桿364、一下連桿366及一 φ 曲軸臂(Crank arm)368，其連接而繞著一銷370旋轉。該些 下連桿366連接至拉桿354，該拉桿354相鄰用於第_膨脹 活塞40及壓縮活塞32的連接桿尬。該上連桿辦樞接於 一軸372，其將該上連桿364固定至曲軸箱3〇6。每曲 軸臂368依次連接至曲軸總成362中的其中一個輪 (l〇be)374。應該知道的是，該些連桿364、366、曲軸臂/368 以及輪葉瓣374上的連接點的軌跡，決定了該進膨服活塞 40、42的運動。在本實施例中，該些膨脹活塞4〇、似的運 ❷ 動被5免置成工作流體同時從兩個膨脹汽紅36、38排出。該 曲軸總成362更包含一傳動軸376，其將熱機引擎35〇產生 的旋轉運動傳遞出。應該知道的是，該熱機引擎35〇也包 含軸承座(bearing housings)，為了簡潔所以圖未示。 在本實施例中，該熱力運作循環是由壓縮活塞32及膨 服活塞40、42的運作模式所定義之。該循環從絕熱地壓縮 —低溫工作流體開始。該工作流體之後通過一熱交換器（例 如第一圖的高溫熱交換器24)而被加熱。位在第一膨脹活 塞40的閥46(如第-圖所示）開啟’以允許該高溫工作流體 流進該第一膨脹汽缸36。當該第膨脹活塞4〇向下移動時， 17/28 201030229 該工作流體等溫地膨脹（工作流體的壓力下降而溫度保持 相同）。一旦該第一膨脹活塞40到達移動路徑的底部，原 本開啟的閥46將關閉。在第一膨脹汽缸36的工作流體的 容積變成在第二膨脹汽缸38的工作流體的初始膨脹容積。 為第二膨脹活塞42向下移動，該工作流體絕熱地膨脹(工作 . 流體的壓力和溫度都會下降)。一旦第二膨脹活塞42移動到 它的移動路徑的底部，該排氣閥48(如第一圖所示）開啟， 並且兩個膨脹活塞4 0、4 2實質地同時將較低壓及低溫的工 作流體從膨脹汽缸36、38排出至回熱器28。當被排出的工 作流體通過回熱器28時，熱能將傳遞至低溫且被壓縮的工 _ 作"ilIk，上述工作流體係從壓縮汽缸34流到高溫熱交換器 24)。離開回熱器28後，藉由一適當的介質中(例如冷卻水 (cooling water任何殘留在工作流體的熱通過低溫熱交 換器排出。該低溫的工作流體之後位在一個可再度開始該 循環的位置。 在本實施例中，第二膨脹活塞42的剖面面積比第一膨 服活塞36小。熱源n (如第一圖所示）與用以移走散熱器 54 (如第—圖所示）的熱的低溫介質之間的溫差，影響了 肇 β亥些膨脹活塞4〇、42及壓縮活塞的尺寸。該低溫介質 通常為大氣（例如大氣溫度），但是也可使用其它的形式， 例如/可水’或甚至是液體丙烧(liquid propane)。膨脹比的定? ι 義為尚溫除以低溫(Thot /TC0W)。例如，高溫侧為700K，：而. 低溫侧為300K，則膨脹比為2.333 : 1 :。.在此例子中，第笱搞;心 膨，汽虹36的初始膨脹容積與兩個膨脹汽缸363、:m的全^ 部谷積之間的比值為大的1在高溫熱交換器.24..與低溫熱绞六 功之間的溫差高的情況下，第二膨脹活塞,;42·的罐面彳的^ 18/28 201030229 面積將大於第一膨脹活塞40。在溫差低的情況下，例如用 於蒸汽冷凝（steam condensing)，該比值大致為1 : 1 25。 在這些低溫差的情況下，該高溫側可位於37〇κ至425K之 間，低溫侧為大氣溫度。在這些實施例中，該第一膨脹活 塞40將大於第二膨脹活塞42。此外，活塞的直徑及衝程長 度(stroke length)可由一特定頻率所產生的所需功率決定 之。在一給定的功率下，頻率越高，膨脹活塞4〇、42將越 小。在部分實施例中，所需的運作頻率位於5到1〇赫茲(Hz) 之間。在此頻率運作下的熱機引擎可提供些優點，例如減 少流體損失以及零件磨耗的保養問題。 第十三及十四圖顯示出另一個實施例的熱機引擎 380。本貫施例中，該熱機引擎380包括多個活塞組$82 , 每一個實質地跟第十一及十二圖所示的實施例相同。應該 知道的疋，5亥熱機引擎380也包含有先前敘述的一回熱器 28、熱交換器24、26及多個閥46、48、50、52，然而為了 簡潔，該些元件沒繪製在第十三及十四圖。此外該熱機引 擎380包含先前敘述的槽3〇8、310。每一個活塞組382包 含有一壓縮活塞32、一第一膨脹活塞4〇及一第二膨脹活塞 42。如先前所述，該壓縮活塞32及第二膨脹活塞42透過 一拉桿354連接。每一個活塞組382透過一傳動連桿44連 接至一個具有一曲軸386的曲軸總成384。該曲軸386連接 每一個活塞組382,以將運作過程中產生的功率傳送至一外 部過程，例如一發電機。應該知道的是，該些活塞組3幻 互相配合以依序運作，藉此讓曲軸386實質地連續轉動。 應該知道的是’雖然在此敘述的實施例的熱機引擎具 有單一個壓縮活塞及汽缸，然而，本發明所保護不應侷限 19/28 201030229 於此。該其他實施例中，該熱機引擎可具有多個壓縮汽缸， 但仍然提供工作流般的單向流動。在一實施例中，該工作 流體在兩個壓縮汽缸之間分離。 相對於習知振盪流體的熱機引擎，在此揭露的熱機引 擎提供出多個優點。該熱機引擎去除了質量傳遞效率的問 題，因為全部被壓縮的工作流體都到達熱機引擎的高溫 側，以傳送有用的功。利用單向流動，一逆流式熱交換器 了取代振鹽:流體熱機引擎中的傳統回熱器，藉此提供另一 個優點。因為逆流式熱交換器用於橫跨回熱器的長度而能 、、隹持較尚/JBL度梯度之能力，逆流式熱回收比起振盪流體式 回熱器更有效率。 惟以上所述僅為本發明之較佳實施例，非意欲侷限本 务月之專利保濩範圍，故舉凡運用本發明說明書及圖式内 =所為之等效變化’均同理皆包含於本發明之權利保護範 園内，合予陳明。 【圖式簡單說明】 第一圖為本發明的一實施例的一熱機引擎的示意圖。 第二圖為第-圖的熱機引擎伴隨著第一膨脹活塞位於參 下死點位置的示意圖。 第二圖為第-圖的熱機引擎伴隨第二膨脹活塞位於下 死點位置的示意圖。 見-,±.. 0 ; _ =丨“第五圖為第-_熱機引擎伴隨第·第:_脹活塞 -10 °1；'-/ 〜〜策六圖為用於第-至五圖的熱機引賴働循環的壓 20/28 201030229 力容積範例圖。 第七圖為另-實施例的具有八個膨脹活塞的熱機引擎 的平面示意圖。201030229 VI. Description of the invention: [Technical field to which the invention belongs]. The present invention relates to a heat engine for a closed system, and more particularly to a heat engine that provides a one-way flow of jh gas and gas pressure in the engine. [Prior Art] The external combustion engine heat (8) is associated with a plurality of cycles that take heat out from the outside (for example, waste heat of solar energy or a pin furnace) and transfer heat to the engine (or engine): L as a fluid In the middle of it produces useful work. The Stirling cycle (S-cut ng eye|es) and the Ehrlich cycle (EH_n is called part of these cycles, which utilizes external heat sources. Although Sterling is an open loop, and Eric The biocycle is a closed loop' However, both loops use a regenerator (4) (10) coffee.). Today, for a simple cycle, the Stirling cycle has achieved the highest efficiency, because the regenerator can recover the heat that is normally drained in one cycle and transfer this heat to the next cycle of working gas. in. Traditionally, Sterling engines operate at high temperatures (75 degrees Celsius) and high speeds (30 to 50 (Hei, tz)) to achieve high power to weightmtios. Because of the high operating temperatures and pressures, the high-temperature Stirling engine suffers permanent damage due to riding stress (ereep st), even if the Stirling engine uses an ex-tic metal, such as a chromium alloy ( I_d). Recent developments in the Stirling engine have been converted to electrical energy using heat sources such as waste heat, solar energy or geothermal heat. However, a very small number of productive engines are shown and can only be used in the range of low power rounds. The operation of a conventional Stirling engine is achieved by vibrating the working gas between a high and low temperature heat exchanger 4/28 201030229 (hot and cold heat exchanger) and an expansion and compression piston. The main drawback of this oscillating gas engine is that the volume of the high and low temperature heat exchanger is the same as the piston's swept volume. In half of the cycle, 'the volume must be compressed and expanded. Although in the other half of the cycle, the dead space is considered to have a negative effect. The compression piston compresses the gas into a low temperature heat exchanger for isothermal compression. The further action of the compression piston is that the low temperature of the moving part φ gas enters the high temperature heat exchanger through the regenerator. The gas in the high temperature heat exchanger is