201020482 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種冷凍式空氣乾燥機’其係藉由將壓 縮空氣冷卻、使該壓縮空氣中的水分凝縮之方式’將該壓 縮空氣除濕。 【先前技術】 在利用電磁閥或氣缸等空氣壓機器之空氣壓系統中’ 爲了防止被供給至該空氣壓系統的壓縮空氣中的水分造成 故障，因而期望事先去除壓縮空氣中的水分’爲了去除其 水分而使用冷凍式空氣乾燥機。 第2圖係顯示以往的冷凍式空氣乾燥機中的冷媒系統 和空氣系統之電路。該冷凍式空氣乾燥機中的冷媒系統係 具有：冷媒壓縮機10;將利用該冷媒壓縮機10被壓縮後 ，通過高溫冷媒配管22被傳送的高溫冷媒進行凝縮之冷 ® 凝器11;將利用該冷凝器11被凝縮後的冷媒，藉由隔熱 膨脹使其減壓之膨脹閥12;及將利用空氣系統的第1再 熱器14進行預備冷卻後的空氣，藉由來自該膨脹閥12的 低溫冷媒，進行再冷卻並除濕之冷卻器13;且來自該冷 卻器13的冷媒係通過反饋冷媒配管26，返回上述冷媒壓 縮機10。 另一方面，上述空氣系統係具有：除濕對象之溫熱且 濕潤的一次空氣流入的空氣入口 20;藉由將從該空氣入 口 2 0流入的一次空氣和除濕後的低溫除濕空氣進行熱交 -5- 201020482 換，以進行預備冷卻之上述再熱器14;將利用該再熱器 14進行預備冷卻後的空氣，進行再冷卻之上述冷卻器13 :及將利用該冷卻器1 3再冷卻後的空氣，於進行排水分 離使其呈低溫的上述除濕空氣之狀態下，傳送到上述再熱 器14之排水分離器16;且藉由將上述除濕空氣和一次空 氣在上述再熱器14進行熱交換的方式，將上述一次空氣 進行預備冷卻，並且將上述低溫除濕空氣升溫，且作爲二 次空氣而從出口配管21送出至外部。 @ 因而，上述冷卻器13係連接在上述冷媒系統和空氣 系統兩方，與該等冷媒系統和空氣系統以功能性結合者。 此外，在進行上述排水分離的排水分離器16設有排 水閥15，其係用於將產生的水滴分離並排出至外部。 上述以往的冷凍式空氣乾燥機中，通常，來自上述冷 媒壓縮機10通過高溫冷媒配管22流到冷凝器11的冷媒 之溫度爲大約90 °C，利用膨脹閥12進行隔熱膨脹後通過 低溫冷媒配管23流到冷卻器13的冷媒之溫度爲大約5。(： 〇 。又’從空氣入口 20被取入再熱器14的一次空氣之溫度 爲40 °C (額定），利用再熱器14進行預備冷卻後通過空 氣配管24流到冷卻器13的空氣之溫度爲大約25。(：，利 用冷卻器1 3再冷卻後經由排水分離器1 6被送到再熱器 1 4的除濕空氣之溫度爲大約1 〇 °C，利用再熱器1 4升溫後 通過出口配管21流出至外部的二次空氣之溫度爲大約3〇 °C 。 此外，連結上述冷媒壓縮機10和冷凝器11之高溫冷 201020482 媒配管22、和連結膨脹閥12和冷卻器13之低溫冷媒配 管23’係由支路冷媒配管25連通，該支路冷媒配管25 具備可調節打開度之容量調整閥17。該支路·冷·媒配管25 係於上述冷卻器13的負荷變小時，爲了避免因來自膨脹 閥12通過低溫冷媒配管23流到冷卻器13的冷媒之溫度 過度下降，以致於來自再熱器14通過空氣配管24流到冷 卻器13之濕潤的壓縮空氣中的水分凍結，因而將容量調 整閥17僅打開必要量，使來自冷媒壓縮機1〇流到冷凝器 1 1的高溫冷媒之一部分，混入低溫冷媒配管2 3中的低溫 冷媒’用以保持該低溫冷媒的溫度不會下降至一定溫度以 下者。 在上述第2圖所示之以往的冷凍式空氣乾燥機中，因 使用條件而有再熱器的性能降低之問題。若要具體地説明 該問題，首先，使用上述再熱器14的目的係如下述。 1. 藉由將進入到空氣乾燥機的壓縮空氣，利用再熱器 ❹ 進行預備冷卻的方式，減少對冷凍電路（冷媒系統）的負 荷（減少冷凍電路負荷，謀求省能源化）。 2. 藉由利用從空氣入口重新進來的一次空氣之熱，使 利用空氣乾燥機除濕後的壓縮空氣升溫之方式，防止空氣 乾燥機的二次側之空氣配管結露。 但是’當從空氣乾燥機的空氣入口流入的一次空氣之 溫度低時（大約20 °C)，再熱器的性能降低，會有無法 使從出口配管21流出的二次空氣升溫至達到防止結露之 溫度的情形，該情形即以往的空氣乾燥機之重大問題。亦 201020482 即，由於空氣乾燥機的空氣配管通常是使用鐵（經鍍鋅者 )，因此有出口配管21結露腐蝕之顧慮，及因爲結露而 在配管下部的地面等形成積水的情形。爲了將配管隔熱， 無法避免繁複的作業和高成本。 因而，可以考慮藉由將上述再熱器，設在將利用冷媒 壓縮機10壓縮後的冷媒送到冷凝器11之高溫冷媒配管 22、和將來自排水分離器16的除濕空氣送出至外部的出 口配管21之間的方式，使來自出口配管21的二次空氣充 @ 分地升溫，但該情形下，無法將來自空氣入口 20的空氣 (一次空氣）進行預備冷卻，因此全部的熱負荷施加在冷 凍電路（冷媒系統），以致於形成空氣乾燥機的處理空氣 量降低，爲了使處理空氣量與第2圖的情形相同，必須擴 大該冷凍電路。 針對這種以往的冷凍空氣乾燥機，謀求節省能源的方 法有擴大冷凝器、或增加冷凝器的冷卻媒體之量、或降低 溫度來對應，但該方法卻連帶有乾燥機大型化、冷卻設備 ® (空調機、冷卻裝置（Chiller )、冷卻塔等）大型化、冷 卻設備非省能源化之缺點。 爲了謀求上述冷凍式空氣乾燥機之省能源化，此處， 針對上述第2圖之以往的冷凍式空氣乾燥機中的各主要部 分之能源的輸出入關係進行考察，首先，[Technical Field] The present invention relates to a refrigerating air dryer which dehumidifies compressed air by cooling compressed air to condense moisture in the compressed air. [Prior Art] In an air pressure system using an air pressure machine such as a solenoid valve or a cylinder, in order to prevent malfunction of moisture in the compressed air supplied to the air pressure system, it is desirable to remove moisture in the compressed air beforehand in order to remove A refrigerating air dryer is used for its moisture. Fig. 2 is a view showing a circuit of a refrigerant system and an air system in a conventional refrigerating air dryer. The refrigerant system in the refrigerating air dryer includes a refrigerant compressor 10, and a cold condenser 11 that is compressed by the refrigerant compressor 10 and then condensed by a high-temperature refrigerant that is transported through the high-temperature refrigerant pipe 22; The refrigerant that has been condensed by the condenser 11 is decompressed by thermal expansion and expansion, and the air that has been preliminarily cooled by the first reheater 14 of the air system is supplied from the expansion valve 12 The low-temperature refrigerant is cooled and dehumidified by the cooler 13; and the refrigerant from the cooler 13 passes through the feedback refrigerant pipe 26 and returns to the refrigerant compressor 10. On the other hand, the air system has