1257472 (1) 九、發明說明 【發明所屬之技術領域】 本發明是有關使用兩段壓縮式可變壓縮機的冷藏庫， 特別是根據儲藏空間內溫度決定壓縮機迴轉數的冷藏庫。 【先前技術】 近年來，大多數的冷藏庫搭載著可藉由變頻控制來變 換冷凍能力的壓縮機，藉由可變換其冷凍能力，可獲得因 應負何的冷卻性能並降低消費電力。 一般來說，普遍的家用冷藏庫具有：可冷卻至-18〜 -2 0 °C左右的冷凍空間、可保持+ 1〜+ 5 °C左右之冷藏和蔬 果保存空間，利用單一冷卻器對雙方空間進行冷卻的冷藏 室，是利用傾卸裝置（dumper )來控制對冷凍及冷藏空間 的冷氣流分配，並因應整體的負荷來驅動或停止壓縮機’ 而利用變頻控制的冷藏庫，可進一步藉由控制壓縮機的迴 轉數使上述雙方儲藏空間保持一定的溫度。 此外，冷凍及冷藏空間分別具有冷卻器的冷藏庫，是 利用切換冷媒的流路來分配控制冷媒流向配置於前述各冷 卻空間內的冷卻器，並對應於冷卻空間的整體溫度和溫度 差等來控制壓縮機。 另外，現今市場上用於冷凍冷藏庫的冷媒壓縮機’於 壓縮機殼內存在單一壓縮部，也就是所謂的一段壓縮方式 ，近年來公開一種兩段壓縮冷凍冷藏裝置的技術思想’如 第1 3圖所示，在密閉容器內設有具備馬達、低段壓縮元 -5- (2) (2)1257472 件（39a )、高段壓縮元件（39b )的兩段壓縮機（39 )， 在連接來自高段壓縮元件（39b )的冷凝器（40 )之排出 管（46 )出口側連接有中間壓膨脹裝置（43 )，連通低段 側壓縮元件（3 9a )的排出側及高段側壓縮元件（3 9b )的 吸入側與中間壓用吸入管（4 7 )，在該中間壓用吸入管（ 47 )與前述中間壓用膨脹裝置（43 )之間連接著中間壓用 蒸發器（3 5 )，並在抵接於冷凝器（40 )出口側的低壓用 膨脹裝置（42 )與兩段壓縮機之低段壓縮元件吸入側之間 連接著低壓用蒸發器（34)，藉由使低段壓縮元件（39a )的排出側與高段壓縮元件（39b )的吸入側連通於密閉 容器（39)內，可提高庫內溫度控制的精確度，並達成庫 內各部溫度的均一化、高效率化及低消費電力化（請參考 專利文獻1 )。 【專利文獻1】 日本特開200 1 -743 25號公報 【發明內容】 〔發明欲解決之課題〕 上述專利文獻1所記載的冷凍循環，是藉由使作爲冷 藏用冷卻器之中間壓用蒸發器（3 5 )的蒸發溫度高於作爲 冷凍用冷卻器之低壓蒸發器（34)的蒸發溫度，來提高循 環效率。由於兩段壓縮循環之冷凍用冷卻器（3 4 )的吸入 管是直接連結於壓縮機的低段側壓縮部（3 9a )，而冷藏 用冷卻器（3 5 )的吸入管（4 7 )是連接於中間壓部，因此 -6- (3) (3)1257472 冷凍空間的冷凍能力不易受到流向冷藏用冷卻器的冷媒影 響’在根據冷凍側負荷與冷藏側負荷之總負荷來控制壓縮 機迴轉數的傳統方法中，舉例來說，當冷凍空間之冷卻度 充足而冷藏空間卻過度冷卻時，會降低壓縮機的迴轉數， 而導致冷凍空間產生冷卻不足的問題。 本發明便是有鑑於上述問題所硏發的發明，本發明的 目的是提供一種：根據冷凍空間溫度資訊，對具有冷凍用 及冷藏用冷卻器之兩段壓縮式可變冷凍循環進行控制，而 可分別將冷凍空間及冷藏空間控制在適當溫度的冷藏庫。 〔解決課題之手段〕 爲了解決上述的課題，本發明的冷藏庫，是由：由低 段側壓縮部與高段側壓縮部構成壓縮元件，且可藉由變頻 控制改變能力的壓縮機；和設置在可接受上述壓縮機所排 出之氣體的冷凝器出口側，並可控制冷媒流路與流量的切 換閥；及經由個別的減壓裝置連接於上述切換閥之冷凍用 冷卻器與冷藏用冷卻器所構成的冷凍循環之冷藏庫，其特 徵爲··是根據冷凍空間溫度與其目標値來決定前述壓縮機 的迴轉數。 申請專利範圍第2項所記載的冷藏庫’是由：由低段 側壓縮部與高段側壓縮部構成壓縮元件’且可藉由變頻控 制改變能力的壓縮機；和設置在可接受上述壓縮機所排出 之氣體的冷凝器出口側，並可控制冷媒流路與流量的切換 閥；及經由個別的減壓裝置連接於上述切換閥之冷凍用冷 (4) 1257472 卻器與冷藏用冷卻器所構成的冷凍循環之冷藏庫，其特徵 爲：是根據冷凍空間溫度及其目標値、與冷藏空間溫度及 其目標値來決定壓縮機的迴轉數，當決定迴轉數之際，冷 藏空間之溫度資訊的回饋量是大於冷凍空間之溫度資訊的 回饋量。 〔發明的效果〕 根據上述的構成方式，不僅可因應各儲藏空間的冷卻 來提高冷凍用及冷藏用冷卻器雙方的蒸發溫度也就是冷凍 循環的效率，並可切換冷媒朝各冷卻器的流路及流量，更 可藉由同時冷卻冷凍空間及冷藏空間的方式來抑制各空間 內的溫度變動，而適當地控制各空間的溫度。 【實施方式】 以下，根據圖面說明本發明的1種實施形態。第2圖 之縱剖面圖所示的冷藏庫本體（1 )，是於斷熱箱體的內 部形成儲藏空間，並藉由分隔壁區分成冷凍室和製冰室的 冷凍空間（2 )、冷藏室和蔬果室的冷藏空間等複數個儲 藏室。 各儲藏室，是藉由配置於每個冷凍空間和冷藏空間的 冷凍用冷卻器（4)與冷藏用冷卻器（5)、及冷氣循環風 扇（6 ) 、( 7 )，而分別冷卻保持一定的設定溫度，各冷 卻器（4 ) 、 ( 5 )，是藉由設置於本體背面下方之機械室 (8 )的壓縮機（9 )所供應的冷媒進行冷卻。 -8- (5) (5)1257472 第1圖，是顯示本發明上述冷藏庫內的冷凍循環’前 述壓縮機（9 )、冷凝器（1 0 )、冷媒流路的切換閥（1 1 )及形成並列連接的前述冷凍用與冷藏用冷卻器（4) ' (5 )是連結成環狀。前述的冷凝器（1 0 )是配設在冷藏 庫本體（1 )的外底面空間，而該冷藏庫本體（1 )是位於 形成平板狀之前述機械室（8 )的前方，由冷凝器（1 〇 ) 所液化的冷媒是通過切換閥（1 1 )後，分別經由作爲減壓 裝置的毛細管（1 2 )、（ 1 3 )而供給製冷凍用冷卻器（4 )及冷藏用冷卻器（5 )，並藉由蒸發的方式使冷卻器形 成低溫化，藉由冷卻風扇（6 ) 、（ 7 )的循環使儲藏室內 冷卻至一定的空氣溫度，蒸發汽化後的冷媒’是經由蓄壓 器（14 )在度回到壓縮機（9 )。 壓縮機（9 )，其詳細如第3圖所示，是由低段側壓 縮部（9a)與高段側壓縮部（9b)構成壓縮元件的往復式 (r e c i p r 〇 c a 1 )兩段壓縮機，並構成藉由偏心軸（9 f )使 連桿（9g)形成往復運動，而該偏心軸（9〇是藉由收納 於密閉外殼（9c )內的電動機構（9d )之迴轉軸（9e )的 迴轉於形成偏心後轉動。 活塞（9i )是利用球關節（9h )鑲嵌固定於連桿（9g )的前端，藉由活塞（9 i )於汽缸（9 j )內的往復運動使 前述低段側壓縮部（9a )與高段側壓縮部（9b )交互吸入 冷媒，並於壓縮後排出，藉由對上述壓縮部採用球關節（ 9 h )，可提高容積效率，並抑制需要兩個壓縮部（9 a )、 (9b )的兩段壓縮機（9 )之外形空間的擴大。 -9- (6) 1257472 低段側壓縮部（9a )的吸入口（ 9k )連接著吸入 1 5 )的端部，該吸入管（1 5 )是經由蓄壓器（1 4 )連 前述冷凍用冷卻器（4 )，用來排出壓縮後之冷媒氣 排出口 （ 9 m )，是朝外殼（9 c )的內部形成開口， 側壓縮部（9b )的排出口則連結於朝向冷凝器（1 〇 ) 出管（1 6 )。 前述蓄壓器（1 4 )的作用，是儲存氣液分離後冷 (4 )所未完全蒸發的液態冷媒並僅排出氣態冷媒， 止因液態冷媒流入壓縮機（9 )的汽缸（9j )所造成 障，在本實施例中，僅設置於冷凍用冷卻器（4 )的 〇 來自於上述冷藏用冷卻器（5 )的吸入管（1 7 ) 導入連接於密閉外殼（9c )內可形成中間壓的空間部 此，由於來自冷藏用冷卻器（5 )的吸入冷媒不會直 入壓縮機的汽缸內，因此不必特別於冷藏冷卻器（5 後段設置蓄壓器，當設置蓄壓器時也只需設置小型蓄 。接著，由冷藏用冷卻器側之吸入管（1 7 )所吸入的 氣體，與被前述逼段側壓縮部（9a )之排出口（ 9m 排出的冷媒氣體，一起被形成連通之高段側壓縮部（ 的吸入口（ 9p )吸入形成壓縮。 上述壓縮機（9 )，可藉由變頻控制形成能力變 根據冷凍及冷藏空間所測得的溫度和設定目標間的差 溫度變化率等，舉例來說，將迴轉週波數設定爲 7 0Hz，並利用微處理器所構成的控制裝置形成運轉。 管（ 結於 體的 局段 的排 卻器 可防 的故 後段 ，是 。據 接流 )的 壓器 冷媒 )所 9b ) 化， 値、 30〜 -10- (7) 1257472 切換閥（11 )，是設置在承接來自於壓縮機（9 )之 排出氣體的冷凝器（10)出口側’可切換朝冷卻器（4) 、（5 )側的冷媒流路並控制流量，如第4圖所示，在閥 殼（1 8 )內設有閥座（1 9 )，閥座（1 9 )上形成有通往冷 凍用冷卻器（4 )側的閥口 A ( 1 9a )及通往冷藏用冷卻器 (5 )側的閥口 B ( 1 9b )，並在閥座（1 9 )的上方設置閥 體（2 0 )的三向閥。 閥體（20 )在成形爲特定端緣形狀之厚壁段部（20d )的下面形成有2處剖面呈V字型的凹溝A ( 20a)及凹 溝B(20b)，該凹溝A(20a)及凹溝B(20b)是以迴轉 軸（20c )爲中心且採不同的迴轉移動半徑，分別對應於 上述閥口 A ( 19a)與閥口 B ( 19b )而在迴轉軌跡上遍佈 一定長度延伸成圓弧狀，一邊使閥座（1 9 )的頂面與閥體 (20 )形成緊密重疊，一邊利用圖面中未標示之設置於上 部的步進馬達以〇〜80的脈衝步進形成迴轉驅動。 該切換閥（1 1 )’可根據冷凍循環控制訊號所形成的 脈衝訊號使閥體（2 0 )產生迴轉，當於特定的脈衝位置使 位於上述閥體迴轉外側的凹溝A ( 2 0 a )與閥口 A ( 1 9 a ) 上下重疊而連通時’從流入閥口（ 2 1 )流入閥殻（丨8 )內 的冷媒，將會由凹溝A ( 2 0 a )位於前述厚壁段部（2 〇 d ) 側的開放端緣進入V字型的凹溝a ( 20a )內，並由連通 於凹溝A的閥口 A ( 1 9a )流出後導入冷凍用毛細管（j 2 )’而由冷凍用冷卻器（4)蒸發汽化。 另外，與上述相同，當連通迴轉半徑內側的凹溝B ( -11 - (8) 1257472 2 0 b )與閥口 B ( 1 9 b )時，流入凹溝b ( 2 0 b )的冷媒， 是從形成連通的閥口 B ( 1 9b )流入冷藏用毛細管（1 3 ) 後由冷藏用冷卻器（5)蒸發。 此外，位於冷藏側的凹溝B ( 2 0 b )，其 V字型溝的 剖面積是隨著從迴轉前端朝向厚壁段部（20d )的開放端 而形成擴大，藉由閥體（2 0 )的迴轉，從最小變成最大的 流通開口面積而連通閥口 B ( 1 9b )，由於流路切換和流 量調整可精密的控制，故可有效率地藉由脈衝的迴轉控制 將冷媒流量變更成線性。 三向閥（20 )之閥的開放控制，雖然流向冷凍用冷卻 器（4 )與冷藏用冷卻器（5 )之閥口（ 19a ) 、（ 19b )的 開口大小可選擇雙方全開、全關、冷凍側開口縮小而冷藏 側全開、或冷藏側開口縮小而冷凍側全開等共種組合，但 在本實施例中，冷凍用冷卻器（4 )與冷藏用冷卻器（5 ) 是形成並列連接，所以冷卻控制是形成冷凍冷藏側同時冷 卻及僅冷卻冷凍側的2種。 從冷凍側閥口 A ( 1 9a )流出的冷媒，通過位於冷凍 空間（2 )內設定成冷卻溫度也就是蒸發溫度的毛細管（ 12 )而形成減壓，並於冷凍冷卻器（4 )以-25 °C左右的溫 度蒸發，而來自於冷藏用閥口 B(19b)的冷媒，也同樣 地通過位於冷藏空間（3 )內設定成接近冷卻溫度（-5 °C 左右）也就是蒸發溫度的冷藏用毛細管（1 3 )後’送入冷 藏用冷卻器（5)形成蒸發。 而位於上述冷凍循環內的冷凍用及冷藏用毛細管（1 2 -12- (9) (9)1257472 )、（13) ’由於冷凍用冷卻器（4)與冷藏用冷卻器（5 )的冷媒蒸發溫度具有溫度差，一旦強力縮小冷凍側毛細 管（1 2 )的結果，當在如上所述冷媒流向冷凍冷藏雙方的 狀況中’必然是形成容易流向低抗較小的冷藏側，且不易 流向冷凍側的傾向，在極端的場合中將產生冷媒無法流入 冷凍側的狀況。 爲了改善上述的問題，在上述切換閥（1 1 )中，對用 來冷卻冷凍及冷藏空間（2 )、（ 3 )冷卻之冷媒流動的進 行控制，並爲了防止冷媒的單向流動，加入限制冷媒朝容 易流入之冷藏側的流量控制。 倘若冷凍側的凹溝A ( 20a)與閥口 A ( 19a)間連通 且形成全開時，幾乎不受冷藏側之冷媒流動狀態影響的冷 凍側冷卻器（4 )，幾乎可獲得預定的冷凍能力，即使是 冷藏側的冷凍能力，也能根據上述切換閥（1 1 )之凹溝B (2 0b )與閥口 B ( 1 9b )間的連通狀態所形成之全閉到全 開的範圍、及壓縮機（9 )的迴轉數變化作出細微的控制 〇 藉由上述的冷媒流動控制，可提高冷藏用冷卻器（5 )之蒸發溫度與冷凍側的溫度差’進而可將冷藏室溫冷卻 至1〜2°C，倘若增加冷藏用冷卻器（5)之傳熱表面積而 增加對冷藏空間冷卻的熱交換量’可更進一步提高蒸發溫 度，在上述的場合中，進一步縮小冷藏空間（3 )之冷卻 溫度與冷卻器溫度間的溫度差可降低附著於冷藏用冷卻器 (5 )之霜的數量，可達到防止空間內乾燥並保持庫內高 -13- (10) 1257472 溼度的效果。 此外，在一般的家用冷藏庫中，由於冷凍空間與冷藏 空間之冷卻所需的冷凍能力大致相同，故可藉由使冷藏用 冷卻器（5)之傳熱表面積等於或大於冷凍用冷卻器（4) ，而有效率地對各冷卻空間進行冷卻。 接下來針對冷凍循環的動作進行說明。當輸入電源而 驅動壓縮機（9 )時，形成被壓縮成高溫高壓的冷媒氣體 ’將從排出管（1 6 )處被排出至冷凝器（1 〇 )後抵達切換 閥（1 1 )。切換閥（1 1 )可設定成上述的各種組合，當輸 入前述電源之際，由於冷凍、冷藏空間（2 ) 、（ 3 )均呈 未冷卻的狀態，因此閥口 A ( 1 9 a ) 、B ( 1 9 b )形成全開 狀態，冷媒將魚流入冷凍用及冷藏用毛細管（1 2 ) 、（ 1 3 )後，分別流入減壓的冷凍用及冷藏用冷卻器（4 ) 、（5 )而以各蒸發溫度形成蒸發，並將各冷卻器冷卻至一定溫 度。 來自於冷凍用冷卻器（4 )的冷媒將流入蓄壓器（1 4 )，當冷卻器中殘留未蒸發的液態冷媒時，殘留的冷媒將 貯留於蓄壓器（1 4 )內部，僅有氣體冷媒從吸入管（1 5 ) 被吸入壓縮機（9 )的低段側壓縮部（9a )。此外，於冷 藏用冷卻器（5 )蒸發的冷媒，是經由吸入管（1 7 )後導 入前述壓縮機（9 )之形成中間壓的密閉外殼（9 c )內。 從冷凍用冷卻器（4 )被吸入低段側壓縮部（9a )， 並從壓縮的排出口（ 9m )排出至外殼（9c )內的冷媒氣 體，與從冷藏用冷卻器（5 )流入密閉外殼（9c )之中間 -14 - (11) 1257472 壓部的冷媒氣體形成合流後，從吸入口（ 9 p )被吸入高段 側壓縮部（9 b )，再由壓縮的排出口（ 9 n )排出至排出管 (1 6 )後導入冷凝器（1 0 )而形成冷凍循環。 因此，根據上述的冷凍循環’設置有分別具備毛細管 (12) 、（13)的冷凍及冷藏用冷卻器（4) 、（5)，上 述毛細管（1 2 )、（ 1 3 )的蒸發溫度是配合冷凍空間與冷 藏空間各自的設定溫度，藉由令於冷藏用冷卻器（5 )蒸 發的冷媒氣體保持高於冷凍側壓力之中間壓的狀態’並直 接吸入壓縮機外殼（9 c )內的中間壓部’不僅可使冷藏用 冷卻器（5 )的蒸發溫度相較於冷凍用冷卻器（4 )高於室 內冷卻溫度，由於可降低壓縮機的輸入而提高循環效率’ 故可降低消費電力。 此外，藉由提高冷藏用冷卻器（5 )的蒸發溫度後將 縮小與冷藏空間之間的溫差，可減少附著於冷卻器（5 ) 的霜量，防止冷藏空間內的乾燥並保持庫內的高溼度’能 長時間保持食物的新鮮度，不僅如此，由於冷媒可同時流 入冷凍用及冷藏用冷卻器（4) 、（5)雙方並形成冷卻’ 相較於傳統的交互冷卻的方式可抑制各室內的溫度變動。 