heated and the expansion piston begins to expand. As far as it is concerned: the Gujizhong Temple, which is the hot father of the south of the country, is warmly spread. This configuration is missing. When expansion occurs, a large amount of working gas is left in the volume of the low temperature splash exchanger. In high temperature engines, because of the valley ratio of the heat exchanger to the working volume of the piston, the remaining working gas is acceptable in the low temperature heat exchanger. In the high temperature (four) engine, the ratio is usually 1:3, while in the low temperature engine, the ratio can be as low as US: i. It can be seen that in the low temperature engine, the heat exchanger has a larger capacity than the piston jade volume, and the excess body is left in the low temperature heat exchange. In fact, more work is used to compress a gas, and 5 hectares of gas do not have a high temperature zone to produce useful work. This is the main reason why the traditional Sterling engine is not effectively able to operate in degrees below Celsius. Although the existing heat engine is suitable for various timings, the temperature is low, and the temperature is low. [Inventive content] 5/28 201030229 According to a part of the present invention, a closed cycle heat engine is raised. The engine includes a first expansion piston, and the first expansion piston is disposed in a first cylinder. A second expansion piston is disposed in a second cylinder and is coupled to the first expansion piston in a linked manner, wherein the second steam communicates (m_c_e) with the first steam. a compression piston disposed in a third steam and coupled to the first expansion piston, wherein the third steam is connected to receive the working fluid from the second cylinder to the working fluid In the first cylinder. And the Boao engine, the second part of the engine, a heat engine with a working fluid is supplied. The pinning engine includes - a first steam (four), a piston, the first expansion piston is connected and connected in series, and a first-secret. - a first compression piston is connected to and coupled to the first piston and the second expansion piston. The first cylinder-cylinder ridge is formed with a first-seal ring to provide a one-way flow of the servant fluid. The =, _--partial--three methods of closed-loop heat engine are provided. The method includes heating 4 as a fluid. The X heated by the expansion enters the expansion of the first-cylinder to move the plug to the - position. The heated shield fluid flows into the second cylinder and moves - the second expansion piston to the second position. The fluid flows from the first cylinder and the second steam to the - cylinder. And the working fluid is compressed in the _ two cylinder towel - compression piston. The working fluid flows from the third cylinder into the first cylinder. According to still another aspect of the present invention, a heat engine is provided, the heat engine including at least two expansion pistons in communication with each other, each of the expansion plugs being disposed on a ship cylinder. At least - the pressure wheel plugs are at least two expansion pistons, each of which is disposed in a compression cylinder. A transmission 6/28 201030229 is coupled to the at least two expansion pistons in linkage with the at least one compression movable transmission link disposed in a crankcase, wherein the crankcase communicates with the expansion cylinders and the compression cylinders. A pressure tank is also provided to communicate with the crankcase, wherein the pressure tank is used to add a pressurized gas to the crankcase to reflect changes in the operation of the heat engine. According to still another aspect of the present invention, a closed cycle heat engine is provided, the heat engine comprising a first expansion piston, the first expansion piston being disposed in a first cylinder. A second expansion piston is disposed in a second cylinder and is coupled to the first expansion piston in a coordinated manner, wherein the second cylinder communicates with the first cylinder. a compression piston disposed in a third cylinder and coupledly coupled to the first expansion piston 'where the third cylinder is in communication for receiving a working fluid from the second cylinder and transmitting the working fluid To the second cylinder. A transmission speed lever connects the first expansion piston, the second expansion piston, and the compression piston, wherein the transmission link is a cam plate or an articulated crankshaft (articulated C1'ankshaft). a transmission box connecting the transmission link, the transmission box operating under a pressure less than or equal to "the working fluid is in the first cylinder and the second cylinder during operation of the closed circulation heat engine Minimum pressure. The thermal energy of the working fluid flowing from the second cylinder to the third cylinder is transferred to the working fluid flowing from the third cylinder to the first cylinder by a regenerator, wherein the regenerator is a counterflow type Heat exchanger. A heater is coupled between the regenerator and the first cylinder in a heat