an air inlet 20 into which the warm and humid primary air flows in the dehumidification object; and the hot air from the primary air flowing in from the air inlet 20 and the dehumidified low-temperature dehumidified air - 5-201020482 The above-mentioned reheater 14 for preliminary cooling, the pre-cooled air by the reheater 14 is recooled, and the cooler 13 is recooled by the cooler 13 The air is sent to the drain separator 16 of the reheater 14 in a state where the drainage is separated to make it dehumidified at a low temperature; and the dehumidified air and the primary air are heated in the reheater 14 by the above-mentioned dehumidified air and the primary air. In the exchange mode, the primary air is pre-cooled, and the low-temperature dehumidified air is heated and sent out from the outlet pipe 21 to the outside as secondary air. @ Thus, the cooler 13 is connected to both the refrigerant system and the air system, and is functionally combined with the refrigerant system and the air system. Further, the drain separator 16 that performs the above-described drain separation is provided with a drain valve 15 for separating and discharging the generated water droplets to the outside. In the above-described conventional refrigerating air dryer, the temperature of the refrigerant flowing from the refrigerant compressor 10 through the high-temperature refrigerant pipe 22 to the condenser 11 is usually about 90 ° C, and the expansion valve 12 is used to thermally insulate and then pass through the low-temperature refrigerant. The temperature of the refrigerant flowing from the piping 23 to the cooler 13 is about 5. (: 〇. Further, the temperature of the primary air taken into the reheater 14 from the air inlet 20 is 40 ° C (nominal), and the air that has been pre-cooled by the reheater 14 and then flows through the air pipe 24 to the cooler 13 The temperature is about 25. (:, the temperature of the dehumidified air sent to the reheater 14 via the drain separator 16 after being cooled by the cooler 13 is about 1 〇 ° C, and the temperature is raised by the reheater 14 The temperature of the secondary air which flows out to the outside through the outlet pipe 21 is about 3 ° C. Further, the high-temperature cold 201020482 medium pipe 22 connecting the refrigerant compressor 10 and the condenser 11 and the joint expansion valve 12 and the cooler 13 are connected. The low-temperature refrigerant pipe 23' is connected by the branch refrigerant pipe 25, and the branch refrigerant pipe 25 is provided with a capacity adjustment valve 17 that can adjust the opening degree. The branch/cold medium pipe 25 is loaded with the load of the cooler 13 described above. In order to avoid excessive decrease in the temperature of the refrigerant flowing from the expansion valve 12 through the low-temperature refrigerant pipe 23 to the cooler 13, the moisture from the reheater 14 flowing through the air pipe 24 to the humidified compressed air of the cooler 13 Freeze On the other hand, the capacity adjustment valve 17 is opened only by a necessary amount, and a portion of the high-temperature refrigerant that flows from the refrigerant compressor 1 to the condenser 11 is mixed with the low-temperature refrigerant in the low-temperature refrigerant pipe 23 to maintain the temperature of the low-temperature refrigerant. In the conventional refrigerating air dryer shown in Fig. 2, there is a problem that the performance of the reheater is lowered depending on the use conditions. To specifically describe the problem, first use The purpose of the reheater 14 is as follows: 1. By reducing the compressed air entering the air dryer and using the reheater 预备 to reduce the load on the refrigeration circuit (refrigerant system) (reducing the refrigeration circuit) Load, seek energy saving.) 