200839164 ⑴ 九、發明說明 【發明所屬之技術領域】 本發明關於具備複數個蒸發器，由1台壓縮機對這些 蒸發器供給冷媒之冷卻儲藏庫及其運轉方法。 【先前技術】 作爲這種冷卻儲藏庫，下述者爲眾所皆知，即，在隔 熱性的儲藏庫本體絕熱區劃形成例如冷凍室與冷藏室，並 且在各室分別配置蒸發器，對這些的蒸發器，由1台壓縮 機交互地供給冷媒以產生冷卻作用之冷卻儲藏庫，在下述 專利文獻1揭示有該種冷卻儲藏庫。 這種冷藏庫的冷凍循環是藉由壓縮機壓縮冷媒，並且 藉由凝縮器液化，將其交互地供給至，分別經由微管連接 於三方閥的出口側之冷凍室用蒸發器及冷藏室用蒸發器， 當在接近設定溫度的溫度領域進行通常的冷卻運轉所謂控 、 制運轉時，例如當冷卻側的室到達了 OFF溫度的話，切 換三方閥，切換成另一方側的室之冷卻模式，若兩室的檢 測溫度均到達OFF溫度的話，停止壓縮機。 若依據此結構的話，具有下述優點，即，在進行上述 控制運轉時，當使用者將溫度高的食品等收容至其中一方 的儲藏室時，由於充分地進行該儲藏室的冷卻後再移行至 另一方的儲藏室之冷卻，故能夠將新收容的食品充分地冷 卻。 但，在上述結構，在將溫度高的食品收容至雙方的儲 -5- 200839164 (2) 藏室之情況時，先被冷卻之儲藏室尙可，但在之後的被冷 卻之儲藏室，會有食品之溫度不易下降之問題。 作爲這種情況之對策，在例如專利文獻2，提案有控 制裝置以預定的時間比率交互地切換兩儲藏室之技術。在 此，例如當冷藏室與冷凍室雙方的儲藏室溫度超過ON溫 度時，實行以例如3 0分鐘：20分鐘的比例交互地切換冷 凍室的冷卻與冷藏室的冷卻之交互冷卻模式，進一步即使 在此交互冷卻模式仍冷卻不足而冷凍室的溫度上升時，當 冷凍室內到達預定溫度（例如-1 2 °C )時，將上述時間比 率變更成優先冷凍室側之時間比率（例如40分鐘：20分 鐘），抑制冷凍室的庫內溫度上升。 專利文獻1 :日本實開昭6 0 - 1 8 8 9 2 8號公報 專利文獻2 :日本特開2002_223 3 6號公報 但，即使在上述結構，例如溫度高的食品被收容至冷 凍室，其室內溫度超過ON溫度而移行至冷凍室冷卻模式 、 後，則冷藏室的門被頻繁地開閉，其室內溫度即使是暫時 ，超過其ON溫度時，則會立即移行至交互冷卻模式。於 是’冷凍能力的一部分被分至冷藏室的冷卻，造成冷凍室 的冷卻變慢，其結果，變得無法充分地抑制冷凍室的溫度 上升。 又’在非通常的控制運轉，而是進行儲藏室溫度由接 近室溫的狀態冷卻至接近設定溫度之所謂下拉（pull_ down)運轉之情況，當進行上述30分鐘：20分鐘之長期 間的循環之交互冷卻模式時，則無法進行以預定設定的溫 -6- 200839164 (3) 度曲線冷卻儲藏室溫度之運轉，根據儲藏庫本體的容積等 的規格，在冷卻性能上會產生參差不齊。雖長期間循環會 有上述溫度，但若以例如3分鐘：2分鐘之短的循環進行 接互冷卻模式之切換時，則即使在急速地冷卻上述這種冷 凍室之情況時，冷凍能力分至冷藏室的冷卻之問題尤爲顯 著，極不理想。。 本發明是爲了解決上述情事而開發完成之發明，其目 的在於提供針對由1台壓縮機，對分別設置於熱負荷不同 的複數個儲藏室之複數個蒸發器選擇性地供給冷媒之冷卻 儲藏庫，可防止當成爲其中一方的儲藏室之冷卻模式時不 必要地移行至交互冷卻模式，並且亦能以預先決定的溫度 曲線執行下拉運轉之冷卻儲藏庫。 【發明內容】 作爲達成上述目的之手段，本發明的運轉方法，是針 對具備壓縮機、凝縮器、閥裝置、第1及第2蒸發器以及 用來節流流入至前述各蒸發器的冷媒之節流裝置，利用藉 由前述閥裝置，將以壓縮機壓縮並以凝縮器加以液化之冷 媒，選擇性地供給至第i及第2蒸發器，以第丨及第2蒸 發器交互地冷卻熱負荷不同之第1及第2各儲藏室之冷卻 儲藏庫的運轉方法，其特徵爲：在每預定時間算出，設定 於第1及第2的各儲藏室之目標溫度與在各儲藏室所測定 到的實際庫內溫度之偏差，並加以累積，藉由根據該累積 値控制閥裝置，來使對第1及第2各蒸發器之冷媒供給時 200839164 (4) 間的比率變化。 這樣的控制方法是可藉由具備以下結構的冷卻儲藏庫 來加以實施。 具備： 冷凍循環，其具有下述（A 1 )〜（A6 )的結構； 儲藏庫本體，其具有：相互的熱負荷不同並藉由下述 第1及第2蒸發器所產生的冷氣加以冷卻的第1及第2各 儲藏室； 目標溫度設定器，其是用來設定第1及第2各儲藏室 內的目標溫度； 第1及第2溫度感測器，這些感測器是用來檢測各儲 藏室內的庫內溫度； 裝置溫度偏差算出裝置，其是針對各儲藏室，算出目 標溫度設定器所設定的各儲藏室的各目標溫度與藉由各溫 度檢測器所檢測到的各儲藏室庫內溫度的差之溫度偏差； 夂 裝置室間溫度偏差累積裝置，其是針對藉由此裝置溫 度偏差算出裝置所算出的溫度偏差，算出每各儲藏室的差 之室間溫度偏差並累積該偏差者；以及 閥控制裝置，其是將藉由此裝置室間溫度偏差累積裝 置所累積的累積値與基準値加以比較，使閥裝置之第1及 第2的各冷媒供給路徑的開放比率變化者 (A 1 )藉由變頻馬達所驅動來壓縮冷媒的壓縮機、 (A2 )由受到此壓縮機所壓縮的冷媒散熱之凝縮器 -8- 200839164 (5) (A3 )入口連接於凝縮器側，並且兩個出口連接於 第1及第2冷媒供給路徑，可進行將入口側選擇性地連通 於第1及第2冷媒供給路徑中的任一者之流路切換動作的 閥裝置、 (A4 )分別設置於第1及第2冷媒供給路徑之第1 及第2蒸發器、 (A5 )用來節流流入至各蒸發器的冷媒之節流裝置 Λ (Α6 )由第1及第2蒸發器的冷媒出口側連接至壓 縮機的冷媒吸入側之冷媒環流路徑。 若根據本發明的話，可提供下述冷卻儲藏庫及其運轉 方法，即，由於對第1及第2各蒸發器之冷媒供給時間的 比率，不是根據設定於第i及第2的各儲藏室之目標溫度 與在各儲藏室所測定到的實際庫內溫度之偏差進行控制， 而是根據累積這些的偏差之差的累積値進行控制，故，即 使因例如門被暫時地打開，外氣流入至儲藏室內，造成庫 內溫度暫時性上升，也不會有溫度偏差的累積値急劇改變 ’因此，能夠防止，當成爲其中一方的儲藏室的冷卻模式 時，不必要地移行至交互冷卻模式。並且，由於能夠短的 循環反復進行交互冷卻模式，故，亦能以預先決定的溫度 曲線進行下拉運轉。 【實施方式】 (實施形態1 ) -9- 200839164 (6) 以下，根據圖1至圖6，說明本發明的實施形態。在 此實施形態1，是以適用於業務用的橫式（桌型）冷卻儲 藏庫之情況爲例，首先，根據圖1，說明全體構造。符號 10爲儲藏庫本體，藉由前面開口的橫長隔熱箱體所構成 ，藉由設置於底面的四角之腳1 1所支承。儲藏庫本體1 〇 的內部是藉由後安裝的隔熱性區隔壁1 2區隔成左右，左 邊的相對窄側爲相當於第1儲藏室的冷凍室1 3 F，右邊的 寬廣側爲相當於第2儲藏室的冷藏室1 3 R。再者，在冷凍 室1 3 F、冷藏室1 3 R的前面之開口，裝設有可開閉之搖動 式絕熱門（未圖示）。 在儲藏庫本體1 〇之由正面觀看時的左側部，設有機 械室1 4。在機械室1 4的上部深部側，突出形成有與冷凍 室13F連通的隔熱性冷凍室13F用之蒸發器室15，在此 設有導管15A與蒸發器風扇15B，並且在其下方，壓縮機 單元1 6可置入、取出地被收納著。又，在區隔壁1 2的冷 藏室13R側之面，藉由張設導管17形成冷藏室13R用之 蒸發器室18，在此設有蒸發器風扇18A。 前述壓縮機單元16是在基台19上設置：藉由未圖示 的馬達以定速驅動，來壓縮冷媒之壓縮機20 ;與連接於 該壓縮機2 0的冷媒吐出側之凝縮器2 1，而可由機械室1 4 內取出、置入至機械室1 4內者，並且亦搭載有用來將凝 縮器21空冷用之凝縮器風扇22 (僅圖2揭示）。 如圖2所示，凝縮器21的出口側透過乾燥機23連接 於作爲閥裝置之三方閥24的入口 24A。三方閥24是具有 -10- 200839164 (7) 1個入口 24A與兩個出口 24B、24C，各出口 24B、24C連 結於第1及第2冷媒供給路徑25F、25R。此三方閥24可 進行：使入口 24A選擇性地連通於第1及第2冷媒供給 路徑25F、25R中的任一方之流路切換動作。 在第1冷媒供給路徑25F，設有：相當於節流裝置的 冷凍室側之微管26F ;及收容於冷凍室13F側的蒸發器室 15內之冷凍室用蒸發器（第1蒸發器）2 7F。又，在第2 冷媒供給路徑25R，設有：作爲節流裝置之冷藏室側微管 2 6R ;及收容於冷藏室13R側之蒸發器室18內的冷藏室 用蒸發器（第2蒸發器）27R。兩蒸發器27F、2 7R是將 累積器28F、止向閥29及累積器2 8R依序重疊並共通連 接，並且設有由該止向閥29的下游側分歧而連接於壓縮 機2 0的吸入側之冷媒環流路3 1。由以上的壓縮機2 0的 吐出側返回至吸入側之冷媒的循環路徑是構成，藉由1台 的壓縮機20，對2個蒸發器27F、2 7R供給冷媒之習知的 t 冷凍循環40，能夠藉由三方閥24變更液態冷媒之供給對 方。 上述壓縮機20及三方閥24是受到內裝有CPU之冷 凍循環控制電路5 0。在此冷凍循環控制電路5 0 ’賦予來 自於檢測冷凍室1 3 F內的空氣溫度之相當於第1溫度感測 器之溫度感測器5 1 F及檢測冷藏室1 3 R內的空氣溫度之 相當於第2室溫度感測器之溫度感測器5 1 R的訊號。另外 ，設有目標溫度設定器5 5，使用者能夠在此設定冷凍室 1 3 F及冷藏室1 3 R的目標溫度，因應其設定操作’決定各 -11 - 200839164 (8) 儲藏室13F、13R之目標溫度TFa、TRa、上限設定溫度 TF(ON) 、丁11(〇>0以及下限設定溫度丁17(〇1；'17)、 T R ( O F F )，將因應這些溫度之訊號賦予冷凍循環控制電 路50。 在冷凍循環控制電路5 0，溫度感測器5 1 F的檢測溫 度TF較冷凍室1 3F的上限設定溫度TF ( ON )高或溫度 感測器5 1 R的檢測溫度TR較冷藏室1 3 R的上限設定溫度 ί TR ( ON )高之情況，起動壓縮機20開始進行冷卻運轉， 並且當這些的檢測溫度TF、TR低於冷凍室1 3 F及冷藏室 13R各自的下限測定溫度TF ( OFF ) 、TR ( OFF )時，停 止壓縮機20的運轉。 進一步，在冷凍循環控制電路5 0，設有裝置溫度偏 差算出裝置56，其是用來算出，目標溫度設定器55所設 定的冷凍室13F的目標溫度TFa與藉由溫度感測器51F 所檢測到的冷凍室1 3F的實際庫內溫度TF之差（TF-TFa 、 )的F室溫度偏差^TF，並且算出，目標溫度設定器55 所設定的冷藏室1 3 R的目標溫度TRa與藉由溫度感測器 5 1 R所檢測到的冷藏室1 3 R的實際庫內溫度TR之差（ TR-TRa )的R室溫度偏差△ TR。又，一倂設有，針對所 算出的各溫度偏差，算出這些差量（△ TF_ △ TR )之「室 間溫度偏差」’將該「室間溫度偏差」累積預定時間（例 如5分鐘）之裝置室間溫度偏差累積裝置5 7。因應此裝 置室間溫度偏差累積裝置57所累積之値，閥控制裝置58 控制即述二方閥24之第1及第2各冷媒供給路徑25F、 -12- 200839164 (9) 25R之開放比率。具體而言，上述兩冷媒供給路徑25F、 2 5 R的開放比率是作爲初期値，控制成R (第2冷媒供給 路徑25R) : F (第1冷媒供給路徑25F)之比率成爲3 : 7，即，冷藏室1 3 R被冷卻的時間比率（R室冷卻時間比 率）成爲〇·3，該R室冷卻時間比率是以〇.1爲刻度，可 在0.1〜0.9之範圍內變更。再者，上述裝置溫度偏差算 出裝置5 6、裝置室間溫度偏差累積裝置5 7及閥控制裝置 58是藉由執行預定軟體之CPU所構成的，其具體控制形 態如圖3及圖4所示的流程圖，以下將此控制形態與本實 施形態的作用一同進行說明。 當開啓電源，以目標溫度設定器5 5設定各目標溫度 TF a、TRa時，壓縮機20起動，首先，開始進行如圖3所 示的「R室F室冷卻時間控制」之控制流程。首先，將累 積値B初期化（步驟S 1 1 )，算出在該時間點由R室感測 器51R賦予R室（冷藏室13R)之實際庫內溫度TR與R 、 室的目標溫度TR之偏差（R室溫度偏差）ΔΤΙΙ (步驟 S 1 2 )，其次，還是在該時間點算出，由F室感測器5 1 F 所賦予F室（冷凍室13F)的實際庫內溫度TF與F室的 目標溫度TF之偏差（F室溫度偏差）△ TF (步驟S13 ) 。然後，算出在此所求出的各儲藏室1 3 F、1 3 R的溫度偏 差ATF、ATR之各儲藏室13F、13R的差之「室間溫度偏 差」（ATR-ATF )，將此作爲累積値B加以累積（步驟 S 1 4 )，在步驟S 1 5判定預定時間所決定的1個循環是否 結束，若未結束的話，則至結束爲止反復進行步驟S 1 2〜 -13- 200839164 (10) S14，算出1個循環之累積値b。 其次’將在步驟S15所算出的累積値B來與兩個上 限基準値L_UP、下限基準値L — DOWN進行比較（步驟 S16)，若累積値B較上限基準値L_UP大的話，則意味 著R室溫度偏差ATR相當大，故，將R室冷卻時間比率 RR由初期値的〇 · 3增加1級（0 · 1 )(步驟s 1 7 )，若累 積値B較下限基準値L_DOWN小的話，則意味著，R室 溫度偏差ATR的累積値小，而F室溫度偏差ATF相當大 ，因此將R室冷卻時間比率RR由初期値的0.3縮小1級 (0 · 1 )(步驟S 1 8 )，將累積値B予以初期化（步驟S 1 9 )，返回至步驟S12。再者，在累積値B處於上限基準値 L —UP與下限基準値L_D OWN之間的情況時，不需變更R 室冷卻時間比率RR而返回至步驟S 1 2。 當如以上決定了累積値B時，接著執行如圖4所示的 「R室F室切換冷卻控制」之控制流程。在此，首先重整 ( 循環經過時間計時器的値ts (步驟S2 1)，首先切換三方 閥24以打開冷藏室13R側（第2冷媒供給路徑25R側） (步驟S22 )，判斷R室冷卻時間是否結束（步驟S23 ) ，在該時間結束爲止反復進行步驟s 2 2〜S 2 3，執行冷藏 室1 3 R的冷卻。再者，R室冷卻時間是以對預定周期To (例如5分鐘）乘上前述R室冷卻時間比率RR來加以算 出的。 然後，當循環經過時間計時器的値t S成爲對周期Τ 0 乘上R室冷卻時間比率RR之値（ToxRR)以上時’則切 -14- 200839164 (11) 換三方閥24以打開（第1冷媒供給路徑2 5 F側（步驟 S24)，至經過周期To爲止反復進行步驟S24〜S25’執 行冷凍室1 3 F之冷卻，當經過周期To時，則返回至步驟 S2 1，反復進行以上的循環。其結果，在經過例如5分鐘 爲1周期To期間，冷藏室13R與冷凍室13F被交互地冷 卻，這些的冷卻時間之比率是藉由R室冷卻時間比率RR 決定。 這種冷凍室13F與冷藏室13R被交互地冷卻之交互 冷卻模式執行至雙方的儲藏室13F、13R均低於下限測定 溫度TF(OFF) 、TR (OFF)爲止（下拉運轉）。其結果 ，當各儲藏室1 3 F、1 3 R均被冷卻至接近設定溫度附近時 ，則成爲通常的控制運轉，然後，當任一個儲藏室1 3F、 13R的庫內檢測溫度TF、TR成爲較其各自的上限設定溫 度TF ( ON ) 、TR ( ON )高時，則再次開始進行壓縮機 20的運轉，移行至該儲藏室之冷卻模式。又，當處於進 行例如冷藏室13R的冷卻之冷藏室冷卻模式時，當冷凍室 1 3 F的檢測溫度TF高於上限設定溫度TF ( ON )時，則移 行至兩儲藏室1 3 F、1 3 R被交互地冷卻的交互冷卻模式。 在此，假使在決定對冷藏室13R及冷凍室13F之冷 媒供給時間的比率之際，僅監視各儲藏室1 3 F、1 3 R的目 標溫度與實際的庫內溫度之偏差ATF、ATR，控制成這些 的偏差ATF、ΔΤΙΙ大的儲藏室冷卻更長的時間時，則例如 儲藏室的門被打開，外氣流入至儲藏室內，造成庫內溫度 暫時地上升時，則對該儲藏室之冷媒供給會立即增大，因 -15- 200839164 (12) 此，會擔心不論門被關閉，庫內溫度處於返回傾 也會持續進行，使該儲藏室過度地冷卻。相對於 據本發明的話，由於取得ATR之差，根據將這 步累積所獲得的累積値B進行控制，故，即使庫 時性上升’也不會有溫度偏差的累積値B急劇改 ，不會有不必要地變更冷卻比率，能夠穩定地進 制。 (實施形態2 ) 在上述實施形態1，於目標溫度設定器5 5 於不會時間性地改變之一定的下限測定溫度TF ( TR(OFF)之訊號，將各儲藏室13F、13R的庫 室溫溫度帶冷卻至各設定溫度附近爲止之下拉運 將庫內溫度維持於設定溫度之控制運轉，均將其 定溫度控制成目標，但，在此實施形態2，目標 器是隨著時間經過一同依次地輸出不同的目標溫 〇 即，可作成下述結構，即凍室1 3 F及冷藏_ 各目標溫度是作爲其隨時間經過之變化形態（即 一同使目標溫度改變之樣子）予以賦予，作爲該 的變化形態，具有將食品等的儲藏室冷卻至使用 的設定溫度的控制運轉時之目標溫度的變化形態 設置此冷凍冷藏庫而最初開啓電源時，由較控制 設定溫度相當高的溫度冷卻至控制運轉時的溫度 向，冷卻 此，若根 些差進一 內溫度暫 變，因此 行冷卻控 輸出相當 OFF )、 內溫度由 轉、然後 一定的設 溫度設定 度之結構 【1 3 R的 與時間t 目標溫度 者所設定 、及例如 運轉時的 領域爲止 -16- 200839164 (13) 之所謂下拉冷卻運轉時之目標溫度的變化形態的2種類’ 兩種形態的任一者均是針對每個冷凍室1 3 F及冷藏室1 3 R ，根據以時間t爲變數之函數加以表示，將該函數預先記 憶於藉由例如EPROM等所構成的記憶裝置，藉由CPU等 讀出記憶於此記憶裝置之函數’配合時間經過’算出目標 溫度。在此實施形態2，其他的結構是與實施形態1完全 相同。 如此實施形態2所示’當作成下述結構’即目標溫度 設定器，隨著時間經過一同依次地輸出不同的目標溫度時 ，則如圖5的虛線所示，能夠描繪出欲冷卻之溫度的目標 曲線R、F。如此，當以2個目標曲線爲基礎，交互地冷 卻儲藏室1 3 F、1 3 R時，則冷藏室1 3 R的庫內溫度與冷凍 室1 3 F的庫內溫度是如同圖的實線R、F所示地變化。同 圖是顯示冷凍循環40的冷凍能力不足以使兩儲藏室13F 、1 3 R同時如目標曲線地進行下拉冷卻，圖6是顯示相反 的冷凍能力過剩之情況。但’即使是能力不足或過剩之情 況，也不會產生僅其中一方的儲藏室被過剩冷卻或產生冷 卻不足之情事，可均衡地將兩儲藏室1 3 F、1 3 R加以冷卻 (實施形態3 ) 在上述實施形態1、2，壓縮機20爲使用定速型者， 但亦可使用藉由變頻馬達來驅動該壓縮機2 0之可變速型 者，藉此，能夠調節冷凍循環40的能力。其實施形態作 -17- 200839164 (14) 爲實施形態3，參照圖7至圖1 0進行說明。 在此實施形態，與上述實施形態1、2不同點是壓縮 機2 0藉由變頻馬達所驅動的這一點。壓縮機2 0的變頻馬 達之旋轉數是藉由例如具備變換器並輸出可變頻率的交流 之旋轉數控制裝至6 0來控制的，對該旋轉數控制裝至6 0 ，賦予來自於溫度偏差累積値算出裝置70之訊號。又， 與實施形態2同樣地，目標溫度設定器80之結構爲隨著 時間經過，一同依次輸出不同之目標溫度，其他的點是與 實施形態1相同，對於相同的部分賦予相同的符號。 在本實施形態3的目標溫度設定器8 0，如上所述， 冷凍室13F及冷藏室13R的各目標溫度是作爲其隨時間 經過之變化形態（即與時間t 一同使目標溫度改變之樣子 )予以賦予，作爲該目標溫度的變化形態，具有將食品等 的儲藏室冷卻至使用者所設定的設定溫度的控制運轉時之 目標溫度的變化形態、及例如設置此冷凍冷藏庫而最初開 啓電源時，由較控制運轉時的設定溫度相當高的溫度冷卻 至控制運轉時的溫度領域爲止之所謂下拉冷卻運轉時之目 標溫度的變化形態的2種類，兩種形態的任一者均是針對 每個冷凍室13F及冷藏室13R，根據以時間t爲變數之函 數加以表示，該函數被記憶於藉由例如EPROM等所構成 的記憶裝置8 1。