transferable manner. A cooler is coupled to the third cylinder and the hot state of the face in a heat transferable manner. A first valve is in communication between the heater and the first cylinder. The second valve is connected between the second cylinder and the regenerator. A first one-way chamber communicates with the third cylinder to allow the working fluid to flow into the third cylinder command. The second check valve is connected to the third cylinder to allow the worker 7/28 201030229 to flow out of the third cylinder. A further part of the invention provides a computer with a working fluid. The heat engine includes a -th steam red set having a first-expansion piston and a -th compression piston, the first expansion piston being connected and linked in series - a second expansion piston, - (d) The piston connects and interlocks the first expansion cylinder and the second expansion cylinder. Wherein the first piston set is arranged in a first closed loop to provide a one-way flow of the working fluid. - the second cylinder group is coupled to the first group of cylinders in series, the second = a third expansion piston and a "second compression piston", the third expansion activating connection - a fourth expansion piston, the second compression piston is connected and f The third expansion chamber and the fourth expansion cylinder are movably connected, wherein the first group of second closed cycles to provide the working fluid of the unit A and the second group are spaced 90 degrees apart from each other. a first way of connecting the first closed loop and the second closed heat exchanger to the portion of the first seal between the second and the lower pistons, and the regenerator is set to live The second compression seal located in the first _ swelled piston field is followed by two points. A heater connects the first closed cycle and the second one transfers thermal energy to the working fluid. ^ Yes. A gearbox, table ^ f transfers heat from the working fluid. The transmission rt is connected (four) f-cylinder group to listen to the second steam red group, the engine is 乍; 乍: m 'the operating pressure is less than or equal to the hot two cylinder The most ^pressure two working fluids in the group are in the first-missing group and the first/. The remote method involves heating a working fluid. The expansion is heated 8/28 201030229 The working fluid enters a first vapor red to move a first expansion piston to a first position. The heated working fluid flows into a second cylinder to move a second expansion piston to a second position. The working fluid flows from the first cylinder and the second cylinder into a third cylinder. The working fluid is compressed by a compression piston in the third cylinder. The working fluid flows from the third cylinder into the first vapor red. The heat of the working fluid flowing from the second cylinder to the third cylinder is transferred to the working fluid flowing from the third cylinder to the first cylinder before the step of heating the working fluid. The working fluid is cooled 'before the working fluid in the step of flowing the working fluid flowing to the second cylinder is compressed. The second expansion piston is retained in the second position during the flow of the working fluid from the first cylinder to the third cylinder. Finally, when the second expansion piston is in the second position, a transmission case is pressurized to a first pressure that is less than or equal to the operation in the first cylinder and the second cylinder. The pressure of the fluid. The present invention is to be understood as being limited by the following detailed description and the accompanying drawings. [Embodiment] Referring to Figures 1 to 5, an embodiment of an external heat engine 20, or a heat engine 2, is shown. The heat engine 20 utilizes an external heat source 22 to transfer thermal energy to a 'working gas' in the heat engine 20. The heat engine 2 is a closed system that includes a hot heat exchanger 24 (or heater 24) and a low temperature heat exchanger 26 (or A cooler 26) and a regenerator 28. The heat engine 20 further includes a 9/28 201030229 housing 30 that includes at least three cylinders (cyHnders) 34, 36, 38. The first or compressed steam rainbow 34 includes a compression piston 32 for compressing the low temperature working gas. The compression piston 32 is connected to two expansion pistons (eXpansi〇n pist〇n) which are respectively accommodated in the two expansion cylinders 36,38. Each piston is connected to a drivelinkage 44. The heat engine 20 also includes a plurality of valves 46, 48, 50, 52 to control the flow of working gas through the heat engine 20. The heat engine 20 utilizes an imidirectional flow of working gas from the compression cylinder 34 through the regenerator 28 and then into the high temperature heat exchanger 24 and the expansion cylinders 36, 38, and then back . As will be more clearly explained below, by passing all of the compressed working fluid through the high temperature heat exchanger 24, the unidirectional flow of the gas can provide advantages because all of the working gas is directed to the heat engine in one direction. Capture 