201219731 六、發明說明： 【發明所屬之技術销域】 本發明係一種滿硬式 提供一種量測實際冰次入、*器冷媒液位控制方法，其係 媒蒸發壓力值與冷媒冷凝=水溫差值、冷媒吐出溫度、冷 出溫度誤差值及一實際與塾力，/而得出一實際與期望吐 根據該誤差值調整電子=望算術平均溫差誤差值，進而 冷媒液位，而可有效發撞之開度’以控制蒸發器之 蒸發溫度。 Γ，，、"器之熱交換面積，並能提升 【先前技術】 近年冷束空調的技術已趨近於成熟，然冷束或空調的 基本概念，其係利用冷媒與液體熱交換，以提升或降低液 體的溫度，或者，降低或提升冷媒的溫度，進而達到空調 或冷凍的目的。 而於熱交換過程中較常見的裝置，其係為滿液式冷媒 系統，該滿液式冷媒系統具有一壓縮機、一冷凝器、一電 子式膨脹閥與一滿液式蒸發器，壓縮機具有一入口端與一 出口端，出口端係以一管路連接冷凝器，冷凝器係以一管 線連接電子式膨脹間γ電子式膨脹閥係一管線連接滿液式 蒸發器，滿液式蒸發器係以一管線連接壓縮機，另於滿液 式蒸發器中設有一液位感測器。 滿液式蒸發器中冷媒的液面於最佳狀態下，其係剛好 覆盘位於滿液式蒸發裔中最ί排的銅管，以使冷媒斑流動 於銅管中之液體進行熱交換，該液體可為水、油或鹵水等， 201219731 2!有===，高度’現有之技術中以採用液位 谓幻冷凝态之壓力與漸進溫度的三種常見方式。 種液位感測器的方式，其係將液位感測器配 :式賴閥，來作為控制冷舰面之方法，於 100〇/〇il# , + 7 K 立*於實際狀態中’壓縮機有可能只有部分： 丄由於液位感測II所設定之冷媒液位與實際液位，二者 ΐ數極再者’冷媒的蒸發彿騰亦會增加整:之 k數而使仵冷媒非處於最佳液位處，因此蒸發器益 之功ί ’並造成冷媒蒸發溫度與壓縮機運轉 度較Γ，並^衫現有的液位感測11的液位解析精準 第二_㈣測冷凝器㈣的方式，其係將所 聖力轉換纽度’再加上—溫度差值，以作為 H ’進而㈣冷職位，但冷媒餘之高度係受到4 崧發溫度的影響’而冷媒之吐出溫度變化量可說甚人' :化量力:上溫度侦測之誤差值造成冷媒液 =外::卜界因素亦會造成誤判，如外界之熱氣= 4:難ΐΐ!溫度與吐出溫度過高之假象，而使增： 度，再者’偵測冷凝器之壓力亦無法應用於部分 、載或較低冷凝壓力條件下之最佳液位的需求。、 出水!;進溫度的控制方式，其係利用保持冰水 度固定的溫度差值，來達到冷媒液 =制的目的，但仍無法適用於部分貞載條件時， 最佳液位與最佳蒸發溫度條件下的需求。 '、 201219731 综合上述，現有的三種常見單一 位控制方法，其分別具#_較 目/㈣疋值之冷媒液 無法達到械控制部分貞編_度較差、 現有的冷媒液位控制方法仍有改善空間。令w立，所以 【發明内容】 *有鑑於上述之缺點，本發明之目的在於提供一 ^器冷雜位控制方法，其_用所設定之冰水1出 =差、所測得之實際冰水人出水溫差值、冷媒吐出溫度、 冷媒蒸發壓力值與冷媒冷凝壓力值，以懸電子 二進而控制蒸發器中之冷媒液位，而可有效發揮蒸 Iβ之熱交換面積，並能提升蒸發溫度，以使蒸發器得以 於最佳的冷職發溫度下，提升冰水機部份負載條件 下的運轉效率，並亦具有成本低廉與液位控制精準度 優點。 為了達到上述之目的，本發明之技術手段在於提供一 種滿液式蒸發器冷媒液位控制方法，其步驟包括如下：〃 A、設定基本條件：設定多個溫差值與多個修正值。 、量測溫度與壓力：量測一冰水入水溫度、一冰水出 水概度、一冷媒蒸發壓力值、一冷媒冷凝壓力值與一冷 吐出溫度值。 7 ' C、 計算誤差值：依據該步驟A及B所得之數據，而 得出誤差值。 D、 控制電子式膨脹閥之開度：依該步驟C所得之誤 差值，以控制該電子式膨脹閥之開度。 201219731 述之步μ中，溫差值與修正值為—蒸發器之 溫差、一額定冰水入出水溫差值、一算術平 = 算術平均溫差值$立帶與—吐出溫度修 正值，异術平均溫度修正值在_〇·5〜〇 5之間，吐出溫度修正 ΐίΓ5之：。並且額定算術平均溫差值、額定冰水入出 7二值三算術平均溫差修正值與吐出溫度修正值係設定 於-控制$中；以及電子式膨脹閥於—壓縮機啟動運轉的 初始開度所設定之設定值可為50〜100%。 如上所述之步驟Β，其係以多個溫度感測器分別量测 林入水溫度、冰水出水溫度與冷媒吐出溫度，另以多個 壓力感測11分職㈣發料㈣機之吸氣管的冷媒落發 壓力值與冷凝料壓縮機之吐出管的冷媒冷凝壓力值了溫 度感測器與壓力感測H係將所量測之冰水人水溫度、冰水 出水溫度、冷媒吐出溫度、冷媒蒸發壓力值與冷媒冷凝 力值傳送給控制器。 如上所述之步驟C，其進一步具有： C1、計算壓縮機之期望吐出溫度與蒸發器之算術平均 溫差之期望值：依據冷媒蒸發壓力值、冷媒冷凝壓力值與 吐出溫度修正值，而得出壓縮機之期望吐出溫度；以及ς 據冰水入水溫度與冰水出水溫度的溫差值、該算術平均严 差修正值與該敎算術平均溫差，而得㈣紐器之期= 算術平均溫差值。 C2、計算冷媒蒸發溫度：依據冷媒蒸發壓力值，而 出一冷媒蒸發溫度。 C3、計算實際的算術平均溫差：依據冰水入水溫度、 201219731 冰水出水溫度與冷媒蒸發溫度，而得出一實際算術平均溫 差值。 C4、計算冷媒吐出溫度與算術平均溫差之誤差值：依 據冷媒吐出溫度與期望冷媒吐出溫度，而得出一實際與期 ^吐出溫度誤差值；以及依據實際算術平岣溫差值與期望 算術平均溫差值，而得出一實際與期望算術平均溫差誤差 於步驟C1中 βm !刀值乙π ，产媒 冷凝壓力值之簡稱為RSCp，吐出溫度修正值之簡^為 CSHDT，期望吐出湓度之簡稱為SHDTexp，期望吐 之計算公式為：SHDTexp={a + b χ (RSCp)+c = + d x (RSEP) + Cshdt}，而 &、b、c、d 為常數。 =步驟Cl中’冰水人水溫度之簡稱為CWrt ^溫度之簡稱為CWLT，額定冰水 出 算術平均溫絲正值之，駭為201219731 VI. Description of the invention: [Technical sales field of the invention] The present invention provides a method for measuring the actual ice sub-injection and the refrigerant liquid level control method, which is the difference between the medium evaporation pressure value and the refrigerant condensation=water temperature difference. , the refrigerant discharge temperature, the cold temperature error value and an actual and the force, / and an actual and expected spit according to the error value to adjust the electronic = expected arithmetic mean temperature difference error value, and then the refrigerant liquid level, and can effectively hit The opening degree 'to control the evaporation temperature of the evaporator. The heat exchange area of Γ,,, " can be improved [previous technology] In recent years, the technology of cold beam air conditioner has approached maturity, but the basic concept of cold beam or air conditioner is to use heat exchange between refrigerant and liquid to Raise or lower the temperature of the liquid, or lower or raise the temperature of the refrigerant to achieve the purpose of air conditioning or freezing. The more