200526912 (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 應負荷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-1 8〜 一 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 利用切換冷煤的流路來分配控制冷煤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煤壓縮機，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 200526912 (2) 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（3 9b )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（4 〇 )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（3 4 )，藉由使低段壓縮元件（3 9a )的排出側與高段壓縮元件（3 9b )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2 0 0 1 - 7 4 3 2 5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；^ 冷凍用冷卻器之低壓蒸發器（3 4 )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 冬 200526912 (3) 冷凍空間的冷凍能力不易受到流向冷藏用冷卻器的冷煤影 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，並可控制冷煤流路與流量的切 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，並可控制冷煤流路與流量的切換 閥；及經由個別的減壓裝置連接於上述切換閥之冷凍用冷 -7- 200526912 (4) 卻器與冷臧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，並可切換冷煤朝各冷卻器的流路及流量，更 可錯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 )所供應的冷煤進行冷卻。 -8 - 200526912 (5) 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 )、冷煤流路的切換閥（]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（〗G )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 0 ) 所液化的冷煤是通過切換閥（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，蒸發汽化後的冷煤，是經由蓄壓 器（1 4 )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 C 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（9f)是藉由收納 於密閉外殼（9 c )內的電動機構（9 d )之迴轉軸（9 e )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 冷煤，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 )、 C 9b )的兩段壓縮機（9 )之外形空間的擴大。 -9- 200526912 (6) 低段側壓縮部（9a )的吸入口（ 9k )連接著吸入管（ 1 5 )的端部，該吸入管（1 5 )是經由蓄壓器（Μ )連結於 前述冷凍用冷卻器（4 )，用來排出壓縮後之冷煤氣體的 排出口 （ 9 m )，是朝外殼（9 c )的內部形成開口，高段 側壓縮部（9b )的排出口則連結於朝向冷凝器（1 0 )的排 出管（16)。 前述蓄壓器（1 4 )的作用，是儲存氣液分離後冷卻器 (4 )所未完全蒸發的液態冷煤並僅排出氣態冷煤，可防 止因液態冷煤流入壓縮機（9 )的汽缸（9j )所造成的故 障，在本實施例中，僅設置於冷凍用冷卻器（4 )的後段 〇 來自於上述冷藏用冷卻器（5 )的吸入管（1 7 )，是 導入連接於密閉外殻（9 c )內可形成中間壓的空間部。據 此，由於來自冷藏用冷卻器（5 )的吸入冷煤不會直接流 入壓縮機的汽缸內’因此不必特別於冷藏冷卻器（5 )的 後段設置蓄壓器’當設置蓄壓器時也只需設置小型蓄壓器 。接著，由冷藏用冷卻器側之吸入管（1 7 )所吸入的冷煤 氣體，與被前述逼段側壓縮部（9a )之排出口 （ 9m )所 排出的冷煤氣體’一起被形成連通之高段側壓縮部（9 b ) 的吸入口（ 9 p )吸入形成壓縮。 上述壓縮機（9 )，可藉由變頻控制形成能力變化， 根據冷凍及冷藏空間所測得的溫度和設定目標間的差値、 溫度變化率等’舉例來說’將迴轉週波數設定爲3 0〜 7 0 Η z，並利用微處理器所構成的控制裝置形成運轉。 - 10- 200526912 (7) 切換閥（Η )，是設置在承接來自於壓縮機（9 )之 排出氣體的冷凝器（1 〇 )出口側，可切換朝冷卻器（4 ) 、（5 )側的冷煤流路並控制流量，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 9 a )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（2 0 c )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 (2 0 )形成緊密重疊，一邊利用圖面中未標示之設置於上 部的步進馬達以〇〜8 0的脈衝步進形成迴轉驅動。 該切換閥（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 (] 9 a ) 上下重疊而連通時，從流入閥口（ 2 1 )流入閥殼（1 8 )內 的冷煤，將會由凹溝A ( 2 0 a )位於前述厚壁段部（2 0 d ) 側的開放端緣進入V字型的凹溝A ( 2 0 a )內，並由連通 於凹溝A的閥口 A ( 1 9 a )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 - 200526912 (8) 2 0b )與閥口 B ( 19b )時，流入凹溝B ( 20b )的冷煤’ 是從形成連通的閥口 B ( 1 9 b )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 Ob )，其V字型溝的 剖面積是隨著從迴轉前端朝向厚壁段部（2〇d )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 將冷煤流量變更成線性。 三向閥（2 0 )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 (] 9 a )流出的冷煤，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（ 1 2 )而形成減壓，並於冷凍冷卻器（4 )以—2 5 □左右的 溫度蒸發’而來自於冷藏用閥口 B(19b)的冷煤，也同 樣地通過位於冷藏空間（3 )內設定成接近冷卻溫度（一 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（！ 2 -12 - 200526912 (9) )、(13 )，由於冷凍用冷卻器（4 )與冷藏用冷卻器（5 )的冷煤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，當在如上所述冷煤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煤無法流入 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 )冷卻之冷煤流動的進 行控制，並爲了防止冷煤的單向流動，加入限制冷煤朝容 易流入之冷藏側的流量控制。 倘若冷凍側的凹溝A ( 2 0 a )與閥口 A ( 1 9 a )間連通 且形成全開時，幾乎不受冷藏側之冷煤流動狀態影響的冷 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（11 )之凹溝B (20b)與閥口 B ( 1 9 b )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 藉由上述的冷煤流動控制，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。(：，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- 200526912 (10) 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煤氣體 ，將從排出管（1 6 )處被排出至冷凝器（1 0 )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 9a ) 、B ( 1 9b )形成全開 狀態，冷煤將魚流入冷凍用及冷藏用毛細管（1 2 ) 、 （13 )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 )的冷煤將流入蓄壓器（1 4 )，當冷卻器中殘留未蒸發的液態冷煤時，殘留的冷煤將 貯留於蓄壓器（1 4 )內部，僅有氣體冷煤從吸入管（1 5 ) 被吸入壓縮機（9 )的低段側壓縮部（9 a )。此外，於冷 藏用冷卻器（5 )蒸發的冷煤，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（9c )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 )內的冷煤氣 體，與從冷藏用冷卻器（5 )流入密閉外殼（9 c )之中間 -14 - 200526912 (11) 壓部的冷煤氣體形成合流後’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】])排出至排出管 (1 6 )後導入冷凝器（]〇 )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Μ) 、 （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 發的冷煤氣體保持高於冷凍側壓力之中間壓的狀態，並直 接吸入壓縮機外殻（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，由於冷煤可同時流 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 )、冷煤流 路的切換閥（]1 )形成直列連接，從切換閥（1 ])起作爲 冷藏用毛細管（1 3 )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- 200526912 (12) (1 2 )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，冷煤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 )的冷煤，是於氣液分離器（23 )內分離成氣態冷煤與液 態冷煤，其中液態冷煤是流向冷凍用冷卻器（4 )側，氣 態冷煤則通過冷藏側吸入管（24 )回流至壓縮機（9 )的 中間壓部，且液態冷煤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 煤僅流向冷藏側冷卻器（5 )的場合，b點是表示使冷煤 僅流向冷凍側冷卻器（4 )的場合，c點則是在閥口（ 1 9a )、（]9b )全開的狀態下冷煤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（9 a )的冷煤質量或體積， -16- 200526912 (13) 是取決於低段壓縮部的汽缸排除容積，相對應的冷凍力， 相較於僅流入冷凍側時的6 9 W，同時流入冷凍、冷藏側時 則爲 64W，幾乎不受從冷藏用冷卻器（5 )回流至壓縮機 (9 )之中間壓部的冷煤影響而形成一定値。 相對於此，冷藏側對應於從冷藏用冷卻器（5 )被吸 入壓縮機（9 )之冷煤量的冷凍力，相較於僅流入冷藏側 時的1 5 5 W，同時流入冷凍、冷藏側時則大幅下降至7 5. W 左右’冷藏側的冷凍能力，會因爲是否從冷凍用冷卻窃（ 4 )吸入冷煤，也就是僅有來自於冷藏用冷卻器（5 )的冷 煤、或者與從冷凍用冷卻器（4 )吸入之冷煤的合流量而 產生極大的變化。 此外，相較於一般冷藏空間的室內溫度爲+ 3〜5 °C， 由於冷凍空間溫度爲一 1 8〜一2 0 °C ’因此與室外溫度間的 溫差甚大，冷卻冷凍空間所需的冷凍能力’是大於冷藏空 間所需要的値，如此一來，當冷凍側的冷凍能力大於冷藏 側的冷凍能力時，也就是當冷凍側的負荷設定成大於冷藏 側時的冷凍運轉，是如採用第6圖模式來表現的第7圖所 示，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易受到 從冷藏用冷卻器（5 )處回流之冷煤的影響’故冷凍空間 的冷卻控制，根據壓縮機（9 )的迴轉數進行控制即可’ 當冷卻不足時如箭號所示，提高壓縮機（9 )的迴轉數以 增加冷凍力，當過度冷卻時可藉由降低迴轉數或者停止的 方式來保持適當的冷卻溫度。而冷藏側的控制則非根據壓 -17- 200526912 (14) 縮機（9 )的迴轉數，而是藉由控制切換閥（1 1 )之閥開 口的開閉來調整冷煤流量，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（25 )。 