20 spreads. The heat engine 2 can also produce advantages by utilizing adiabatic compression after the isothermal heating step of the temperature heat exchanger 24. Referring to the first figure, the first expansion piston 4 has an intake valve 46. When the first expansion piston 4 moves, the intake valve 46 is opened and the pressure is high (pmax) and high temperature. The working gas of (Tmax) flows into the first expansion cylinder 36. Since the compression piston 32 and the first expansion piston 40 move simultaneously, the total volume of the first expanded working gas is slightly changed. The effect is that the pressure and temperature of the working gas remain substantially the same, just like an isobaric (1^^) / isothermal (isotherman expansion. As shown in the first figure, once the first expansion piston 4〇 reaches The dead center position 'intake valve 46 is closed' and the second expansion piston 42 parked at the top dead center position is allowed to move. The following explains: the movement of the pistons '32, 40, 42 It is defined by the transmission link 44. In an embodiment, 10/28 201030229 the transmission link 44 is a cam plate having at least one profile. The first expansion piston 36 The volume determines the initial expansion volume of the second expansion cylinder 38. The expansion of the working gas in the second expansion cylinder 38 is substantially adiabatic. The third figure shows that when the second expansion piston 42 moves, the first expansion piston 40 stays At the bottom dead center position, after the second expansion piston 42 reaches the bottom dead center position, the working gas expands to the minimum pressure (Pmin) of the heat engine 20. After the second expansion piston 42 reaches the bottom dead center position, the row Exhaust valve 48 is open And the working gas is allowed to move into the low temperature heat exchanger 26. As shown in the fourth figure, it is known that the heat engine 20 can be disposed from the expansion cylinders 36, 3 or by the configuration of the transmission 44. The working gas is removed in sequence. The working gas still contains a large amount of thermal energy as the working gas is removed from the expansion cylinders 36, 38. The working gas first flows through the regenerator 28' toward the low temperature heat exchanger 26. The working fluid is taken out of the thermal energy by the regenerator 28. In the embodiment, the regenerator 28 is a counter flow heat exchanger, which may be a plurality of plates or tubes of a tubular exchanger. In the tubular exchanger, the high temperature gas flows through a chamber in one direction and the low temperature gas flows through an adjacent chamber in an opposite direction. The main function of the regenerator 28 is: the working gas reaches the low temperature heat exchanger Before 26, heat energy is extracted from the discharged working gas (meaning the working gas flowing to the low temperature heat exchanger 26), and the compressed and low temperature working gas flowing out from the compression cylinder 34 reaches the high temperature heat exchanger 24 Before, the heat energy is transferred to the working gas. When the working gas passes through the regenerator 28, the working gas comes to the low temperature heat exchanger 26, where all the irreversible heat energy is substantially removed 11/28 201030229 And discharged to the atmosphere by a radiator 54. The low temperature working gas leaves the low temperature heat exchanger 26 and then enters the compression cylinder 34. In the compression cylinder 34, the compression piston 32 adiabatically compresses the working gas. As shown in Figure 5. Once the pressure of the compression cylinder 34 reaches a maximum (pmax), a check valve 50 opens and allows the compressed working gas to move from the compression cylinder 34 to the regenerator 28. A second one-way valve 52 is disposed adjacent the inlet of the compression cylinder 34 to prevent backflow of gas to the low temperature heat exchanger 26. When the cryogenic working gas flows through the regenerator 28, it is heated by the discharged working gas flowing backwards. As previously explained, the working gas leaves the regenerator 28 at a temperature lower than the maximum operating temperature (Tmax). The working gas is then passed through a high temperature heat exchanger 24 in which an external heat source is again utilized to heat the working gas to a maximum temperature (Tmax) and the thermodynamic cycle is repeated. The operation mode of the heat engine 2 is described in another manner in conjunction with a pressure volume map (pressure_v〇 ume ("PV") diagram) shown in the sixth figure. Pressure volume maps are often used to describe thermodynamic cycles. The pressure volume map can be used to calculate the work produced by the heat engine (Li k) by integrating the pressure against the volume. This work can be quickly calculated by calculating the product of the surface φ surrounded by the cycle of the pressure volume map. Normally, when the heat engine is operating in a clockwise direction as shown in the pressure volume map, positive work can be produced. 