200523515 玖、發明說明： 【發明所屬之技術領域】 本發明-般係關於乾燥系統。更明確而言，本發明係 有關-種具有蓄熱介質相變化材料之冷藏型空氣乾燥器。 【先前技術】 〃空氣乾燥器通常用於除去壓縮空氣或氣體内的水蒸 氣。當應用冷藏型空氣乾燥器時，利用冷媒系統將空氣或 氣體溫度降低至或低於其水的冷凝溫度。纟此溫度下，潮 濕空氣内的水蒸氣將冷凝於冷凝器的内表面而被收集和排 出系統。 為有㈣低潮濕空氣或氣體的溫度，冑乡》媒系統具 有熱交換器而使空氣或氣體在冷媒乾燥過程中釋出熱能。 —般而言，潮濕、s氣釋出的熱能和蒸發器内蒸發之低溫冷 媒相結合。此_ ’當液態冷媒被蒸發時可從潮濃空氣或氣 體釋出熱能而冷卻該空氣。t空氣或氣體到達或低於其水 的冷凝溫度時，空氣或氣體内的水蒸氣開始冷凝（或分離） 而被收集於冷凝器或分離器内。 為了使系統内的冷媒能夠再循環，通常裝設一壓縮機 和一冷水機組一壓縮機使蒸發的冷媒再液化，而冷水機組 則可冷卻壓縮過程中變熱的液態冷媒。此時冷媒可再進行 另一次的蒸發循環。 例如，當極少或無 冷藏型乾燥器通常的困難是在無負載或低負載情況下 決定如何中止冷卻（即，系統，，釋放，，）^ 3 200523515 空氣流經冷藏乾燥器而使冷藏需求量極低或無時，或當進 入的空氣已冷卻時。一般而言，在此期間需減少或中止冷 卻以避免冷媒系統結冰而影響冷藏空氣乾燥器的操作。結 冰會阻塞系統而無法繼續乾燥空氣’或其將阻塞空氣通道 而停止壓縮空氣的流動° 一種避免過度冷卻所導致的問題為利用循環型冷藏乾 燥器。在循環冷藏型乾燥系統内’當潮濕空氣已被冷卻至 一預設溫度時恒溫裝置可釋放冷媒麼縮機。當蒸發器内的 溫度上昇至一預設溫度時該裝置亦可重新啟動壓縮機，此 表示需要進一步冷卻以除去流入空氣的濕氣。因此，在適 當負載和低負載之間，冷卻壓縮機每小時可進行約3 0至 4〇次的開關循環。 由於高循環頻率將增加成本及壓縮機、控制系統和閥 門的耗損，故每小時的循環數極為重要。所以，大為縮短 冷媒系統的壽命。因此，亟需提供一種冷媒空氣乾燥系統 以及可延長其冷媒系統之壽命的方法。 此外，冷媒系統的循環頻率越高其耗電量越大。低耗 電篁可兼具降低成本及保護環境的優點。因此亦亟需提供 一種冷藏乾燥系統以及降低其耗電量的方法。 【發明内容】 本發明在某種程度上符合上述的需求，其中在一實施 例中提供一種空氣乾燥設備其具有進一步含相變化材料的 冷媒系統和熱交換器，其中該冷媒系統可冷卻熱交換器。 4 200523515 空氣乾燥器可乾燥空氣或氣體 氣體。在茸处威 /、視為要可為壓縮空氣或 、 某二實施例中，本發明处齑払π . 離器，其較佳 二、器包括一冷凝分 液相之門/ “有一絲網。相變化材料可變化於固相和 液相在某些實施例中該相變化材料為一種有機石壤。 /、他實施例中，提供一種乾 报一接、人W 死辟空乳的方法其包括提 y、 令媒系統及一種含相變化材粗沾為 > 該冷媒系統冷卻敎…=4的熱交換器，並利用 視1 A 方法乾燥空氣或氣體， =要可為壓縮空氣或氣體。“些實施例中 …氣的方法包括一冷凝分離器，其較佳二 網。相變化材料可變化 ^ 絲 中該相變化材料為 相之間。在某些實施例 τ祁雯化材枓為一種有機石蠟。 又在其他實施例中，担处 ^ ^ 列甲乂供一種乾燥空氣的裝置， 括-種冷藏裝置及一種含相變化材料的熱交換 复包 該冷藏裝置可冷卻熱交換裝置。，氣乾燥裝：中 或氣體，其視需要可為 死你空氣 為壓鈿工軋或氣體。在某些f 本發明空氣乾燥裝罟4 t 例中， 裒置包括一冷凝分離裝置，其較 -絲網。㈣化材料可變化於固相和液相之間。在：具有 施例中該相變化材料為-種有機石蠛。 些實 僅概略而非廣g >、+、1 4 户块泛描返本發明較重要的特性以 詳細說明有更佳的暗由 f下述 的瞭解’並且對本發明的貢獻有更主 認識。本發明當然仍具有其他的優點，其將於下述 楚的 並且為構成附件申請專利範圍的主題。 *說明 本發明在至少以一種實施例詳細說明之前，應 發月之應用並非僅揭限於下述說明或圖例内的構造及解本 5 200523515 的配置。本發明可應用於其他實施例中，並且可有各種不 同的作業和操作方法。肖時’應瞭解本發明的範圍非侷限 於此處使用之措辭和術語以及摘要内，而僅做為說明的用 途。 依此’熟習本技藝之人仕應瞭解可利用本發明所揭示 的概念做為基礎輕易設計出其他的構造、方法和系統以執 行本發明的數種目％。因此，申請專利範圍應視為包括此 類相同構造而未偏離本發明的精神和範圍。 【實施方式】 本發明將參考圖解圖表進行說明，其相同的元件符號 代表全部相同的零件。本發明根據實施例提供一種連結熱 交換器20進行操作的冷媒系統10以冷卻潮濕壓縮空氣至 可充分藉由冷凝而分離和除去其所含之水份的溫度。熱交 換蒸20可具有多種的實施例，其某些將說明如下。在第1 圖的略圖中顯示熱交換器20包含一空氣對空氣（“空氣/空 乳）父換器30以及一空氣對冷媒（‘‘空氣/冷媒，，）交換器 4〇。交換器 ^ 為40進一步包括一熱套筒50，其在實施例中顯 示可直接被冷媒系站 7又卞乐統1 〇所冷卻。 考既 而 、 a ’包括壓縮空氣和氣體之空氣、氣體或通常 為任何需教极 ’、的蒸軋經由入口 60被注入熱交換器20。此 處”空氣’，一兮司勺k 、 。匕括全部上述的液體，並且不應被推斷或限 制 ^壬", 、 夏施例中之液體。空氣然後通過交換器3 0 而至交換^ ^ " 。二軋較佳為流經通過交換器3 〇的徑路6 1， 6 200523515 其可使從入口 6〇進入之較熱潮濕空氣的熱能轉移至從出 口 70流出之較冷的乾燥空氣。舉例來說，從入口 60進入 之空氣的溫度可能高於從出口 70排出之空氣的40至70 度華氏。此溫度上的差異使其在不需機械方法介入之下即 可進行熱轉移。 空氣在流經交換器3 0之後即進入交換器4 〇。交換器 40可將流入空氣之熱能轉移至供應自冷媒系統i 〇的冷媒 11。此實施例中顯示冷媒11可冷卻熱套筒5 〇。熱套筒的 材料可包括目刖技藝中已知可被冷卻至或低於冷凝蒸氣 (即，水）之露點（dew point)的任何材料。適合的材料包括 但不侷限於乙二醇和其混合物。 在某些實施例中，熱套筒5〇含有相 相變化材料（PCM)為藉由固相至液相之雙向變化而可吸 或擴散熱的蓄熱介t。例如在本實施例巾，當相變化材 從潮濕空氣吸收熱能之後開始從固相轉變成液相。然而 由於P C Μ技術的恒溫性質而使其不受限於科學理論，因 熱套筒50在熱轉移時可維姓 々 了」維持在恒溫。此過程視PCM、 氣的$衣境溫度及負荷量雲私八 7置萬數分鐘至數小時的時間。 在某些實施例中，齡# + 季又佳之PCM為可在最小溫度範圍 吸收最大量的熱能。換今之 °之 PCM在一已知所需量的熱 下能維持較長的固相時間。 在科學上，當固相轉變成液 寻可明顯增加液體的熱導性。 导生例如，水在32卞時的熱導 馬0.326 BTU/小時-吸々，鬥〇士」 门寺冰在相同溫度下的敎導 馬1.18 BTUH、時-吸-卞。Λ 士人 …、 由於PCM在固態（高熱導性） 200523515 液態（較低熱導性）均可吸收熱能故比不進行相變化的材料 更能迅速而有效地吸收冷凝的熱能。因此，利用冷缘的潛 熱（固體—液體）可比藉由溫度的改變將更多熱能儲藏於較 小體積的介質内，故可設計出更小體積的熱交換||。 在本發明實施例的一標準作業過程中，冷媒n冷卻 (或”注入”）熱套筒50而使其中的PCM變成固體，因而允 許熱套筒5 0吸收流入空氣6 1的熱能。流入空氣6丨的熱能 通過PCM /熱套筒50而被傳送至熱吸收冷媒η。 當返回的冷媒12達到預設溫度時即關閉冷媒系統 10。選擇之預設溫度可發出不需冷媒系統1〇進一步冷卻的 4吕號’例如，當進入熱套旖50的冷媒11溫度接近套筒5〇 出口的冷媒1 2溫度時。 壓縮機在被關閉之低或無負載期間PCM仍可繼續從 潮濕空氣吸收熱能。換言之’ PCM從固體變成液體之前可 在維持低恒定溫度之丁繼續吸收熱能而提供所需的冷卻效 果。依此方法，本發明之冷媒系統1〇可在保持關閉的情況 下仍能有較長時間的冷卻效果。 預設溫度時，可重 可極迅速地再注入 當返回冷媒12或熱套筒50達到— 新啟動冷媒系統1 〇並且冷媒系統i 〇 PCM(即，固化）。此系統的淨效果為可延長其循環期，並 且較不使用PCM的一般冷藏型空氣乾燥器有較低的耗電 量。其可將壓縮機的循環率從每小時3〇或4〇 a 久减少至， 例如，每小時5至15次或以下。 可研發在不同溫度下改變其狀態的蓄熱介質。例如 8 200523515 種冷卻至+4 C時仍不會使水在交換器40内產生結冰之 組成物的介質。許多公司生產可變化於液相和固相之間的 CM 例如伊利諾州 Naperville 的 PCM Thermal Solutions 公司。PCM A4為一種可冷卻至+4°c的有機石蠟，其由大 量碳氫化合物混合而成。E7和E8型分別在+7。(：和+8。(：產 生相變化’其由氨鹽和硫酸鈉鹽所組成。提供低露點服務 時’此類冷媒系統具有反向冷媒熱交換器，其可利用含有 在-29°C下冷凝之TEA-29的低溫PCM。此TEA介質由無 機水合鹽溶液所組成，例如溶於水的氯化妈。 回顧第1圖’從熱套筒5〇出來的冷凝空氣62必需有 足夠的冷度以啟動其内之水的冷凝作用。此處僅以，，水，，做 為舉例’其可以任何其他準備進行冷凝之蒸發液體取代。 然後在冷凝分離器80内收集並移除該冷凝水。冷凝分離器 已為本技藝中所習知，並且本發明可利用任何其類似的分 離器。 如第1圖所示，冷凝空氣62的返回路徑可視需要用於 交換器3 0内而使熱能可從流入空氣61轉移至排出空氣 62 °依此方法’不僅可使排出空氣接近初進入交換器20 内之流入空氣61的溫度，並且在進入交換器40之前具有 預冷進入交換器20之空氣61的效果。 第1圖的實施例中說明習知的冷媒系統1 〇。其藉由壓 縮機13壓縮氣態冷媒12。壓縮過程中可使冷媒12的壓力 和溫度同時上昇。