201215826 六、發明說明： 【發明所屬之技術領域】 本提案係關於一種空调糸統，特別是一種具有提升工作流體 之過冷度的空調系統及其過冷度調節裝置。 【先前技術】 由於都會區地狹人稠，建築物互相緊鄰，因而容易使熱能聚 集且揮散困難。而現代人物質水平提升，對於生活環境的舒適度 要求亦相對提高，因而都會區的建築物大多會安裝一空調系統。 空調系統係將建築物内的溫度、濕度、壓力、風速及清淨度， 控制在指定範圍内，使建築物内的人員過著舒適生活。而一般空 調系統係由-壓麵將冷媒魏成高溫高壓的冷媒缝，之後則 送入-冷凝n中。接著再由_冷卻水塔配合-泵浦將冷水送入冷 凝器内，歧冷卻水與高溫高_冷職體進行熱錢。而高溫 同廢之冷縣義結成高壓冷舰體後，進人__膨闕進行膨服 以形成低壓冷雜體。接著，健冷職體再進人—蒸發器内， 以使此低壓冷躲顯外界環境進行熱交換而吸收大量的熱能。 接下來再以一風扇系統吹送被冷媒吸熱後的冷空氣，以產生冷房 效果作為室内之冷氣使用。最後，因吸熱而形成健的冷媒氣體 再由低壓官進入-壓縮機内以再次被壓縮為高溫高壓的冷媒氣 體。藉由上述空調系統的循環運作，可使室内空間獲得冷房的效 果。 、、然而現今市面上—般的空調產品，冷職過冷凝ϋ後之溫度 曰遍接近約40〜42 C。依照環境溫度為坑的條件而纟，若經過 201215826 冷凝器的冷媒之溫度賴再降低5〜rc的話，即可提升空調系統的 政益約1G〜15%之間。而目前市面上之空調系統提升魏效益的方 —法，鱗_增大冷凝ϋ、提高冷㈣風4的騎朗列冷凝器 -回路的變更等方法。然而這些方法皆f使空⑽、統整體更新，因 此勢必造成維修賴成本上的提高，對於較老舊的空調系統如須 提升過冷度以提升系統效益時，則將會是個可觀的花費。 【發明内容】 馨於以上的問題，本提案在於提供一種空調系統及其工作流 體之過冷度裝置，#轉決先前技術畴提升空調系統之系 統效益需要較高成本之問題。 本提案所揭露之工作流體之過冷度調節裝置’係用以調節於 一循環狀態下之一冷媒。冷媒在一第一樣態、一第二樣態及一第 二樣態之間變化。其中，第一樣態的冷媒為液態，第二樣態的冷 媒為液態且其壓力與溫度均低於第一樣態的冷媒，第三樣態的冷 媒為氣態且其壓力與溫度均低於第一樣態的冷媒。工作流體之過 • 冷度調節裝置包含有一機體、一第一流管及一第二流管。其中機 體具有一腔室，腔室具有一腔室入口及一腔室出口。第一流管設 置於腔室内’第一流管具有位於機體外的一第一入口及一第一出 口。第二流管設置於腔室内，第二流管具有位於該機體外的一第 一入口及一第二出口。其中，第一樣態之冷媒'第二樣態之冷媒 以及第三樣態之冷媒分別經由第一入口、第二入口以及腔室入口 而進入腔室内，並於腔室内進行熱交換後，分別由第一出口、第 一出口以及腔室出口離開腔室。 201215826 本提案所揭露之空梅統n媒於其内進行循環 。空調 系統包合-工作、m冷度調節裝置、—膨酬、—蒸發器、 -壓縮機以及-冷凝器。其中卫作流體之過冷度靖裝置包含一 機，、-第-流管、-第二流管及u。機體具有一腔室， 腔至具有-腔至人口及_腔室出口。第一流管設置於腔室内，第 -流管具有位於機體外的1—人口及—第—出^第二流管設 置於腔至内’第一流官具有位於機體外的一第二入口及一第二出 口。第一閥設置於該機體外，第一閥連通腔室入口。另外，膨脹 間八有知脹閥入口及一膨脹間出口，膨脹闕入口分別連通第一 間及第出口。洛發具有一蒸發器入口及一蒸發器出口，蒸發 器二連獅闕出口 ’蒸發ϋώπ連通第二人Π。壓縮機具有 £l/s機入口及 — ι缩機出口，壓縮機人口分別連通第二出口及 腔室出口。冷凝器具有一冷凝器入口及一冷凝器出口，冷凝器入 口連通_機出口，冷凝器出口連通第-人σ。其中，由第一入 進入腔至之冷媒、由第二入口進入腔室之冷媒以及由腔室入口 進入腔室之冷媒，於腔室内進行熱交換。 根據上述之空_統’係將由冷難流至膨脹_第一樣態 之冷媒流經過冷度調節裝置。因此使第—樣態之冷媒與過冷度調 即裝置内的第二樣態及第三樣態之冷媒進行熱交換，以降低第一 之冷媒之溫度。由於第一樣態之冷媒之溫度下降，因此也使 得空調糸統的過冷度獲得提升。是以這樣的過冷度調節裝置可提 升空調系統的系統效益。 有關本提案的特徵、實作與功效，兹配合圖式作最佳實施例 201215826 詳細說明如下。 【實施方式】 ' 請參照「第1圖」及「第2圖」，「第1圖」係為根據本提案 - 貝細1例之空5周糸統的結構示意圖，「第2圖」係為根據「第1圖' 之工作流體之過冷度調節裝置的放大示意圖。 」 本提案一實施例之空調系統20，係使一冷媒於其内進行相變 • 循環，以降低一區域之溫度。空調系統20包含一工作流體之過A 度調節裝置10、一膨脹閥2〇〇、一蒸發器3〇〇、一壓縮機4〇〇及一 鲁冷凝器500。並且，空調系統2〇更可包含一油分離器_。 其中，工作流體之過冷度調節裝置10包含有一機體、一 第一流管110及一第二流管130。並且，工作流體之過冷度調節裝 置10更可以包含有一第三流管140、一第一閥150及—第二閥 160。機體1〇〇具有一腔室12〇，腔室12〇具有一腔室入口 及 一腔室出口 124。此外，第一流管110設置於腔室120内，第一流 管U0具有一第一入口 112及一第一出口 114。第一入口 112及第 鲁—出口 114分別設置於機體100外，且第一流管110並不直接與 腔至120連通。意即，第一流管11〇雖設置於腔室12〇内，但第 —流官110上並無任何通孔連通腔室120，如「第2圖」所示。 • 第二流管13〇設置於腔室120内，第二流管130具有一第二 入132及一第二出口 134。第二入口 132及第二出口 134分別設 置於機體100外’且第二流管130並不直接與腔室120連通。並 且，第二流管130可被第一流管110所包覆，第一流管110與第 一机S 130之間可係為同心管之樣態。第二流管130並不直接與 201215826 第-流官11G連通。意即’第二流管13G雖設置於第—流管ιι〇 内’但第二流管130上並無任何通孔連通第一流管ιι〇,如「第2 圖」所示。 此外，第三流管140設置於腔室12〇内，第三流管14〇具有 一第二入口 142及一第三出口 144。第三入口 142及第三出口 144 分別設置於機體100外，且第三流管140並不直接與腔室12〇連 通。並且，第三流管140可係以螺旋環繞的方式，環繞第一流管 110，以及被第一流管110所包覆的第二流管130，如「第2圖」 所示，第一流管110包覆第二流管130亦可採用管中管之設計。 其中，第一流管110、第二流管130及第三流管ho係使用傳導係 數高之材質，例如採用銅(型號C1220T-H)等材料。 換句話說，由腔室入口 122至腔室出口 124、由第一入口 112 至第一出口 114、由第二入口 132至第二出口 134以及由第三入口 142至第三出口 144之路徑，係為四條個別獨立之流道。 此外，第一閥150設置於機體100外，且具有一第一閥入口 152及一第一閥出口 154。第一閥出口 154連通腔室入口 122，第 一閥150用以調節冷媒由腔室入口 122流入腔室120的流量。第 二閥160設置於機體1〇〇外，且具有一第二閥入口 162及一第二 閥出口 164。第二閥出口 164連通第三入口 M2’第二閥160用以 調節一冷媒由第三入口 142流入腔室120的流量。 本實施例之膨脹閥200具有一膨脹閥入口 210及一膨脹閥出 口 220,膨脹閥入口 210分別連通第一閥入口 152及第一出口 114。 膨脹閥200用以將高壓高溫之液態冷媒’膨脹為低壓低溫兩相之 10 201215826 冷媒，更近一步的來說即為氣液態共存之冷媒。 蒸發器300則具有-蒸發器入口训及一蒸發器出口 32〇,塞 -發器入口训連通膨闕出口 220,蒸發器出口 32〇連通第二入;; -〗32。蒸發器用以將由膨脹閥出口 220流出的健低溫兩相之 冷媒，蒸發為低壓低溫之氣態冷媒，朗時吸收大量的熱能以使 室内空氣溫度下降。 本實施例之_機具有-壓縮機入口彻及一氣縮機出 口· ’壓縮機入口 分別連通第二出口 134、該腔室出口 124 •以及第三出口 144。_機4〇〇用以將由工作流體之過冷度謌節裝 置10流出壓低溫之氣態冷媒，麵為高料溫之氣態冷媒: 此外，冷凝器500具有-冷凝器入口獨及一冷凝器出口 別。冷凝器入口 51〇連通壓縮機出口 ，冷凝器出口汹連通 第一入D 112。冷凝器50㈣以將由壓縮機·流出的高壓高溫之 就態冷媒凝結為高麼中溫之液態冷媒。 。 本實施例之油分離器_則設置於冷凝器入口 51〇與壓縮機 •出口 420之間’油分離器_並連通冷凝器入口 51〇及麗縮機出 口 420。並且’油分離器6〇〇還連通第二閥入口 162。由於壓縮機 4〇〇内含有潤滑油質以維持壓縮機棚的正常運 通常會伴隨著冷媒一起由壓縮機猶出。故，油分離 ^以將混合著潤滑油質的冷媒進行分離動作’使冷媒繼續往冷凝 器500方向流入’潤滑油質則被過濾分離而流向第二閥入口 。 接下來，將針對冷媒於本實施例之空調系統内循環運作的原 理加以說明。請參照「第3圖」並搭配「第1圖」及「第2圖， 11 201215826 「第3圖」係為根據「第1圖」之冷媒於空調系統中循環之壓力 對焓值得變化示意圖。 「第3圖」中，標號a區域代表冷媒為液態之型態。標號匕 區域代表冷媒為氣態與液態共存之型態，且越靠近標號a區域， 其液態的比例越高。標號c區域則代表冷媒為氣態之型態。 一第一樣態之冷媒901係由冷凝器500流出，並藉由第—入 口 112流入工作流體之過冷度調節裝置1〇’且第一樣態之冷媒9〇1 一般疋局壓液態的冷媒(如「第3圖」所示）。一第二樣態之冷媒 902係由腔室入口 122流入工作流體之過冷度調節裝置1〇，而第 一樣態之冷媒902是液態的冷媒，且其溫度小於第一樣態之冷媒 901(如「第3圖」所示）。一第三樣態之冷媒9〇3係第二入口 132 流入工作流體之過冷度調節裝置10，而第三樣態之冷媒9〇3是低 壓氣態的冷媒(如「第3圖」所示），且其溫度小於第一樣態之冷媒 901。 其中，第一樣態之冷媒902流進工作流體之過冷度調節裝置 10的腔t 12G後’由於流道體積瞬間增加，使得第二樣態之冷媒 902由液態的冷媒膨脹為氣態與液態共存之冷媒，且溫度低於第一 樣態之冷媒901。第一樣態之冷媒9〇1流經第一流管ι1〇，並與被 第一流管110包覆的第二流管13〇 N之第三樣態之冷媒9〇3進行 熱交換。其中，第二流管130 _第三樣態之冷媒9〇3之溫度低 於第-流管110 _第—樣態之冷媒·約攝氏2G度至3〇度， 因此可降低第-流管11〇之第一樣態之冷媒9〇1的溫度。在此同 時，第-流管110 _第-樣態之冷媒9〇1也與充滿腔室12〇内 12 201215826 的第二樣態之冷媒902進行熱交換。因此，第一樣態之冷媒9〇1 流經第一流管110後，其溫度便下降。當第一樣態之冷媒9〇1由 ‘ 第一出口 114流出後，即為一第四樣態之冷媒904。第四樣態之冷 . 媒904與第一樣態之冷媒901同樣為液態冷媒，差別在於第四樣 態之冷媒904係為第一樣態之冷媒9〇1降溫後之形態，因此第四 樣態之冷媒904的溫度較第一樣態之冷媒9讥的溫度低(如「第3 圖」所示）。 接著，第四樣態之冷媒904 —部分流向膨脹閥2〇〇，一部份流 •向第-閥150。為了使空調系統20的過冷度能夠更精準的控制， 本實施例之第一閥150更可具有膨脹閥的功效，並可精確的控制 冷媒流量。因此當第四樣態之冷媒9〇4的一部份流第一閥15〇 後，其便因體積膨漲而使溫度再次下降而成為第二樣態之冷媒 902(如「第3圖」所示）。值得一提的，第四樣態之冷媒9〇4流經 第一閥150的量可由經由調整第一閥15〇之閥口大小來改變，意 即第一閥150可控制第四樣態之冷媒9〇4分別流向膨脹閥2〇〇與 # 第一閥150的比例。舉例而言，當第一閥150的第一閥入口 152 增大，流經第一閥150的第四樣態之冷媒9〇4之流量便增多，相 對也使流向膨脹閥200的第四樣態之冷媒9〇4流量減少。 