〇 The cycle starts at point 102 and corresponds to the position of the heat engine shown in the first figure. At this point, the heat engine 20_force and volume are the minimum temperature work «received into the _ 46 and entered the expansion cylinder 36: the heat engine engine fine pressure rises, and the volume actually maintains the lion to reach the maximum At the time of pressure 'the intake valve 46 _ and the cycle is at point 12/28 201030229 104, which corresponds to the second figure. The drive link 44 is configured to allow the second expansion piston 42 to move rearwardly, whereby the working gas expands into the second expansion cylinder 38. This increases the volume of the heat engine 20 while allowing the pressure to be independent, as if the cycle moved from point 104 to point 1〇6. After reaching point 1〇6, the venting valve 48 opens, allowing working gas to flow out of the madness 36, 38, bribing through the regenerator 28 and the low temperature heat exchanger 26, into the compression cylinder 34. It should be understood that although the fourth and fifth figures show that the expansion pistons 4, 42 are sequentially moved, the transmission link 44 can also be arranged to simultaneously move the two expansion pistons 40, 42. Since the working gas flows from the expansion cylinders 36, 37 to the compression cylinder bore, the pressure drops and the volume increases until the cycle reaches point 1〇8, which corresponds to the position of the heat engine 20 shown in the fifth figure. _ ° To end the thermodynamic cycle, the low temperature working gas flows back from the compression cylinder, absorbing heat from the regenerative state 28 and the still temperature heat exchanger 24. When the heat engine 20 returns to the position shown in the figure - the volume drops and the pressure remains in the same state. As previously discussed, because the cycle shown in Figure 6 is moving in a clockwise direction, the heat engine 20 produces positive or useful work. The heat engine 200 of another embodiment is shown in Figures 7 through 10. In the present embodiment, the heat engine includes four piston groups (four). Each piston set 2〇2 includes a compression piston 32, a first expansion piston 40 and a second expansion piston a each operating in the same thermodynamic cycle as described in Figures 1 to 5, respectively. The piston groups 202 are arranged in a radial direction with the central axis 2〇4 of the engine casing 2〇6 as a reference axis, so that the piston groups 2〇2 are spaced 9 degrees apart. As shown in the eighth and ninth views, the heat engine 200 includes a transmission link 13/28 201030229 208 (eg, a cam plate) having at least one first cam profile (cam profilepiO and a second cam profile 2丨2). In the present embodiment, the followers 2丨4, 216 engaged with the first cam wear surface 210 affect the movement of the first expansion piston 40 and the crush piston 32. Similarly, the second expansion piston 42 has a The second cam section 212 engages the follower 218. The cam sections '210, 212 are arranged to have a suitable geometry' which can be provided to the pistons 32, 4, 42 which facilitate the thermodynamic cycle shown in the sixth figure. Timing and action. In this embodiment, the followers 2M, 2, 6, 2, 8 include a connecting rod and a roller. Other components (not shown) known in the art can also be used to The followers 214, 216, 218 are in engagement with the drive link 2 〇 8. It should be understood that in other embodiments, the heat engine 2 has a second cam section for the compression piston 32, The compression piston 32 and the expansion pistons 40, 42 are at different stages (or The phase p should know more about the S' drive link. It can also be in the form of a camshaft instead of a cam plate. See Figure IX. It can be seen that each piston group 2〇2 They are located in different stages (or phases) of the thermodynamic cycle of Figure 6. This allows the heat engine 200 to operate smoothly with - substantially the same number of revolutions per minute! She, RPM). Each of the expansion pistons 4 The ports 42 are connected to the previously described valves 46, 48. In contrast, each of the expansion pistons 4 and the intake valve 46 are connected together by a manifold to a single conduit 22, such that The expansion piston 40 is coupled to a single high temperature heat exchanger 24. Similarly, each of the opposing second expansion piston 42 and exhaust valve 48 is connected to a conduit 222 by a ten-inch pipe so that only one connecting pipe connection is required Regenerator. 