而冷凍循環如第5圖所示，第5圖中與第1圖相同的 部分是標示相同的圖號，冷凍用冷卻器（4 )與冷藏用冷 卻器（5 )是對上述壓縮機（9 )、冷凝器（1 〇 )、冷媒流 路的切換閥（1 1 )形成直列連接，從切換閥（1 1 )起作爲 冷藏用毛細管（13)與冷藏用冷卻器（5)之旁通路的旁 通管（2 2 )，是經由氣液分離器（2 3 )並從冷凍用毛細管 -15- (12) (12)1257472 (12)連接於冷凍用冷卻器（4)，並亦可藉由吸入管（ 24 )連接上述氣液分離器（23 )的上方與壓縮機（9 )之 密閉外殼（9c )內形成中間壓的中間壓部。 如此一來，冷媒可根據與上述控制方式相同的切換閥 (11)，同時或選擇性地流入冷藏用冷卻器（5 )及冷凍 用冷卻器（4)，來自於旁通管（22)或冷藏用冷卻器（5 )的冷媒，是於氣液分離器（23 )內分離成氣態冷媒與液 態冷媒，其中液態冷媒是流向冷凍用冷卻器（4 )側，氣 態冷媒則通過冷藏側吸入管（24 )回流至壓縮機（9 )的 中間壓部，且液態冷媒再度於冷凍用冷卻器（4 )以低溫 加以蒸發後回流至壓縮機（9 )的低段側，與上述實施例 同樣具有良好的循環效率，並達成可將各儲藏室內冷卻至 一定溫度的作用效果。 第6圖，是顯示將冷凍用冷卻器（4)及冷藏用冷卻 器（5 )的蒸發溫度、與冷凝器（1 0 )的冷凝溫度設成一 定値，且壓縮機（9 )以一定迴轉數運轉時冷凍側及冷藏 側的冷凍能力，其中縱軸爲冷藏側的冷凍能力，橫軸爲冷 凍側的冷凍能力。在該圖中，a點是表示藉由切換閥使冷 媒僅流向冷藏側冷卻器（5 )的場合，b點是表示使冷媒 僅流向冷凍側冷卻器（4 )的場合，c點則是在閥口（ 1 9 a )、（1 9b )全開的狀態下冷媒流向冷凍用及冷藏用冷卻 器（4 ) 、（ 5 )雙方的場合。 在該圖表中顯示，從冷凍用冷卻器（4 )被直接吸入 壓縮機（9 )之低段側壓縮部（9a )的冷媒質量或體積， -16- (13) 1257472 是取決於低段壓縮部的汽缸排除容積，相對應的冷 相較於僅流入冷凍側時的69W ’同時流入冷凍、冷 則爲64W，幾乎不受從冷藏用冷卻器（5 )回流至 (9 )之中間壓部的冷媒影響而形成一定値。 相對於此，冷藏側對應於從冷藏用冷卻器（5 入壓縮機（9 )之冷媒量的冷凍力’相較於僅流入 時的1 5 5 W，同時流入冷凍、冷藏側時則大幅下降； 左右，冷藏側的冷凍能力，會因爲是否從冷凍用冷 4 )吸入冷媒，也就是僅有來自於冷藏用冷卻器（5 媒、或者與從冷凍用冷卻器（4 )吸入之冷媒的合 產生極大的變化。 此外，相較於一般冷藏空間的室內溫度爲+3〜 由於冷凍空間溫度爲-1 8〜-2 0 °c，因此與室外溫度 差甚大，冷卻冷凍空間所需的冷凍能力’是大於冷 所需要的値，如此一來，當冷凍側的冷凍能力大於 的冷凍能力時，也就是當冷凍側的負荷設定成大於 時的冷凍運轉，是如採用第6圖模式來表現的第7 ，圖中斜線部分是代表冷凍側之冷凍能力大的部分 因此，如上所述地，由於冷凍側的冷凍能力不 從冷藏用冷卻器（5 )處回流之冷媒的影響，故冷 的冷卻控制，根據壓縮機（9 )的迴轉數進行控制 當冷卻不足時如箭號所不’提局壓縮機（9 )的迴 增加冷凍力，當過度冷卻時可藉由降低迴轉數或者 方式來保持適當的冷卻溫度。而冷藏側的控制則非 凍力， 藏側時 壓縮機 )被吸 冷藏側 g 75 W 卻器（ )的冷 流量而 v 5 〇C， 間的溫 藏空間 冷藏側 冷藏側 圖所示 〇 易受到 凍空間 即可， 轉數以 停止的 根據壓 -17- (14) 1257472 縮機（9 )的迴轉數，而是藉由控制切換閥（1 1 )之閥開 口的開閉來調整冷媒流量，並藉此控制其冷卻溫度。 接下來，根據第8圖所示的控制流程圖來說明本發明 之壓縮機迴轉數控制的一個實施例。由冷度感應器所測得 之冷凍空間，譬如冷凍室（4 )的室內溫度（Fa )，與特 定目標値（Fr )進行比較後，將其差値輸入用來決定壓縮 機周波數的PID控制器（2 5 )。 接下來，倘若冷凍空間（2 )的溫度高於目標値（Fr )，將根據差値來增加PID計算値，並藉由將壓縮機（9 )的迴轉數增加一定量來促進冷凍空間（2 )的冷卻，進 而導入一定溫度地執行運轉控制。此外，倘若冷凍空間（ 2 )的溫度低於目標値（Fr )，將降低迴轉數或者停止迴 轉來降低冷凍力。 接著，針對本發明之壓縮機迴轉數控制的其他實施例 作說明。雖然上述實施例是根據冷凍空間（2 )的溫度資 訊來控制壓縮機（9 )的迴轉數，但根據冷藏庫的運轉條 件，對冷凍空間（2 )而言有時認爲冷藏空間的冷凍能力 不足。 因此’輸入冷凍空間（2 )的溫度資訊及冷藏空間（3 )的溫度資訊使壓縮機（9 )在第7圖中的斜線範圍內運 轉的話’由於可提高壓縮機（9 )的迴轉數而增加冷凍能 力，故可增加冷凍空間（2 )及冷藏空間（3 )的冷凍能力 〇 但是’當冷凍空間冷卻至目標値以下時增加壓縮機（ -18- (15) 1257472 9 )的迴轉數，由於冷凍空間（2 )無須冷卻而導致浪費電 力，在第9圖所示的圖表中，將冷凍空間溫度（Fa )與其 目標値（Fr )及冷藏空間溫度（Ra )與其目標値（Rr )輸 人P ID控制器（25 )，當決定壓縮機（9 )的迴轉數之際 ，譬如以2倍來加算冷凍空間側之庫內溫度（Fa )與目標 溫度（Fr )之間的差値資料後輸入，使冷凍空間（2 )側 之溫度資訊資料的回饋量大於冷藏空間。 藉此，壓縮機（9 )的迴轉數，是根據較實際値更大 的差値也就是冷凍空間（2 )側所回饋的溫度資訊’來決 定冷凍側的基準，當冷凍空間（2 )充分冷卻時’不需提 高壓縮機（9 )的迴轉數，是藉由切換閥（1 1 )來控制流 向冷藏用冷卻器（5 )的冷媒流量來增減冷藏側的冷凍能 力，不會導致冷凍側的過度冷卻並將冷藏側控制於適當的 溫度。 此外，在上述的實施例中，雖然是針對增加冷藏空間 (3 )的溫度資訊來決定壓縮機（9 )的迴轉數做說明’當 萬一外部氣溫下降而使冷藏空間（3 )的溫度低於目標値 (Rr )時，則根據其回饋訊號來降低壓縮機（9 )的迴轉 數，如此一來，將導致冷凍空間（2 )側之冷凍能力下降 白勺問題產生。 第1 0圖，是對應上述萬一狀態的流程圖’僅於冷藏 窆間（3 )溫度高於目標値（Rr )時輸入回饋其溫度資訊 的函數（Fx ) ’當冷藏空間溫度（Ra )與目標値（Rr )的 差異小時輸入該値，當負値時則將0訊號輸入PID控制器 -19- (16) (16)1257472 (25 ) ° 藉由上述的控制，即使冷藏空間（3 )的負荷輕而使 實際溫度（R a )低於目標設定値（R r )時，冷凍空間（2 )能以根據其溫度資訊的冷凍力來維持目標値（Fr )，可 防止因冷凍力下降導致冷凍空間（2 )的溫度高於目標値 (Fr )的情形產生。 接下來說明其他的實施例。第1 1圖，是顯示以一定 迴轉數驅動壓縮機（9 )，且使冷凝溫度於一定條件之冷 藏用冷卻器（5 )的溫度產生變化時，冷凍用及冷藏用循 環之冷凍能力（QF1 ) 、（ QR1 )的變化。 此時可得知，冷藏用冷卻器（5 )，可藉由降低其表 面溫度來降低其冷凍能力（QR1)，並可藉由提高其表面 溫度來提高冷凍能力，而冷凍側的冷凍能力（QF 1 )，其 冷卻氣溫度譬如-23.5 °C爲定値，即使冷藏側的冷凍能力 變動也不易後到太大的影響。 接著，針對冷藏用冷卻器（5 )，倘若使冷藏用風扇 的轉數產生變化，譬如降低迴轉數，將使冷藏用冷卻器（ 5 )處的熱交換量下降而降低冷卻器（5 )的表面溫度，如 此一來，冷凍循環的冷凍能力（QR1 )也將隨之下降，相 反地，倘若提高風扇（7)的迴轉數可增加熱交換量而使 冷卻器（5 )的表面溫度上升，進而增加循環的冷凍能力 (QR1 )。 換言之，冷藏空間（3 )的冷卻控制，可藉由增減冷 藏用風扇（7 )的迴轉數來控制空間溫度，當冷藏空間溫 -20- (17) 1257472 度（Ra )高於其目標値（Rr )時，可藉由增加冷 風扇（7 )的迴轉數來冷卻，當過度冷卻而低於 (Rr )時，可藉由降低風扇的迴轉數使冷凍力下 制在適當的溫度。 而第1 2圖，是顯示改變冷凍用冷卻器（4 ) ，冷凍用及冷藏用循環之冷凍能力（QF2 )、（ 變化，藉由降低冷凍用冷卻器（4 )的溫度，可 冷凍用冷卻器（4 )而吸入壓縮機（9 )之低段側 環量，使得冷凍側循環的能力下降。此外，由於 (9 )低段側送入高段側壓縮部的冷媒量也減少 段側壓縮部之排除容積的關係，使從冷藏用冷名 回流至中間壓部後吸入高段側壓縮部的冷媒量增 增加冷藏側循環的冷凍能力（QR2 )。 據此，當冷凍空間（3 )的溫度高於目標値 形成冷卻不足時，或者冷凍空間（2 )的冷凍能 ，可藉由降低冷凍側冷卻風扇（6 )的迴轉數後 凍用冷卻器（4 )的熱交換量進而降低冷卻器（4 溫度的方式，來增加冷藏側的循環能力（QR2 ) 低冷凍側的循環能力（QF2 )，而分別對各空間 當的控制。 根據上述的說明，由於冷媒可同時流向冷凍 (4 )與冷藏用冷卻器（5 )而提高冷凍空間（2 空間（3 )的蒸發溫度，故能以良好的循環效率 卻，即使面對各儲藏空間隨時增加的溫度負荷， 藏側冷卻 其目標値 降，而控 的溫度時 QR2)的 減少通過 的冷媒循 從壓縮機 ，加上高 P 器（5 ) 加，進而 (Rr )而 力過大時 ，減少冷 )之表面 ，或者降 溫度作適 用冷卻器 )與冷藏 來執行冷 也能由三 -21 - (18) 1257472 向閥所構成的冷媒流動控制切換閥（1 1 )確實地分配冷媒 量，進而抑制冷凍空間及冷藏空間的溫度變化，並將各空 間控制在適當的溫度。 以上所說明的冷凍循環中，藉由可同時控制流向冷凍 及冷藏用冷卻器（4 )、（ 5 )的冷媒流量，相較於傳統上 交互控制流向2個冷卻器之冷媒量的方式，不會使冷媒偏 流於其中一個冷卻器而導致冷媒量超出冷凍循環所需的量 以上。據此，即使是採用碳化氫系冷媒之類可燃性冷媒， 由於可減少冷媒塡充量因此可提高安全性。 此外，雖然上述實施例中所說明的兩段壓縮機（9 ) ，其壓縮機外殻（9c )內的壓力爲中間壓，但本發明卻不 侷限於此，雖然圖面中沒有特別標示，但亦可使來自於作 爲低壓外殼之冷凍用冷卻器的吸入管連接於壓縮機外殼內 的空間，並使來自於冷藏用冷卻器的吸入管連接於低段側 壓縮部之排出口與高段側壓縮部之排出口的連結部。此外 ’同樣亦可使來自於作爲局壓外殼之冷凍用冷卻器的吸入 管連接於低段側壓縮部的吸入口，並使來自於冷藏用冷卻 器的吸入管連接於低段側壓縮部之排出口與高段側壓縮部 之排出口的連結部，而使來自於高段側壓縮部的排出氣體 從高壓外殼內排出至流向冷凝器的排出管。 [產業上的利用性] 根據本發明，可用於根據二段壓縮式冷凍循環結構提 高循環效率的冷藏庫。 -22- (19) (19)1257472 【圖式簡單說明】 第1圖：是顯示本發明中一種實施形態之冷藏庫的冷 凍循環圖。 第2圖：爲搭載第1圖之冷凍循環的冷藏庫的慨略縱 剖面圖。 第3圖：顯示第1圖中兩段壓縮機細部的縱剖面圖。 第4圖：顯示第1圖中三向閥之重要細部的平面圖。 第5圖：顯示冷凍循環之其他實施例的構成圖。 第6圖：冷凍及冷藏冷凍能力與冷媒流動間的關係圖 表。 第7圖：第6圖的示意圖。 第8圖：壓縮機迴轉數控制流程圖。 第9圖：於第8圖之控制中添加冷藏溫度資訊的迴轉 數控制流程圖。 第1 0圖：進一步改良第9圖之控制的迴轉數控制流 程圖。 第11圖：顯示改變本發明之冷藏用冷卻器溫度時， 冷凍及冷藏冷凍能力之變化的說明圖。 第1 2圖：顯示改變本發明之冷凍用冷卻器溫度時， 冷凍及冷藏冷凍能力之變化的說明圖。 第1 3圖：傳統冷藏庫之冷凍循環圖。 【主要元件符號說明】 -23- (20) (20)1257472 1 :冷藏室本體 2 :冷凍空間 3 :冷藏空間 4 :冷凍用冷卻機 5 ·冷藏用冷卻機 6、7 :冷卻風扇 8 :機械室 9 :兩段壓縮機 9 a :低段壓縮部 9b :高段壓縮部 9 c :外殼 1 〇 :冷凝器 1 1 :切換閥 1 2 :冷凍用毛細管 1 3 :冷藏用毛細管 14 :蓄壓器 1 5 :冷凍側吸入管 1 6 :排出管 17、24 :冷藏側吸入管 1 8 :閥殼 1 9 :閥座1257472 (1) Description of the Invention [Technical Field] The present invention relates to a refrigerator using a two-stage compression type variable compressor, and more particularly to a refrigerator that determines the number of revolutions of the compressor based on the temperature in the storage space. [Prior Art] In recent years, most refrigerators are equipped with a compressor capable of changing the refrigeration capacity by variable frequency control, and by changing the refrigeration capacity, it is possible to obtain cooling performance and reduce power consumption. In general, the general household refrigerator has: a freezing space that can be cooled to about -18~-200 °C, a storage space for refrigerating and fruits and vegetables that can maintain about + 1~+ 5 °C, using a single cooler for both sides. The refrigerating compartment that cools the space is a dumper that controls the distribution of the cold airflow to the freezer and the refrigerated space, and drives or stops the compressor according to the overall load. The two storage spaces are maintained at a constant temperature by controlling the number of revolutions of the compressor. Further, each of the freezing and refrigerating space has a refrigerator, and the flow path for switching the refrigerant is used to distribute and control the flow of the refrigerant to the coolers disposed in the respective cooling spaces, and to correspond to the overall temperature and temperature