當第四樣態之冷媒904 —部分流過膨脹閥200後，會受到膨 _ 200 _響而膨脹為-第五樣態之冷媒9〇5。第五聽之冷媒 905為氣體與液體共存的冷媒。接著，第五樣態之冷媒9〇5繼續流 過蒸發器300，並受到蒸發器3〇〇的影響而吸收大量的熱，進而蒸 發為氣態的冷媒。此氣態的冷媒即為第三樣態之冷媒903。 13 201215826 值付一提的疋’當氣體與液體共存的第五樣態之冷媒905，直 液體比例較高時’第五樣態之冷媒905流經蒸發器3〇〇所吸收的 熱量會較大，這也代表空調系統20的效能較好。並且由「第3圖」 所示可知’要獲得較高液態比例之第五樣態之冷媒9〇5(即「第3 圖」之標號905越靠近a區域）’第四樣態之冷媒904的溫度便要 降低。思即’第四樣態之冷媒904溫度越低，第五樣態之冷媒905 的液態比例便越高。第五樣態之冷媒905的液態比例越高，空調 系統20的效能便越好。因此，所謂的空調系統2〇之過冷度便是 才θ流入膨脹閥200的第四樣態之冷媒9〇4之溫度。第四樣態之冷 _ 媒904之溫度越低，空調系統2〇之過冷度便越高。 因此’相較於龍的空調設備’由於並未設置工作流體之過 冷度調節裝置！0’因此第一樣態之冷媒痛即直接流入膨闕 200。故本實施例之空調系統2〇之過冷度會較習用的空調設備之 過冷度來的高，相對系統效益也更好。 此外’腔室120内的氣態之第二樣態之冷媒9〇2及第三樣態 之冷媒903於腔室120 _行熱交換後，便分別由腔室出口 124鲁 及第二出口 134流出。並且，腔室12〇内的液態之第二樣態之冷 媒902以及蒸發過程中未蒸發完全之液態的第三樣態之冷媒 9〇3 ’則氣體無__祖而留在腔室12()底部。此目的 ，確保机入£縮機4G0的冷媒皆為氣態，以避免壓縮機柳的損 ^ ?亡本提案之工作流體之過冷度調節裝置10還具有習用氣 ^離益的功月b且本提案之工作流體之過冷度調節裝置1〇可儲 _凝11 糾之冷媒’因此更可具有麵液筒的功能。 14 201215826 是以這樣的工作流體之過冷度調節裝置10，可替代習用空調設備 的氣液分離器與儲液筒’意即工作流體之過冷度調節裝置1〇將氣 液分離器與儲液筒合而為一。因此，工作流體之過冷度調節裝置 ' 10可使本提案之空調系統20的整體體積縮小。 接著，當第二樣態之冷媒902及第三樣態之冷媒9〇3分別由 腔室出口 124及第二出口 134流出後，便聚集一起而形成一第六 樣態之冷媒906。第六樣態之冷媒906為低壓氣態冷媒，且其溫度 魯較同樣為低壓氣態的第三樣態之冷媒903高（因熱交換而吸收第一 樣態之冷媒901的熱所致)。第六樣態之冷媒906由壓縮機入口 41〇 流入壓縮機400,並受壓縮機4〇〇的影響而壓縮為一第七樣態之冷 媒907，第七樣態之冷媒907為高壓高溫的氣態冷媒。 此外，壓縮機400於運轉時，第七樣態之冷媒9〇7 一般會伴 隨著一些微量的潤滑油質908而由壓縮機出口 42〇流出。當二合 著潤滑油質908的第七樣態之冷媒9〇7流經壓縮機與冷凝器 j〇〇間的油分離器600時，油分離器600會將潤滑油質9⑽分離出 _來’使第七樣態之冷媒9〇7繼續流向冷凝器5〇〇。第七樣態之冷媒 907經由冷凝器入口 510流進冷凝器500後，便受到冷凝器75〇〇 =影響續結為高驗_冷媒。此紐鶴的冷騎為前 提到的第一樣態之冷媒9〇1。 a 一另外，油分離器600所分離出來的潤滑油質9〇8更可經由第 ，閥入〇 162流入第二閥廳，並由第二閥出口 164流出，以流向 第三入口 142。第二閥16〇可調整其第二閥入〇 162的大小二二 制潤滑油質908流進第三流管140的量。潤滑油質9〇8為具高二 15 201215826 氣態，當潤滑油質908流進第三流管140後，可與第一樣態之冷 媒90卜第二樣態之冷媒902及第三樣態之冷媒903進行熱交換。 流進第三流管140的潤滑油質908在進行熱交換後，經由第三出 口 144流出為一潤滑油質909。潤滑油質909的溫度較潤滑油質 908低(因熱交換而使熱量被吸走）。潤滑油質909流出工作流體之 過冷度調節裝置10後，則混入第六樣態之冷媒906而再度流回壓 縮機400内以供循環利用。潤滑油質908用以對第一樣態之冷媒 901、第二樣態之冷媒902及第三樣態之冷媒9〇3進行熱交換。當 第四樣態之冷媒904溫度過低時，潤滑油質908可提升第四樣態 之冷媒904的溫度。此外，潤滑油質908並可用以提高第六樣態 之冷媒906的溫渡，避免第六樣態之冷媒9〇6的溫度過低而使壓 縮機400受損。 请參照「第4圖」’「第4圖」係為根據本提案另一實施例之 空5周系統的結構示意圖。本實施例之空調系統更可包含一控制 态700,控制态700電性連接第一閥15〇與第二閥16〇。控制器 用以控制第一閥150之第一閥入口 152與第二間16〇之第二間入 :162的流量大小。此外’空調系統2〇更可包含一第一溫度感測 710以及第一溫度感測益720。第一溫度感測器彻設置於空 調系統20的蒸發器300處，第一溫度感測器71〇用以測量空調系 職經由蒸妓吸熱所麻㈣冷氣之溫度。第二溫度感測 益72〇。又置於工作流體之過冷度調節裝置1〇與壓縮機彻之間的 流管上，用以偵測第六樣態之冷媒906的溫度。控制器分別 與第-溫度感測器710以及第二溫度感測器72〇電性連接。第一 16 201215826 皿度感勒71G以及第二溫度感測器，可將所測得之溫度訊號 回授給控繼·。控彻可朗訂的溫‘度環魏件，適當 _的控制第—閥15G之第-閥人口⑸與第二閥·之第二閥入口 162的流量大小，以使空調系統2〇簡於最佳工作效益之狀態。 ^舉例來說’當第-溫度感測器71〇測得空調系統2〇所排放冷 氣之/皿度與期望之溫度糾，代表流經蒸發器之冷媒不足。 •此時可控制第—閥15G之Hn 152縮小，使流經第一閥150 的冷媒之"IL畺降低，以增加流經蒸發器之冷媒流量。當第二 •溫度感測器72〇測得第六樣態之冷媒9〇6的溫度過低時，此時壓 縮機40G可能會受到過低賴的影響 控制器期控制第二閥之第二閥入σ162增大，使高: 滑油質908流進工作流體之過冷度調節裝置1〇的量增加。高溫的 潤滑油質_可經熱錢而提料六聽之冷媒9()6的溫度，進 而達到保護壓縮機彻之效果。因此，本實施例之空調系統2〇係 利用第-溫度感測器710及第二溫度感測器72〇來監測系統溫 •度，以將溫度資料回授控制器。控制器7〇〇接收溫度資料而調 整第-閥150與第二閥160的流量，使空調系統2〇能夠克服各種 狀態下的溫度變化而保持穩定的系統效益。 根據上述本實施例所揭露之空調系統，係將由冷凝器流至膨 脹閥的第一樣態之冷媒流經過冷度調節裝置。因此使第一樣態之 冷媒與過冷度調祕置_第三樣態及第三娜之冷媒進行熱交 換，以降低第一樣態之冷媒之溫度。由於第一樣態之冷媒之溫度 下降，因此也使得空調系統的過冷度獲得提升。是以這樣的過冷 17 201215826 度调郎裝置可提升空3周糸統的系統效益。 此外，本實施例之細流體之過冷度㈣裝置可 液分離器與習雜液器的功能。是以這樣的讀流體 = 節裝置’可替代習用空調設備的氣液分離器與儲液器，^= 對使本實施例之空調系統的整體體積縮小。 目 並且，由於本實施例之控制ϋ可控制第—閥與第二_間口 ^、’藉以控制流經第-閥之冷媒與流經第二閥之潤滑油質的流 ΐ。因此於溫度感測器的設置下，控制器可視系統溫 當的控制第—嶋二閥的閥口大小，以使靖蝴 的工作效益之狀態。 …雖然本提案以前述之難實施例揭露如上，然其並非用以限 疋本提案，任何熟習相像技藝者，在不脫離本提案之精神和範圍 内二當可作些許之更動與_ ’因此本提案之專娜護範圍須視 本說明書騎之巾請專舰騎界定者為準。 【圖式簡單說明】 第1圖係為根據本提案-實施例之空調系統的結構示意圖。 第2圖係為根據第！圖之工作流體之過冷度調節裝置的放大示 意圖。 第3圖係為根據第1圖之冷媒於空調系統中循環之樣態變化示 意圖。 第圖係為根據本提案另-實施例之空調系統的結構示意圖。 【主要元件符號說明】 工作流體之過冷度調節裝置 10 201215826 20 空調系統 100 機體 110 第一流管 112 第一入口 114 第一出口 120 腔室 122 腔室入口 124 腔室出口 # 130 第二流管 132 第二入口 134 第二出口 140 第三流管 142 第三入口 144 第三出口 150 第一閥 φ 152 第一閥入口 154 第一閥出口 160 第二閥 162 第二閥入口 164 第二閥出口 200 膨脹閥 210 膨脹閥入口 220 膨脹閥出口 19 201215826 300 蒸發器 310 蒸發器入口 320 蒸發器出口 400 壓縮機 410 壓縮機入口 420 壓縮機出口 500 冷凝器 510 冷凝器入口 520 冷凝器出口 600 油分離器 700 控制器 710 第一溫度感測器 720 第二溫度感測器 901 第一樣態之冷媒 902 第二樣態之冷媒 903 第三樣態之冷媒 904 第四樣態之冷媒 905 第五樣態之冷媒 906 第六樣態之冷媒 907 第七樣態之冷媒 908 潤滑油質 909 潤滑油質201215826 VI. Description of the Invention: [Technical Field of the Invention] This proposal relates to an air conditioning system, and more particularly to an air conditioning system having a subcooling degree for lifting a working fluid and a subcooling degree adjusting device thereof. [Prior Art] Since the metropolitan area is narrow and dense, and the buildings are adjacent to each other, it is easy to collect and scatter the heat. However, the modern people's material level is improved, and the requirements for the comfort of the living environment are relatively increased. Therefore, most of the buildings in the metropolitan area will be equipped with an air conditioning system. The air-conditioning system controls the temperature, humidity, pressure, wind speed and cleanness in the building within a specified range, so that people in the building can live comfortably. In the general air conditioning system, the refrigerant is sewed into a high temperature and high pressure refrigerant by a pressure surface, and then sent to the condensing n. Then, the chilled water tower is coupled with the pump to send the cold water into the condenser, and the cooling water and the high temperature and high temperature are used for hot money. The high temperature