為冷卻該溫度，使冷媒1 2通過一可進行 熱交換的冷凝器1 4而降低壓縮後的熱能。當其冷卻後，氣 9 200523515 態冷媒12即冷卻成冷媒液體11。然後以濾過/乾燥裝 乾燥和/或過濾冷媒u内的雜質。 液態冷媒11然後通過可將其從高壓區輸送至低 的膨脹閥1 6，因而蒸發該冷媒11。在蒸發過程中， 11可從熱套筒5 0和/或潮濕空氟61吸收熱能。通常 媒系統亦具有一感應閥i 7。該感應闊1 7通常為一種 知返回冷媒1 2之溫度的溫度感應閥。該感應閥1 7較 可比較冷卻冷媒1 1和返回冷媒1 2之溫度，並且具有 到預設溫度時可關閉和/或開啟系統10的裝置。 第2圖所示為一種根據本發明實施例的熱交 120。此熱交換器120包括空氣/空氣熱交換器130、 冷媒熱交換器140及一冷凝分離器180。空氣/冷媒交 1 4〇即為習知具有一系列層疊之’’散熱片’’的熱交換器 散熱片為在壓力、熱和冷之溫度下仍保持其堅固之極 熱性材料所製成。其較佳為使用金屬板，更明確而言 用不錄鋼板或銅板。 散熱片交換器以不銹鋼和銅片交叉焊接而於散熱 間產生“間隙，，或，，槽縫，，所構成。在本發明某些實施例 其片與片之間至少存有三個該類的間隙。第一個間隙 準備乾燥的流入空氣。第二個間隙内含冷媒而第三個 則内含PCM。冷媒片較佳為和接觸空氣片的PCM片 觸’然而，亦可有不同的組合。 如第2圖所示，進入管160可連接至空氣/空氣交 1 3 0之蒸發器而使進入的空氣流入貯氣室内。如上所 置15 壓區 冷媒 ，冷 可測 佳為 在達 換器 £氣/ 換器 。該 佳導 為使 片之 中， 内含 間隙 相接 換器 述， 10 200523515 流：空氣之流向較佳為和流出空氣呈反向$ 空氣熱交換器的調適功能，因此可在進入$ 預冷流入空氣。此流入空氣然後流至散熱片 —散熱片熱交換器150為由—系列層s 室。基於上述的理由’流入空氣較佳為“ 向的熱交換器140。交換器150亦具有可感 内冷媒和/或PCM狀態的探測器155。在弃 探測益1 55較佳為一種相變化溫度感應探金 於PCM溫度最高的交換器15〇内位置。然 適合被使用於熱交換器120内的任何位置。 旦熱交換i 140呈相反流向，則可冷卻流出 凝。 冷凝分離器18〇可經由排出口 19〇 1 2 〇。分離器1 8 0從氣流中分離出冷凝水。 中，分離器1 80可利用絲網i 8 J以增加冷顏 1 8 1可為任何材料所製成，較佳為在潮濕下 壞的材料，其並不限於某種特定的構造。在 為利用不銹鋼絲網。分離器1 8 0可具有一排 液口 182 。 分離器180連接至管道1〇〇而使乾燥空 父換器1 3 0内，並且經由一排出口 1 7 〇被排 交換器1 3 0可使排出的冷卻乾燥空氣預先冷 氣。 第3圖為根據本發明實施例的熱交換器 I動。由於空氣/ L換器140之前 熱交換器1 5 0。 片所構成的腔 L和冷媒相反流 應和/或報告其 丨些實施例中， •’其並且被置 6，探測器1 5 5 無論如何，一 空氣而使水冷 連接至交換器 在某些實施例 作用。該絲網 不會腐蝕或損 某些實施例中 出冷凝水的排 氣可重新進入 出。空氣/空氣 卻進入的熱空 2 2 0。此熱交 200523515 換器22 0包括空氣/空氣熱交換器230、空氣/冷媒熱交換器 24Q以及輸送空氣於交換器和240之間的管道221和 222 〇 更样細而言，第3圖的熱交換器具有一個流入如壓縮 作氣之浪體的進入口 260。進入口 260連接至交換器230 内的管道23 1，其可進行進入交換器220之熱、潮濕空氣 和排出交換器22〇之冷、乾燥空氣之間的空氣/空氣熱交 換。例如，進入之空氣可流經通過交換器2 3 0中央或周圍 的管道231，而整個管道23 1被從出口 270排出的冷凝空 氣所包圍。如其他實施例所述，進入和排出的空氣較佳為 以相反流向配置以達到最大的熱交換效果。此類設計在本 技藝中通常稱之為”殼管式”或”管内複式管”熱交換器。 流入空氣流經空氣/空氣交換器2 3 0之後，其通過連接 管道221而流入空氣/冷媒交換器240。交換器240由三支 同心管所構成其使冷媒流經最内側管道，pCM保留於第一 和第二管道之間，並且空氣則通過第三和第二管道之間的 環形空間。可利用螺旋狀構成此三管式的設計，或其可為 如圖所示的直管狀。冷媒則通過進入/排出口 24丨於交換器 2 4 〇内進行循環。冷媒則輪流冷卻含p c μ之套筒2 4 5和/ 或流經交換器240的潮濕空氣。 當熱能從流入空氣轉移至冷媒和/或PCM時，空氣被 冷卻至或低於其露點並且開始凝結濕氣（例如，水）。在交 換器240内收集冷凝水，然後從凝液排孔242被排出系統 外。此交換器24〇亦可具有一個液體充填/排放孔243。此 12 200523515 充填/排放孔243需要時可夯搐七 並且亦可200523515 (1) Description of the invention: [Technical field to which the invention belongs] The present invention generally relates to a drying system. More specifically, the present invention relates to a refrigerated air dryer having a phase change material for a heat storage medium. [Prior art] 〃Air dryer is usually used to remove water vapor from compressed air or gas. When a refrigerated air dryer is used, a refrigerant system is used to reduce the temperature of the air or gas to or below the condensation temperature of its water. At this temperature, the water vapor in the humid air will condense on the inner surface of the condenser and be collected and discharged from the system. In order to keep the temperature of humid air or gas low, the “Xiangxiang” media system has a heat exchanger to release heat energy from the air or gas during the drying process of the refrigerant. -Generally speaking, the heat energy released by humidity and s gas is combined with the low temperature refrigerant evaporated in the evaporator. This _ 'can cool the air by releasing heat energy from the tidal air or gas when the liquid refrigerant is evaporated. t When the air or gas reaches or falls below the condensation temperature of its water, the water vapor in the air or gas starts to condense (or separate) and is collected in the condenser or separator. In order to recirculate the refrigerant in the system, a compressor and a chiller-compressor are usually installed to re-liquefy the evaporated refrigerant, and the chiller can cool the liquid refrigerant that becomes hot during the compression process. The refrigerant can now undergo another evaporation cycle. For example, when there are very few or no refrigerated dryers, the usual difficulty is to decide how to stop the cooling (ie, system ,, release, etc.) under no load or low load ^ 3 200523515 Air flows through the refrigerated dryer to make refrigerated demand Very low or no, or when the incoming air has cooled. Generally, cooling should be reduced or discontinued during this period to avoid freezing the refrigerant system and affecting the operation of the refrigerated air dryer. Freezing will block