2. Prevent the condensation of the air piping on the secondary side of the air dryer by using the heat of the primary air re-entered from the air inlet to heat the compressed air dehumidified by the air dryer. But 'when the temperature of the primary air flowing in from the air inlet of the air dryer is low (about 20 ° C), the performance of the reheater is reduced, there will be no The secondary air flowing out from the outlet pipe 21 is heated up to a temperature at which dew condensation is prevented, which is a major problem of the conventional air dryer. Also, 201020482, that is, since the air pipe of the air dryer is usually iron (plated) In the case of zinc, there is a concern that the outlet piping 21 is dew condensation, and water is formed on the floor of the lower part of the piping due to condensation. In order to insulate the piping, complicated work and high cost cannot be avoided. The reheater is disposed between the high-temperature refrigerant pipe 22 that supplies the refrigerant compressed by the refrigerant compressor 10 to the condenser 11 and the outlet pipe 21 that sends the dehumidified air from the drain separator 16 to the outside. The secondary air from the outlet pipe 21 is heated up, but in this case, the air (primary air) from the air inlet 20 cannot be pre-cooled, so that all the heat load is applied to the refrigeration circuit (refrigerant system). Therefore, the amount of process air that forms the air dryer is reduced, and in order to make the amount of process air the same as in the case of FIG. 2, it is necessary to Expand the refrigeration circuit. In order to save energy, such a conventional refrigerating air dryer has a method of expanding the condenser, increasing the amount of the cooling medium of the condenser, or lowering the temperature. However, this method has a large-sized dryer and a cooling device®. (The air conditioner, cooling device (Chiller), cooling tower, etc.) is large-scale, and the cooling equipment is not energy-saving. In order to reduce the energy efficiency of the above-described refrigerating air dryer, the energy input and output relationship of each main part in the conventional refrigerating air dryer of Fig. 2 is examined. First,
Ql=冷卻器13之交換熱量（熱進入冷凍電路） Q2 =冷媒壓縮機10之消耗電力（冷媒壓縮機壓縮冷 媒的工作轉換成熱） 201020482 Q3 =冷凝器11之交換熱量（從冷凍電路釋出熱）時 ，下式（1 )成立。 Q3=Q1+Q2 ---(1) 冷凝器11係藉由空冷或水冷而將冷媒凝縮，但冷凝 器11的出口之冷媒的溫度愈低，則冷媒壓縮機10之上述 Φ 消耗電力Q2愈小。又，相當於冷凍式空氣乾燥機的冷卻 能力之上述冷卻器13的交換熱量Q1、和空冷冷凝器時之 該冷凝器周圍的溫度、和水冷冷凝器時之冷卻水的溫度係 已各自決定、冷凝器11之性能亦已決定。因此，假設冷 凍式空氣乾燥機之消耗電力大致等於冷媒壓縮機10之消 耗電力時，爲了降低冷凝器11的出口之冷媒的溫度以減 少冷媒壓縮機1 〇的消耗電力Q2，必須減少冷凝器1 1的 交換熱量Q3。 【發明內容】 本發明之技術性課題在於提供：基本上是藉由謀求有 效利用上述以往的冷凍式空氣乾燥機内的能源，使該冷凍 式空氣乾燥機中的冷凝器之交換熱量Q3減少，亦即使來 自冷凝器的排熱量減少，利用較少的電力發揮較大的除濕 效果，藉此謀得省能源化之冷凍式空氣乾燥機。 本發明之更具體的技術性課題在於提供：即使在欲除 濕的壓縮空氣之負荷大的情形下（壓縮空氣之溫度、濕度 -9- 201020482 高、或流量多等），仍可穩定地除濕，且即使在上述一次 空氣之溫度低的情形下，仍可確實地防止用於使經除濕後 的二次空氣流出至外部的出口配管產生結露之冷凍式空氣 乾燥機。 爲了解決上述課題，根據本發明，係提供一種冷凍式 空氣乾燥機：其係具備： 冷媒系統，具有：冷媒壓縮機；使利用該冷媒壓縮機 壓縮後的高溫冷媒凝縮之冷凝器；將利用該冷凝器凝縮後 @ 的冷媒，藉由隔熱膨脹使其減壓形成低溫之減壓機構；及 將利用空氣系統的第1再熱器進行預備冷卻後的空氣，藉 由來自上述減壓機構的低溫冷媒再冷卻除濕之冷卻器；構 成使來自該冷卻器的冷媒返回上述冷媒壓縮機；以及 空氣系統，具有：將除濕對象之溫熱且濕潤的壓縮空 氣作爲一次空氣而流入的空氣入口；藉由使從該空氣入口 流入的一次空氣和從上述冷卻器傳送來的低溫除濕空氣進 行熱交換之方式，將上述一次空氣進行預備冷卻且使上述 Θ 除濕空氣升溫之上述第1再熱器；及將利用該第1再熱器 進行預備冷卻後的一次空氣，藉由再冷卻除濕而形成低溫 的上述除濕空氣之上述冷卻器。 然後，該冷凍式空氣乾燥機具備第2再熱器’其係使 藉由在上述第1再熱器與一次空氣之熱交換而升溫後的上 述除濕空氣、和利用上述冷媒壓縮機壓縮後的高溫冷媒， 進行熱交換，且構成爲將藉由在該第2再熱器之熱交換而 再升溫後的上述除濕空氣作爲二次空氣，從出口配管輸出 -10 · 201020482 本發明中，較佳係構成爲上述第2再熱器被連接在冷 媒壓縮機和冷凝器之間，來自冷媒壓縮機的冷媒係經由該 第2再熱器被傳送到上述冷凝器。 又，亦可構成爲使連結上述冷媒壓縮機和上述第2再 熱器之高溫冷媒配管、及連結上述減壓機構和上述冷卻器 之低溫冷媒配管或連結上述冷卻器和上述冷媒壓縮機之反 〇 饋冷媒配管，藉由以具有可調節打開度之容量調整閥的支 路冷媒配管予以連通的方式，當上述冷卻器的負荷變小時 ，將利用上述冷媒壓縮機壓縮後的高溫冷媒的一部分直接 流到上述低溫冷媒配管或反饋冷媒配管。 