作爲顯示例如進行下拉冷卻運轉時的冷 凍室13F及冷藏室13R的各目標溫度TFa、TRa的變化形 態之函數TFa = fF ( t ) 、TRa = fR ( t )，如圖8的圖表所 示者。 -18- 200839164 (15) 來自於目標溫度設定器80的兩個目標溫度TFa， 是與由各溫度感測器5 1 F、5 1 R所獲得的兩個庫內溫, 、TR —同賦予至裝置溫度偏差算出裝置56，在此算 自的溫度偏差ATF= ( TF-TFa)及ATR的値是被賦予 一段的裝置室間溫度偏差累積裝置57及溫度偏差累 算出裝置70。在裝置室間溫度偏差累積裝置57之控 是與前述實施形態1相同地，藉由根據累積値B控制 閥24，來將冷藏室13R與冷凍室13F交互地冷卻， 的冷卻時間之比率是根據R室冷卻時間比率RR來決 〇 一方面，在溫度偏差累積値算出裝置70，進行 的控制，決定驅動壓縮機20之變頻馬達的旋轉數。 即，在例如2分鐘〜1 0分鐘（在此實施形態爲 鐘），將兩偏差ATR、ATF雙方予以合計累積，在將 賦予旋轉數控制裝至6 0。在旋轉數控制裝至6 0，將 差的累積値A與預定的基準値（下限値及上限値） 比較，當累積値A較上限値L_UP大時，使變頻馬達 轉數上升，而當累積値A較下限値L_D OWN小時， 頻馬達的旋轉數下降。再者，上述溫度偏差累積値算 置70及旋轉數控制裝至60是藉由執行預定的軟體之 所構成，該軟體的處理順序如圖9所示。 參照圖9說明該軟體之結構。當藉由CPU開始 壓縮器旋轉控制開始程序（步驟S 3 1 )時，首先將累 A予以初期化成例如0 (步驟S32 )。其次，在目標 TRa f TF 出各 至下 積値 制， 三方 這些 定的 下述 5分 該値 該偏 進行 的旋 使變 出裝 CPU 進行 積値 溫度 -19- (16) (16)200839164 設定器80，由記憶裝置8 1讀出預定的函數，藉由將變數 t (由本程序開始起算的經過時間）代入該函數，分別算 出冷藏室13R及冷凍室13F的各目標溫度TFa、TRa (步 驟S33、S34)，並且算出這些目標溫度TRa、TFa與實際 的庫內溫度TR、TF之偏差A，將其予以累積（裝置溫度 偏差算出裝置56及溫度偏差累積値算出裝置7〇之功能： 步驟S35 )。然後，至步驟S36，將累積値A與上限値 L_UP及下限値L_DOWN進行比較，增減變頻馬達的旋轉 數（旋轉數控制裝至60之功能：步驟S36〜S38 )。 若根據這樣的本實施形態3的話，當將例如下拉冷卻 運轉時之冷藏室13R及冷凍室13F的各目標溫度TFa、 TRa之時間變化形態設定成如圖1 〇的一點虛線所示，而 如實線所示般冷藏室1 3 R及冷凍室1 3 F的實際庫內溫度 TF、TR變化時，則例如在冷藏室1 3 R側，冷卻運轉的開 始當初，被冷卻成，比起目標溫度TRa，庫內溫度TR變 得更低，在冷凍室1 3 F側，被冷卻成，庫內溫度TF與目 標溫度TFa大致相同，因此總合的溫度偏差成爲負（-) ，累積値A亦成爲負（-)。在此，累積値A的圖表成爲 鋸齒狀波形是由於累積値A在每預定時間被初期化之故 (圖9、步驟S9)。然後，由於累積値A變成負，低於 下限値L_D OWN，故當初變更器頻率逐漸降低，其結果， 壓縮機20的旋轉數階段性降低而抑制冷卻能力，因此， 庫內溫度接近目標溫度的降低程度。 冷卻能力將第的結果，當庫內溫度高於目標溫度時， -20- 200839164 (17) 則冷凍室1 3 F及冷藏室丨3 R的各溫度偏差及其累積値a 變遷成正（+ )，總合的累積値A超過上限値L_UP時， 壓縮機旋轉數上升，冷卻能力變高，再次，庫內溫度成爲 接近目標溫度的降低程度。以下，藉由反復進行這樣的控 制’庫內溫度隨著所設定的目標溫度的時間變化形態，逐 漸降低。 在上述下拉冷卻運轉時，即使在途中例如儲藏庫本體 1 〇的隔熱門暫時地被打開，外氣流入，造成庫內溫度暫 時地上升，也由於該溫度上升會受到隔熱門被關閉而極速 地復原，故在作爲溫度偏差的累積値A進行觀察的狀況 下，不會有該累積値A急劇地變化的情事產生。因此， 不會有控制器5 0過度反應造成壓縮機20的旋轉數急劇地 提高，控制溫度進而有助於省電力化。 再者，在以上的說明，敘述了關於下拉冷卻運轉時， 但在將食品等的儲藏物冷卻成使用者所設定的設定溫度之 控制運轉時，也是對以設定溫度爲中間之上下決定上下値 及下限値，將顯示由上限値朝下限値使庫內溫度如何時間 性地加以變化之目標溫度的變化形態予以函數化後，再記 憶至記憶裝置，與下拉冷卻運轉同樣地，控制壓縮機之旋 轉數。因此，在進行控制運轉時，對於因隔熱門的開閉所 引起之暫時性的庫內溫度之急劇變化也不會過度反應，能 夠達到省電力化。又，由於如仿效所記憶的目標溫度之變 化形態般，控制壓縮機2 0，故，能夠適當且確實地取得 壓縮機20之運轉停止時間，在各冷卻器27F、27R發揮 -21 - 200839164 (18) 一種除霜功能，能夠防止大量地著霜。 又’在業務用的冷藏庫，上述下拉冷卻運轉成爲必要 之事態不僅於冷藏庫的初期設置時，對於關閉電源並經過 數小時後之再運轉、搬入多量的食材之際的長時間門開放 、投入多量的剛條理結束的高溫食材之情況等均爲必要， 其冷卻特性極爲重要。有鑑於這一點，在本實施形態，由 於將下拉冷卻運轉時的冷卻特性，非作爲僅溫度的最終目 標値予以賦予，而是作爲目標溫度的隨著時間的經過之變 化形態予以賦予，故對不同規格的隔熱儲藏室，使用共通 的冷凍單元。 並且，在本實施形態，在將目標溫度作爲隨著時間經 過之變化形態予以賦予之際，由於作爲每的預定時間的目 標溫度來予以賦予，故，比起例如作爲每預定時間的溫度 之變化率予以賦予的情況，具有適合於，將來自於1台的 壓縮機20之冷媒交互地供給至兩個冷卻器27F、27R來 將兩室冷卻形態的冷卻儲藏庫之優點。即，在假使作爲每 預定時間的溫度之變化率加以賦予冷卻目標，控制壓縮機 20的旋轉數以接近該變化率之情況，在交互冷卻的形態 ，在其中一方被冷卻之期間，例如另一方的儲藏室之門被 暫時地打開使得庫內溫度上升時，若將門關閉成爲冷卻該 儲藏室的話，庫內溫度會立即降低，故，冷卻運轉作爲目 標之變化率被達成。因此，成爲實際上不論庫內溫度稍微 上升，壓縮機20的旋轉數也會降低之事態，當反復產生 此事態時，則庫內溫度變得無法如期待的狀態降低。 -22- 200839164 (19) 相對於此，在本實施形態，將目標溫度的隨著時間經 過之變化形態，於每個不同預定時間（逐漸降低）之目標 溫度來加以賦予，故在庫內溫度暫時性的上升之情況，在 該時間點未能到達目標溫度的話，則使壓縮機20的旋轉 數提昇，提高冷卻能力，因此，可將庫內溫度如設定般確 實地降低。 (實施形態4 ) 如以上所述，在上述各實施形態，當大的熱負荷被收 容於其中任一方的儲藏室時，對該儲藏室之冷媒供給量立 即增大，促進熱負荷大的儲藏室之冷卻。由於這是意味著 ，另一方的儲藏室之冷卻能力降低，故亦會擔心該儲藏室 的庫內溫度上升。例如，在冷凍冷藏庫之情況，當大的負 荷被收容於冷藏室，冷藏室的冷卻時間比率單方面的增大 時，則亦會有因使用條件等，變得無法將收容於冷凍室的 冷凍食品維持於冷凍狀態之可能性。 因此，在本實施形態4，閥控制裝置5 8是以在將其 中一方的儲藏室之冷媒供給路徑的開放比率增大之情況時 ，另一方的儲藏室之庫內溫度處於較其設定溫度高出預定 値的溫度範圍內爲條件。進一步，在該情況時，以處於高 出預定値的溫度範圍內之狀態持續預定時間爲條件，可進 行更穩定之控制。再者，閥控制裝置5 8以外的結構，是 與前述實施形態3完全相同之結構。 其次，參照圖1 1至圖1 3，詳細說明本實施形態4之 -23- 200839164 (20) 閥控制裝置5 8的動作特徵。 裝置溫度偏差算出裝置5 6、裝置室間溫度偏差累積 裝置57、溫度偏差累積値算出裝置70及旋轉數控制裝至 60，是與前述實施形態3同樣地發揮功能，而壓縮機20 的旋轉數及三方閥24的開閉控制是如上述說明般進行動 作。另外，在本實施形態4，亦開始進行如圖1 1所示的 「冷卻負荷判定控制」（步驟S4 1 )。當開始進行此「冷 卻負荷判定控制」時，首先如步驟S42所示，開始進行「 R室F室冷卻時間控制」。這是如圖4所示之處理，此處 理與圖1 1之「冷卻負荷判定控制」同時被執行。 其次，移行至步驟S43，在此執行「R室庫內溫度判 定」之處理，判斷冷藏室1 3 R的庫內溫度TR爲在其設定 溫度TRa加上預定値（例如2 °C )溫度以上之狀態，是否 持續預定時間（例如5分鐘），若未符合該條件的話，則 移行至下一個步驟S44。進一步執行「F室庫內溫度判定 」之處理，判斷冷凍室13F的庫內溫度TF爲在其設定溫 度TFa加上預定値（例如2°C )溫度以上之狀態，是否持 續預定時間（例如5分鐘）’若未符合該條件的話，返回 至前一個步驟S43，反復進行步驟S43〜S44。 在這種狀態時，設定爲在例如冷藏室1 3 R收容有較大 的熱負荷（熱食品等）。於是，冷藏室1 3 R的庫內溫度上 升，由於該溫度上升持續較長的時間，故在較設定溫度 T R a高出2 °C以上的狀態持續5分裝以上時，由步驟S 4 3 移行至步驟S 4 5，開始進fT「F温度維持冷卻時間控制」 -24- 200839164 (21) 。此內容如圖1 2所示，首先三方閥24待機至冷凍室1 3 F 用的第1冷媒供給路徑25F打開狀態（F電路打開）爲止 (步驟S51 )，若成爲F電路打開的話，移行至步驟S52 ，開始進行用來判斷「R室F室冷卻時間控制」（參照圖 3 )的1個循環是否結束之時間計算，若該1個循環結束 的話（在步驟S53爲「Y」），進行「F室溫度判定」（ 步驟S54 )。此「F室溫度判定」是判斷，冷凍室13F的 庫內溫度TF對在其設定溫度TFa加上預定値α (相當於 例如庫內溫度TF的平均値與其最高値之差量的溫度）之 溫度大、或小。若TF > TFa+ α的話，則可判斷成，冷凍 室1 3 F的庫內溫度上升過高，對於冷凍室1 3 F之冷卻能力 不足，故將R冷卻時間比率降低1級（步驟S53 )。相反 地，若TF < TFa+ α的話，則可判斷成，冷凍室13F的庫 內溫度上升非過度，朝向冷凍室1 3 F之冷卻能力過剩，故 將R冷卻時間提高1級（步驟S56 )，若爲上述以外（即 TF = TFa+ α )的話，不變更R冷卻時間比率而返回至步驟 S52，反復進行以上的每1個循環之「F室溫度判定」。 其結果，由於依據「F溫度維持冷卻時間控制」，一邊考 量冷凍室13F之溫度上升，一邊藉由對冷藏室13R之冷 卻能力的重點分配，將冷藏室1 3 R逐漸地冷卻，故，冷卻 冷藏室1 3 R的庫內溫度TR，進而將心投入的食品冷卻至 冷藏室1 3 R之設定溫度爲止。因此，即使將溫度高的食品 收容至冷藏室1 3 R，也由於爲了進行冷卻，非單方面地投 入冷卻能力，而是在冷凍室13F的庫內溫度TF不會超過 -25- 200839164 (22) TFa+ α之範圍被集中冷卻，故可確實地防止，冷凍室13F 的溫度不小心上升而造成冷凍食品解凍。 又，在實行這樣的「F溫度維持冷卻時間控制」期間 ，同時地進行「R室庫內溫度恢復判定」（圖1 1、步驟 S46 )，故，當冷藏室13R的庫內溫度TR成爲低於其設 定溫度TRa時，則移行至步驟S47，再次開始進行最初的 「R室F室冷卻時間控制」。 又，相反地，當較大的熱負荷（溫度高的食品）被收 容於冷凍室1 3 F時，則由於冷凍室1 3 F的庫內溫度TF上 升，該溫度上升持續較長的時間，故，在較設定溫度TFa 高出2°C以上的狀態持續5分鐘以上時，由步驟S44移行 至步驟S48開始進行「R溫度維持冷卻時間控制」。此內 容是如圖1 3所示，與前述「F溫度維持冷卻時間控制」 的原理相同。即，判斷冷藏室1 3 R的庫內溫度TR對在其 設定溫度TRa加上預定値α (相當於例如庫內溫度TR的 平均値與其最高値之差量的溫度）之溫度大、或小，若 TR> TRa+ α的話，則可判斷成，冷藏室13R的庫內溫度 上升過高，對於冷藏室13R之冷卻能力不足，故將R冷 卻時間比率提高1級，相反地，若TR < TRa+ α的話，則 可判斷成，冷藏室1 3 R的庫內溫度上升非過度，朝向冷藏 室1 3 R之冷卻能力過剩，故將R冷卻時間降低1級。 其結果，由於一邊考量冷凍室13F之溫度上升，一邊 藉由對冷凍室1 3 F之冷卻能力的重點分配，將冷凍室1 3 F 逐漸地冷卻，故即使將溫度高的食品收容至冷凍室1 3 F， -26- 200839164 (23) 也由於爲了進行冷卻，非單方面地投入冷卻能力，而是在 冷藏室13R的庫內溫度TR不會超過TFa+α之範圍被集 中冷卻，故可確實地防止，冷藏室1 3 R的溫度不小心上升 〇 再者，本發明不限於上述說明及依據圖面做了說明之 實施形態者，例如以下的實施形態亦包含於本發明之技術 範圍。 (1)在上述實施形態，以具備冷凍室與冷藏室的冷 卻儲藏庫爲例進行了說明，但，不限於此，亦適用於具備 冷藏室與解凍室、儲藏溫度不同之冷藏雙室或冷凍雙室之 冷卻儲藏庫，即，針對具備熱負荷不同之儲藏室的冷卻儲 藏庫，可廣泛地適用於由共通的壓縮機對設置於各儲藏室 的蒸發器供給冷媒者。 (2 )在上述各實施形態，在每預定時間算出目標溫 度與庫內溫度之偏差並累積，在該累積値超過預定的基準 値之情況，立即提高壓縮機之旋轉數，但在決定壓縮機的 旋轉數之際，亦可進一步增加其他條件。 (3 )在實施形態3，目標溫度設定器80之結構爲， 將顯示目標溫度的隨著時間經過之變化形態的函數記憶於 記憶裝置8 1，讀出記憶於此記憶裝置8 1之函數並配合時 間的經過算出目標溫度，但，不限於此，亦可如圖1 4所 示，目標溫度的隨著時間經過之變化形態做成，將預先製 作將溫度與經過時間對照之參照表’將此參照表預先記憶 於記憶裝置1 〇〇，因應來自於計時裝置1 02之訊號’藉由 -27- 200839164 (24) 表讀出裝置1 〇 〇，配合時間經過，讀出該記億裝置10 〇之 目標溫度。 【圖式簡單說明】 圖1是顯示本發明的實施形態1之全體斷面圖。 圖2是實施形態1的冷凍循環的構成圖。 圖3是顯示實施形態1的冷卻動作的流程圖。 圖4是顯示實施形態1的冷卻動作的流程圖 圖5是顯示在實施形態2 ’冷卻能力不足的情況時之 溫度變化的圖表。 圖6是顯示在實施形態2 ’冷卻能力過剩的情況時之 溫度變化的圖表。 圖7是實施形態3的冷凍循環結構及方塊圖。 圖8是顯示實施形態3之冷凍室及冷藏室的目標溫度 隨著時間改變之變化形態的圖表。 圖9是顯示實施形態3之壓縮機旋轉數的控制順序之 流程圖。 圖1 〇是顯示實施形態3之下拉冷卻運轉時的庫內溫 度之變化形態與壓縮機的旋轉數之關係的圖表。 圖1 1是顯示實施形態4之「冷卻負荷判定控制」的 處理順序之流程圖。 圖1 2是顯示實施形態4之「F溫度維持冷卻時間控 制」的處理順序之流程圖。 圖1 3是顯示實施形態4之「R溫度維持冷卻時間控 -28- 200839164 (25) 制」的處理順序之流程圖。 圖14是顯示不同的目標溫度設定裝置的其他實施形 態之方塊圖。 【主要元件符號說明】 1 0 :儲藏庫本體 2 0 :壓縮機 2 1 :凝縮器 24 :三方閥（閥裝置） 2 5 F、2 5 R :第1及第2冷媒供給路徑 26F、26R :微管（節流裝置） 2 7F:冷凍室用蒸發器（第1蒸發器） 2 7R :冷卻室用蒸發器（第2蒸發器） 3 1 :冷媒環流路 40 :冷凍循環 50:冷凍循環控制電路 5 1 F :感測器（第1溫度感測器） 5 1 R :感測器（第2溫度感測器） 5 5、8 0 :目標溫度感測器 56 :溫度偏差算出手段 57 :室間溫度偏差累積手段 5 8 :閥控制手段 60 :旋轉數控制手段 70 :溫度偏差累積値算出手段 -29- 200839164 (26) 8 1 :記憶手段 100 :記憶手段 1 0 1 :表讀出手段 102 :計時手段[Technical Field] The present invention relates to a cooling storage tank having a plurality of evaporators and supplying a refrigerant to the evaporators by one compressor, and a method of operating the same. [Prior Art] As such a cooling storage, it is known that, for example, a freezer compartment and a refrigerating compartment are formed in a heat insulating partition body, and evaporators are respectively disposed in the respective chambers, In the evaporators, the refrigerant is alternately supplied to the refrigerant by a single compressor to generate a cooling storage for cooling, and the following Patent Document 1 discloses such a cooling storage. The refrigerating cycle of the refrigerator is a refrigerant compressed by a compressor, and is liquefied by a condenser to supply it alternately, and is connected to the evaporator for the freezer compartment and the refrigerating compartment of the outlet side of the three-way valve via microtubes. When the normal cooling operation is performed in the temperature range close to the set temperature, the evaporator is controlled, for example, when the cooling side chamber reaches the OFF temperature, the three-way valve is switched to switch to the cooling mode of the other chamber. If the detected temperatures of both chambers reach the OFF temperature, stop the compressor. According to this configuration, when the user performs the control operation, when the user stores the food or the like having a high temperature in one of the storage compartments, the storage compartment is sufficiently cooled and then moved. The cooling of the other storage compartment allows the newly contained food to be sufficiently cooled. However, in the above configuration, when the food having a high temperature is stored in