and the cold county of the county became a high-pressure cold hull, and then swelled into a __ expansion to form a low-pressure cold body. Then, the cold-working body is re-entered into the evaporator, so that the low-pressure cold can hide the external environment for heat exchange and absorb a large amount of heat. Next, a cold air that is absorbed by the refrigerant is blown by a fan system to generate a cold room effect as an indoor air conditioner. Finally, a strong refrigerant gas is formed by the heat absorption and then enters the compressor by the low pressure officer to be compressed again into a high temperature and high pressure refrigerant gas. Through the circulation operation of the above air conditioning system, the indoor space can be obtained as a cold room. However, today's air-conditioning products on the market, the temperature after the cold condensing entanglement is close to about 40~42 C. According to the conditions of the ambient temperature for the pit, if the temperature of the refrigerant in the condenser of 201215826 is lowered by 5~rc, the economic benefit of the air conditioning system can be improved by about 1G~15%. At present, the air conditioning system on the market improves the efficiency of the method, the scale _ increases the condensing enthalpy, and the method of increasing the cold (four) wind 4 riding the collateral condenser - the circuit changes. However, all of these methods are used to update the air (10) and the overall system. Therefore, it will inevitably lead to an increase in the cost of maintenance. For older air-conditioning systems, if it is necessary to increase the degree of cooling to improve system efficiency, it will be a considerable expense. SUMMARY OF THE INVENTION In order to solve the above problems, the present invention proposes to provide a subcooling device for an air conditioning system and its working fluid, and the problem of higher cost is required for the system efficiency of the prior art domain to improve the air conditioning system. The subcooling degree adjusting device of the working fluid disclosed in the present proposal is for adjusting one of the refrigerants in a cycle state. The refrigerant changes between a first state, a second state, and a second state. Wherein, the refrigerant in the first state is in a liquid state, the refrigerant in the second state is in a liquid state, and the pressure and temperature are lower than the refrigerant in the first state, and the refrigerant in the third state is in a gaseous state and the pressure and temperature are lower than the temperature. The same state of refrigerant. The working fluid passes through • The cold regulating device comprises a body, a first flow tube and a second flow tube. The body has a chamber having a chamber inlet and a chamber outlet. The first flow tube is disposed in the chamber. The first flow tube has a first inlet and a first outlet outside the body. The second flow tube is disposed in the chamber, and the second flow tube has a first inlet and a second outlet outside the machine body. Wherein, the refrigerant of the second state, the refrigerant of the second state and the refrigerant of the third state enter the chamber through the first inlet, the second inlet and the inlet of the chamber, respectively, and after heat exchange in the chamber, respectively The chamber exits the first outlet, the first outlet, and the chamber outlet. 201215826 The media disclosed in this proposal is looped within it. Air conditioning systems include - work, m cooling regulators, - inflation, - evaporators, - compressors and - condensers. The subcooling device of the Weigong fluid comprises a machine, a - flow tube, a second flow tube and u. The body has a chamber, from chamber to chamber to population and chamber outlet. The first flow tube is disposed in the chamber, and the first flow tube has a first population located outside the body and a second flow tube disposed in the chamber. The first flow member has a second inlet and a body outside the machine body. Second exit. The first valve is disposed outside the machine body, and the first valve communicates with the chamber inlet. In addition, the expansion chamber has a valve inlet and an expansion port, and the expansion port is connected to the first and the outlet, respectively. Luofa has an evaporator inlet and an evaporator outlet, and the evaporator has two lion's exits evaporating ϋώπ connected to the second person. The compressor has a £1/s machine inlet and an ι compressor outlet, and the compressor population is connected to the second outlet and the chamber outlet, respectively. The condenser has a condenser inlet and a condenser outlet, the condenser inlet is connected to the machine outlet, and the condenser outlet is connected to the first person σ. Wherein, the refrigerant entering the chamber from the first inlet to the refrigerant, the refrigerant entering the chamber from the second inlet, and the refrigerant entering the chamber from the inlet of the chamber exchange heat in the chamber. According