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P ID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（Fi·)，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g舌’由於可提局壓縮機（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’ S冷凍空間冷卻至目標値以下時增加壓縮機（ -18- 200526912 (15) 9 )的迴轉數，由於冷凍空間（2 )無須冷卻而導致 力，在第9圖所示的圖表中，將冷凍空間溫度（F; 目標値（Fr )及冷藏空間溫度（Ra )與其目標値（ 入PID控制器（25 ) ’當決定壓縮機（9 )的迴轉 ，譬如以2倍來加算冷凍空間側之庫內溫度（Fa ) 溫度（Fr )之間的差値資料後輸入，使冷凍空間 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 的差値也就是冷凍空間（2 )側所回饋的溫度資訊 定冷凍側的基準，當冷凍空間（2 )充分冷卻時， 高壓縮機（9 )的迴轉數，是藉由切換閥（1 1 )來 向冷藏用冷卻器（5 )的冷煤流量來增減冷藏側的 力，不會導致冷凍側的過度冷卻並將冷藏側控制於 溫度。 此外，在上述的實施例中，雖然是針對增加冷 (3 )的溫度資訊來決定壓縮機（9 )的迴轉數做說 萬一外部氣溫下降而使冷藏空間（3 )的溫度低於 (Ri·)時’則根據其回饋訊號來降低壓縮機（9 ) 數，如此一來，將導致冷凍空間（2 )側之冷凍能 的問題產生。200526912 (1) IX. Description of the invention [Technical field to which the invention belongs] The present invention relates to a refrigerator using a two-stage compression type variable compressor, and particularly to a refrigerator that determines the number of compressor revolutions according to the temperature in the storage space. [Previous technology] In recent years, most refrigerators are equipped with a compressor that can change the freezing capacity by frequency conversion control. By changing its freezing capacity, the cooling performance can be obtained according to the load and the power consumption can be reduced. Generally speaking, common household refrigerators have a freezing space that can be cooled to about -18 to -20 ° C, a refrigeration and vegetable and fruit storage space that can maintain about +1 to +5 ° C, and a single cooler to The refrigerating room that cools both sides of the space uses a dumper to control the distribution of cold airflow to the refrigerated and refrigerated spaces, and drives or stops the compressor in accordance with the overall load. A refrigerator controlled by frequency conversion can further By controlling the number of revolutions of the compressor, the storage space at both sides is kept at a constant temperature. In addition, the refrigerators each having a cooler in the freezing and refrigerating space are used to switch the flow path of the cold coal to control the flow of the cold coal to the coolers arranged in the aforementioned cooling spaces, and correspond to the overall temperature and temperature difference of the cooling space. Wait to control the compressor. In addition, the cold coal compressors used in freezers and freezers on the market today have a single compression section 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 and refrigerating device has been disclosed, As shown in Fig. 3, a two-stage compressor (39) equipped with a motor, a low-stage compression element 200526912 (2) (39a), and a high-stage compression element (39b) is provided in the closed container. The outlet (46) of the condenser (40) of the element (39b) is connected with an intermediate pressure expansion device (43) at the outlet side, and communicates with the discharge side of the low-stage compression element (39a) and the high-stage compression element (3). 9b), the suction side for intermediate pressure and the suction pipe for intermediate pressure (4 7), and the evaporator for intermediate pressure (3 5) is connected between the suction pipe for intermediate pressure (47) and the expansion device for intermediate pressure (43), 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 low-stage compression element suction side of the two-stage compressor. The discharge side of the segment compression element (39a) and the high segment compression element 3 9b) The suction side is connected to the closed container (39), which can improve the accuracy of temperature control in the store, and achieve temperature uniformity, high efficiency and low power consumption in the store (please refer to Patent Document 1) . [Patent Document 1] Japanese Patent Laid-Open No. 2000-1-7 4 3 2 5 [Summary of the Invention] [Problems to be Solved by the Invention] The refrigerating cycle described in the above Patent Document 1 is used as a cooler for refrigeration. The evaporation temperature of the intermediate pressure evaporator (3 5) is higher than that of the operation; ^ The evaporation temperature of the low pressure evaporator (3 4) of the refrigeration cooler is used 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 compressor's low-stage compression part (39 a), while the refrigerating cooler (3 5) of the suction pipe (4 7) It is connected to the intermediate pressure section, so winter 200526912 (3) The freezing capacity of the freezer space is not easily affected by the cold coal flowing to the cooler for refrigeration, and the tradition of controlling the number of compressor revolutions based on the total load of the refrigeration side load and the refrigeration side load In the method, 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 reduced, resulting in a problem of insufficient cooling of the freezing space. The present invention has been developed in view of the above problems, and an object of the present invention is to provide a method for controlling two-stage compression type variable refrigeration cycles having a refrigerating and refrigerating cooler according to temperature information of a freezing space, and Freezer and refrigerated space can be controlled at appropriate temperatures. [Means for Solving the Problems] In order to solve the above-mentioned problems, the refrigerator of the present invention is a compressor in which a compression element is constituted by a low-stage compression section and a high-stage compression section, and the capacity can be changed by frequency conversion control; and A switching valve provided on the outlet side of the condenser that can receive the gas discharged from the compressor and capable of controlling the flow path and flow rate of the cold coal; and a freezing cooler and a refrigerating device connected to the switching valve through a separate pressure reducing device The refrigerator of the refrigerating cycle constituted by a cooler is characterized in that the number of revolutions of the compressor is determined according to the temperature of the freezing space and its target temperature. The refrigerator described in item 2 of the scope of patent application is composed of: a compression element composed of a low-stage compression section and a high-stage compression section, and a compressor whose capacity can be changed by frequency conversion control; and a compressor installed to accept the compression The condenser outlet side of the gas discharged from the engine, and a switching valve that can control the flow path and flow rate of the cold coal; and a refrigerating refrigeration unit connected to the above switching valve through a separate pressure reducing device. 