difference of the cooling space. Control the compressor. In addition, the refrigerant compressor for refrigerating refrigerators on the market today has a single compression portion in the compressor casing, which is a so-called one-stage compression method. In recent years, a technical idea of a two-stage compression refrigeration system has been disclosed as in the first As shown in Fig. 3, a two-stage compressor (39) having a motor, a low-stage compression element -5 - (2) (2) 1,257,724 (39a), and a high-stage compression element (39b) is provided in the hermetic container. An intermediate pressure expansion device (43) is connected to the outlet side of the discharge pipe (46) connecting the condenser (40) from the high stage compression element (39b) to communicate the discharge side and the high side of the low stage side compression element (39a) The suction side of the compression element (39b) and the intermediate pressure suction pipe (47), and the intermediate pressure suction device (47) and the intermediate pressure expansion device (43) are connected to the intermediate pressure evaporator ( 3 5), and a low-pressure evaporator (34) is connected between the low-pressure expansion device (42) abutting on the outlet side of the condenser (40) and the suction side of the low-stage compression element of the two-stage compressor. Discharge side and high section compression element of low stage compression element (39a) The suction side of 9b) is connected to the inside of the sealed container (39), and the accuracy of the temperature control in the interior of the chamber can be improved, and the temperature uniformity, high efficiency, and low power consumption of each part in the chamber can be achieved (refer to Patent Document 1). [Problem to be Solved by the Invention] The refrigerating cycle described in Patent Document 1 is to evaporate the intermediate pressure as a refrigerating cooler. The evaporation temperature of the device (35) is higher than the evaporation temperature of the low pressure evaporator (34) as a cooler for freezing to improve the cycle efficiency. The suction pipe of the refrigerating cooler (3 4 ) of the two-stage compression cycle is directly connected to the low-stage side compression portion (39a) of the compressor, and the suction pipe (4 7) of the refrigerating cooler (3 5) It is connected to the intermediate pressure part, so the freezing capacity of the -6-(3) (3)1257472 freezer space is not easily affected by the refrigerant flowing to the refrigerating cooler. 'The compressor is controlled according to the total load of the freezing side load and the refrigerating side load. In the conventional method of the number of revolutions, for example, when the degree of cooling of the freezing space is sufficient and the refrigerating space is excessively cooled, the number of revolutions of the compressor is lowered, resulting in a problem of insufficient cooling in the freezing space. The present invention has been made in view of the above problems, and an object of the present invention is to provide a two-stage compression type variable refrigerating cycle having a refrigerating and refrigerating cooler according to freezing space temperature information, and The freezing space and the refrigerating space can be separately controlled in a refrigerator at an appropriate temperature. [Means for Solving the Problems] In order to solve the above-described problems, the refrigerator of the present invention is a compressor in which a compression element is constituted by a low stage side compression unit and a high stage side compression unit, and the ability can be changed by inverter control; a switching valve that is provided on the condenser outlet side that can receive the gas discharged from the compressor, and that can control the refrigerant flow path and the flow rate; and a cooling cooler and refrigeration cooling device that are connected to the switching valve via an individual pressure reducing device The refrigerator of the refrigeration cycle constituted by the apparatus is characterized in that the number of revolutions of the compressor is determined based on the temperature of the freezing space and the target enthalpy. The refrigerator described in claim 2 is a compressor in which a compression element is constituted by a low-stage compression portion and a high-stage compression portion and can be changed by inverter control; and is set to be acceptable for the above compression. a condenser valve on the condenser outlet side of the gas discharged from the machine, and a refrigerant flow path and a flow rate control valve; and a refrigeration cooler connected to the switching valve via an individual pressure reducing device (4) 1257472 and a refrigerating cooler The refrigerator of the refrigeration cycle is characterized in that the number of revolutions of the compressor is determined according to the temperature of the freezing space and its target enthalpy, the temperature of the refrigerating space and its target enthalpy, and the temperature of the refrigerating space is determined when the number of revolutions is determined. The amount of feedback of the information is greater than the amount of feedback of the temperature information of the freezer space. [Effects of the Invention] According to the above-described configuration, not only the evaporation temperature of each of the cooling and refrigerating coolers, that is, the efficiency of the refrigerating cycle, but also the flow path of the refrigerant to the respective coolers can be switched in accordance with the cooling of the respective storage spaces. Further, the flow rate can be controlled by suppressing the temperature fluctuation in each space by simultaneously cooling the freezing space and the refrigerating space, and appropriately controlling the temperature of each space. [Embodiment] Hereinafter, one embodiment of the present invention will be described based on the drawings. The refrigerator main body (1) shown in the longitudinal sectional view of Fig. 2 is a freezing space (2) and a refrigerating compartment which are formed into a storage space inside the heat-dissipating box and divided into a freezing compartment and an ice-making compartment by a partition wall. A plurality of storage rooms, such as the refrigerated space of the vegetable and fruit room. Each of the storage compartments is cooled and held separately by a refrigerating cooler (4), a refrigerating cooler (5), and a refrigerating air circulating fan (6) and (7) disposed in each of the freezing space and the refrigerating space. The set temperature, each of the coolers (4) and (5) is cooled by the refrigerant supplied from the compressor (9) of the machine room (8) provided below the back of the main body. -8- (5) (5)1257472 Fig. 1 is a switching valve (1 1 ) showing the refrigeration cycle "the compressor (9), the condenser (10), and the refrigerant flow path in the refrigerator in the present invention. The refrigeration and refrigerating coolers (4) '(5) for forming the parallel connection are connected in a ring shape. The condenser (10) is disposed in an outer bottom space of the refrigerator body (1), and the refrigerator body (1) is located in front of the machine room (8) forming a flat plate, and is configured by a condenser ( 1 〇) The liquefied refrigerant is supplied to the refrigeration cooler (4) and the refrigerating cooler via the switching valves (1 1 ) through the capillary tubes (1 2 ) and ( 13 ) as the decompression devices. 