to the above-described air conditioning system, the refrigerant flow from the cold to the expansion state is passed through the coldness adjusting device. Therefore, the refrigerant of the first state is exchanged with the refrigerant of the second state and the third state in the supercooling degree adjustment device to lower the temperature of the first refrigerant. Since the temperature of the refrigerant in the first state is lowered, the degree of subcooling of the air conditioner is also improved. With such a subcooling regulator, the system benefits of the air conditioning system can be improved. For the characteristics, implementation and efficacy of this proposal, the best example is to match the drawing 201215826. [Embodiment] 'Please refer to "1st picture" and "2nd picture", and "1st picture" is a schematic diagram of the structure of an empty 5-week system based on this proposal - "1" It is an enlarged schematic view of the supercooling degree adjusting device of the working fluid according to "Fig. 1". The air conditioning system 20 of the embodiment of the present invention causes a refrigerant to undergo a phase change and a cycle therein to lower the temperature of a region. . The air conditioning system 20 includes a working fluid passing through the A degree adjusting device 10, an expansion valve 2, an evaporator 3, a compressor 4, and a condenser 500. Moreover, the air conditioning system 2 can further include an oil separator _. The supercooling degree adjusting device 10 of the working fluid comprises a body, a first flow tube 110 and a second flow tube 130. Moreover, the supercooling degree adjusting device 10 of the working fluid may further include a third flow tube 140, a first valve 150 and a second valve 160. The body 1 has a chamber 12, and the chamber 12 has a chamber inlet and a chamber outlet 124. In addition, the first flow tube 110 is disposed in the chamber 120, and the first flow tube U0 has a first inlet 112 and a first outlet 114. The first inlet 112 and the second outlet 115 are respectively disposed outside the body 100, and the first flow tube 110 is not directly connected to the cavity 120. That is, although the first flow tube 11 is disposed in the chamber 12, there is no through hole communicating with the chamber 120 on the first flow cell 110, as shown in "Fig. 2". • The second flow tube 13 is disposed in the chamber 120, and the second flow tube 130 has a second inlet 132 and a second outlet 134. The second inlet 132 and the second outlet 134 are respectively disposed outside the body 100 and the second flow tube 130 is not directly in communication with the chamber 120. Moreover, the second flow tube 130 can be covered by the first flow tube 110, and the first flow tube 110 and the first machine S 130 can be connected to a concentric tube. The second flow tube 130 is not directly in communication with the 201215826 first-flow officer 11G. That is, the second flow pipe 13G is disposed in the first flow pipe ιι〇, but the second flow pipe 130 does not have any through holes communicating with the first flow pipe ιι, as shown in "Fig. 2". In addition, the third flow tube 140 is disposed in the chamber 12, and the third flow tube 14 has a second inlet 142 and a third outlet 144. The third inlet 142 and the third outlet 144 are respectively disposed outside the body 100, and the third flow tube 140 is not directly connected to the chamber 12A. Moreover, the third flow tube 140 can surround the first flow tube 110 and the second flow tube 130 covered by the first flow tube 110 in a spiral manner, as shown in FIG. 2, the first flow tube 110 The coating of the second flow tube 130 can also adopt the design of the tube in the tube. Among them, the first flow tube 110, the second flow tube 130, and the third flow tube ho are made of a material having a high conductivity, and for example, a material such as copper (model C1220T-H) is used. In other words, the path from the chamber inlet 122 to the chamber outlet 124, from the first inlet 112 to the first outlet 114, from the second inlet 132 to the second outlet 134, and from the third inlet 142 to the third outlet 144, It is divided into four separate independent channels. In addition, the first valve 150 is disposed outside the body 100 and has a first valve inlet 152 and a first valve outlet 154. The first valve outlet 154 communicates with the chamber inlet 122, and the first valve 150 regulates the flow of refrigerant from the chamber inlet 122 into the chamber 120. The second valve 160 is disposed outside the body 1 and has a second valve inlet 162 and a second valve outlet 164. The second valve outlet 164 communicates with the third inlet M2'. The second valve 160 regulates the flow of a refrigerant from the third inlet 142 into the chamber 120. The expansion valve 200 of the present embodiment has an expansion valve inlet 210 and an expansion valve outlet 220. The expansion valve inlet 210 communicates with the first valve inlet 152 and the first outlet 114, respectively. The expansion valve 200 is used to