the system and not be able to continue to dry the air 'or it will block the air passages and stop the flow of compressed air. One problem that can be avoided by excessive cooling is the use of a circulation type refrigerated dryer. In the circulating refrigerating type drying system 'when the humid air has been cooled to a preset temperature, the thermostatic device can release the refrigerant. The unit can also restart the compressor when the temperature in the evaporator rises to a preset temperature, which means that further cooling is required to remove the moisture that flows into the air. Therefore, between a moderate load and a low load, the cooling compressor can make about 30 to 40 switching cycles per hour. The high number of cycles per hour is extremely important as high cycle frequencies will increase costs and wear on compressors, control systems and valves. Therefore, the life of the refrigerant system is greatly shortened. Therefore, it is urgent to provide a refrigerant air drying system and a method for extending the life of the refrigerant system. In addition, the higher the cycle frequency of the refrigerant system, the greater its power consumption. Low power consumption can combine the advantages of cost reduction and environmental protection. Therefore, there is also an urgent need to provide a refrigeration drying system and a method for reducing its power consumption. [Summary of the Invention] The present invention meets the above-mentioned needs to a certain extent. In one embodiment, an air drying device is provided which has a refrigerant system and a heat exchanger further containing a phase change material, wherein the refrigerant system can cool heat exchange. Device. 4 200523515 Air dryer can dry air or gas. In the second embodiment, it is considered to be compressed air or, in some two embodiments, the present invention deals with a π. A separator, the preferred second, the device includes a condensed liquid phase door / "has a screen The phase change material can be changed between the solid phase and the liquid phase. In some embodiments, the phase change material is an organic stone soil. / In other embodiments, a method for dry-removing the milk and removing the milk is provided. It includes the extraction system, the medium system, and a phase change material containing the coarse change. The refrigerant system cools the heat exchanger 敎 ... = 4, and uses the method 1A to dry the air or gas. It should be compressed air or Gas. "In some embodiments ... the method of gas includes a condensing separator, which is preferably a second network. Phase change material can change ^ The phase change material in the filament is between phases. In some embodiments τ Qiwen chemical material is an organic paraffin. In still other embodiments, the apparatus for supplying dry air includes a refrigerating device and a heat-exchanging package containing a phase-change material. The refrigerating device can cool the heat-exchanging device. Gas drying equipment: medium or gas, if necessary, you can die air or press roll or gas. In some embodiments of the air drying apparatus of the present invention, the apparatus includes a condensation separation device, which is more than a wire mesh. The tritiated material may vary between a solid phase and a liquid phase. In: With the examples, the phase change material is an organic ballast. These facts are only brief and not broad, and the +, 1 and 4 blocks describe the more important features of the present invention in order to explain in detail the better understanding of the following, and have a better understanding of the contribution of the present invention. Of course, the present invention still has other advantages, which will be described below and are the subject of the scope of patent application for attachments. * Explanation Before the present invention is described in detail with at least one embodiment, the application of the corresponding month is not limited to the structure and solution in the following description or illustration. The present invention can be applied to other embodiments, and there can be various different operations and