the storage room of both sides, the storage room that is cooled first may be used, but in the subsequent storage room that is cooled, There is a problem that the temperature of the food is not easy to fall. As a countermeasure against such a situation, for example, Patent Document 2 proposes a technique in which the control device alternately switches the two storage compartments at a predetermined time ratio. Here, for example, when the storage compartment temperature of both the refrigerating compartment and the freezing compartment exceeds the ON temperature, the interactive cooling mode of the cooling of the freezing compartment and the cooling of the refrigerating compartment is alternately switched at a ratio of, for example, 30 minutes: 20 minutes, further even When the intercooling mode is still insufficiently cooled and the temperature of the freezing compartment rises, when the freezing compartment reaches a predetermined temperature (for example, -1 2 °C), the time ratio is changed to the ratio of the time of the priority freezing compartment side (for example, 40 minutes: 20 minutes), the temperature inside the freezer compartment was suppressed from rising. In the above configuration, for example, a food having a high temperature is stored in a freezer compartment, and the above-described configuration is disclosed in Japanese Laid-Open Patent Publication No. JP-A-2002-223-36. When the indoor temperature exceeds the ON temperature and moves to the freezer compartment cooling mode, the door of the refrigerating compartment is frequently opened and closed, and even if the indoor temperature exceeds the ON temperature, the indoor temperature is immediately shifted to the interactive cooling mode. Then, part of the refrigeration capacity is cooled to the refrigerator compartment, and the cooling of the freezer compartment is slowed down. As a result, the temperature rise of the freezer compartment cannot be sufficiently suppressed. Further, in the case of an abnormal control operation, a case where the storage compartment temperature is cooled from a state close to room temperature to a so-called pull-down operation close to the set temperature is performed, and the cycle of the above 30 minutes: 20 minutes is performed. In the interactive cooling mode, the operation of cooling the storage compartment temperature with a predetermined temperature of -6-200839164 (3) degree curve cannot be performed, and the cooling performance may vary depending on the size of the storage body. Although the above temperature is circulated for a long period of time, when the mutual cooling mode is switched in a cycle of, for example, 3 minutes: 2 minutes, the refrigeration capacity is divided even when the above-described freezer compartment is rapidly cooled. The problem of cooling in the cold room is particularly significant and extremely undesirable. . The present invention has been made in order to solve the above-described problems, and an object of the invention is to provide a cooling storage tank for selectively supplying a refrigerant to a plurality of evaporators each provided in a plurality of storage chambers having different heat loads by one compressor. It is possible to prevent unnecessarily moving to the interactive cooling mode when it is the cooling mode of the storage compartment of one of the parties, and it is also possible to perform the cooling storage of the pull-down operation with a predetermined temperature profile. SUMMARY OF THE INVENTION As a means for achieving the above object, an operation method of the present invention includes a compressor, a condenser, a valve device, first and second evaporators, and a refrigerant for restricting flow into the respective evaporators. The throttling device selectively supplies the refrigerant compressed by the compressor and condensed by the condenser to the i-th and second evaporators by the valve device, and alternately cools the heat by the second and second evaporators. A method of operating a cooling storage of each of the first and second storage compartments having different loads is characterized in that the target temperature of each of the first and second storage compartments is calculated for each predetermined time and is measured in each storage compartment. The deviation of the actual internal temperature is accumulated and accumulated, and the ratio between 200839164 (4) when the refrigerant is supplied to the first and second evaporators is changed by the cumulative 値 control valve device. Such a control method can be implemented by a cooling storage having the following structure. There is provided a refrigeration cycle having the following structures (A1) to (A6); and a storage body having a mutual heat load and being cooled by cold air generated by the first and second evaporators described below. The first and second storage compartments; the target temperature setter for setting the target temperatures in the first and second storage compartments; the first and second temperature sensors, which are used for detecting The internal temperature of each storage compartment; the device temperature deviation calculation means for calculating the respective target temperatures of the respective storage compartments set by the target temperature setter and the respective storage compartments detected by the respective temperature detectors for each storage compartment The temperature deviation of the difference in the temperature inside the chamber; the device for accumulating the temperature difference between the devices; the temperature deviation calculated by the device temperature deviation calculating device is calculated, and the temperature difference between the chambers is calculated and accumulated And a valve control device that compares the accumulated enthalpy accumulated by the device-to-device inter-room temperature deviation accumulating device with the reference enthalpy to cause the first and second refrigerant supply paths of the valve device The open ratio changer (A 1 ) is a compressor that is driven by a variable frequency motor to compress the refrigerant, and (A2 ) a condenser that is cooled by the refrigerant compressed by the compressor. -8- 200839164 (5) (A3) inlet connection On the condenser side, the two outlets are connected to the first and second refrigerant supply paths, and a valve for selectively switching the inlet side to the flow path switching operation of any of the first and second refrigerant supply paths is possible. The device (A4) is provided in the first and second evaporators of the first and second refrigerant supply paths, and (A5) is used to throttle the refrigerant flowing into each of the evaporators (Α6) by the first And the refrigerant outlet side of the second evaporator is connected to the refrigerant circulation path of the refrigerant suction side of the compressor. According to the present invention, it is possible to provide a cooling storage tank and a method of operating the same, that is, the ratio of the supply time of the refrigerant to the first and second evaporators is not based on the storage compartments set in the i-th and the second The target temperature is controlled by the deviation from the actual internal temperature measured in each storage compartment, but is controlled based on the cumulative 値 of the difference in the accumulated deviations, so that even if, for example, the door is temporarily opened, the external airflow is In the storage chamber, the temperature inside the storage chamber temporarily rises, and the accumulation of temperature deviation does not change abruptly. Therefore, it is possible to prevent unnecessary transition to the interactive cooling mode when the cooling mode of one of the storage compartments is reached. Further, since the interactive cooling mode can be repeated in a short cycle, the pull-down operation can be performed with a predetermined temperature profile. [Embodiment] (Embodiment 1) -9- 200839164 (6) Hereinafter, an embodiment of the present invention will be described with reference to Figs. 1 to 6 . In the first embodiment, a case of a horizontal (table type) cooling storage suitable for business use is taken as an example. First, the overall structure will be described based on Fig. 1 . Reference numeral 10 denotes a storage body which is constituted by a horizontally long heat insulating box which is open at the front, and is