5), and the lowering of the cooler is formed by evaporation, and the storage chamber is cooled to a certain air temperature by circulation of the cooling fans (6), (7), and the vaporized vaporized refrigerant 'is passed through the accumulator (14) Return to the compressor (9). The compressor (9), as shown in Fig. 3 in detail, is a reciprocating (recipr 〇ca 1 ) two-stage compressor in which a compression element is constituted by a low stage side compression portion (9a) and a high stage side compression portion (9b). And constituting a reciprocating motion of the connecting rod (9g) by the eccentric shaft (9f), and the eccentric shaft (9〇 is a rotary shaft (9e) of the motor-driven mechanism (9d) housed in the sealed casing (9c) The rotation of the piston is rotated after the eccentricity is formed. The piston (9i) is fixedly fixed to the front end of the connecting rod (9g) by the ball joint (9h), and the reciprocating motion of the piston (9 i ) in the cylinder (9 j ) causes the aforementioned The low-stage side compression portion (9a) and the high-stage side compression portion (9b) exchange the refrigerant, and are discharged after being compressed. By using the ball joint (9 h) for the compression portion, the volumetric efficiency can be improved, and the need for both is suppressed. Expansion of the outer space of the two-stage compressor (9) of the compression sections (9a) and (9b) -9- (6) 1257472 The suction port (9k) of the low-stage side compression section (9a) is connected to the suction 1 The end portion of 5), the suction pipe (15) is connected to the freezing cooler (4) via an accumulator (14) for discharging compression The refrigerant gas outlet port (9 m), is towards the inside of the housing (9 c) forming an opening, side compression portion (9b) is connected to the discharge port toward the condenser (1 billion) the tube (16). The pressure accumulator (14) functions to store the liquid refrigerant that has not been completely evaporated after the gas-liquid separation, and to discharge only the gaseous refrigerant, and the liquid refrigerant flows into the cylinder (9j) of the compressor (9). In the present embodiment, only the suction pipe (1 7 ) provided from the refrigerating cooler ( 5 ) from the refrigerating cooler ( 5 ) is introduced into the sealed casing ( 9 c ) to form an intermediate portion. In this case, since the suction refrigerant from the refrigerating cooler (5) does not enter the cylinder of the compressor, it is not necessary to specifically refrigerate the cooler (5 is provided with an accumulator in the rear stage, and only when the accumulator is installed) The gas to be sucked in by the suction pipe (17) on the cooler side of the refrigerator is connected to the refrigerant gas discharged from the discharge port (9a) of the forced section side (9a). The suction port (9p) of the high-stage side compression portion is sucked to form a compression. The compressor (9) can be changed in temperature according to the temperature measured by the freezing and refrigerating space and the temperature difference between the set targets by the variable frequency control forming ability. Rate, etc. In this case, the number of revolutions is set to 70 Hz, and the control device formed by the microprocessor is used to form the operation. The tube (the block that is attached to the body can be prevented, the latter is, according to the flow) Pressurizer (9b), 値, 30~ -10- (7) 1257472 The switching valve (11) is disposed on the outlet side of the condenser (10) that receives the exhaust gas from the compressor (9). Switching the refrigerant flow path toward the coolers (4) and (5) and controlling the flow rate. As shown in Fig. 4, a valve seat (1 9 ) is provided in the valve casing (18), and the valve seat (1 9) A port A (1 9a ) leading to the side of the refrigerating cooler (4) and a port B (1 9b) leading to the side of the refrigerating cooler (5) are formed, and are at the valve seat (1 9 ) A three-way valve of the valve body (20) is disposed above. The valve body (20) is formed with two V-shaped grooves A (20a) under the thick wall portion (20d) formed into a specific end edge shape. And a groove B (20b), the groove A (20a) and the groove B (20b) are centered on the rotary axis (20c) and have different rotational movement radii, respectively corresponding to the valve port A (19a) With valve port B ( 19b ) The top surface of the valve seat (19) is closely overlapped with the valve body (20) over the trajectory by a certain length, and the stepping motor provided on the upper portion, not shown in the drawing, is used. The pulse step of 〇~80 forms a slewing drive. The switching valve (1 1 )' can rotate the valve body (20) according to the pulse signal formed by the refrigeration cycle control signal, and is located at the specific pulse position. When the groove A ( 2 0 a ) on the outer side of the body rotation overlaps the valve port A (19 a), the refrigerant flowing into the valve casing (丨8) from the inflow port (2 1) will be concave. The open end of the groove A (20 a ) on the side of the thick-walled section (2 〇d ) enters the V-shaped groove a ( 20a ) and is connected to the port A of the groove A ( 19a) After the effluent, the freezing capillary (j 2 ) is introduced and evaporated by the freezing cooler (4). Further, similarly to the above, when the groove B ( -11 - (8) 1257472 2 0 b ) inside the radius of gyration and the valve port B (1 9 b ) are connected, the refrigerant flowing into the groove b ( 2 0 b ), It flows into the refrigerating capillary (1 3 ) from the port B (1 9b) that forms the communication, and is then evaporated by the refrigerating cooler (5). Further, the groove B (20b) located on the refrigerating