28. Reheating, the device is micro-connected to a conduit 224, the conduit 224 is caught back to the turbulence 28 - and the low temperature heat exchanger 26. The low temperature heat exchanger 26; Connected to 14/28 201030229 a single conduit 226 'distributes the working gas through the second check valve 52 to reach the In the cylinder 34, after the working gas is compressed, each of the compressed steam red 34 is connected to a manifold 228 by a one-way valve 5A. A conduit 230 connects the manifold 228 and the regenerator 28. The fluid circuit 28 is correspondingly connected to the high temperature heat exchanger 24 by means of a conduit 232. As shown in the tenth embodiment, it is another embodiment of a heat engine 300. Similar to the previously described In an embodiment, the heat engine 300 includes one or more piston sets 302. The piston set 302 includes a first expansion piston 40, a φ second expansion piston 42, and a compression piston 32. The heat engine 300 also includes a high temperature heat exchanger 24, a low temperature heat exchanger 26, and a regenerator 28, as previously described. The expansion pistons 40, 42 and the compression piston 32 are coupled in series to a drive link 304 located in a crankcase 306. Fluidly coupled to the crankcase 3〇6 is a first high pressure vessel or pressure tank 308 (e.g., 2000 psi) and a second low pressure. The vessel or pressure tank 31 is (for example, 1 psi). The φ slots 308, 31〇 add or reduce gas to the heat engine 300 depending on the desired operating speed. It should be understood that the grooves 308, 310 may include one or more components (not shown) such as valve 312, pump 314, and sensor 316 to assist in the flow of gas. The pressure of the crankcase 3〇6 is maintained at a pressure equal to or less than the minimum pressure generated by the heat engine in the thermodynamic cycle, such as the pressure at points 102, 108 on the pressure volume map shown in FIG. In one embodiment, the pressure sensor 316 measures the pressure of the conduit 318 between the low temperature heat exchanger 26 and the compression cylinder 34. At this level, by adjusting the pressure of the crankcase 3〇6, any working gas leaking from the cylinder will flow into the crankcase 3〇6, and then 15/28 201030229 degrees will be utilized. Maintaining the pressure of the crankcase 306 also provides advantages because the pressure differential between the piston seals (not shown) can be minimized so that the force exerted on the drive link 304 can be reduced. The slots 308, 310 are also coupled to a conduit 320 between the regenerator 28 and the compression piston 32. A pump 314 is connected between the slots 308, 31 , to transfer working gas from the low pressure tank 3 0 to the high pressure tank 3 〇 8. It will be appreciated that the conduits connecting the slots 308, 310 to the crankcase 306 and conduit 320 are depicted as being coupled to the slots 308, 310, respectively, although other configurations are contemplated. During operation, the slots 3〇8, 31〇 Φ are arranged to remove the working gas of the conduit 320 into the low pressure tank 31〇 when the power needs to be reduced. Once the valve connecting the low pressure tank 310 and the conduit 320 is closed, the pump 314 delivers the working gas to the high pressure tank 308. When increased power is required, the working gas flows back from the pressure tank 308 to the conduit 320. This offers the advantage that the heat engine can still maintain the same speed at different power outputs. This also provides the advantage of balancing the amount of working gas in the heat engine engine 3 at any time. As shown in the eleventh and twelfth drawings, another heat engine 350 is implemented. Similar to the previously described embodiments, the heat engine has a plurality of cylinders disposed in the housing 30. It should be understood that the heat engine 350 also includes a regenerator 28, heat exchangers 24, 26 and a plurality of valves 46, 48, 50, 52 as previously described, however, for the sake of brevity, the components are not drawn ^ 11 to 12 maps. In addition, the heat engine 350 may also include the described ...:... 4: l slots 308, 310. The heat engine 350 further includes a piston set. The engine 31 includes a first expansion piston 40, a second expansion piston 42 and a compression piston 52 m. •, 丨r: "::: a mother piston 32, 40, 4Z Each has: one: a connected connecting rod (connector 丨 2 each A 13⁄4 rod) 352. Unlike the previously described embodiments of the present embodiment, the compressed piston 16 and the second expansion piston 42 are connected to a first tie rod 354. The first pull rod is pivotally connected to a shaft 356. The connection of the second expansion piston 42 to the compression piston 32 provides advantages in that a transmission link 44 can be used, the transmission link 44 includes a crankshaft assembly (cmnk aSSembly) 362, and the second expansion piston 42 can stay on top. The point position, while the compression piston 32 can stay in the lower position. The first ship piston 4 〇 is connected to a second pull rod 358, and the second pull rod 358 is pivotally connected to a shaft 36 。. The drive link 44 includes an upper link 364, a lower link 366 and a φ crank arm 368 that are coupled for rotation about a pin 370. The lower links 366 are connected to a tie rod 354 which is adjacent to the connecting rods of the first expansion piston 40 and the compression piston 32. The upper link is pivotally coupled to a shaft 372 that secures the upper link 364 to the crankcase 3〇6. Each of the axle arms 368 is in turn coupled to one of the crankshaft assemblies 362. It will be appreciated that the trajectories of the connecting points 364, 366, crank arm/368 and the attachment points on the vane 374 determine the movement of the inflating pistons 40, 42. In the present embodiment, the expansion pistons 4, like