supported by a four-legged foot 1 1 provided on the bottom surface. The inside of the storage body 1 is partitioned by the rear wall 1 2 of the heat insulating partition, and the relatively narrow side on the left side is the freezer compartment 1 3 F corresponding to the first storage compartment, and the wide side on the right side is equivalent. In the refrigerator compartment of the second storage room, 1 3 R. Further, in the opening of the front side of the freezing compartment 1 3 F and the refrigerating compartment 13 3 R, an openable and slidable hot type (not shown) is mounted. A mechanical chamber 14 is provided on the left side portion of the storage body 1 when viewed from the front. On the deep side of the upper portion of the machine room 14 , an evaporator chamber 15 for the heat insulating freezing chamber 13F communicating with the freezing chamber 13F is formed, and a duct 15A and an evaporator fan 15B are provided therein, and underneath, compression is performed. The machine unit 16 can be housed and taken out. Further, on the side of the cold storage chamber 13R side of the partition wall 12, the evaporator chamber 18 for the refrigerator compartment 13R is formed by the extension duct 17, and the evaporator fan 18A is provided here. The compressor unit 16 is provided on the base 19: a compressor 20 that compresses the refrigerant at a constant speed by a motor (not shown), and a condenser 2 that is connected to the refrigerant discharge side of the compressor 20; It can be taken out of the machine room 14 and placed in the machine room 14 and also equipped with a condenser fan 22 for air-cooling the condenser 21 (only shown in Fig. 2). As shown in Fig. 2, the outlet side of the condenser 21 is connected to the inlet 24A of the three-way valve 24 as a valve device through the dryer 23. The three-way valve 24 has -10-200839164 (7) one inlet 24A and two outlets 24B, 24C, and each of the outlets 24B, 24C is connected to the first and second refrigerant supply paths 25F, 25R. The three-way valve 24 is configured to selectively connect the inlet 24A to the flow switching operation of either of the first and second refrigerant supply paths 25F and 25R. The first refrigerant supply path 25F is provided with a microtube 26F corresponding to the freezer side of the expansion device, and an evaporator for the freezer compartment (first evaporator) housed in the evaporator chamber 15 on the side of the freezer compartment 13F. 2 7F. Further, the second refrigerant supply path 25R is provided with a refrigerator-side microtube 2 6R as a throttle device and a refrigerator compartment evaporator (a second evaporator) housed in the evaporator chamber 18 on the refrigerator compartment 13R side. ) 27R. The two evaporators 27F, 27R are in that the accumulator 28F, the stop valve 29, and the accumulator 28R are sequentially overlapped and connected in common, and are provided to be connected to the compressor 20 by the downstream side of the check valve 29. The refrigerant ring flow path 3 1 on the suction side. A circulation path of the refrigerant returning to the suction side from the discharge side of the compressor 20 described above is configured, and a conventional t refrigeration cycle 40 for supplying refrigerant to the two evaporators 27F and 2 7R by one compressor 20 is provided. It is possible to change the supply of the liquid refrigerant to the other party by the three-way valve 24. The compressor 20 and the three-way valve 24 are subjected to a refrigeration cycle control circuit 50 in which a CPU is incorporated. Here, the refrigeration cycle control circuit 50' gives a temperature sensor 5 1 F corresponding to the first temperature sensor and an air temperature in the detection refrigerator 1 3 R from the temperature of the air in the detection freezing compartment 1 3 F It is equivalent to the signal of the temperature sensor 5 1 R of the second room temperature sensor. Further, a target temperature setter 55 is provided, and the user can set the target temperatures of the freezing compartment 1 3 F and the refrigerating compartment 13 R here, and determine the respective -11 - 200839164 (8) storage compartments 13F in accordance with the setting operation. Target temperature TFA, TRa of 13R, upper limit set temperature TF(ON), Ding 11 (〇>0, and lower limit set temperature D17 (〇1; '17), TR (OFF), will be given to these temperatures in response to freezing The cycle control circuit 50. In the refrigeration cycle control circuit 50, the detected temperature TF of the temperature sensor 5 1 F is higher than the upper limit set temperature TF ( ON ) of the freezer compartment 1 3F or the detected temperature TR of the temperature sensor 5 1 R When the upper limit setting temperature ί TR (ON ) of the refrigerating chamber 1 3 R is high, the starter compressor 20 starts the cooling operation, and when these detected temperatures TF, TR are lower than the respective freezing chambers 13 F and the refrigerating chamber 13R When the lower limit is measured at temperatures TF (OFF) and TR (OFF), the operation of the compressor 20 is stopped. Further, the refrigeration cycle control circuit 50 is provided with a device temperature deviation calculating means 56 for calculating the target temperature setter. 55 target temperature TFA of the freezer compartment 13F and The F chamber temperature deviation TF of the difference (TF-TFa, ) of the actual internal temperature TF of the freezing compartment 1 3F detected by the temperature sensor 51F is calculated, and the refrigerating compartment set by the target temperature setter 55 is calculated. The R chamber temperature deviation ΔTR of the difference between the target temperature TRa of 1 3 R and the actual internal temperature TR of the refrigerating compartment 1 3 R detected by the temperature sensor 5 1 R (TR-TRa). In addition, for each of the calculated temperature deviations, the "inter-room temperature deviation" of the difference (ΔTF_ ΔTR) is calculated, and the "room temperature deviation" is accumulated for a predetermined time (for example, 5 minutes) between the devices The temperature deviation accumulating device 57. The valve control device 58 controls the first and second refrigerant supply paths 25F, -12-200839164 of the two-way valve 24 in response to the accumulation of the inter-chamber temperature deviation accumulating device 57. 9) The opening ratio of 25R. Specifically, the opening ratio of the two refrigerant supply paths 25F and 25R is controlled as R (second refrigerant supply path 25R) as the initial value: F (first refrigerant supply path 25F) The ratio becomes 3: 7, that is, the ratio of the time during which the refrigerator compartment 1 3 R is cooled (R chamber cold Time) become square-3 ratio, the R room cooling time ratio is square. 1 is the scale, which can be 0. 1~0. Change within the scope of 9. Further, the device temperature deviation calculating means 56, the inter-device temperature difference accumulating means 57, and the valve control means 58 are constituted by a CPU executing a predetermined software, and the specific control mode thereof is as shown in FIGS. 3 and 4. The flowchart will be described below together with the action of this embodiment. When the power is turned on and the target temperatures TF a and TRa are set by the target temperature setter 5 5 , the compressor 20 is started. First, the control flow of the "R chamber F chamber cooling time control" as shown in Fig. 3 is started. First, the cumulative 値B is initialized (step S1 1 ), and the actual internal temperature TR and R of the R chamber (refrigeration chamber 13R) given by the R chamber sensor 51R at this time point are calculated, and the target temperature TR of the chamber is calculated. Deviation (R chamber temperature deviation) ΔΤΙΙ (step S 1 2 ), and secondly, at this point in time, the actual internal temperature TF and F of the F chamber (freezer chamber 13F) given by the F chamber sensor 5 1 F are calculated. The deviation of the target temperature TF of the chamber (F chamber temperature deviation) Δ TF (step S13). Then, the "inter-room temperature deviation" (ATR-ATF) of the difference between the temperature deviation ATF of each of the storage chambers 1 3 F and 1 3 R and the storage chambers 13F and 13R of the ATR is calculated. The cumulative 値B is accumulated (step S1 4), and it is determined in step S15 whether or not one cycle determined by the predetermined time is over. If not, the steps S 1 2 to -13-200839164 are repeated until the end. 10) S14, calculate the cumulative 値b of one cycle. Next, 'the cumulative 値B calculated in step S15 is compared with the two upper limit reference 値L_UP and the lower limit reference 値L- DOWN (step S16), and if the cumulative 値B is larger than the upper limit reference 値L_UP, it means R Since the room temperature deviation ATR is relatively large, the R chamber cooling time ratio RR is increased by one step (0·1) from the initial 〇·3 (step s 1 7 ), and if the cumulative 値B is smaller than the lower limit reference 値L_DOWN, This means that the accumulation of the R chamber temperature deviation ATR is small, and the F chamber temperature deviation ATF is quite large, so the R chamber cooling time ratio RR is from the initial 値0. 