side has a sectional area of the V-shaped groove which is enlarged as it goes from the turning front end toward the open end of the thick-walled portion (20d), by the valve body (2) The rotation of 0) is from the minimum to the maximum flow opening area and communicates with the valve port B (1 9b ). Since the flow path switching and the flow rate adjustment can be precisely controlled, the flow rate of the refrigerant can be efficiently changed by the pulse rotation control. Linear. The open control of the valve of the three-way valve (20), although the opening of the valve port (19a), (19b) flowing to the freezing cooler (4) and the refrigerating cooler (5) can be selected to be fully open, fully closed, The freezing side opening is narrowed, the refrigerating side is fully opened, or the refrigerating side opening is reduced, and the freezing side is fully opened. However, in the present embodiment, the refrigerating cooler (4) and the refrigerating cooler (5) are formed in parallel. Therefore, the cooling control is to form two types of the freezing and freezing side while cooling and cooling only the freezing side. The refrigerant flowing out from the freezing side port A (19a) is decompressed by a capillary (12) set in the freezing space (2) to a cooling temperature, that is, an evaporating temperature, and is supplied to the refrigerating cooler (4). The temperature of about 25 ° C evaporates, and the refrigerant from the refrigerating valve port B (19b) is similarly set in the refrigerating space (3) to be close to the cooling temperature (about -5 ° C), that is, the evaporating temperature. After cooling the capillary (1 3 ), it is sent to the refrigerating cooler (5) to form evaporation. The freezing and refrigerating capillary (1 2 -12- (9) (9) 1254742) and (13) ' in the above-mentioned refrigerating cycle are the refrigerant of the refrigerating cooler (4) and the refrigerating cooler (5) The evaporating temperature has a temperature difference. When the freezing side capillary (12) is strongly reduced, in the case where the refrigerant flows to both sides of the freezing and refrigerating as described above, it is inevitably formed to easily flow to a low-resistance refrigeration side and is not easy to flow to the freezing side. The tendency of the side causes a situation in which the refrigerant cannot flow into the freezing side in an extreme case. In order to improve the above problem, in the above-described switching valve (1 1 ), the flow of the refrigerant for cooling the freezing and refrigerating spaces (2) and (3) is controlled, and in order to prevent the one-way flow of the refrigerant, a restriction is added. The flow control of the refrigerant on the refrigerating side that is easy to flow into. If the freezing side groove A (20a) communicates with the valve port A (19a) and forms a full opening, the freezing side cooler (4) which is hardly affected by the refrigerant flow state on the refrigerating side can obtain a predetermined freezing capacity. Even in the refrigeration capacity on the refrigerating side, it can be fully closed to fully open according to the state of communication between the groove B (20b) of the switching valve (1 1 ) and the valve port B (19b), and Fine control of the change in the number of revolutions of the compressor (9), by the above-described refrigerant flow control, the temperature difference between the evaporation temperature of the refrigerating cooler (5) and the freezing side can be increased, and the refrigerating room temperature can be cooled to 1 ～2°C, if the heat transfer surface area of the refrigerating cooler (5) is increased and the amount of heat exchange for cooling in the refrigerating space is increased, the evaporating temperature can be further increased. In the above case, the refrigerating space (3) is further reduced. The temperature difference between the cooling temperature and the cooler temperature reduces the amount of frost adhering to the refrigerating cooler (5), which prevents the drying in the space and maintains the high internal humidity of -13-(10) 1257472. Further, in a general domestic refrigerator, since the freezing capacity required for cooling the freezing space and the refrigerating space is substantially the same, the heat transfer surface area of the refrigerating cooler (5) can be made equal to or larger than the freezing cooler ( 4), and efficiently cool each cooling space. Next, the operation of the refrigeration cycle will be described. When the compressor (9) is driven by the input of the power source, the refrigerant gas "compressed into high temperature and high pressure" is discharged from the discharge pipe (16) to the condenser (1?) and reaches the switching valve (1 1 ). The switching valve (1 1 ) can be set to various combinations as described above. When the power source is input, since the freezing and refrigerating spaces (2) and (3) are in an uncooled state, the valve port A (19a), B (1 9 b ) is in a fully open state, and the refrigerant flows into the freezing and refrigerating capillary tubes (1 2 ) and ( 13 ), and then flows into the decompressing cooling and refrigerating coolers (4) and (5). Evaporation is formed at each evaporation temperature, and each cooler is cooled to a certain temperature. The refrigerant from the freezing cooler (4) flows into the accumulator (14). When the non-evaporating liquid refrigerant remains in the cooler, the residual refrigerant is stored in the accumulator (14), only The gas refrigerant is sucked into the low stage side compression portion (9a) of the compressor (9) from the suction pipe (15). Further, the refrigerant evaporated in the cooling cooler (5) is introduced into the sealed casing (9c) of the compressor (9) to form an intermediate pressure via the suction pipe (17). The low-stage side compression portion (9a) is sucked from the freezing cooler (4), and is discharged from the compressed discharge port (9m) to the refrigerant gas in the outer casing (9c), and flows into the airtight portion from the refrigerating cooler (5). Middle 14 - (11) 1257472 of the outer casing (9c), after the refrigerant gas in the pressure portion is merged, it is sucked into the high-stage compression portion (9b) from the suction port (9p), and then the compressed discharge port (9 n) After being discharged to the discharge pipe (16), it is introduced into the condenser (10) to form a refrigeration cycle. Therefore, according to the above-described refrigeration cycle, the cooling and refrigerating coolers (4) and (5) each having the capillary tubes (12) and (13) are provided, and the evaporation temperatures of