the movements, are removed from the two expansion steams 36, 38 while being free from the working fluid. The crankshaft assembly 362 further includes a drive shaft 376 that transmits rotational motion generated by the heat engine 35A. It should be understood that the heat engine 35〇 also includes bearing housings, which are not shown for the sake of brevity. In the present embodiment, the thermal operating cycle is defined by the mode of operation of the compression piston 32 and the expansion pistons 40,42. The cycle begins with adiabatic compression, a low temperature working fluid. The working fluid is then heated by a heat exchanger (e.g., the high temperature heat exchanger 24 of the first figure). A valve 46 (shown in Figure-FIG.) located in the first expansion piston 40 is opened to allow the high temperature working fluid to flow into the first expansion cylinder 36. When the first expansion piston 4 〇 moves downward, the working fluid expands isothermally (the pressure of the working fluid drops while the temperature remains the same). Once the first expansion piston 40 reaches the bottom of the path of travel, the originally opened valve 46 will close. The volume of working fluid at the first expansion cylinder 36 becomes the initial expansion volume of the working fluid at the second expansion cylinder 38. As the second expansion piston 42 moves downward, the working fluid expands adiabatically (working. The pressure and temperature of the fluid will decrease). Once the second expansion piston 42 is moved to the bottom of its path of travel, the exhaust valve 48 (as shown in the first figure) is opened, and the two expansion pistons 40, 42 are substantially simultaneously lower and lower. The working fluid is discharged from the expansion cylinders 36, 38 to the regenerator 28. When the discharged working fluid passes through the regenerator 28, the thermal energy is transferred to the low temperature and compressed ("ilIk, which flows from the compression cylinder 34 to the high temperature heat exchanger 24). After leaving the regenerator 28, it is discharged through a suitable medium (for example, cooling water (the heat remaining in the working fluid is discharged through the low temperature heat exchanger. The low temperature working fluid is then placed in a recurring cycle) In this embodiment, the second expansion piston 42 has a smaller cross-sectional area than the first expansion piston 36. The heat source n (as shown in the first figure) and the heat sink 54 are removed (as in the first figure) The temperature difference between the hot, low-temperature media, which affects the size of the expansion pistons 4〇, 42 and the compression piston. The low-temperature medium is usually atmospheric (for example, atmospheric temperature), but other forms may be used. For example, / can be water' or even liquid propane. The expansion ratio is determined by dividing the temperature by the low temperature (Thot / TC0W). For example, the high temperature side is 700K, and the low temperature side is 300K. Then the expansion ratio is 2.333 : 1 :. In this example, the third expansion; the heart expansion, the initial expansion volume of the steam rainbow 36 and the ratio of the total expansion volume of the two expansion cylinders 363, : m is large. The temperature between the high temperature heat exchanger .24.. and the low temperature hot twisted six work In the high case, the area of the second expansion piston, the surface of the tank ^ 18/28 201030229 will be larger than the first expansion piston 40. In the case of a low temperature difference, for example for steam condensing, The ratio is approximately 1:25. In the case of these low temperature differences, the high temperature side may be between 37 〇 κ and 425 K, and the low temperature side is atmospheric temperature. In these embodiments, the first expansion piston 40 will be larger than the first Second, the expansion piston 42. In addition, the diameter of the piston and the stroke length can be determined by the required power generated by a specific frequency. At a given power, the higher the frequency, the more the expansion pistons 4, 42 will be. In some embodiments, the required operating frequency is between 5 and 1 Hz. The heat engine operating at this frequency provides advantages such as reduced fluid loss and maintenance of part wear. Figures 13 and 14 show another embodiment of the heat engine 380. In the present embodiment, the heat engine 380 includes a plurality of piston groups $82, each substantially identical to the implementation shown in Figures 11 and 12. The same example. It should Knowing that the 5H heat engine 380 also includes a regenerator 28, heat exchangers 24, 26 and a plurality of valves 46, 48, 50, 52 as previously described, however, for the sake of brevity, the components are not drawn 13 and 14. In addition, the heat engine 380 includes the previously described slots 3〇8, 310. Each piston set 382 includes a compression piston 32, a first expansion piston 4〇, and a second expansion piston 42. As previously described, the compression piston 32 and the second expansion piston 42 are coupled by a tie rod 354. Each piston assembly 382 is