expand the high-pressure high-temperature liquid refrigerant into a low-pressure low-temperature two-phase 10 201215826 refrigerant, and more recently, a gas-liquid coexisting refrigerant. The evaporator 300 has an evaporator inlet and an evaporator outlet 32, the plug inlet is connected to the expansion outlet 220, and the evaporator outlet 32 is connected to the second inlet; The evaporator is used to evaporate the low-temperature two-phase refrigerant flowing out of the expansion valve outlet 220 into a low-pressure low-temperature gaseous refrigerant, which absorbs a large amount of heat energy to lower the indoor air temperature. The machine of this embodiment has a compressor inlet and a gas compressor outlet. The compressor inlet communicates with the second outlet 134, the chamber outlet 124, and the third outlet 144, respectively. _ machine 4 〇〇 is used to flow out the low temperature gaseous refrigerant from the supercooling damper device 10 of the working fluid, and the surface is a high temperature temperature gaseous refrigerant: In addition, the condenser 500 has a condenser inlet and a condenser outlet. do not. The condenser inlet 51 is connected to the compressor outlet, and the condenser outlet is connected to the first inlet D 112. The condenser 50 (4) is a liquid refrigerant that condenses the high-pressure high-temperature refrigerant flowing out of the compressor to a high medium temperature. . The oil separator _ of the present embodiment is disposed between the condenser inlet 51 and the compressor/outlet 420 'oil separator _ and communicates with the condenser inlet 51 and the condensing machine outlet 420. And the 'oil separator 6' also communicates with the second valve inlet 162. Since the compressor 4 contains lubricating oil to maintain the normal operation of the compressor shed, it is usually accompanied by the refrigerant. Therefore, the oil separation is performed by separating the refrigerant mixed with the lubricating oil, and the refrigerant continues to flow in the direction of the condenser 500. The lubricating oil is separated by filtration and flows to the second valve inlet. Next, the principle of circulating the refrigerant in the air conditioning system of the present embodiment will be explained. Please refer to "3" and "1" and "2", 11 201215826 "3" is a schematic diagram of the pressure change of the refrigerant circulating in the air-conditioning system according to "1". In "Fig. 3", the area marked with a indicates that the refrigerant is in a liquid state. The label 匕 area represents the type in which the refrigerant coexists in a gaseous state and a liquid state, and the closer to the label a region, the higher the liquid proportion. The area labeled c indicates that the refrigerant is in a gaseous state. The refrigerant 901 of the first state flows out of the condenser 500, and flows into the supercooling degree adjusting device 1' of the working fluid through the first inlet 112, and the refrigerant 9〇1 in the first state is generally in a liquid state. Refrigerant (as shown in Figure 3). A refrigerant 902 of a second state flows into the supercooling degree adjusting device 1 of the working fluid from the chamber inlet 122, and the refrigerant 902 in the first state is a liquid refrigerant, and the refrigerant 901 having a temperature lower than the first state. (as shown in Figure 3). A third type of refrigerant 9〇3 is connected to the subcooling degree adjusting device 10 of the working fluid, and the third type of refrigerant 9〇3 is a low pressure gaseous refrigerant (as shown in FIG. 3). And the refrigerant 901 whose temperature is lower than the first state. Wherein, the refrigerant 902 of the first state flows into the cavity t 12G of the supercooling degree adjusting device 10 of the working fluid. 'Since the volume of the flow channel is instantaneously increased, the refrigerant 902 of the second state is expanded from the liquid refrigerant into a gaseous state and a liquid state. The coexisting refrigerant and the refrigerant 901 having a lower temperature than the first state. In the first state, the refrigerant 9〇1 flows through the first flow tube ι1〇, and exchanges heat with the refrigerant 9〇3 of the third state of the second flow tube 13〇N covered by the first flow tube 110. Wherein, the temperature of the second flow tube 130_the third state of the refrigerant 9〇3 is lower than the temperature of the first flow tube 110_the first state, about 2G to 3 degrees Celsius, so the first flow tube can be lowered. The temperature of the refrigerant of the first state of 11〇 is 9〇1. At the same time, the refrigerant 9 第 of the first-flow tube 110_th-state is also in heat exchange with the refrigerant 902 of the second state filled in the chamber 12 12 12 201215826. Therefore, when the refrigerant 9'1 in the first state flows through the first flow tube 110, its temperature drops. When the refrigerant 9'1 of the first state flows out of the first outlet 114, it is a refrigerant 904 of a fourth state. The coldness of the fourth state. The medium 