3 is reduced by one level (0 · 1) (step S 18), and the cumulative 値B is initialized (step S1 9), and the process returns to step S12. Further, when the cumulative 値B is between the upper limit reference 値 L —UP and the lower limit reference 値L_D OWN, the R chamber cooling time ratio RR is not changed and the process returns to step S 1 2 . When the cumulative 値B is determined as described above, the control flow of "R chamber F chamber switching cooling control" as shown in Fig. 4 is next executed. Here, first, the 値ts (step S2 1) of the cycle elapsed time timer are first switched, and the three-way valve 24 is first switched to open the refrigerating compartment 13R side (the second refrigerant supply path 25R side) (step S22), and it is judged that the R chamber is cooled. Whether or not the time is over (step S23), the steps s 2 2 to S 2 3 are repeated until the end of the time, and the cooling of the refrigerating compartment 13 R is performed. Further, the R chamber cooling time is for a predetermined period To (for example, 5 minutes). It is calculated by multiplying the aforementioned R chamber cooling time ratio RR. Then, when 値t S of the cycle elapsed time timer is multiplied by the R chamber cooling time ratio RR (ToxRR) or more, the time is cut. -14- 200839164 (11) The three-way valve 24 is opened to open (the first refrigerant supply path 2 5 F side (step S24), and the steps S24 to S25' are repeated until the cycle To is performed to perform the cooling of the freezer compartment 1 3 F. When the cycle To has elapsed, the process returns to step S2 1, and the above cycle is repeated. As a result, during a period of, for example, 5 minutes, the refrigerator compartment 13R and the freezer compartment 13F are alternately cooled, and the ratio of the cooling time is increased. Is by R chamber cooling time ratio RR The alternate cooling mode in which the freezing compartment 13F and the refrigerating compartment 13R are alternately cooled is performed until both of the storage compartments 13F and 13R are lower than the lower limit measurement temperatures TF(OFF) and TR(OFF) (downward operation). As a result, when each of the storage compartments 1 3 F and 1 3 R is cooled to near the set temperature, the normal control operation is performed, and then the internal detection temperatures TF and TR of any of the storage compartments 1 3F and 13R become When the respective upper limit set temperatures TF ( ON ) and TR ( ON ) are higher, the operation of the compressor 20 is resumed and the cooling mode is shifted to the storage compartment. In the refrigerating compartment cooling mode, when the detected temperature TF of the freezing compartment 13F is higher than the upper limit set temperature TF(ON), the transition to the alternate cooling mode in which the two storage compartments 1 3 F, 1 3 R are alternately cooled. When the ratio of the refrigerant supply time to the refrigerating compartment 13R and the freezing compartment 13F is determined, only the deviations between the target temperatures of the respective storage compartments 1 3 F and 1 3 R and the actual interior temperature ATF and ATR are monitored. The deviation of these into ATF, ΔΤΙΙ When the storage compartment is cooled for a longer period of time, for example, when the door of the storage compartment is opened and the external airflow enters the storage compartment, causing the temperature inside the storage compartment to rise temporarily, the supply of the refrigerant to the storage compartment is immediately increased, because - 15- 200839164 (12) Therefore, it is feared that regardless of whether the door is closed or not, the temperature inside the storage chamber will continue to be performed, and the storage chamber will be excessively cooled. Compared with the present invention, since the difference in ATR is obtained, according to this Since the cumulative enthalpy B obtained by the step accumulation is controlled, even if the accumulation of the time is increased, the accumulation of the temperature deviation 也不B does not change sharply, and the cooling ratio is not unnecessarily changed, and the gradation can be stably performed. (Embodiment 2) In the first embodiment, the target temperature setter 5 measures the temperature TF (TR (OFF) signal at a constant lower limit, and the storage chambers of the respective storage chambers 13F and 13R are provided. The temperature is cooled to a temperature near the set temperature, and the control operation is performed to maintain the temperature inside the set temperature at the set temperature, and the fixed temperature is controlled as a target. However, in the second embodiment, the target is along with the time. By sequentially outputting different target temperatures, it is possible to provide a structure in which the freezing chamber 1 3 F and the refrigerating_ target temperature are given as a change pattern with time (i.e., the target temperature is changed together). In this modification, there is a change in the target temperature during the control operation in which the storage compartment of the food or the like is cooled to the set temperature to be used. When the refrigerator is first turned on, the temperature is cooled by a temperature higher than the control set temperature. To control the temperature direction during operation, to cool this, if the root is delayed into an internal temperature transient, the cooling control output is quite OFF), the internal temperature is turned, The structure of the temperature setting degree is set to a certain extent [1 3 R and the time t target temperature are set, and, for example, the area at the time of operation - 16-200839164 (13) The change of the target temperature during the so-called pull-down cooling operation 2 types 'Either of the two forms is for each freezer compartment 1 3 F and the refrigerating compartment 1 3 R, and is expressed as a function of time t as a variable, and this function is previously stored in, for example, EPROM or the like. The memory device is configured to calculate a target temperature by a function such as "time of passage" by a CPU or the like reading and reading the memory device. In the second embodiment, the other configuration is completely the same as that in the first embodiment. As described in the second embodiment, the target temperature setter, which is a structure having the following structure, outputs different target temperatures in sequence as time passes, and the temperature to be cooled can be drawn as indicated by a broken line in FIG. 5 . Target curves R, F. Thus, when the storage compartments 1 3 F, 1 3 R are alternately cooled based on the two target curves, the internal temperature of the refrigerating compartment 13 R and the internal temperature of the freezing compartment 1 3 F are as shown in the figure. The lines R and F change as shown. The same figure shows that the freezing capacity of the refrigerating cycle 40 is insufficient to cause the two storage compartments 13F and 13 3 to simultaneously pull down and cool as the target curve, and Fig. 6 shows the case where the opposite freezing capacity is excessive. However, even if the capacity is insufficient or excessive, there is no possibility that only one of the storage rooms will be cooled excessively or insufficiently cooled, and the two storage rooms 1 3 F and 1 3 R can be cooled in a balanced manner (embodiment) 3) In the first and second embodiments, the compressor 20 is of a fixed speed type, but a variable speed type of the compressor 20 may be driven by a variable