7- 200526912 (4) The refrigerating cycle of a refrigerating cycle composed of a cooler for cold storage is characterized in that the number of revolutions of the compressor is determined according to the temperature of the freezing space and its target value, and the temperature of the refrigerating space and its target value. The feedback amount of the temperature information in the refrigerated space is greater than the feedback amount of the temperature information in the refrigerated space. [Effects of the Invention] According to the above-mentioned configuration, not only the evaporating temperature of both the refrigerating and refrigerating coolers, that is, the efficiency of the refrigerating cycle can be increased in accordance with the cooling of each storage space, but the flow of cold coal to each cooler can be switched It is also possible to control the temperature of each space appropriately by suppressing the temperature fluctuations in each space by simultaneously cooling the freezing space and the refrigerating space by way of the way and flow rate. [Embodiment] Hereinafter, one embodiment of the present invention will be described with reference to the drawings. The refrigerator body (1) shown in the longitudinal sectional view of FIG. 2 forms a storage space inside the thermal insulation box, and is divided into a freezing space (2) and a freezing room by a partition wall into a freezing compartment and an ice-making compartment. There are several storage rooms such as the refrigerated space of the fruit and vegetable room. Each storage room is cooled by a cooler (4), a cooler (5), and a cooling air circulation fan (6), (7) arranged in each freezing space and refrigerating space. The set temperature of each cooler (4), (5) is cooled by the cold coal supplied by the compressor (9) located in the mechanical room (8) below the back of the body. -8-200526912 (5) Fig. 1 shows the refrigeration cycle in the refrigerator according to the present invention, the compressor (9), the condenser (1 0), and the switching valve (] 1) of the cold coal flow path and the formation thereof. The above-mentioned freezing and refrigerating coolers (4) and (5) connected in parallel are connected in a ring shape. The aforementioned condenser (〗 G) is arranged on the outer bottom space of the refrigerator body (1), and the refrigerator body (1) is located in front of the aforementioned mechanical room (8) forming a flat plate, and the condenser ( 1 0) The liquefied cold coal passes through the switching valve (1 1), and is supplied to the refrigerating cooler (4) and the refrigerating cooler through the capillary tubes (1 2) and (1 3) as decompression devices, respectively. (5), and reduce the temperature of the cooler by evaporation, and cool the storage room to a certain air temperature by the circulation of the cooling fans (6), (7), and evaporate the cold coal after storage. The compressor (1 4) returns to the compressor (9) in degrees. The compressor (9), as shown in FIG. 3 in detail, is a reciprocating C recipr 〇ca 1) two-stage compressor in which a compression element is composed of a low-stage compression section (9a) and a high-stage compression section (9b). And constitute a reciprocating movement of the connecting rod (9g) by an eccentric shaft (9f), and the eccentric shaft (9f) is a rotary shaft of an electric mechanism (9d) housed in a sealed housing (9c) The rotation of (9 e) turns after forming eccentricity. The piston (9i) is fixed to the front end of the connecting rod (9g) by using a ball joint (9h) inlay. The reciprocating motion of the piston (9i) in the cylinder (9j) makes the aforementioned low-end side compression part (9a) and The high section side compression section (9b) alternately sucks cold coal and discharges it after compression. By using a ball joint (9h) for the compression section, the volumetric efficiency can be improved and the need for two compression sections (9a), C 9b) The expansion of the external space of the two-stage compressor (9). -9- 200526912 (6) The suction port (9k) of the lower compression part (9a) is connected to the end of the suction pipe (1 5), which is connected to the accumulator (Μ) via The above-mentioned freezing cooler (4) is used to discharge the compressed cold gas gas discharge port (9m), and the opening is formed toward the inside of the casing (9c), and the discharge port of the high-stage side compression part (9b) is It is connected to a discharge pipe (16) facing the condenser (1 0). The function of the pressure accumulator (1 4) is to store liquid cold coal that is not completely evaporated by the cooler (4) after gas-liquid separation and only discharge gaseous cold coal, which can prevent liquid cold coal from flowing into the compressor (9). In this embodiment, the failure caused by the cylinder (9j) is only provided in the rear section of the refrigerating cooler (4). The suction pipe (17) from the refrigerating cooler (5) is introduced and connected to An intermediate pressure space can be formed in the closed casing (9c). According to this, since the sucked cold coal from the refrigerating cooler (5) does not directly flow into the cylinder of the compressor ', it is not necessary to install a pressure accumulator particularly in the rear section of the refrigerating cooler (5). Just set up a small pressure accumulator. Next, the cold gas gas sucked in by the suction pipe (17) on the side of the cooler for cooling is communicated with the cold gas gas' discharged by the discharge port (9m) of the compression section (9a) of the forcing section side. The suction port (9 p) of the compression section (9 b) of the high section side is sucked to form compression. The compressor (9) can change its capacity by frequency conversion control, and set the number of revolutions to 3 based on the measured temperature of the freezing and refrigerating space, the difference between the set target, and the temperature change rate, for example. 