本發明中，期待在從上述冷卻器到第1再熱器之流路 ，具有用於將利用該冷卻器再冷卻後之空氣進行排水分離 之排水分離器。 在具有上述構成的本發明之冷凍式空氣乾燥機中，由 ® 於倂用第1再熱器及第2再熱器，該第1再熱器係使從空 氣入口流入的一次空氣和經由冷卻器的低溫除濕空氣進行 熱交換，該第2再熱器係使利用冷媒壓縮機被壓縮而形成 高溫之冷媒和在上述第1再熱器被供應於一次空氣之預備 冷卻而升溫後之除濕空氣進行熱交換，因此可減少冷凍式 空氣乾燥機中的冷凝器之交換熱量Q3，亦即減少來自冷 凝器之排熱量，而以較少的電力發揮較大的除濕效果，例 如減少對於空冷冷凝器之空調機、水冷冷凝器之冷卻塔或 冷卻裝置等設備環境之冷熱源之熱負荷，而可節省能源進 -11 - 201020482 行運轉。又，不僅即使在欲除濕之壓縮空氣的負荷大之情 形下，仍可穩定地除濕，即使在上述壓縮空氣的空氣溫度 低之情形下，仍可確實地防止在送出至外部的除濕後之壓 縮空氣的出口配管產生的結露。 【實施方式】 第1圖係關於本發明之冷凍式空氣乾燥機的實施例。 本實施例之冷凍式空氣乾燥機和上述第2圖之以往的冷凍 © 式空氣乾燥機，具備一部分共通之冷媒系統和空氣系統， 因此第1圖中，針對與第2圖共通的構件，賦予附加在第 2圖之構件的符号相同之符號。本實施例和第2圖之以往 的冷凍式空氣乾燥機之主要相異點，係本實施例中，利用 第1再熱器18及第2再熱器19謀求減少消耗電力，而且 實現冷凍式空氣乾燥機穩定的稼働之點。 第1圖之冷凍式空氣乾燥機中的冷媒系統係具有：冷 媒壓縮機10;使藉由該冷媒壓縮機10壓縮後，從高溫冷 ® 媒配管22通過第2再熱器19被傳送的高溫冷媒進行凝縮 之冷凝器11;將藉由該冷凝器11凝縮後的冷媒，藉由隔 熱膨脹使其減壓形成低溫之膨脹閥12;及將利用空氣系 統的第1再熱器18進行預備冷卻後的空氣，藉由來自該 膨脹閥12的低溫冷媒再冷卻並除濕之冷卻器13;且來自 該冷卻器13的冷媒通過反饋冷媒配管26返回上述冷媒壓 縮機1〇。 此外，上述膨脹閥12係作爲上述減壓機構之一例而 -12- 201020482 顯示者’取代該膨脹閥，尙可利用例如毛細管等。 另一方面，該冷凍式空氣乾燥機的空氣系統係具有： 除濕對象之溫熱且濕潤的壓縮空氣（額定溫度4 (TC )作 爲一次空氣流入之空氣入口 20;藉由將從該空氣入口 20 流入的一次空氣和來自上述冷卻器13的低溫除濕空氣進 行熱交換之方式，將上述一次空氣進行預備冷卻，並且使 上述除濕空氣升溫之上述第1再熱器18;將利用該第1 φ 再熱器18進行預備冷卻後的空氣，藉由上述冷媒再冷卻 使其凝縮之上述冷卻器1 3 ;將利用該冷卻器1 3再冷卻後 的空氣進行排水分離，於呈低溫之除濕空氣（約1(TC) 狀態，送到上述第1再熱器18之排水分離器16;及將藉 由在上述第1再熱器18與溫熱的上述一次空氣進行熱交 換之方式，使升溫後的上述除濕空氣，藉由與高溫冷媒之 熱交換而再升溫之上述第2再熱器19;且使利用該第2 再熱器19再升溫後的除濕空氣，作爲二次空氣從出口配 Ο 管2 1流出至外部。 因而，上述冷卻器13和第2再熱器19係連接在上述 冷媒系統和空氣系統兩方，該等冷媒系統和空氣系統係以 功能性結合者。 在進行上述排水分離的排水分離器1 6設有排水閥1 5 ，其係用於分離產生的水滴並排出至外部。 上述第2再熱器19係配設在冷媒壓縮機1〇和冷凝器 1 1之間；其係用於將利用該冷媒壓縮機1 0被壓縮而形成. 高溫之冷媒、和利用第1再熱器18—旦被升溫後通過空 -13- 201020482 氣配管28被傳送來的除濕空氣，藉由利用它們的溫度差 進行熱交換之方式，使該除濕空氣再升溫者。因而，在該 第2再熱器19設有：將利用上述冷媒壓縮機10被升溫後 的冷媒送入之高溫冷媒配管22、和將藉由與該冷媒進行 熱交換的方式而升溫後的除濕空氣朝外部送出之上述出口 配管21。 上述冷凍式空氣乾燥機中的冷媒系統及空氣系統中的 各部之冷媒或壓縮空氣之溫度，係除了上述出口配管21 Q 中的壓縮空氣（二次空氣）之溫度爲大約45 °C之處以外 ，大致與上述第2圖之以往的冷凍式空氣乾燥機的情形相 同，但它們的溫度穩定性有很大的差異。 連結上述冷媒壓縮機1〇和第2再熱器19之高溫冷媒 配管22、和連結膨脹閥12和冷卻器13之低溫冷媒配管 23，係以支路冷媒配管25而被連通’該支路冷媒配管25 具備可調節打開度的容量調整閥17。該支路冷媒配管25 係於上述冷卻器13的負荷變小時’用於爲了避免因來自 © 膨脹閥1 2通過低溫冷媒配管23流到冷卻器1 3的冷媒之 溫度過度降低，以致於從第1再熱器18通過空氣配管24 流到冷卻器13的濕潤空氣中之水分凍結’而將容量調整 閥17僅打開必要量，使來自冷媒壓縮機的高溫冷媒之 一部分，在上述第2再熱器19和冷凝器11和膨脹閥12 迂迴，並混入低溫冷媒配管23中的低溫冷媒’將該低溫 冷媒的溫度保持成不會降低至一定溫度以下者。因而’該 支路冷媒配管25係進行調節流過上述第2再熱器19和冷Ql = heat exchanged by the cooler 13 (heat entering the refrigeration circuit) Q2 = power consumption of the refrigerant compressor 10 (the operation of the refrigerant compressor compressing the refrigerant is converted into heat) 201020482 Q3 = heat exchanged by the condenser 11 (released from the refrigeration circuit) When hot), the following formula (1) holds. Q3 = Q1 + Q2 --- (1) The condenser 11 condenses the refrigerant by air cooling or water cooling, but the lower the temperature of the refrigerant at the outlet of the condenser 11, the more the Φ power consumption Q2 of the refrigerant compressor 10 small. Further, the heat exchange amount Q1 of the cooler 13 corresponding to the cooling capacity of the refrigerating air dryer, the temperature around the condenser in the case of the air-cooling condenser, and the temperature of the cooling water in the case of the water-cooled condenser are determined. The performance of the condenser 11 has also been determined. Therefore, if the power consumption of the refrigerating air dryer is substantially equal to the power consumption of the refrigerant compressor 10, in order to reduce the temperature of the refrigerant at the outlet of the condenser 11 to reduce the power consumption Q2 of the refrigerant compressor 1 ,, the condenser 1 must be reduced. 