frequency motor, whereby the refrigeration cycle 40 can be adjusted. ability. Embodiment -17-200839164 (14) Embodiment 3 will be described with reference to Figs. 7 to 10 . In this embodiment, the difference from the above-described first and second embodiments is that the compressor 20 is driven by the inverter motor. The number of rotations of the inverter motor of the compressor 20 is controlled by, for example, a rotation number control of an alternating current having an inverter and outputting a variable frequency, and the rotation number is controlled to 60, and is given from the temperature. The deviation accumulates the signal of the device 70. Further, in the same manner as in the second embodiment, the target temperature setter 80 has a configuration in which different target temperatures are sequentially outputted as time passes, and other points are the same as those in the first embodiment, and the same portions are denoted by the same reference numerals. In the target temperature setter 80 of the third embodiment, as described above, the target temperatures of the freezing compartment 13F and the refrigerating compartment 13R are changed as a function of time (i.e., the target temperature is changed together with the time t). In the change form of the target temperature, there is a change in the target temperature during the control operation in which the storage compartment of the food or the like is cooled to the set temperature set by the user, and when the refrigerator is first turned on, for example, when the refrigerator is installed. There are two types of changes in the target temperature during the so-called pull-down cooling operation from the temperature at which the set temperature is relatively high during the control operation to the temperature range at the time of the control operation, and either of the two forms is for each of the two types. The freezer compartment 13F and the refrigerating compartment 13R are represented by a function of time t as a variable, and the function is stored in a memory device 81 composed of, for example, an EPROM. The function TFa = fF ( t ) and TRa = fR ( t ) which change the respective target temperatures TFa and TRa of the freezing compartment 13F and the refrigerating compartment 13R during the pull-down cooling operation, for example, as shown in the graph of FIG. . -18- 200839164 (15) The two target temperatures TFa from the target temperature setter 80 are the same as the two internal temperatures obtained by the temperature sensors 5 1 F, 5 1 R, and TR. The device temperature deviation calculation means 56, the temperature deviation ATF = (TF - TPa) and the ATR calculated here are the inter-device temperature difference accumulation means 57 and the temperature deviation accumulation means 70 which are given one stage. In the apparatus room temperature deviation accumulating device 57, the cooling chamber 13R and the freezing chamber 13F are alternately cooled by the cumulative 値B control valve 24 in the same manner as in the first embodiment, and the ratio of the cooling time is based on The R chamber cooling time ratio RR is determined on the one hand, and the temperature deviation is accumulated by the calculation device 70, and the control is performed to determine the number of rotations of the inverter motor that drives the compressor 20. In other words, for example, in the case of 2 minutes to 10 minutes (in this embodiment, the clock), the two deviations ATR and ATF are collectively accumulated, and the rotation number control is applied to 60. When the number of rotations is controlled to 60, the cumulative 値A of the difference is compared with the predetermined reference 値 (the lower limit 値 and the upper limit 値). When the cumulative 値A is larger than the upper limit 値L_UP, the number of revolutions of the inverter motor is increased, and when the accumulation is made, When 値A is lower than the lower limit 値L_D OWN, the number of rotations of the frequency motor decreases. Further, the temperature deviation cumulative calculation unit 70 and the rotation number control unit 70 are constituted by executing a predetermined software, and the processing sequence of the software is as shown in Fig. 9. The structure of the soft body will be described with reference to Fig. 9 . When the compressor start control program is started by the CPU (step S 3 1 ), the tired A is first initialized to, for example, 0 (step S32). Secondly, in the target TRa f TF, the following five points are accumulated, and the following five points of the three sides are determined. The rotation of the partial rotation is changed to the CPU to perform the accumulation temperature -19- (16) (16) 200839164 setting The device 80 reads a predetermined function from the memory device 81, and substitutes the variable t (the elapsed time from the start of the program) into the function, and calculates the respective target temperatures TFa, TRa of the refrigerating compartment 13R and the freezing compartment 13F (steps). S33 and S34), and the deviations A between the target temperatures TRa and TFa and the actual internal temperatures TR and TF are calculated and accumulated (the functions of the device temperature deviation calculating device 56 and the temperature deviation cumulative 値 calculating device 7): S35). Then, in step S36, the cumulative 値A is compared with the upper limit 値 L_UP and the lower limit 値L_DOWN, and the number of revolutions of the inverter motor is increased or decreased (the function of the number of rotations control 60: steps S36 to S38). According to the third embodiment, the temporal change of each of the target temperatures TFa and TRa of the refrigerating compartment 13R and the freezing compartment 13F during the pull-down cooling operation is set as shown by a dotted line in FIG. When the actual internal temperature TF and TR of the refrigerating compartment 1 3 R and the freezing compartment 1 3 F are changed as shown by the line, for example, in the refrigerating compartment 13 R side, the cooling operation is started, and is cooled to a target temperature. TRa, the internal temperature TR becomes lower, and is cooled in the freezer compartment 1 3 F side, and the internal temperature TF is substantially the same as the target temperature TFA, so the total temperature deviation becomes negative (-), and the cumulative 値A is also Become negative (-). Here, the graph in which the cumulative 値A is a sawtooth waveform is because the cumulative 値A is initialized every predetermined time (Fig. 9, step S9). Then, since the cumulative 値A becomes negative and falls below the lower limit 値L_D OWN, the frequency of the changer is gradually lowered, and as a result, the number of revolutions of the compressor 20 is lowered to suppress the cooling ability, and therefore, the temperature inside the chamber is close to the target temperature. Reduce the degree. The cooling capacity will be the first result. When the temperature in the library is higher than the target temperature, -20- 200839164 (17), the temperature deviation of the freezer compartment 1 3 F and the refrigerating compartment 丨3 R and its cumulative 値a transition to positive (+) When the cumulative 値A of the total exceeds the upper limit 値L_UP, the number of compressor revolutions increases, the cooling capacity increases, and again, the internal temperature becomes a degree of decrease close to the target temperature. Hereinafter, by repeating such control, the temperature inside the library gradually decreases as the time change pattern of the set target temperature. At the time of the above-described pull-down cooling operation, even if the heat insulating door of the storage body 1 is temporarily opened, for example, the external airflow is introduced, causing the temperature inside the storage to temporarily rise, and the temperature rise is caused to be closed by the heat insulating door. Since it is restored, in the case where it is observed as the cumulative 値A of the temperature deviation, there is no possibility that the cumulative 値A changes abruptly. Therefore, there is no excessive reaction of the controller 50, and the number of revolutions of the compressor 20 is drastically increased, and the temperature is controlled to contribute to power saving. In the above description, in the case of the pull-down cooling operation, when the storage of the food or the like is cooled to the control