operation methods. Xiao Shi 'should understand that the scope of the present invention is not limited to the words and terms used herein and the abstract, and is used for illustrative purposes only. Those skilled in the art should understand that other structures, methods, and systems can be easily designed to implement the present invention using the concepts disclosed in the present invention as a basis. Therefore, the patentable scope should be considered to include such similar constructions without departing from the spirit and scope of the invention. [Embodiment] The present invention will be described with reference to diagrams and drawings, and the same element symbols represent all the same parts. The present invention provides a refrigerant system 10 operating in conjunction with a heat exchanger 20 to cool moist compressed air to a temperature at which moisture contained therein can be sufficiently separated and removed by condensation, according to an embodiment. The heat exchange steam 20 may have various embodiments, some of which will be described below. The outline of Figure 1 shows that the heat exchanger 20 includes an air-to-air ("air / air milk") parent converter 30 and an air-to-refrigerant ("air / refrigerant") exchanger 40. The exchanger ^ The number 40 further includes a hot sleeve 50, which is shown in the embodiment to be directly cooled by the refrigerant system station 7 and the Letong 100. In addition, a 'includes compressed air and gas in the air, gas, or generally any need to teach The steam is rolled into the heat exchanger 20 through the inlet 60. Here, "air" is a spoon of k,. All the above-mentioned liquids should be included, and should not be inferred or restricted. The liquids in Xia Shi's example. The air then passes through the exchanger 30 to exchange ^ ^ ". The second rolling preferably flows through the path 6 1, 6 200523515 through the exchanger 30, which can transfer the thermal energy of the hotter humid air entering from the inlet 60 to the cooler dry air flowing from the outlet 70. For example, the temperature of the air entering from the inlet 60 may be 40 to 70 degrees Fahrenheit higher than the air exiting from the outlet 70. This temperature difference allows thermal transfer without the need for mechanical intervention. The air enters the exchanger 40 after passing through the exchanger 30. The exchanger 40 can transfer the thermal energy of the inflow air to the refrigerant 11 supplied from the refrigerant system i 0. In this embodiment, it is shown that the refrigerant 11 can cool the hot sleeve 50. The material of the thermal sleeve may include any material known in the art that can be cooled to or below the dew point of the condensing vapor (i.e., water). Suitable materials include, but are not limited to, ethylene glycol and mixtures thereof. In some embodiments, the thermal sleeve 50 contains a phase change material (PCM), which is a heat storage medium t that can absorb or diffuse heat by a bidirectional change from a solid phase to a liquid phase. For example, in the towel of this embodiment, when the phase change material absorbs thermal energy from moist air, it starts to change from a solid phase to a liquid phase. However, due to the thermostatic nature of the PCM technology, it is not limited to scientific theory, because the thermal sleeve 50 can maintain the surname 」during thermal transfer. This process depends on the temperature of the PCM, the temperature of the environment, and the load. It can take tens of minutes to several hours. In some embodiments, the aging # + season-best PCM is capable of absorbing a maximum amount of thermal energy in a minimum temperature range. At this point, PCM can maintain a longer solid phase time under a known required amount of heat. Scientifically, when the solid phase is transformed into a liquid, the thermal conductivity of the liquid can be significantly increased. Induction, for example, the thermal conductivity of water at 32 ° C is 0.326 BTU / hour-suction, and the warrior's guide is 1.18 BTUH, hour-suction-sucking at the same temperature. Λ Scholars…, because PCM can absorb thermal energy in the solid state (high thermal conductivity) 200523515 liquid (lower thermal conductivity), it can absorb the thermal energy of condensation more quickly and effectively than the material without phase change. Therefore, using the latent heat of the cold edge (solid-liquid) can store more thermal energy in a smaller volume of medium than by changing the temperature, so a smaller volume of heat exchange can be designed || In a standard operation of the embodiment of the present invention, the refrigerant n cools (or "injects") the hot sleeve 50 so that the PCM therein becomes solid, thereby allowing the hot sleeve 50 to absorb the heat energy of the incoming air 61. The thermal energy of the inflow air 6 丨 is transmitted to the heat absorption refrigerant η through the PCM / thermal sleeve 50. When the returned refrigerant 12 reaches a preset temperature, the refrigerant system 10 is shut down. The selected preset temperature can be issued as No. 4 'which does not require further cooling by the refrigerant system 10. For example, when the temperature of the refrigerant 11 entering the hot jacket 50 is close to the temperature of the refrigerant 12 at the outlet of the sleeve 50. The PCM can continue to absorb heat from the humid air while the compressor is switched off at low or no load. In other words, PCM can continue to absorb thermal energy and provide the required cooling effect while maintaining a low constant temperature before changing from solid to liquid. According to this method, the refrigerant system 10 of the present invention can still have a long-term cooling effect while remaining closed. It can be re-injected at a preset temperature, and can be refilled very quickly. When the return refrigerant 12 or the hot sleeve 50 is reached—the refrigerant system 10 is newly started and the refrigerant system i is PCM (ie, solidified). The net effect of this system is that it can extend its cycle time and consume less power than a general refrigerated air dryer that does not use PCM. It can reduce the compressor's cycle rate from 30 or 40 a hour to, for example, 5 to 15 times or less per hour. A heat storage medium that can change its state at different temperatures can be developed. For example, 8 200523515 is a medium that does not cause water to generate icing composition in the exchanger 40 when cooled to +4 C. Many companies produce CMs that can vary between liquid and solid phases, such as PCM Thermal Solutions of Naperville, Illinois. PCM A4 is an organic paraffin that can be cooled to + 4 ° C. It is a mixture of large amounts of hydrocarbons. E7 and E8 are at +7 respectively. (: And +8. (: Phase change occurs 'It is composed of ammonia salt and sodium sulfate salt. When providing low dew point service' This type of refrigerant system has a reverse refrigerant heat exchanger, which can be used at -29 ° C Low-temperature PCM of TEA-29 under condensing. This TEA medium consists of an inorganic hydrated salt solution, such as chloromethane dissolved in water. Review Figure 1 'The condensing air 62 from the hot sleeve 50 must be sufficient The coldness is to start the condensation of the water in it. Here, only, water, as an example, it can be replaced by any other evaporation liquid that is ready to be condensed. Then the condensation is collected and removed in the condensation separator 80 Water. Condensation separators are well known in the art, and the present invention can use any similar separators. As shown in FIG. 1, the return path of the condensing air 62 can be used in the exchanger 30 as required. The thermal energy can be transferred from the inflow air 61 to the exhaust air 62 °. According to this method, not only can the exhaust air approach the temperature of the inflow air 61 that has initially entered the exchanger 20, but it also has a pre-cooling Effect of air 61 The embodiment of FIG. 1 illustrates a conventional refrigerant system 10. It compresses a gaseous refrigerant 12 by a compressor 13. During the compression process, the pressure and temperature of the refrigerant 12 can be raised at the same time. In order to cool the temperature, the refrigerant 1 2 The heat energy after compression is reduced