1 exchange heat Q3. SUMMARY OF THE INVENTION A technical problem of the present invention is to provide a method for substantially reducing the heat exchange amount Q3 of a condenser in the refrigerating air dryer by effectively utilizing the energy in the conventional refrigerating air dryer described above. Even if the amount of heat discharged from the condenser is reduced, a large dehumidification effect is exerted by using less electric power, thereby achieving a energy-saving refrigerating air dryer. A more specific technical object of the present invention is to provide stable dehumidification even when the load of the compressed air to be dehumidified is large (the temperature of the compressed air, the humidity of the -9-201020482 is high, or the flow rate is high). Further, even in the case where the temperature of the primary air is low, it is possible to reliably prevent the refrigerating air dryer for causing dew condensation of the outlet pipe through which the dehumidified secondary air flows out to the outside. In order to solve the above problems, according to the present invention, there is provided a refrigerating air dryer comprising: a refrigerant system comprising: a refrigerant compressor; and a condenser that condenses the high temperature refrigerant compressed by the refrigerant compressor; After the condenser is condensed, the refrigerant of the refrigerant is decompressed by thermal expansion to form a low-temperature pressure-reducing mechanism; and the air cooled by the first reheater of the air system is preliminarily cooled by the pressure reducing mechanism. a cooler for re-cooling and dehumidifying the low-temperature refrigerant; configured to return the refrigerant from the cooler to the refrigerant compressor; and an air system having: an air inlet into which the warm and humid compressed air of the dehumidification object flows as primary air; a first reheater that preliminarily cools the primary air and raises the enthalpy dehumidified air by exchanging heat between the primary air flowing in from the air inlet and the low-temperature dehumidified air sent from the cooler; and The primary air after preliminary cooling by the first reheater is cooled by decooling to form a low temperature The above-mentioned cooler for dehumidifying air. Then, the refrigerating air dryer includes a second reheater that cools the dehumidified air by heat exchange between the first reheater and the primary air, and is compressed by the refrigerant compressor. The high-temperature refrigerant is subjected to heat exchange, and the dehumidified air which has been further heated by heat exchange in the second reheater is used as secondary air, and is output from the outlet pipe -10 · 201020482. The second reheater is connected between the refrigerant compressor and the condenser, and the refrigerant from the refrigerant compressor is sent to the condenser via the second reheater. Further, the high-temperature refrigerant pipe connecting the refrigerant compressor and the second reheater, and the low-temperature refrigerant pipe connecting the pressure reducing mechanism and the cooler, or the reverse of the cooler and the refrigerant compressor may be configured The refrigerant feed pipe is connected to the branch refrigerant pipe having the capacity adjustment valve having an adjustable opening degree, and when the load of the cooler is small, a part of the high-temperature refrigerant compressed by the refrigerant compressor is directly used. The flow to the above-mentioned low-temperature refrigerant piping or feedback refrigerant piping. In the present invention, it is expected that a flow separator for separating and draining air cooled by the cooler from the flow path from the cooler to the first reheater is provided. In the refrigerating air dryer of the present invention having the above configuration, the first reheater and the second reheater are used for the primary