0 ~ 7 0 Η z, and the control device constituted by the microprocessor is operated. -10- 200526912 (7) The switching valve (Η) is installed on the outlet side of the condenser (10) which receives the exhaust gas from the compressor (9), and can be switched to the cooler (4), (5) side As shown in Figure 4, a valve seat (1 9) is provided in the valve housing (1 8), and the valve seat (1 9) is formed with a cooling cooler (4) ) Side valve port A (1 9 a) and the refrigerating cooler (5) side valve port B (1 9b), and the valve body (2 0) three To the valve. The valve body (20) has two grooves A (20a) and grooves B (20b) having a V-shaped cross section formed under the thick wall section (20d) formed into a specific end edge shape. The groove A (20a) and groove B (20b) are centered on the rotation axis (20c) and adopt different rotation movement radii, respectively corresponding to the above-mentioned valve port A (19a) and valve port B (19b), and are on the turning track The upper part extends over a certain length into an arc shape, while the top surface of the valve seat (19) and the valve body (20) form a close overlap, while using a stepper motor not shown in the figure, which is arranged on the upper part, the distance is 0 ~ 80 pulse steps form a rotary drive. The switching valve (1).) Can rotate the valve body (2 0) according to the pulse signal formed by the refrigerating cycle control signal, and the groove A (2 0) located outside the rotation of the valve body is rotated at a specific pulse position. a) When it communicates with the valve port A (] 9 a), the cold coal flowing from the inflow valve port (2 1) into the valve housing (1 8) will be located by the groove A (2 0 a). The open end edge on the side of the thick-walled section (20 d) enters the V-shaped groove A (20a), flows out from the valve port A (19a) that communicates with the groove A, and is introduced for freezing. Capillaries (J 2), and vaporized by the freezing cooler (4). In addition, 'Same as above, when the groove B (-11-200526912 (8) 2 0b) inside the turning radius is connected with the valve port B (19b), the cold coal flowing into the groove B (20b) is formed from The valve port B (1 9 b) flows into the refrigerating capillary (1 3) and is evaporated by the refrigerating cooler (5). In addition, the cross-sectional area of the V-shaped groove B (2 Ob) located on the refrigerating side is enlarged from the turning end toward the open end of the thick-walled section (20d), and the valve body ( 2 0) rotation, from the smallest to the largest flow opening area to communicate with valve port B (19 b), because the flow path switching and flow adjustment can be precisely controlled, the cold coal can be efficiently controlled by the pulse rotation control Flow is changed to linear. The opening control of the valve of the three-way valve (20), although the openings of the valve ports (19a) and (19b) of the cooling cooler (4) and the refrigerating cooler (5) can be selected to be fully open and fully closed. , The freezing side opening is reduced and the refrigerating side is fully opened, or the freezing side opening is reduced and the freezing side is fully opened, but in this embodiment, the freezing cooler (4) and the refrigerating cooler (5) are connected in parallel Therefore, the cooling control is to form two types of simultaneous cooling and only the freezing side. The cold coal flowing out of the freezing side valve port A (] 9 a) is decompressed by a capillary (1 2) located in the freezing space (2), which is set to a cooling temperature, that is, an evaporation temperature, and is cooled in a freezing cooler (4 ) The cold coal evaporating at a temperature of about -2 5 □, and the cold coal 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 refrigerating capillary (1 3) having the evaporation temperature is sent to a refrigerating cooler (5) to form an evaporator. The freezing and refrigerating capillaries (! 2 -12-200526912 (9)) and (13) located in the refrigerating cycle are due to the cold coal evaporation temperature of the refrigerating cooler (4) and refrigerating cooler (5). As a result of the temperature difference, once the freezing side capillary (1 2) is strongly reduced, when the cold coal flows to both sides of the freezing and refrigerating as described above, it is bound to form a cold side that is easy to flow and has a low resistance, and it is not easy to flow to the freezing side. In extreme cases, there will be a situation where cold coal cannot flow into the freezing side. In order to improve the above problems, the switching valve (1 1) controls the flow of cold coal used to cool the freezing and refrigerating spaces (2) and (3), and to prevent the unidirectional flow of cold coal, Add flow control to restrict cold coal to the refrigerated side where it can easily flow in. If the groove A (20a) on the freezing side communicates with the valve port A (19a) and is fully opened, the freezing side cooler (4), which is hardly affected by the cold coal flow state on the refrigeration side, can almost be used. Obtaining a predetermined freezing capacity, even the freezing capacity on the refrigerating side, can be fully closed to fully opened according to the communication state between the groove B (20b) of the switching valve (11) and the valve port B (19b). The temperature range of the compressor and the change in the number of revolutions of the compressor (9) are finely controlled. Through the above-mentioned cold coal flow control, the difference between the evaporation temperature of the cooler (5) and the