temperature set by the user, the upper and lower sides of the set temperature are determined. And the lower limit 値, the function of changing the target temperature in which the temperature in the library is temporally changed from the upper limit to the lower limit is functionalized, and then stored in the memory device, and the compressor is controlled in the same manner as the pull-down cooling operation. The number of rotations. Therefore, during the control operation, the transient change in the internal temperature caused by the opening and closing of the heat insulating door does not excessively react, and power saving can be achieved. Further, since the compressor 20 is controlled in accordance with the change in the target temperature that is memorized, the operation stop time of the compressor 20 can be appropriately and surely obtained, and the respective coolers 27F and 27R can be used as -21 - 200839164 ( 18) A defrosting function that prevents a large amount of frost from being applied. In addition, in the cold storage of the business, the above-mentioned pull-down cooling operation is necessary, and it is necessary to open the power supply for a long time, and to open the power supply for a long time, and to open the power supply for a long time. It is necessary to invest a large amount of high-temperature ingredients that have just been finished, and the cooling characteristics are extremely important. In view of the above, in the present embodiment, the cooling characteristic at the time of the pull-down cooling operation is not given as the final target of temperature alone, but is given as a change in the target temperature over time. Different sizes of insulated storage rooms use a common freezing unit. Further, in the present embodiment, when the target temperature is given as a change over time, since it is given as the target temperature for each predetermined time, it is compared with, for example, the temperature change per predetermined time. In the case where the rate is given, there is an advantage in that the refrigerant from the one compressor 20 is alternately supplied to the two coolers 27F and 27R to cool the two-chamber cooling form. In other words, if the rate of change of the temperature per predetermined time is given to the cooling target, the number of revolutions of the compressor 20 is controlled to approach the rate of change, and in the form of cross-cooling, for example, while the other side is being cooled, for example, the other side When the door of the storage compartment is temporarily opened to raise the temperature inside the storage compartment, if the door is closed to cool the storage compartment, the temperature inside the storage compartment is immediately lowered, so that the rate of change of the cooling operation as a target is achieved. Therefore, in actuality, the number of revolutions of the compressor 20 is actually lowered regardless of the temperature in the interior of the cylinder. When the situation is repeated, the temperature in the interior of the cylinder cannot be lowered as expected. -22- 200839164 (19) In contrast to this, in the present embodiment, the change in the target temperature over time is given at the target temperature for each predetermined time (gradually decreasing), so that the temperature in the interior is temporarily When the temperature rises, the number of rotations of the compressor 20 is increased and the cooling capacity is increased. Therefore, the temperature in the interior can be surely lowered as set. (Embodiment 4) As described above, in the above-described respective embodiments, when a large heat load is accommodated in one of the storage compartments, the supply amount of the refrigerant to the storage compartment is immediately increased, and the storage with a large heat load is promoted. Cooling of the room. Since this means that the cooling capacity of the other storage compartment is lowered, there is also concern that the temperature inside the storage compartment rises. For example, in the case of a freezer, when a large load is accommodated in the refrigerating compartment, and the cooling time ratio of the refrigerating compartment increases unilaterally, it may become unacceptable in the freezer compartment due to the use conditions and the like. The possibility that frozen foods will remain frozen. Therefore, in the fourth embodiment, when the valve control device 58 increases the opening ratio of the refrigerant supply path of one of the storage compartments, the temperature of the other storage compartment is higher than the set temperature. It is a condition within the predetermined temperature range. Further, in this case, more stable control can be performed on the condition that the predetermined time is maintained in a temperature range higher than the predetermined threshold. Further, the configuration other than the valve control device 58 is the same as that of the above-described third embodiment. Next, the operational characteristics of the valve control device 58 of the -23-200839164 (20) of the fourth embodiment will be described in detail with reference to Figs. 11 to 13. The device temperature deviation calculating device 56, the inter-device temperature difference accumulating device 57, the temperature deviation cumulative 値 calculating device 70, and the number-of-rotations control device 60 function in the same manner as in the third embodiment, and the number of revolutions of the compressor 20 The opening and closing control of the three-way valve 24 is performed as described above. Further, in the fourth embodiment, the "cooling load determination control" shown in Fig. 11 is started (step S4 1). When the "cooling load determination control" is started, first, as shown in step S42, "R chamber F chamber cooling time control" is started. This is the processing shown in Fig. 4. Here, it is executed simultaneously with the "cooling load determination control" of Fig. 11. Next, the process proceeds to step S43, where the processing of "R chamber internal temperature determination" is performed, and it is determined that the internal temperature TR of the refrigerating chamber 13 R is higher than the predetermined temperature (for example, 2 ° C) at the set temperature TRa. Whether the state continues for a predetermined time (for example, 5 minutes), if the condition is not met, the process proceeds to the next step S44. Further, the process of "F-chamber temperature determination" is further performed, and it is determined whether or not the internal temperature TF of the freezer compartment 13F is equal to or higher than a predetermined temperature (for example, 2 ° C) at the set temperature TFA, and is continued for a predetermined time (for example, 5). If the condition is not met, the process returns to the previous step S43, and steps S43 to S44 are repeated. In this state, for example, a large heat load (hot food or the like) is accommodated in, for example, the refrigerating compartment 13R. Then, the temperature in the refrigerator compartment 1 3 R rises, and since the temperature rise continues for a long period of time, when the temperature is higher than 2 ° C or higher than the set temperature TR a for 5 minutes or more, the step S 4 3 is performed. Move to step S 4 5 and start the fT "F temperature maintenance cooling time control" -24- 200839164 (21). As shown in FIG. 12, the three-way valve 24 waits until the first refrigerant supply path 25F for the freezing compartment 1 3 F is opened (the F circuit is turned on) (step S51), and if the F circuit is turned on, the process proceeds to In step S52, the calculation of the time for determining whether or not one cycle of the "R chamber F room cooling time control" (see Fig. 3) is completed is started, and if the one cycle is completed ("Y" in step S53), the process proceeds. "F chamber temperature determination" (step S54). This "F chamber temperature determination" is determined by adding the predetermined temperature TFα to the set temperature TFa of the freezer compartment 13F (corresponding to, for example, the temperature of the difference between the average 値 of the internal temperature TF and the highest enthalpy thereof). The temperature is large or small. When TF > TFa + α, it can be judged that the temperature in the freezer compartment 1 3 F rises too high, and the cooling capacity of the freezer compartment 13 F