coupled through a transmission link 44 to a crankshaft assembly 384 having a crankshaft 386. The crankshaft 386 connects each of the piston sets 382 to transfer power generated during operation to an external process, such as a generator. It will be appreciated that the sets of pistons 3 cooperate to operate in sequence, thereby allowing the crankshaft 386 to substantially continuously rotate. It should be understood that although the heat engine of the embodiment described herein has a single compression piston and cylinder, the protection of the present invention should not be limited to 19/28 201030229. In other embodiments, the heat engine may have multiple compression cylinders, but still provide a one-way flow like a workflow. In one embodiment, the working fluid is separated between two compression cylinders. The heat engine engine disclosed herein provides a number of advantages over conventional heat engine engines for oscillating fluids. The heat engine removes the problem of mass transfer efficiency because all of the compressed working fluid reaches the high temperature side of the heat engine to deliver useful work. With one-way flow, a counter-flow heat exchanger replaces the vibrating salt: a conventional regenerator in a fluid heat engine, which provides another advantage. Countercurrent heat recovery is more efficient than oscillating fluid regenerators because of the ability of the counterflow heat exchanger to span the length of the regenerator and maintain a higher/JBL gradient. However, the above description is only the preferred embodiment of the present invention, and is not intended to limit the scope of the patent protection of the current month. Therefore, the equivalent changes in the specification and the drawings of the present invention are all included in the present invention. In the scope of the invention of the invention, Chen Ming was given. BRIEF DESCRIPTION OF THE DRAWINGS The first figure is a schematic diagram of a heat engine according to an embodiment of the present invention. The second figure is a schematic diagram of the heat engine of the first diagram with the first expansion piston at the bottom dead center position. The second figure is a schematic diagram of the heat engine of the first diagram with the second expansion piston at the bottom dead center position. See -, ±.. 0 ; _ = 丨 "The fifth picture is the first - _ heat engine with the first: _ swell piston -10 °1; '- / ~ ~ tactics for the first to five figures The heat engine is based on the pressure of the cycle 20/28 201030229 force volume example diagram. The seventh diagram is a plan view of a heat engine with eight expansion pistons of another embodiment.
第八圖為第七圖的熱機引擎的另一平面示意圖。 第九圖為第七圖的熱機引擎的示意圖。“ 第十圖為另-實施例的具有曲轴箱壓力控制的熱機引 擎的示意圖。 第十一圖為又一實施例的具有曲轴配置的熱機引擎的 部分立體圖。 第十二圖為第十-圖的熱機弓丨擎的側視平面圖。 第十三圖為又-實施例的具有六個活夷！ 的部分立體圖。 、 第十四圖為第十三圖的熱機弓I擎的俯視平面圖 【主要元件符號說明】 B 組的熱機引擎The eighth figure is another schematic plan view of the heat engine of the seventh figure. The ninth diagram is a schematic diagram of the heat engine of the seventh figure. Figure 11 is a schematic view of another embodiment of a heat engine with crankcase pressure control. Figure 11 is a partial perspective view of a heat engine having a crankshaft configuration in accordance with yet another embodiment. A side view of the heat engine bow engine. The thirteenth image is a partial perspective view of the embodiment of the present invention with six actives! The fourteenth figure is a top plan view of the heat engine bow I engine of the thirteenth figure [mainly Component Symbol Description] Group B heat engine
外燃機、熱機引擎 外部熱源 高溫熱交換器（加熱器） 低溫熱交換器（冷卻器） 回熱器 20 22 24 26 殼體 壓縮活塞 汽缸 膨脹活塞 傳動連捍 閥 散熱器 28 30 32 34、36、38 40、42 44 46、48、50、52 54 21/28 201030229 102、104、106、108 熱機引擎200 活塞組 202 中心軸204 引擎殼體 206 傳動連桿 208 ' 第一凸輪截面 210 第二凸輪截面 212 從動件 214、216、218 參 導管 220、222、224、226、230、232 岐管 228 熱機引擎 300 活塞組 302 傳動連桿 304 曲軸箱 306 壓力容器（壓力槽） 308 壓力容器（壓力槽） 310 閥 312 ® 泵浦 314 感測器 316 導管 318 、 320 熱機引擎 350 連接桿 ά: 352 第一拉桿 354 弟一 轴 356^ - — 第二拉桿 22/28 201030229 軸 360 曲軸總成 362 上連桿 364 下連桿 366 曲軸臂 368 銷 370 軸 372 輪葉瓣 374 傳動軸 376 熱機引擎 380 活塞組 382 曲軸總成 384 曲軸 386External combustion engine, heat engine external heat source High temperature heat exchanger (heater) Low temperature heat exchanger (cooler) Regenerator 20 22 24 26 Housing compression piston Cylinder expansion piston drive flail valve radiator 28 30 32 34 , 36, 38 40, 42 44 46, 48, 50, 52 54 21/28 201030229 102, 104, 106, 108 Heat Engine 200 Piston Set 202 Center Shaft 204 Engine Housing 206 Drive Link 208 'First Cam Section 210 Second cam section 212 follower 214, 216, 218 reference conduit 220, 222, 224, 226, 230, 232 manifold 228 heat engine 300 piston set 302 drive link 304 crankcase 306 pressure vessel (pressure tank) 308 pressure Container (pressure tank) 310 Valve 312 ® Pump 314 Sensor 316 Catheter 318, 320 Heat engine 350 Connecting rod ά: 352 First rod 354 Brother one shaft 356^ - — Second rod 22/28 201030229 Shaft 360 Crankshaft total 362 Upper Link 364 Lower Link 366 Crankshaft Arm 368 Pin 370 Shaft 372 Vane 374 Drive Shaft 376 Hot Engine 380 Piston Set 382 Crankshaft Assembly 384 Crankshaft 386
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