reheater and the primary air flowing in from the air inlet and through the cooling. Heat exchange is performed by the low-temperature dehumidified air of the apparatus, and the second reheater is a refrigerant that is compressed by a refrigerant compressor to form a high temperature, and a dehumidified air that is heated by pre-cooling of the first reheater to supply primary air. Heat exchange is performed, thereby reducing the exchange heat Q3 of the condenser in the refrigerating air dryer, that is, reducing the heat removal from the condenser, and exerting a large dehumidification effect with less power, for example, reducing the air cooling condenser The heat load of the cold and heat source of the equipment environment such as the air conditioner, the cooling tower of the water-cooled condenser or the cooling device can save energy and operate in the line - 2010-20482. Further, not only can the dehumidification be stably performed even in the case where the load of the compressed air to be dehumidified is large, and even after the air temperature of the compressed air is low, the decompression after being sent to the outside can be surely prevented from being compressed. Condensation from the outlet piping of the air. [Embodiment] Fig. 1 is an embodiment of a refrigerating air dryer according to the present invention. The refrigerating air dryer of the present embodiment and the conventional refrigerating air dryer of the second embodiment have a part of a common refrigerant system and an air system. Therefore, in the first drawing, the member common to the second drawing is given. The symbols attached to the components of Fig. 2 are the same symbols. The main difference between the present embodiment and the conventional refrigerating air dryer of Fig. 2 is that in the present embodiment, the first reheater 18 and the second reheater 19 are used to reduce power consumption, and the refrigerating type is realized. The point where the air dryer stabilizes the crop. The refrigerant system in the refrigerating air dryer of Fig. 1 includes a refrigerant compressor 10, and a high temperature that is passed through the second reheater 19 from the high-temperature cold refrigerant supply pipe 22 after being compressed by the refrigerant compressor 10. The condenser 11 is condensed by the refrigerant; the refrigerant condensed by the condenser 11 is decompressed by thermal expansion to form a low temperature expansion valve 12; and the first reheater 18 using the air system is prepared. The cooled air is cooled and dehumidified by the low-temperature refrigerant from the expansion valve 12, and the refrigerant from the cooler 13 is returned to the refrigerant compressor 1 through the feedback refrigerant pipe 26. Further, the expansion valve 12 is an example of the above-described pressure reducing mechanism, and the display valve is replaced by, for example, a capillary tube or the like. On the other hand, the air system of the refrigerating air dryer has: warm and humid compressed air for the dehumidification object (rated temperature 4 (TC) as the air inlet 20 for the primary air inflow; from the air inlet 20 The primary air is preliminarily cooled by the heat exchange between the primary air flowing in from the cooler 13 and the low temperature dehumidified air from the cooler 13, and the first reheater 18 that raises the dehumidified air is heated; the first φ is used again. The heat device 18 performs pre-cooled air, and the chiller 13 is condensed by the refrigerant, and the air cooled by the cooler 13 is drained and separated to dehumidify air at a low temperature. In the 1 (TC) state, the drain separator 16 is sent to the first reheater 18; and