the capillary tubes (1 2 ) and (13) are In conjunction with the respective set temperatures of the freezing space and the refrigerating space, the refrigerant gas evaporated in the refrigerating cooler (5) is maintained at a state higher than the intermediate pressure of the freezing side pressure and directly sucked into the compressor casing (9c). The intermediate pressure portion 'can not only make the evaporation temperature of the refrigerating cooler (5) higher than the indoor cooling temperature compared to the freezing cooler (4), but also reduce the input efficiency of the compressor to improve the cycle efficiency'. . Further, by increasing the temperature difference between the refrigerating cooler (5) and the refrigerating space, the amount of frost adhering to the cooler (5) can be reduced, and the drying in the refrigerating space can be prevented and kept in the storage. High humidity 'can maintain the freshness of the food for a long time, not only that, because the refrigerant can flow into both the freezing and refrigerating coolers (4) and (5) and form cooling, which is suppressed compared with the traditional interactive cooling method. The temperature of each room changes. The refrigeration cycle is as shown in Fig. 5. In Fig. 5, the same portions as those in Fig. 1 are denoted by the same reference numerals, and the refrigerating cooler (4) and the refrigerating cooler (5) are for the above compressor (9). The condenser (1 〇) and the switching valve (1 1 ) of the refrigerant flow path are connected in series, and serve as a bypass passage for the refrigerating capillary (13) and the refrigerating cooler (5) from the switching valve (1 1 ). The bypass pipe (2 2 ) is connected to the freezing cooler (4) via a gas-liquid separator (2 3 ) and from a freezing capillary -15-(12) (12) 1254722 (12), and can also be borrowed An intermediate pressure portion that forms an intermediate pressure in the sealed casing (9c) of the compressor (9) is connected to the upper portion of the gas-liquid separator (23) by a suction pipe (24). In this way, the refrigerant can be simultaneously or selectively flowed into the refrigerating cooler (5) and the refrigerating cooler (4) according to the switching valve (11) having the same control method as described above, from the bypass pipe (22) or The refrigerant of the refrigerating cooler (5) is separated into a gaseous refrigerant and a liquid refrigerant in a gas-liquid separator (23), wherein the liquid refrigerant flows to the side of the refrigerating cooler (4), and the gaseous refrigerant passes through the refrigerating side suction pipe. (24) returning to the intermediate pressure portion of the compressor (9), and the liquid refrigerant is again evaporated at a low temperature by the freezing cooler (4), and then returned to the lower stage side of the compressor (9), which has the same function as the above embodiment. Good cycle efficiency and the effect of cooling each storage chamber to a certain temperature. Fig. 6 is a view showing that the evaporating temperature of the refrigerating cooler (4) and the refrigerating cooler (5) and the condensation temperature of the condenser (10) are set to be constant, and the compressor (9) is rotated at a certain speed. The refrigeration capacity on the freezing side and the refrigerating side during the operation, wherein the vertical axis is the refrigeration capacity on the refrigerating side, and the horizontal axis is the freezing capacity on the freezing side. In the figure, the point a indicates that the refrigerant flows only to the refrigerating side cooler (5) by the switching valve, and the point b indicates that the refrigerant flows only to the refrigerating side cooler (4), and the point c is When the valve ports (19 a) and (1 9b) are fully open, the refrigerant flows to both the freezing and refrigerating coolers (4) and (5). It is shown in the graph that the refrigerant mass or volume directly sucked from the freezing cooler (4) into the low-stage side compression portion (9a) of the compressor (9), -16-(13) 1257472 is dependent on the low-stage compression The cylinder exclusion volume of the part, the corresponding cold phase is 69W when it flows into the freezing side only, and it is 64W when it flows into the freezing and cold, and is hardly reflowed from the refrigerating cooler (5) to the intermediate pressure part of (9). The influence of the refrigerant has formed a certain flaw. On the other hand, the refrigerating side corresponds to a large decrease in the refrigerating capacity from the refrigerating cooler (5 to the refrigerant amount of the compressor (9) compared to 155 W when it flows only at the same time. ; The left and right, the refrigerating capacity of the refrigerating side will be sucked into the refrigerant from the freezing cold 4), that is, only the refrigerating cooler (5 medium or the refrigerant inhaled from the freezing cooler (4) In addition, the indoor temperature is +3~ compared to the general refrigerated space. Since the freezing space temperature is -1 8~-2 0 °c, the temperature difference between the outdoor and the outdoor is very large, and the required freezing capacity for cooling the freezing space is required. 'It is larger than the enthalpy required for cold, so that when the freezing capacity of the freezing side is greater than the freezing capacity, that is, when the freezing side load is set to be larger than the freezing operation, it is expressed by the pattern of Fig. 6. In the seventh embodiment, the hatched portion represents the portion having a large freezing capacity on the freezing side. Therefore, as described above, since the freezing ability of the freezing side is not affected by the refrigerant flowing back from the refrigerating cooler (5), cold However, the control is controlled according to the number of revolutions of the compressor (9). When the cooling is insufficient, the arrow does not raise the freezing force of the compressor (9), and when the cooling is excessively cooled, the number of revolutions or the way can be reduced. Maintain proper cooling temperature. The control on the refrigerated side is non-frozen, and the compressor on the storage side is cooled by the cold flow of the g 75 W (v 5 〇C), and the refrigerated side is refrigerated. The side view shows that it is easy to receive the frozen space, and the number of revolutions is stopped according to the number of revolutions of the pressure -17-(14) 1257472 compressor (9), but by controlling the valve opening of the switching valve (1 1 ) Open and close to adjust the refrigerant flow and thereby control