by a heat-exchangeable condenser 14. When it is cooled, the gas 9 200523515 refrigerant 12 is cooled to a refrigerant liquid 11. Then, the filter / dryer is used to dry and / or filter the refrigerant u The liquid refrigerant 11 then passes through the expansion valve 16 which can transport it from the high pressure region to the low, thereby evaporating the refrigerant 11. During the evaporation process, 11 can be removed from the hot sleeve 50 and / or humid air fluorine 61 Absorbs heat energy. Generally, the medium system also has an induction valve i 7. The induction valve 17 is usually a temperature sensing valve that knows the temperature of the return refrigerant 12. The induction valve 17 is more comparable to the cooling refrigerant 1 1 and the return refrigerant 1. 2 and has a device that can close and / or turn on the system 10 when a preset temperature is reached. Figure 2 shows a heat transfer 120 according to an embodiment of the present invention. The heat exchanger 120 includes air / air heat exchange 130, refrigerant hot exchange 140 and a condensing separator 180. Air / refrigerant delivery 140 is a conventional heat exchanger with a series of stacked `` radiating fins ''. The radiating fins of the heat exchanger are maintained under pressure, heat and cold temperatures. Made of sturdy, extremely heat-resistant material. It is better to use metal plates, or more specifically, non-recorded steel or copper plates. The heat sink exchanger is welded with stainless steel and copper plates to create a "gap" between the heat sinks, or Slot,, constituted. In some embodiments of the present invention, there are at least three gaps of this type between the sheets. The first gap is prepared to dry into the air. The second gap contains refrigerant and the third PCM is included. The refrigerant sheet is preferably in contact with the PCM sheet that is in contact with the air sheet. However, different combinations are also possible. As shown in FIG. 2, the inlet pipe 160 may be connected to an evaporator of the air / air exchange 130 to allow the incoming air to flow into the air storage chamber. As described above, the 15 nip refrigerant is used, and the cold can be measured preferably in the air conditioner. In order to make the film, there is a gap connection converter in the film. 10 200523515 Flow: The air flow direction is preferably the adjustment function of the air heat exchanger in the opposite direction to the outgoing air, so it can be pre-cooled when entering Into the air. This inflow air then flows to the fins—the fin heat exchanger 150—for a series of s-chambers. Based on the above reasons, the inflow air is preferably the “direction heat exchanger 140. The exchanger 150 also has a detector 155 that can sense the state of the internal refrigerant and / or PCM. The detection benefit 1 55 is preferably a phase change temperature Inductive gold detection is located within 15 ° of the PCM's highest temperature exchanger. However, it is suitable to be used anywhere in the heat exchanger 120. Once the heat exchange i 140 has the opposite flow direction, it can cool and flow out of condensation. The condensation separator 18 ° can Via the outlet 19201 2 0. The separator 1 80 separates the condensate from the airflow. In the separator 1 80, the screen i 8 J can be used to increase the coolness 1 8 1 can be made of any material. It is preferably a material that is damaged under moisture, and it is not limited to a specific structure. In the use of stainless steel wire mesh. The separator 180 may have a liquid discharge port 182. The separator 180 is connected to the pipe 100. Cooling the dry cooling air inside the heat exchanger 130 and exhausting it through the heat exchanger 1 300 through a discharge port 170 allows the exhausted cooling and drying air to be pre-cooled. Fig. 3 is a heat exchanger I according to an embodiment of the present invention. Because of the air / L exchanger 140 before the heat exchanger 150. The cavity L formed by the sheet and the reverse flow of the refrigerant should and / or report them. In some embodiments, • 'It is also placed 6, the detector 1 5 5 anyway, an air-cooled