temperature on the freezing side can be increased, and the refrigeration can be further reduced. Cool to room temperature to 1 ~ 2. (: If the heat transfer surface area of the refrigerating cooler (5) is increased and the amount of heat exchange for cooling the refrigerated space is increased, the evaporation temperature can be further increased. In the above-mentioned occasions, the cooling temperature of the refrigerated space (3) can be further reduced. The temperature difference from the temperature of the cooler can reduce the amount of frost attached to the cooler (5) for refrigerating, and can achieve the effect of preventing the space from drying and maintaining the high humidity in the room -13- 200526912 (10). In addition, in general In a domestic refrigerator, since the freezing capacity required for cooling of the freezing space and the refrigerating space is approximately the same, the heat transfer surface area of the cooling cooler (5) can be made equal to or larger than the cooling cooler (4), and Efficiently cooling each cooling space. Next, the operation of the refrigeration cycle will be described. When the compressor (9) is driven by inputting power, a cold gas gas that is compressed into a high temperature and high pressure is formed, and will be discharged from the discharge pipe (1 6 ) Is discharged to the condenser (1 0) and reaches the switching valve (1 1). The switching valve (1 1) can be set to various combinations as described above. The refrigerated spaces (2) and (3) are uncooled, so the valve ports A (19a), B (19b) are fully opened, and the cold coal flows the fish into the freezing and refrigerating capillary (1 2), (13) After that, it flows into the decompressed refrigerating and refrigerating coolers (4) and (5), and evaporates at each evaporation temperature, and cools each cooler to a certain temperature. From the refrigerating cooler (4 The cold coal will flow into the accumulator (1 4). When the uncooled liquid cold coal remains in the cooler, the remaining cold coal will be stored inside the accumulator (1 4), and only the gas cold coal will be sucked in The pipe (1 5) is sucked into the low-pressure side compression part (9a) of the compressor (9). In addition, the cold coal evaporated in the refrigerating cooler (5) is introduced into the compression through the suction pipe (17). The machine (9) forms an intermediate-pressure sealed casing (9c). It is sucked into the low-stage compression part (9a) from the freezing cooler (4), and discharged from the compressed discharge port (9m) to the casing (9c). The cold gas gas inside is flowing from the cooler (5) into the closed casing (9c) -14-200526912 (11) After the cold gas from the coalesce merges, it is sucked into the high-end compression part (9b) from the suction port (9p), and then discharged from the compressed discharge port (9)] to the discharge pipe (16), and then introduced into the condensation () 〇) to form a refrigerating cycle. Therefore, according to the refrigerating cycle, the refrigerating and refrigerating coolers M) and (5) each including the capillary tubes (12) and (13) are provided, and the capillary tube (1 2) is provided. (1 3) The evaporation temperature is matched with the respective set temperatures of the freezing space and the refrigerating space. The cold gas gas evaporated in the refrigerating cooler (5) is maintained at a state higher than the intermediate pressure of the freezing side pressure, and directly The intermediate pressure part sucked into the compressor casing (9c) can not only make the evaporating temperature of the refrigerating cooler (5) higher than the refrigerating cooler (4), but also lower the indoor cooling temperature. Input to improve cycle efficiency 'so it can reduce power consumption. '' In addition, by increasing the evaporation temperature of the refrigerating cooler (5), the temperature difference between the refrigerating space and the refrigerating space can be reduced, which can reduce the amount of frost attached to the cooler (5), prevent the refrigerating space from drying, and keep the inside of the store. The high humidity can keep the food fresh for a long time. Not only that, because cold coal can flow into both the freezing and refrigerating coolers (4) and (5) at the same time and form cooling, compared to the traditional interactive cooling method. It is possible to suppress temperature fluctuation in each room. The refrigerating cycle is shown in Fig. 5. The same parts in Fig. 5 as those in Fig. 1 are marked with the same drawing numbers. The refrigerating cooler (4) and the refrigerating cooler (5) refer to the compressor (9). ), Condenser (1 0), and the switching valve (] 1) of the cold coal flow path form an in-line connection. From the switching valve (1), it acts as a refrigeration capillary (1 3) and a refrigeration cooler (5). The bypass pipe (2 2) of the passage is connected to the refrigerating cooler (4) through the gas-liquid separator (2 3) and from the freezing capillary-15-200526912 (12) (1 2). A suction pipe (24) connects the upper part of the gas-liquid separator (23) and the sealed casing (9c) of the compressor (9) to form an intermediate pressure intermediate pressure part. In this way, the cold coal can flow into the refrigerating cooler (5) and the refrigerating cooler (4) at the same time or selectively according to the switching valve (11) in the same control mode as described above, and come from the bypass pipe (22). The cold coal or cold coal cooler (5) is separated into gaseous cold coal and liquid cold coal in the gas-liquid separator (23), where the liquid cold coal flows to the side of the cooler (4) for freezing and the gas cold coal Then, it is returned to the intermediate pressure part of the compressor (9) through the refrigerating side suction pipe (24), and the liquid cold coal is again evaporated at a low temperature in the freezing cooler (4), and then returned to the low section side of the compressor (9). It has the same cycle efficiency as the above embodiment, and achieves the effect of cooling each storage room to a certain temperature. Fig. 6 shows that the