the heat is exchanged between the first reheater 18 and the warm primary air. The dehumidified air is heated by the heat exchange with the high-temperature refrigerant to reheat the second reheater 19; and the dehumidified air heated by the second reheater 19 is used as a secondary air from the outlet distribution pipe. 2 1 flows out to the outside. Therefore, the cooler 13 and the second reheater 19 are connected to both the refrigerant system and the air system, and the refrigerant system and the air system are functionally combined. The drain separator 16 is provided with a drain valve 15 for separating the generated water droplets and discharging them to the outside. The second reheater 19 is disposed between the refrigerant compressor 1A and the condenser 1 1; It is used to form a high-temperature refrigerant by the refrigerant compressor 10, and a dehumidified air that is transported through the air-13-201020482 gas pipe 28 after the first reheater 18 is heated. The dehumidified air is heated again by heat exchange using the temperature difference between them. Therefore, the second reheater 19 is provided with a high-temperature refrigerant that feeds the refrigerant heated by the refrigerant compressor 10 The piping 22 and the outlet pipe 21 that is sent to the outside by the dehumidified air heated by the heat exchange with the refrigerant. The refrigerant system in the refrigerating air dryer and the refrigerant or pressure in each part of the air system The temperature of the air is substantially the same as that of the conventional refrigerating air dryer of Fig. 2 except that the temperature of the compressed air (secondary air) in the outlet pipe 21 Q is about 45 °C. The temperature stability of the refrigerant compressor 1〇 and the second reheater 19 and the low-temperature refrigerant piping 23 connecting the expansion valve 12 and the cooler 13 are branched. The refrigerant pipe 25 is connected. The branch refrigerant pipe 25 is provided with a capacity adjustment valve 17 that can adjust the degree of opening. The branch refrigerant pipe 25 is charged with the load of the cooler 13 "for use in order to avoid the valve from the expansion valve. 1 2 The temperature of the refrigerant flowing to the cooler 13 through the low-temperature refrigerant pipe 23 is excessively lowered, so that the water flowing from the first reheater 18 through the air pipe 24 to the humid air of the cooler 13 freezes, and the capacity is adjusted. The valve 17 is opened only by a necessary amount, and a part of the high-temperature refrigerant from the refrigerant compressor is bypassed by the second reheater 19, the condenser 11, and the expansion valve 12, and mixed into the low-temperature refrigerant pipe 23 for low-temperature cooling. 'Maintaining the temperature of the refrigerant into a low temperature does not decrease to a temperature of age. Therefore, the branch refrigerant pipe 25 is regulated to flow through the second reheater 19 and the cold
-14- 201020482 凝器11和膨脹閥12之冷媒的流量之動作者，藉由該流量 調節，可防止上述第2再熱器19中的除濕空氣之過度再 升溫。 此外，上述支路冷媒配管25亦可連接在上述高溫冷 媒配管22、和連結上述冷卻器13和上述冷媒壓縮機1〇 之反饋冷媒配管26。於該情形下，藉由流過冷卻器13的 冷媒之流量減少的方式，可獲得與上述情形同樣的效果， ® 亦即獲得防止利用該冷卻器13冷卻的空氣中之水分凍結 的效果。 爲了與上述第2圖之以往的冷凍式空氣乾燥機中的主 要各部分之能源輸出入關係做對比，顯示關於第1圖之實 施側之同樣的能源輸出入關係時， 第1圖中，若設定Q1-Q3和第2圖的情形同樣， 設定Q4 =第2再熱器19的交換熱量（從冷凍電路將 熱釋出至壓縮空氣），則 ❹ Q3+Q4=Q1+Q2 Q3=Q1 + Q2-Q4 . . · ( 2 ) 比較上述式（1)和式（2)時，第1圖之冷凍式空氣 乾燥機較第2圖之以往的冷凍式空氣乾燥機，熱量Q3只 少了熱量Q4，然後，因爲熱量Q3變小，同時地熱量Q2 也變小，因此得知較爲節省能源。 此外，從冷凍式空氣乾燥機排出之熱，係利用空調機 -15- 201020482 、冷卻瘩、冷卻裝置等溫度管理設備予以處理。 藉由具有這種構成的冷凍式空氣乾燥機’由於可達到 如上述之節省能源化，因此可用較少的電力發揮大的除濕 效果，具體例爲可減少冷凝器的交換熱量（來自冷凝器的 排熱量），因此可減少對於冷熱源（空冷冷凝器爲空調機 、水冷冷凝器爲冷卻塔或冷卻裝置等）之熱負荷。且即使 被供給的濕潤壓縮空氣之負荷大的情形下，仍可穩定地除 濕，提高冷凍式空氣乾燥機之性能，當負荷大的時候，冷 凍機的保護繼電器作動，可增加稼働停止的界限負荷。