its cooling temperature. Next, an embodiment of the compressor number control of the present invention will be described based on the control flowchart shown in Fig. 8. The freezing space measured by the cold sensor, such as the indoor temperature (Fa) of the freezing chamber (4), is compared with a specific target 値 (Fr), and the difference is input into the PID used to determine the compressor cycle number. Controller (2 5 ). Next, if the temperature of the freezing space (2) is higher than the target 値(Fr), the PID calculation 値 is increased according to the 値, and the freezing space is promoted by increasing the number of revolutions of the compressor (9) by a certain amount (2) The cooling is performed, and the operation control is performed by introducing a certain temperature. In addition, if the temperature of the freezing space ( 2 ) is lower than the target 値 (Fr ), the number of revolutions will be reduced or the rotation will be stopped to reduce the freezing force. Next, another embodiment of the compressor number control of the present invention will be described. Although the above embodiment controls the number of revolutions of the compressor (9) based on the temperature information of the freezing space (2), depending on the operating conditions of the refrigerator, the freezing capacity of the refrigerating space is sometimes considered for the freezing space (2). insufficient. Therefore, 'the temperature information of the input freezing space (2) and the temperature information of the refrigerating space (3) cause the compressor (9) to operate within the oblique line range in Fig. 7 'because the number of revolutions of the compressor (9) can be increased Increase the freezing capacity, so it can increase the freezing capacity of the freezing space (2) and the refrigerating space (3), but increase the number of revolutions of the compressor (-18-(15) 1257472 9) when the freezing space is cooled below the target level. Since the freezing space (2) does not require cooling and wastes power, in the graph shown in Fig. 9, the freezing space temperature (Fa) and its target enthalpy (Fr) and refrigerating space temperature (Ra) are compared with the target enthalpy (Rr). The human P ID controller (25), when determining the number of revolutions of the compressor (9), for example, the difference between the internal temperature (Fa) and the target temperature (Fr) of the freezing space side is increased by 2 times. After the input, the feedback amount of the temperature information on the side of the freezing space (2) is greater than that of the refrigerating space. Thereby, the number of revolutions of the compressor (9) is determined based on a larger difference than the actual enthalpy, that is, the temperature information fed back on the side of the freezing space (2), and the freezing side (2) is sufficient. When cooling, it is not necessary to increase the number of revolutions of the compressor (9), and the flow rate of the refrigerant flowing to the refrigerating cooler (5) is controlled by the switching valve (1 1 ) to increase or decrease the freezing capacity of the refrigerating side without causing freezing. The side is overcooled and the refrigerated side is controlled to the appropriate temperature. Further, in the above-described embodiment, although the number of revolutions of the compressor (9) is determined in order to increase the temperature information of the refrigerating space (3), it is explained that the temperature of the refrigerating space (3) is low in case the outside temperature is lowered. At the target 値(Rr), the number of revolutions of the compressor (9) is reduced according to the feedback signal, and as a result, the problem of a decrease in the freezing capacity on the side of the freezer space (2) is caused. Figure 10 is a flow chart corresponding to the above-mentioned state. 'Function (Fx) is input when the temperature of the refrigerating compartment (3) is higher than the target 値(Rr). When the refrigerating space temperature (Ra) Enter the 小时 when the difference with the target 値(Rr) is small, and input the 0 signal to the PID controller when negative -19-19- (16) (16)1257472 (25 ) ° With the above control, even the refrigerated space (3 When the load is light and the actual temperature (R a ) is lower than the target setting 値(R r ), the freezing space (2) can maintain the target enthalpy (Fr) with the freezing force according to the temperature information, thereby preventing the freezing force The fall causes the temperature of the freezing space (2) to be higher than the target 値(Fr). Next, other embodiments will be described. In the first aspect, the refrigeration capacity of the refrigerating and refrigerating cycle (QF1) is shown when the compressor (9) is driven at a constant number of revolutions and the temperature of the refrigerating cooler (5) whose condensing temperature is constant is changed. ), (QR1) changes. At this time, it can be known that the refrigerating cooler (5) can reduce its freezing ability (QR1) by lowering its surface temperature, and can improve the freezing ability by increasing the surface temperature thereof, and the freezing ability of the freezing side ( QF 1), the cooling gas temperature is determined to be -23.5 °C, even if the refrigeration capacity of the refrigerating side changes, it is not easy to have too much influence. Next, in the refrigerating cooler (5), if the number of revolutions of the refrigerating fan is changed, for example, the number of revolutions is reduced, the amount of heat exchange at the refrigerating cooler (5) is lowered to lower the cooler (5). The surface temperature, as a result, the refrigeration capacity (QR1) of the refrigeration cycle will also decrease. Conversely, if the number of revolutions of the fan (7) is increased, the amount of heat exchange can be increased to increase the surface temperature of the cooler (5). This in turn increases the refrigeration capacity of the cycle (QR1). In other words, the cooling control of the refrigerating space (3) can control the space temperature by increasing or decreasing the number of revolutions of the refrigerating fan (7), when the refrigerating space temperature is -20-(17) 1257472 degrees (Ra) is higher than its target 値In the case of (Rr), it can be cooled by increasing the number of revolutions of the cooling fan (7). When it is excessively cooled and lower than (Rr), the freezing force can be lowered to an appropriate temperature by reducing the number of revolutions of the fan. In the first drawing, the freezing capacity (4) for freezing, the freezing capacity (QF2) for