evaporating temperature of the freezing cooler (4) and the refrigerating cooler (5) and the condensing temperature of the condenser (1 0) are set to a constant temperature, and the compressor (9) is rotated at a constant speed. The freezing capacity of the freezing side and the refrigerating side during the operation are counted, where the vertical axis is the freezing capacity on the refrigerating side and the horizontal axis is the freezing capacity on the freezing side. In the figure, point a indicates that the cold coal flows only to the refrigerating side cooler (5) through the switching valve, and point b indicates that the cold coal flows only to the refrigerating side cooler (4), and point c indicates When the valve ports (19a) and (] 9b) are fully opened, the cold coal flows to both the freezing and refrigerating coolers (4) and (5). The graph shows' the mass or volume of cold coal that is drawn directly from the cooling cooler (4) into the lower compression section (9a) of the compressor (9), -16-200526912 (13) depends on the low Compared with the 6-9 W when only flowing into the freezing side and 64 W when flowing into the freezing and refrigerating side, the corresponding refrigerating force of the cylinder exhaust volume of the compression section of the segment compression section is hardly affected by the return from the refrigerating cooler (5). The effect of cold coal to the intermediate pressure part of the compressor (9) forms a certain slug. On the other hand, the refrigerating side corresponds to the freezing power corresponding to the amount of cold coal sucked into the compressor (9) from the refrigerating cooler (5), and flows into the refrigerating and refrigerating unit at the same time as compared with 155 W when it only flows into the refrigerating side. On the side, it drops sharply to about 7. 5. W. The refrigerating capacity on the refrigerating side will be due to whether cold coal is drawn from the refrigerating cooler (4), that is, only the cold coal from the refrigerating cooler (5), Or the combined flow rate of the cold coal sucked in from the cooling cooler (4) changes greatly. In addition, compared with the normal indoor refrigerated space, the indoor temperature is + 3 ~ 5 ° C. Since the temperature of the frozen space is -18 ~ 20 ° C ', the temperature difference between it and the outdoor temperature is very large. “Capacity” is greater than the capacity required for the refrigerated space. In this way, when the freezing capacity on the freezing side is greater than the freezing capacity on the refrigerating side, that is, when the load on the freezing side is set to be greater than the refrigerating side, the freezing operation As shown in FIG. 7 represented by the 6-picture mode, the oblique line in the figure represents the part with a large freezing capacity on the freezing side. Therefore, as described above, since the freezing capacity on the freezing side is not easily affected by the cold coal flowing back from the refrigerating cooler (5), the cooling control of the freezing space is controlled based on the number of revolutions of the compressor (9). You can increase the number of revolutions of the compressor (9) to increase the freezing power when the cooling is insufficient, as shown by the arrow. When the amount of cooling is excessive, the proper cooling temperature can be maintained by reducing the number of revolutions or stopping. The control of the refrigerating side is not based on the number of revolutions of the pressure reducer (17) 2005-200526912 (14), but by adjusting the opening and closing of the valve opening of the switching valve (1 1), and thereby Control its cooling temperature. Next, an embodiment of the compressor rotation number control according to the present invention will be described with reference to a control flowchart shown in FIG. The freezing space measured by the coldness 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's peripheral wave number. Controller (25). Next, if the temperature of the freezing space (2) is higher than the target 値 (Fr), the PID will be increased according to the rate 値, and the freezing space will be 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 constant temperature. In addition, if the temperature of the freezing space (2) is lower than the target temperature (Fi ·), the number of revolutions will be reduced or the rotation will be stopped to reduce the freezing power. Next, another embodiment of the compressor rotation 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), according to the operating conditions of the refrigerator, the freezing capacity of the refrigerating space (2) is sometimes considered as the freezing capacity of the refrigerating space. insufficient. Therefore, 'enter the temperature information of the freezing space (2) and the temperature information of the refrigerating space (3) to make the compressor (9) operate within the slanted range in Fig. 7' due to the mention of the compressor (9) The number of revolutions increases the freezing capacity, so the freezing capacity of the freezing space (2) and the refrigerating space (3) can be increased. However, when the 'S freezing space is cooled below the target level, the compressor (-18-200526912 (15) 9) is increased. The number of revolutions is caused by the fact that the freezing space (2) does not need to be cooled. In the chart shown in Figure 9, the freezing space temperature (F; target 値 (Fr) and refrigerated space temperature (Ra)) and its target 値 (into PID The controller (25) 'determines the rotation of the compressor (9), for example, it calculates the difference between the internal temperature (Fa) and the temperature (Fr) of the freezer space side by 2 times, and enters the temperature of the freezer space. The feedback amount of information and data is larger than the refrigerated space. Therefore, the number of revolutions of the compressor (9) is based on the actual temperature, which is the temperature information returned from the refrigerated space (2). (2) When fully cooled, high pressure The number of revolutions of the shrinking machine (9) is to increase or decrease the force on the refrigerating side by switching the cold coal flow rate of the refrigerating cooler (5) through the switching valve (1 1), without causing excessive cooling on the freezing side and reducing the refrigerating side. In addition, in the above-mentioned embodiment, although the temperature information of the cold (3) is increased to determine the number of revolutions of the compressor (9), the temperature of the refrigerating space (3) is reduced in case the external temperature drops. When it is lower than (Ri ·), the number of compressors (9) is reduced according to its feedback signal. As a result, the problem of freezing energy on the side of the freezing space (2) will be caused.