connection to the exchanger in some cases The effect of the embodiment. The wire mesh will not corrode or damage the condensed water in some embodiments. The exhaust air can be re-entered. The air / air enters the hot air 2 2 0. This hot hand 200523515 The switch 22 0 includes air / Air heat exchanger 230, air / refrigerant heat exchanger 24Q, and pipes 221 and 222 that transport air between the exchanger and 240. More specifically, the heat exchanger of FIG. 3 has an inflow such as compressed air The inlet 260 of the wave body. The inlet 260 is connected to the pipe 23 1 in the exchanger 230, and it can perform the air between the hot and humid air entering the exchanger 220 and the cold and dry air exiting the exchanger 220. Air heat exchange. For example, the incoming air can flow through a duct 231 passing through the center or surrounding of the exchanger 230, while the entire duct 23 1 is surrounded by the condensed air exhausted from the outlet 270. As described in other embodiments, the incoming and Better exhaust air In the opposite flow configuration for maximum heat exchange effect. This type of design is commonly referred to in the art as a "shell-and-tube" or "pipe-and-tube" heat exchanger. The inflow air flows through the air / air exchanger 2 3 After 0, it flows into the air / refrigerant exchanger 240 through the connecting pipe 221. The exchanger 240 is composed of three concentric pipes, which makes the refrigerant flow through the innermost pipe, pCM remains between the first and second pipes, and the air It passes through the annular space between the third and second pipes. This three-tube design can be constructed in a spiral shape, or it can be a straight tube as shown. Refrigerant is circulated in the exchanger 24 through the inlet / outlet port 24 丨. The refrigerant alternates to cool the sleeves 2 4 5 containing p c μ and / or the humid air flowing through the exchanger 240. When thermal energy is transferred from the incoming air to the refrigerant and / or PCM, the air is cooled to or below its dew point and begins to condense moisture (for example, water). The condensed water is collected in the exchanger 240, and then discharged out of the system through the condensate drain hole 242. This exchanger 240 may also have a liquid filling / discharging hole 243. This 12 200523515 filling / draining hole 243 can tamp seven when needed and also
町j死填或再充填PCM 排放其内所含的氣體或熱氣。 在某些實施例中，空氣/冷媒交換器24〇較佳為且有一 探測器244。探測器244較佳為一種㈣化溫度感應探針， 其並且被置於PCM溫度最高的交換器24〇内位置。然而， 探測器244適合被使用於熱交換器12〇内的任何位置。在 某些實施例中此探測器2 4 4亦可發出關閉或操作冷媒系統 的信號。 在第3圖的實施例中，一旦乾燥之後利用另一連接管 222引導冷凝空氣回流至交換器23〇。在所示的配置中，交 換器2 3 0内之管道2 3 1的冷凝空氣和流入空氣呈反向流 動。此過程不僅可冷卻管道23丨内的流入空氣亦可使乾燥 空氣經由出口 270排出交換器220。 第4圖說明另一種熱交換器32〇。此熱交換器32〇具 有一空氣/冷媒父換器340和一分離器380以及視需要亦可 具有一空氣/空氣交換器。交換器340由如圖所示之三個纏 繞之螺旋管束所構成。進入交換器3 2 0時三個螺旋管3 6 1 之一可通過空氣並排出乾燥空氣。該空氣可經由整體管道 設計中之管道的入口 /出口 365進入/排出交換器320。 此外，螺旋管361周圍至少放置/隱藏其他兩支管道 311和351。其中一支管道351内含PCM，而另一支管道 則含冷媒。在本發明較佳實施例中，管道3 11、3 5 1和3 6 1 由銅所製成，並且三支管道之管線均置於不相互重疊的位 置 13 200523515 然而，热習本技藝之人仕應瞭解該三支管道可由任何 其他材料所製成，或分別由不同的材料所製成。熟習本技 藝之人仕亦應瞭解該三支管道之管線可有不同的配置方 法。 第4圖實施例之交換器32〇另外具有可從乾燥空氣中 機械性分離冷凝濕氣的分離器38〇。如上述實施例所示， 交換器320内亦可裝設一具探測器355。 從詳細專利說明書中可彰顯本發明的許多特性及優 點’因此，專利申請範圍附件涵蓋屬於本發明真正精神和 範圍内之本發明的全部該類特性及優‘點。再者，由於孰習 本技藝之人仕可輕易進行 造和操作並不僅侷限於上 當的修改及同等物仍均屬 修改和變化，故本發明之精確構 述的描述和說明，因此，全部適 於本發明的範圍。 【囷式簡單說明】 冷藏空氣乾燥器之蒸發器的分離 第1圖為根據本發曰月 視圖。 之冷藏冰水機的 之冷藏冰水機的 之冷藏冰水機的 第2圖》根據本發明冷藏空氣乾燥器 分離視圖。 第3圖為根據本發明、人_ ，明冷藏空氣乾燥器 分離視圖。 第4圖為根據本發明、人产上 @ %冷藏空氣乾燥器 分離視圖。 14 200523515 【主要元件符號說明】 1 0冷媒系統 1 2氣態冷媒 1 4冷凝器 1 6膨脹閥 20熱交換器 40空氣/冷媒交換器 60入口 62冷凝空氣 8 0冷凝分離器 120熱交換器 140空氣/冷媒熱交換器 1 5 5探測器 170排出口 1 8 1絲網 190排出口 221管道 230空氣/空氣熱交換器 240空氣/冷媒熱交換器 242凝液排孔 244探測器 260進入口 311管道 340空氣/冷媒交換器 11液態冷媒 1 3壓縮機 15濾過/乾燥裝置 1 7感應閥 3 0空氣/空氣交換器 50熱套筒 6 1流入空氣 70出口 100管道 130空氣/空氣熱交換器 150散熱片熱交換器 160進入管 1 8 0冷凝分離器 1 8 2排液口 220熱交換器 222連接管 231管道 241進入/排出口 243充填/排放孔 245套筒 270 出口 320熱交換器 351管道 15 200523515 3 5 5探測器 3 6 1螺旋管 365入口 /出口 380分離器 16Mach j fills or refills PCM and discharges the gas or hot gas contained in it. In some embodiments, the air / refrigerant exchanger 240 is preferably and has a detector 244. The detector 244 is preferably a tritium temperature-sensing probe, and it is placed in the position of the