freezing and refrigerating cycles, and the temperature of the cooling cooler (4) are reduced. The amount of the lower side ring of the compressor (9) is sucked, so that the capacity of the circulation on the freezing side is lowered. In addition, since the amount of refrigerant fed to the high-stage side compression portion at the low-stage side is also reduced, the side-side compression is also reduced. In the relationship of the excluded volume, the amount of refrigerant sucked into the high-stage compression unit from the refrigerating cold name to the intermediate pressure portion is increased by the refrigeration capacity (QR2) of the refrigerating side cycle. Accordingly, when the freezing space (3) When the temperature is higher than the target 値 to form insufficient cooling, or the freezing energy of the freezing space (2), the number of revolutions of the cooling side cooling fan (6) can be reduced, and the heat exchange amount of the chiller (4) can be lowered to further reduce the chiller. (4 temperature method to increase the circulation capacity of the refrigerating side (QR2) and the circulation capacity of the low freezing side (QF2), and control each space separately. According to the above description, since the refrigerant can flow to the freezing at the same time (4) Refrigerator coolers (5) However, the freezing temperature of the freezing space (2 space (3) is increased, so that the cycle efficiency can be improved, even if the temperature load is increased at any time in the storage space, the target side is cooled down, and the temperature is controlled, QR2) The reduction of the refrigerant passing through the compressor, plus the high P (5) plus, and (Rr) force too large, reduce the surface of the cold, or lower the temperature for the application of the cooler) and refrigeration to perform the cold can also The refrigerant flow control switching valve (1 1 ) composed of three - 21 - (18) 1257472 valve is surely distributed with the amount of refrigerant, thereby suppressing temperature changes in the freezing space and the refrigerating space, and controlling each space to an appropriate temperature. In the refrigerating cycle described above, by controlling the flow rate of the refrigerant flowing to the refrigerating and refrigerating coolers (4) and (5) at the same time, compared with the conventional method of interactively controlling the amount of refrigerant flowing to the two coolers, It will cause the refrigerant to flow to one of the coolers and cause the amount of refrigerant to exceed the amount required for the refrigeration cycle. According to this, even if a flammable refrigerant such as a hydrocarbon-based refrigerant is used, safety can be improved because the amount of refrigerant charge can be reduced. Further, although the pressure in the compressor casing (9c) of the two-stage compressor (9) described in the above embodiment is intermediate pressure, the present invention is not limited thereto, and although not specifically indicated in the drawings, However, the suction pipe from the refrigerating cooler as the low-pressure casing may be connected to the space inside the compressor casing, and the suction pipe from the refrigerating cooler may be connected to the discharge port and the high section of the low-stage compression portion. A connecting portion of the discharge port of the side compression portion. In addition, the suction pipe from the refrigerating cooler as the pressure housing may be connected to the suction port of the low-stage compression unit, and the suction pipe from the refrigerating cooler may be connected to the low-stage compression unit. The outlet portion of the discharge port and the discharge port of the high-stage side compression portion discharges the exhaust gas from the high-stage side compression portion from the inside of the high-pressure casing to the discharge pipe that flows to the condenser. [Industrial Applicability] According to the present invention, it can be used for a refrigerator which improves cycle efficiency in accordance with a two-stage compression type refrigerating cycle structure. -22- (19) (19)1257472 BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a freeze cycle diagram showing a refrigerator in an embodiment of the present invention. Fig. 2 is a schematic longitudinal sectional view showing a refrigerator in which the refrigeration cycle of Fig. 1 is mounted. Fig. 3 is a longitudinal sectional view showing the details of the two compressors in Fig. 1. Figure 4: A plan view showing important details of the three-way valve in Figure 1. Fig. 5 is a view showing the constitution of another embodiment of the refrigeration cycle. Figure 6: Diagram of the relationship between freezing and refrigerating capacity and refrigerant flow. Figure 7: Schematic diagram of Figure 6. Figure 8: Flow chart of compressor revolution control. Fig. 9 is a flow chart showing the control of the number of revolutions in which the refrigeration temperature information is added to the control of Fig. 8. Fig. 10: Flow chart of the control of the number of revolutions of the control of Fig. 9 is further improved. Fig. 11 is an explanatory view showing changes in the freezing and refrigerating and freezing capacities when the temperature of the refrigerating cooler of the present invention is changed. Fig. 1 2 is an explanatory view showing changes in the freezing and refrigerating and freezing ability when the temperature of the refrigerating cooler of the present invention is changed. Figure 13: Refrigeration cycle diagram of a traditional refrigerator. [Description of main component symbols] -23- (20) (20)1257472 1 : Refrigerator compartment main body 2 : Freezer space 3 : Refrigerated space 4 : Freezer cooler 5 · Refrigeration cooler 6 , 7 : Cooling fan 8 : Mechanical Chamber 9: Two-stage compressor 9 a : Low-stage compression part 9b : High-stage compression part 9 c : Case 1 〇: Condenser 1 1 : Switching valve 1 2 : Freezing capillary 1 3 : Refrigeration capillary 14 : Pressure accumulation 1 5 : Freezer side suction pipe 1 6 : Discharge pipe 17 , 24 : Refrigeration side suction pipe 1 8 : Valve casing 1 9 : Seat
1 9 a :冷凍側閥口 A 19b :冷藏側閥口 B 20 :閥體（三向閥） -24- (21) (21)1257472 2 0 a :冷凍側凹溝 20b :冷藏側凹溝 2 0 c :迴轉軸 20d :厚壁段部 2 1 :流入閥口 22 :旁通管 2 3 :氣液分離器 25 : PID控制器1 9 a : Freezer side valve port A 19b : Refrigeration side valve port B 20 : Valve body (three-way valve) -24- (21) (21)1257472 2 0 a : Freezing side groove 20b: Refrigerator side groove 2 0 c : rotary shaft 20d : thick wall section 2 1 : inflow port 22 : bypass pipe 2 3 : gas-liquid separator 25 : PID controller