第1 〇圖，是對應上述萬一狀態的流程圖，僅 空間（3 )溫度高於目標値（Rr )時輸入回饋其溫 的函數（Fx )，當冷藏空間溫度（Ra )與目標値（ 差異小時輸入該値，當負値時則將〇訊號輸入P I D 浪費電 a)與其 Rr )輸 數之際 與目標 (2 )側 値更大 ，來決 不需提 控制流 冷凍能 適當的 藏空間 明，當 目標値 的迴轉 力下降 於冷藏 度資訊 R1.)的 控制器 - 19 - 200526912 (16) (25 ) 〇 藉由上述的控制，即使冷藏空間（3 )的負荷輕而使 實際溫度（Ra )低於目標設定値（Rr )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（F〇 ，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（Q F 1 ) 、 （ Q R 1 )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（Q R 1 ) ’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（Q F 1 )，其 冷卻氣溫度譬如- 2 3 . 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（Q R1 )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- 200526912 (17) 度（R a )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煤量也減少 段側壓縮部之排除容積的關係，使從冷藏用冷g 回流至中間壓部後吸入高段側壓縮部的冷煤量增 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（Q R2 ) 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，由於冷煤可同時流向冷凍 (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 的冷煤循 從壓縮機 ，加上高 P 器（5 ) 加，進而 (R r )而 力過大時 ，減少冷 )之表面 ，或者降 溫度作適 用冷卻名吝 )與冷藏 來執行冷 也能由三 -21 - 200526912 (18) 向閥所構成的冷煤流動控制切換閥（n )確實地分配冷煤 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 )的冷煤流量’相較於傳統上 交互控制流向2個冷卻器之冷煤量的方式’不會使冷煤偏 流於其中一個冷卻器而導致冷煤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煤之類可燃性冷煤， 由於可減少冷煤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 ) ，其壓縮機外殼（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 爲低壓外殻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高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 從高壓外殻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- 200526912 (19) 【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煤流動間的關係圖 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1 1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- 200526912 (20) 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Fig. 10 is a flow chart corresponding to the above-mentioned case. Only when the temperature of the space (3) is higher than the target temperature (Rr), a function (Fx) of the temperature feedback is input. When the temperature of the refrigerated space (Ra) and the target temperature (Ra) Enter this signal when the difference is small, and input the 0 signal into the PID when it is negative. When the signal is wasted a) and its Rr), it will be larger than the target (2). It is clear that when the turning force of the target 値 drops below the refrigerating degree information R1.) Controller-19-200526912 (16) (25) 〇 With the above control, even if the load of the refrigerated space (3) is light and the actual temperature ( When Ra) is lower than the target setting 値 (Rr), the freezing space (2) can maintain the target 以 (F0) with the freezing force according to its temperature information (F0, which can prevent the temperature of the freezing space (2) from being higher than the freezing force due to the decrease in freezing force. The situation of the target 値 (Fr) occurs. Next, other embodiments will be described. Fig. 11 shows a refrigerating cooler (5) for driving the compressor (9) with a certain number of revolutions and keeping the condensing temperature at a certain condition. When the temperature changes, freeze and refrigerate Changes in the freezing capacity (QF 1) and (QR 1) of the cycle. At this time, it can be known that the refrigerating cooler (5) can reduce its freezing capacity (QR 1) by reducing its surface temperature. By increasing its surface temperature to increase the freezing capacity, the freezing side freezing capacity (QF 1), the temperature of the cooling gas, such as-2 3 .5 ° C is fixed, even if the freezing capacity of the refrigeration side changes, it is not easy to get too large. For the cooler (5) for refrigerating, if the number of revolutions of the refrigerating fan is changed, for example, if the number of revolutions is reduced, the amount of heat exchange at the cooler (5) will be reduced and the cooler (5) will be reduced. ) Surface temperature. In this way, the freezing capacity (Q R1) of the refrigeration cycle will also decrease. On the contrary, if the number of revolutions of the fan (7) is increased, the heat exchange amount can be increased to make the surface of the cooler (5) The temperature rises, thereby increasing the refrigeration capacity of the cycle (QR1). In other words, the cooling control of the refrigerated space (3) can be controlled by increasing or decreasing the number of revolutions of the refrigerating fan (7). When the refrigerated space temperature is -20- 200526912 (17) When the degree (R a) is higher than its target 値 (Rr), it can be cooled by increasing the number of revolutions of the cooling fan (7). When the degree of cooling is lower than (Rr), it can be reduced by reducing the number of revolutions of the fan The freezing power is controlled at an appropriate temperature. And Figure 12 shows the change of the freezing capacity (QF2) of the freezing cooler (4), the freezing and refrigerating cycles, and the change by reducing the freezing cooler ( The temperature of 4) can be cooled by the cooler (4) and sucked into the lower section of the compressor (9), thereby reducing the ability of the refrigeration side to circulate. In addition, (9) The amount of cold coal sent to the high-end compression section on the low-end side also reduces the volume exclusion relationship of the section-side compression section, so that the cold g for refrigerating is returned to the middle pressure