is insufficient, so the R cooling time ratio is lowered by one step (step S53) . Conversely, if TF < TFa + α, it can be determined that the temperature in the freezer compartment 13F is not excessively increased, and the cooling capacity toward the freezer compartment 13 F is excessive, so that the R cooling time is increased by one step (step S56), and (Terminal TF = TFa + α), the process returns to step S52 without changing the R cooling time ratio, and the "F chamber temperature determination" for each of the above cycles is repeated. As a result, the temperature of the freezing compartment 13F is increased in accordance with the "F temperature-maintaining cooling time control", and the refrigerating compartment 1 3 R is gradually cooled by focusing on the cooling capacity of the refrigerating compartment 13R, so that cooling is performed. The inner temperature TR of the refrigerator compartment 13 R is further cooled to the set temperature of the refrigerator compartment 13 R. Therefore, even if the food having a high temperature is stored in the refrigerating chamber 13 R, the cooling capacity is not unilaterally input for cooling, but the temperature TF in the freezer compartment 13F does not exceed -25-200839164 (22 The range of TFa+α is concentrated and cooled, so that it is possible to surely prevent the temperature of the freezing compartment 13F from rising undesirably and causing the frozen food to thaw. In addition, during the "F temperature maintenance cooling time control", the "R chamber internal temperature recovery determination" is performed simultaneously (FIG. 1 1 and S46), so that the internal temperature TR of the refrigerating compartment 13R is low. When the temperature TRa is set, the process proceeds to step S47, and the first "R chamber F chamber cooling time control" is resumed. On the contrary, when a large heat load (food having a high temperature) is accommodated in the freezer compartment 1 3 F, the temperature rise TF of the freezer compartment 1 3 F rises, and the temperature rises for a long time. Therefore, when the state is higher than the set temperature TFA by 2 ° C or more for 5 minutes or longer, the process proceeds from step S44 to step S48 to start the "R temperature maintenance cooling time control". This content is as shown in Fig. 13 and is the same as the principle of "F temperature maintenance cooling time control" described above. That is, it is judged that the internal temperature TR of the refrigerating compartment 13 R is larger or smaller than the temperature at which the predetermined temperature Δα is added to the set temperature TRa (corresponding to, for example, the temperature of the difference between the average enthalpy of the internal temperature TR and the highest enthalpy thereof). If TR > TRa + α, it can be judged that the temperature inside the refrigerator compartment 13R rises too high, and the cooling capacity of the refrigerator compartment 13R is insufficient, so the R cooling time ratio is increased by one step, and conversely, if TR < TRa + α, it can be judged that the temperature inside the refrigerator compartment 13 R is not excessively increased, and the cooling capacity toward the refrigerator compartment 13 R is excessive, so that the R cooling time is lowered by one step. As a result, the temperature of the freezer compartment 13F is increased, and the freezing compartment 1 3 F is gradually cooled by focusing on the cooling capacity of the freezer compartment 13 F. Therefore, even if the food having a high temperature is stored in the freezer compartment 1 3 F, -26- 200839164 (23) Also, in order to perform cooling, the cooling capacity is not unilaterally input, but the inside temperature T of the refrigerating chamber 13R does not exceed the range of TFa + α, and is concentrated and cooled. The present invention is not limited to the above description and the embodiments described with reference to the drawings. For example, the following embodiments are also included in the technical scope of the present invention. (1) In the above embodiment, the cooling storage compartment including the freezing compartment and the refrigerating compartment has been described as an example. However, the present invention is not limited thereto, and is also applicable to a refrigerating double compartment or a freezing compartment having a refrigerating compartment and a defrosting compartment, and having different storage temperatures. A two-chamber cooling storage, that is, a cooling storage having storage compartments having different heat loads, can be widely applied to a refrigerant supplied to an evaporator provided in each storage compartment by a common compressor. (2) In each of the above embodiments, the deviation between the target temperature and the internal temperature is calculated and accumulated every predetermined time, and when the accumulated enthalpy exceeds a predetermined reference enthalpy, the number of revolutions of the compressor is immediately increased, but the compressor is determined. When the number of rotations is increased, other conditions can be further increased. (3) In the third embodiment, the target temperature setter 80 is configured to store a function of the change in the display target temperature over time in the memory device 8.1, and read the function stored in the memory device 8 1 and The target temperature is calculated based on the elapse of the time. However, as shown in FIG. 14 , the target temperature may be changed over time, and a reference table in which the temperature is compared with the elapsed time will be prepared in advance. The reference table is pre-stored in the memory device 1 〇〇, and the signal from the timing device 102 is read by the device 1 -27-200839164 (24), and the device is read out. The target temperature of 〇. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing the entire structure of a first embodiment of the present invention. Fig. 2 is a configuration diagram of a refrigeration cycle in the first embodiment. Fig. 3 is a flow chart showing the cooling operation in the first embodiment. Fig. 4 is a flow chart showing the cooling operation in the first embodiment. Fig. 5 is a graph showing the temperature change in the case where the cooling capacity of the second embodiment is insufficient. Fig. 6 is a graph showing temperature changes in the case where the cooling capacity of the second embodiment is excessive. Fig. 7 is a block diagram and a block diagram of a refrigeration cycle according to a third embodiment; Fig. 8 is a graph showing a change in the target temperature of the freezing compartment and the refrigerating compartment according to the third embodiment as a function of time. Fig. 9 is a flow chart showing the control procedure of the number of revolutions of the compressor in the third embodiment. Fig. 1 is a graph showing the relationship between the variation of the internal temperature and the number of revolutions of the compressor during the lower cooling operation in the third embodiment. Fig. 11 is a flow chart showing the processing procedure of "cooling load determination control" in the fourth embodiment. Fig. 12 is a flow chart showing the processing procedure of "F temperature maintenance cooling time control" in the fourth embodiment. Fig. 13 is a flow chart showing the processing procedure of "R temperature maintenance cooling time control -28 - 200839164 (25) system" in the fourth embodiment. Fig. 14 is a block diagram showing another embodiment of different target temperature setting means. [Description of main component symbols] 1 0 : Storage main body 2 0 : Compressor 2 1 : Condenser 24 : Three-way valve (valve device) 2 5 F, 2 5 R : First and second refrigerant supply paths 26F, 26R: Microtube (throttle device) 2 7F: Freezer evaporator (first evaporator) 2 7R: Cooling chamber evaporator (2nd evaporator) 3 1 : Refrigerant circulation path 40: Refrigeration cycle 50: Refrigeration cycle control Circuit 5 1 F : Sensor (1st temperature sensor) 5 1 R : Sensor (2nd temperature sensor) 5 5, 8 0 : Target temperature sensor 56 : Temperature deviation calculation means 57 : Inter-chamber temperature deviation accumulating means 5 8 : Valve control means 60 : Rotation number control means 70 : Temperature deviation accumulation 値 Calculation means -29 - 200839164 (26) 8 1 : Memory means 100 : Memory means 1 0 1 : Table reading means 102: Timing means