再 者’可確實地防止空氣乾燥機的二次側之空氣配管結露。 【圖式簡單說明】 第1圖係關於本發明之冷凍式空氣乾燥機的實施例之 冷凍電路及壓縮空氣電路之電路圖。 第2圖係習知之冷凍式空氣乾燥機的冷凍電路及壓縮 空氣電路之電路圖。 【主要元件符號說明】 10 :冷媒壓縮機 11 :冷凝器 12 :膨脹閥 13 :冷卻器 14、18 :第1再熱器 1 5 :排水閥 -16 - 201020482 1 6 :排水分離器 1 7 :容量調整閥 19 :第2再熱器 20 :空氣入口 21 :出口配管 22 :高溫冷媒配管 23 :低溫冷媒配管 φ 24、28:空氣配管 25 :支路冷媒配管 26 :反饋冷媒配管-14- 201020482 The flow rate of the refrigerant flow of the condenser 11 and the expansion valve 12 can prevent excessive de-heating of the dehumidified air in the second reheater 19 by the flow rate adjustment. Further, the branch refrigerant pipe 25 may be connected to the high-temperature refrigerant pipe 22 and the feedback refrigerant pipe 26 that connects the cooler 13 and the refrigerant compressor 1〇. In this case, the same effect as described above can be obtained by reducing the flow rate of the refrigerant flowing through the cooler 13, i.e., the effect of preventing freezing of moisture in the air cooled by the cooler 13 is obtained. In comparison with the energy input/output relationship of the main parts in the conventional refrigerating air dryer of the above-mentioned Fig. 2, when the same energy input/output relationship on the implementation side of Fig. 1 is displayed, in Fig. 1, Similarly, in the case of setting Q1-Q3 and Fig. 2, Q4 = exchange heat of the second reheater 19 (release of heat from the refrigeration circuit to compressed air) is set, then ❹ Q3 + Q4 = Q1 + Q2 Q3 = Q1 + Q2-Q4 . . . ( 2 ) When the above formula (1) and formula (2) are compared, the refrigerating air dryer of Fig. 1 has less heat than the conventional refrigerating air dryer of Fig. 2 Q4, then, because the heat Q3 becomes smaller, and the ground heat Q2 also becomes smaller, it is known that energy is saved. In addition, the heat discharged from the refrigerating air dryer is treated by temperature management equipment such as air conditioners -15- 201020482, cooling crucibles, and cooling devices. With the refrigerating air dryer having such a configuration, since the energy saving as described above can be achieved, a large dehumidification effect can be exerted with less electric power, and specific examples can reduce the exchange heat of the condenser (from the condenser) Exhaust heat), so the heat load for the cold heat source (the air-cooled condenser is an air conditioner, the water-cooled condenser is a cooling tower or a cooling device, etc.) can be reduced. Moreover, even if the load of the humidified compressed air supplied is large, the dehumidification can be stably performed, and the performance of the refrigerating air dryer can be improved. When the load is large, the protection relay of the refrigerating machine acts to increase the limit load of the stop of the crucible. . Furthermore, it is possible to reliably prevent condensation of the air piping on the secondary side of the air dryer. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a circuit diagram of a refrigeration circuit and a compressed air circuit in an embodiment of a refrigerating air dryer of the present invention. Fig. 2 is a circuit diagram of a refrigeration circuit and a compressed air circuit of a conventional refrigerating air dryer. [Description of main components] 10: Refrigerant compressor 11 : Condenser 12 : Expansion valve 13 : Cooler 14 , 18 : 1st reheater 1 5 : Drain valve - 16 - 201020482 1 6 : Drain separator 1 7 : Capacity adjustment valve 19: 2nd reheater 20: Air inlet 21: Outlet piping 22: High-temperature refrigerant piping 23: Low-temperature refrigerant piping φ 24, 28: Air piping 25: Branch refrigerant piping 26: Feedback refrigerant piping
Ql、Q3、Q4 :交換熱量 Q2 :消耗電力、熱量 -17Ql, Q3, Q4: exchange heat Q2: power consumption, heat -17