904 is the same as the refrigerant 901 of the first state, and the difference is that the refrigerant 904 of the fourth state is in the form of the refrigerant of the first state, 9〇1, and thus the fourth state. The temperature of the refrigerant 904 is lower than the temperature of the refrigerant 9 of the first state (as shown in "Fig. 3"). Next, the refrigerant 904 of the fourth state flows partially to the expansion valve 2, and a portion flows to the first valve 150. In order to enable the supercooling degree of the air conditioning system 20 to be more accurately controlled, the first valve 150 of the present embodiment can further have the function of an expansion valve and can accurately control the flow rate of the refrigerant. Therefore, when a portion of the refrigerant 9 〇 4 of the fourth state flows through the first valve 15 , the temperature is again decreased due to the volume expansion, and the refrigerant 902 becomes the second state (for example, "Fig. 3" Shown). It is worth mentioning that the amount of the refrigerant 9 〇 4 flowing through the first valve 150 can be changed by adjusting the size of the valve port of the first valve 15 , that is, the first valve 150 can control the fourth state. The refrigerant 9〇4 flows to the ratio of the expansion valve 2〇〇 and the #first valve 150, respectively. For example, when the first valve inlet 152 of the first valve 150 is increased, the flow rate of the refrigerant 9〇4 flowing through the fourth state of the first valve 150 is increased, and the fourth flow to the expansion valve 200 is relatively increased. The state of the refrigerant 9〇4 flow is reduced. When the refrigerant 904 of the fourth state partially flows through the expansion valve 200, it is expanded by the expansion of the refrigerant _200 to the fifth state of the refrigerant 9〇5. The fifth refrigerant is 905, which is a refrigerant in which gas and liquid coexist. Then, the fifth refrigerant 9〇5 continues to flow through the evaporator 300, and is absorbed by the evaporator 3〇〇 to absorb a large amount of heat, thereby evaporating into a gaseous refrigerant. This gaseous refrigerant is the third refrigerant 903. 13 201215826 The value of 冷 'When the gas and the liquid coexist in the fifth state of the refrigerant 905, when the ratio of the straight liquid is high, the heat of the fifth state of the refrigerant 905 flowing through the evaporator 3 会 will be higher. Large, this also represents the better performance of the air conditioning system 20. Further, as shown in "Fig. 3", it is known that the refrigerant of the fifth state of the higher liquid ratio is 9〇5 (i.e., the label 905 of "Fig. 3" is closer to the a region). The temperature is reduced. The lower the temperature of the refrigerant 904 in the fourth state, the higher the liquid proportion of the fifth refrigerant 905. The higher the liquid proportion of the fifth refrigerant 905, the better the performance of the air conditioning system 20. Therefore, the subcooling degree of the so-called air conditioning system 2 is the temperature of the refrigerant 9〇4 which flows into the fourth state of the expansion valve 200. The fourth state of cold _ The lower the temperature of the medium 904, the higher the degree of subcooling of the air conditioning system. Therefore, the air conditioner of the dragon is not equipped with the supercooling regulator for the working fluid! 0' Therefore, the same type of refrigerant pain directly flows into the expansion 200. Therefore, the degree of subcooling of the air conditioning system 2 of the present embodiment is higher than that of the conventional air conditioning equipment, and the system efficiency is also better. In addition, the refrigerant 9 〇 2 in the second state in the chamber 120 and the refrigerant 903 in the third state are heat exchanged in the chamber 120 _, and then flow out from the chamber outlet 124 and the second outlet 134, respectively. . Moreover, the second state of the refrigerant 902 in the chamber 12 以及 and the third state of the refrigerant 9 〇 3 ′ which does not evaporate in the liquid state during the evaporation process remain in the chamber 12 without the ancestors. )bottom. For this purpose, it is ensured that the refrigerant of the machine 4G0 is in a gaseous state to avoid the damage of the compressor willow. The working fluid supercooling adjusting device 10 of the present proposal also has the function of the conventional gas and the benefit of the benefit. The subcooling degree adjusting device 1 of the working fluid of the present invention can store the condensed refrigerant and thus has the function of a liquid cartridge. 