section and sucked into the high-end compression section. The increase in the amount of cold coal increases the refrigeration capacity of the refrigeration side cycle (QR2). According to this, when the temperature of the freezing space (3) is higher than the target temperature and insufficient cooling is formed, or the freezing energy of the freezing space (2) can be reduced, the number of revolutions of the freezing side cooling fan (6) can be reduced and the freezing cooler ( 4) The amount of heat exchange further reduces the cooler (4 temperature method to increase the circulation capacity of the refrigerating side (Q R2) and the circulation capacity of the refrigerating side (QF2), and controls each space accordingly. According to the above description Because the cold coal can flow to the freezing (4) and refrigerating cooler (5) at the same time, the evaporation temperature of the freezing space (2 space (3)) can be increased, so it can be used with good circulation efficiency, even if the storage space is increased at any time. When the temperature load on the reservoir side is cooled, its target temperature drops, and when the temperature is controlled, QR2 is reduced. The cold coal passes through the compressor, plus the high-pressure device (5), and then (R r) is too strong. It can also reduce the surface of cold), or reduce the temperature to apply the cooling. 吝) and refrigerating to perform cold can also use the cold coal flow control switching valve (n) composed of three -21-200526912 (18) valve to reliably distribute cold coal. Amount, which in turn inhibits freezing And the temperature change between the refrigerated space 'between each of the empty and an appropriate temperature control. In the above-mentioned refrigeration cycle, the amount of cold coal flowing to the coolers (4) and (5) for freezing and refrigerating can be controlled simultaneously compared to the traditional method of interactively controlling the amount of cold coal flowing to the two coolers. 'Don't divert cold coal to one of the coolers and cause the amount of cold coal to exceed the amount required for the refrigeration cycle. According to this, even if a combustible cold coal such as a hydrocarbon-based cold coal is used, safety can be improved because the amount of chilled coal can be reduced. In addition, although the two-stage compressor (9) described in the above embodiment, The pressure in the compressor casing (9c) is intermediate pressure, but the present invention is not limited to this. Although not shown in the drawing, the suction pipe from the refrigerating cooler as a low-pressure casing can also be connected. In the space inside the compressor casing, the suction pipe from the refrigerating cooler is connected to the connection portion between the discharge port of the low-stage compression section and the discharge port of the high-stage compression section. In addition, it is also possible to connect the suction pipe from the refrigerating cooler as a high-pressure casing to the suction port of the low-stage compression section, and connect the suction pipe from the refrigerating cooler to the row of the low-stage compression section. The connection portion between the outlet and the discharge port of the high-stage compression section allows the exhaust gas from the high-stage compression section to be discharged from the high-pressure casing to a discharge pipe flowing to the condenser. [Industrial Applicability] According to the present invention, the present invention can be used in a refrigerator that improves cycle efficiency based on a two-stage compression refrigeration cycle structure. -22- 200526912 (19) [Brief description of the drawings] Fig. 1: A diagram showing a refrigeration cycle of a refrigerator in an embodiment of the present invention. Fig. 2: A schematic longitudinal sectional view of a refrigerator equipped with the refrigerating cycle of Fig. 1. Fig. 3: A longitudinal sectional view showing details of the two-stage compressor in Fig. 1. Figure 4: A plan view showing important details of the three-way valve in Figure 1. Fig. 5 is a block diagram showing another embodiment of the refrigeration cycle. Figure 6: The relationship between freezing and refrigerating capacity and the flow of cold coal. Figure 7: Schematic of Figure 6. Figure 8: Flow chart of compressor rotation control. Fig. 9: Flow chart of the number of revolutions control in which refrigeration temperature information is added to the control of Fig. 8. Fig. 10: A flowchart for further improving the control of the number of revolutions of Fig. 9 control. FIG. 11 is an explanatory diagram showing changes in freezing and refrigerating capacity when the temperature of the refrigerating cooler of the present invention is changed. Fig. 12 is an explanatory diagram showing changes in freezing and refrigerating capacity when the temperature of the freezing cooler of the present invention is changed. Figure 13: The freezing cycle diagram of a traditional refrigerator. [Description of Symbols of Main Components] -23- 200526912 (20) 1: Refrigerator compartment 2: Freezer space 3: Refrigerator space 4: Freezer cooler 5: Refrigerator cooler 6, 7: Cooling fan 8: Machine room
9 :兩段壓縮機9: Two-stage compressor
9 a :低段壓縮部 9b :高段壓縮部 9c :外殼 1 0 :冷凝器 1 1 :切換閥 1 2 :冷凍用毛細管 ]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9 a: low-end compression part 9b: high-end compression part 9c: housing 1 0: condenser 1 1: switching valve 1 2: refrigerating capillary tube] 3: refrigerating capillary tube 14: pressure accumulator 1 5: freezing side suction tube 1 6: Discharge pipes 17, 24: Refrigerating side suction pipe 1 8: Valve housing 1 9: Valve seat
1 9 a :冷凍側閥口 A ]9 b :冷藏側閥口 B 2 0 :閥體（三向閥） -24 - 200526912 (21) 20a :冷凍側凹溝 20b :冷藏側凹溝 2 0 c :迴轉軸 2 0 d :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: Freezing side port A] 9 b: Refrigerating side port B 2 0: Valve body (three-way valve) -24-200526912 (21) 20a: Freezing side groove 20b: Refrigerating side groove 2 0 c : Rotary shaft 2 0 d: Thick wall section 2 1: Inflow valve port 22: Bypass pipe 2 3: Gas-liquid separator 25: PID controller