exchanger 240 with the highest PCM temperature. However, the detector 244 is suitable for use at any location within the heat exchanger 120. In some embodiments this detector 2 4 4 can also signal to shut down or operate the refrigerant system. In the embodiment of FIG. 3, once dried, another condensing pipe 222 is used to guide the condensed air back to the exchanger 23o. In the configuration shown, the condensed air and the inflow air in the duct 2 3 1 in the switch 230 flow in opposite directions. This process not only cools the incoming air in the duct 23, but also allows the dry air to exit the exchanger 220 through the outlet 270. Figure 4 illustrates another heat exchanger 32o. The heat exchanger 32 is provided with an air / refrigerant parent converter 340 and a separator 380 and optionally an air / air exchanger. The exchanger 340 is composed of three coiled spiral tube bundles as shown. When entering the exchanger 3 2 0, one of the three spiral tubes 3 6 1 can pass through the air and discharge dry air. This air can enter / exit the exchanger 320 via the inlet / outlet 365 of the duct in the integrated duct design. In addition, at least two other pipes 311 and 351 are placed / hidden around the spiral pipe 361. One of the pipes 351 contains PCM and the other pipe contains refrigerant. In the preferred embodiment of the present invention, the pipes 3 11, 3 5 1 and 3 6 1 are made of copper, and the pipes of the three pipes are placed in positions that do not overlap each other. 13 200523515 It should be understood that the three pipes may be made of any other material, or of different materials. Those who are familiar with this technology should also understand that the pipelines of the three pipelines can have different configuration methods. The exchanger 32 of the embodiment shown in FIG. 4 further includes a separator 38 that can mechanically separate condensed moisture from dry air. As shown in the above embodiment, a detector 355 may also be installed in the switch 320. Many detailed features and advantages of the present invention can be revealed from the detailed patent specification. Therefore, the appendix to the scope of patent application covers all such features and advantages of the present invention that fall within the true spirit and scope of the present invention. Furthermore, since those skilled in the art can easily make and operate and are not limited to the above-mentioned modifications and equivalents, they are also modifications and changes. Therefore, the precise description and description of the present invention are suitable for Within the scope of the present invention. [Simplified description of 囷 style] Separation of the evaporator of the refrigerated air dryer Figure 1 shows the month view according to the present invention. Fig. 2 of the refrigerated ice water machine Fig. 2 of the refrigerated ice water machine according to the present invention is a separate view. Fig. 3 is a separate view of the refrigerator air dryer according to the present invention. Fig. 4 is a separated view of a @% refrigerated air dryer according to the present invention. 14 200523515 [Description of symbols of main components] 1 0 Refrigerant system 1 2 Gaseous refrigerant 1 4 Condenser 1 6 Expansion valve 20 Heat exchanger 40 Air / refrigerant exchanger 60 Inlet 62 Condensed air 8 0 Condensation separator 120 Heat exchanger 140 Air / Refrigerant heat exchanger 1 5 5 Detector 170 outlet 1 8 1 Wire mesh 190 outlet 221 pipe 230 air / air heat exchanger 240 air / refrigerant heat exchanger 242 condensate drain hole 244 detector 260 inlet 311 pipe 340 air / refrigerant exchanger 11 liquid refrigerant 1 3 compressor 15 filter / dryer 1 7 induction valve 3 0 air / air exchanger 50 thermal sleeve 6 1 incoming air 70 outlet 100 pipe 130 air / air heat exchanger 150 heat dissipation Sheet heat exchanger 160 enters the tube 1 8 0 condensation separator 1 8 2 liquid discharge port 220 heat exchanger 222 connection tube 231 pipe 241 inlet / outlet port 243 filling / discharging hole 245 sleeve 270 outlet 320 heat exchanger 351 pipe 15 200523515 3 5 5 Detector 3 6 1 Spiral tube 365 inlet / outlet 380 separator 16