14 201215826 is a supercooling degree adjusting device 10 of such a working fluid, which can replace the gas-liquid separator and the liquid storage tank of the conventional air-conditioning device, that is, the supercooling degree adjusting device of the working fluid, and the gas-liquid separator and the storage The liquid cylinders are combined into one. Therefore, the supercooling degree adjusting device '10 of the working fluid can reduce the overall volume of the air conditioning system 20 of the present proposal. Next, when the refrigerant 902 of the second state and the refrigerant 9〇3 of the third state flow out from the chamber outlet 124 and the second outlet 134, respectively, they are gathered together to form a sixth state refrigerant 906. The refrigerant 906 of the sixth state is a low-pressure gaseous refrigerant, and its temperature is higher than that of the refrigerant 903 which is also the third state of the low-pressure gas state (caused by the heat of the refrigerant 901 of the first state due to heat exchange). The refrigerant 906 of the sixth state flows into the compressor 400 from the compressor inlet 41, and is compressed into a seventh state of refrigerant 907 by the influence of the compressor 4, and the refrigerant 907 of the seventh state is high-pressure and high-temperature. Gaseous refrigerant. Further, when the compressor 400 is in operation, the refrigerant 9 〇 7 of the seventh state is generally discharged from the compressor outlet 42 by a small amount of lubricating oil 908. When the refrigerant 9 〇 7 of the seventh state of the lubricating oil 908 is passed through the oil separator 600 between the compressor and the condenser j, the oil separator 600 separates the lubricating oil 9 (10). 'The seventh state of the refrigerant 9〇7 continues to flow to the condenser 5〇〇. The refrigerant of the seventh state, 907, flows into the condenser 500 via the condenser inlet 510, and is subjected to the condenser 75 〇〇 = effect and continues to be a high test _ refrigerant. This New Crane's cold ride is the first refrigerant of the first mentioned 9〇1. In addition, the lubricating oil 9〇8 separated by the oil separator 600 can flow into the second valve chamber via the first valve inlet 162 and out of the second valve outlet 164 to flow to the third inlet 142. The second valve 16A can adjust the amount of the second valve inlet 162 to the amount of the lubricating oil 908 flowing into the third flow tube 140. Lubricating oil quality 9〇8 is a high two 15 201215826 gas state, when the lubricating oil 908 flows into the third flow tube 140, it can be in the same state as the refrigerant 90, the second state of the refrigerant 902 and the third state The refrigerant 903 performs heat exchange. The lubricating oil 908 flowing into the third flow tube 140 flows out through the third outlet 144 into a lubricating oil 909 after heat exchange. The temperature of the lubricating oil 909 is lower than that of the lubricating oil 908 (the heat is absorbed by the heat exchange). After the lubricating oil 909 flows out of the supercooling degree adjusting device 10 of the working fluid, the refrigerant 906 of the sixth state is mixed and returned to the compressor 400 for recycling. The lubricating oil quality 908 is used to exchange heat between the refrigerant 901 of the first state, the refrigerant 902 of the second state, and the refrigerant 9〇3 of the third state. When the temperature of the refrigerant 904 of the fourth state is too low, the lubricating oil 908 can raise the temperature of the refrigerant 904 of the fourth state. In addition, the lubricating oil 908 can be used to increase the temperature of the refrigerant 906 of the sixth state, and the temperature of the refrigerant 9 〇 6 of the sixth state is too low to damage the compressor 400. Please refer to "Fig. 4" and "Fig. 4" for a schematic diagram of the structure of an empty 5-week system according to another embodiment of the present proposal. The air conditioning system of this embodiment may further include a control state 700 electrically connected to the first valve 15A and the second valve 16A. The controller is configured to control the flow rate of the first valve inlet 152 of the first valve 150 and the second interval of the second chamber 16: 162. In addition, the air conditioning system 2 can further include a first temperature sensing 710 and a first temperature sensing benefit 720. The first temperature sensor is disposed at the evaporator 300 of the air conditioning system 20, and the first temperature sensor 71 is used to measure the temperature of the air conditioning system through the steam absorbing heat (4). The second temperature sense is 72 〇. It is also placed on the flow tube between the supercooling degree adjusting device 1〇 of the working fluid and the compressor to detect the temperature of the refrigerant 906 of the sixth state. The controller is electrically connected to the first temperature sensor 710 and the second temperature sensor 72, respectively. The first 16 201215826, the sensory sensor 71G and the second temperature sensor, can feedback the measured temperature signal to the control unit. The temperature of the temperature-degree ring is controlled by the control, and the flow rate of the first valve population (5) of the first valve 15G and the second valve inlet 162 of the second valve is appropriately controlled so that the air conditioning system 2 is simplified. The state of the best work efficiency. For example, when the first temperature sensor 71 measures the temperature of the air discharged from the air conditioning system 2 and the desired temperature, it indicates that the refrigerant flowing through the evaporator is insufficient. • At this time, the Hn 152 of the first valve 15G can be controlled to be reduced, and the "IL畺 of the refrigerant flowing through the first valve 150 is lowered to increase the flow rate of the refrigerant flowing through the evaporator. When the second temperature sensor 72 detects that the temperature of the sixth state of the refrigerant 9〇6 is too low, at this time, the compressor 40G may be affected by the low voltage, and the second period of the second valve is controlled by the controller. The valve inlet σ162 is increased to increase the amount of the subcooling regulator 1〇 into which the lubricating oil 908 flows into the working fluid. The high-temperature lubricating oil _ can be used to raise the temperature of the refrigerant 9 () 6 by the hot money, thereby achieving the effect of protecting the compressor. Therefore, the air conditioning system 2 of the present embodiment uses the first temperature sensor 710 and the second temperature sensor 72A to monitor the system temperature to return the temperature data to the controller. The controller 7 receives the temperature data and adjusts the flow rates of the first valve 150 and the second valve 160 so that the air conditioning system 2 can maintain stable system benefits by overcoming temperature changes in various states. According to the air conditioning system disclosed in the above embodiment, the refrigerant flow in the first state from the condenser to the expansion valve passes through the coldness adjusting device. Therefore, the refrigerant of the first state is thermally exchanged with the subcooling and the third refrigerant and the third refrigerant to reduce the temperature of the refrigerant in the first state. As the temperature of the refrigerant in the first state decreases, the degree of subcooling of the air conditioning system is also improved. With such a cold, 17 201215826 degree adjustment device can improve the system efficiency of the empty 3 weeks. Further, the subcooling degree (4) of the fine fluid of the present embodiment functions as a liquid separator and a liquid trap. It is possible to replace the gas-liquid separator and the accumulator of the conventional air-conditioning apparatus with such a reading fluid = knot device, and to reduce the overall volume of the air-conditioning system of the present embodiment. Further, since the control unit of the present embodiment can control the first valve and the second port ^, ', the flow of the refrigerant flowing through the first valve and the lubricating oil flowing through the second valve can be controlled. Therefore, under the setting of the temperature sensor, the controller can control the size of the valve port of the second valve to visually control the state of the working efficiency of Jinghua. ... although this proposal is disclosed above in the above-mentioned difficult examples, it is not intended to limit this proposal. Anyone who is familiar with the similar skills can make some changes and _ 'without the spirit and scope of this proposal. The scope of the special protection of this proposal shall be subject to the definition of the riding towel of this manual. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic structural view of an air conditioning system according to the present proposal-embodiment. Figure 2 is based on the first! An enlarged schematic view of the subcooling degree adjusting device of the working fluid of the drawing. Fig. 3 is a schematic diagram showing the state of the circulation of the refrigerant according to Fig. 1 in the air conditioning system. The figure is a schematic structural view of an air conditioning system according to another embodiment of the present proposal. [Main component symbol description] Working fluid subcooling adjusting device 10 201215826 20 Air conditioning system 100 Body 110 First flow pipe 112 First inlet 114 First outlet 120 Chamber 122 Chamber inlet 124 Chamber outlet # 130 Second flow tube 132 second inlet 134 second outlet 140 third flow tube 142 third inlet 144 third outlet 150 first valve φ 152 first valve inlet 154 first valve outlet 160 second valve 162 second valve inlet 164 second valve outlet 200 expansion valve 210 expansion valve inlet 220 expansion valve outlet 19 201215826 300 evaporator 310 evaporator inlet 320 evaporator outlet 400 compressor 410 compressor inlet 420 compressor outlet 500 condenser 510 condenser inlet 520 condenser outlet 600 oil separator 700 controller 710 first temperature sensor 720 second temperature sensor 901 refrigerant in the same state 902 refrigerant in the second state 903 refrigerant in the third state 904 refrigerant in the fourth state 905 fifth state The refrigerant 906 The sixth state of the refrigerant 907 The seventh state of the refrigerant 908 Lubricating oil 909 Lubricating oil
2020