common device in the heat exchange process is a flooded refrigerant system having a compressor, a condenser, an electronic expansion valve and a flooded evaporator, and a compressor. The utility model has an inlet end and an outlet end, wherein the outlet end is connected to the condenser by a pipeline, and the condenser is connected by a pipeline to the electronic expansion chamber γ electronic expansion valve system to connect the full liquid evaporator, full liquid evaporation The unit is connected to the compressor by a pipeline, and a liquid level sensor is provided in the full liquid evaporator. In the liquid-liquid evaporator, the liquid level of the refrigerant is in an optimal state, and it is just the copper tube which is placed in the full liquid evaporating body to heat exchange the liquid in the copper tube. The liquid can be water, oil or brine, etc. 201219731 2! There is ===, height 'there are three common ways of using the pressure and progressive temperature of the liquid level in the existing technology. A method of liquid level sensor, which is equipped with a liquid level sensor: a method of controlling a cold ship surface, at 100 〇 / 〇 il # , + 7 K 立 * in actual state ' There may be only a part of the compressor: 丄Because of the liquid level and the actual liquid level set by the liquid level sensing II, the number of the two is extremely high. The evaporation of the refrigerant will also increase the whole: the k number will make the refrigerant It is not in the optimal liquid level, so the evaporator benefits and the refrigerant evaporation temperature and compressor operation are relatively low, and the liquid level sensing of the existing liquid level sensing 11 is accurate. Second _ (four) condensing The way of (4) is to convert the Holy Force to Newton' plus the temperature difference as H' and then (4) cold position, but the height of the refrigerant is affected by the temperature of 4 bursts' and the refrigerant is spit out. The amount of temperature change can be said to be '':' The amount of force: the error value of the upper temperature detection causes the refrigerant liquid = outside:: The boundary factor will also cause misjudgment, such as the external heat = 4: difficult! Temperature and discharge temperature is too high The illusion, but increase: degree, and then 'detect the pressure of the condenser can not be applied to the part, load or lower The best level of demand under the condensate pressure. , the water supply!; the temperature control method, which uses the temperature difference fixed to maintain the ice water temperature to achieve the purpose of the refrigerant liquid = system, but still can not be applied to some load conditions, the best liquid level and the best Demand under evaporation temperature conditions. ', 201219731 In summary, the existing three common single-position control methods, respectively, have a #_目目/(四)疋 value of the refrigerant liquid can not reach the mechanical control part _ _ degree is poor, the existing refrigerant level control method still improves space. Therefore, in view of the above disadvantages, the object of the present invention is to provide a cold trap control method, which uses the set ice water 1 out = difference, the measured actual ice The water temperature difference between the water, the refrigerant discharge temperature, the refrigerant evaporation pressure value and the refrigerant condensation pressure value, and the suspension electrons to control the refrigerant liquid level in the evaporator, can effectively exert the heat exchange area of the steam Iβ, and can raise the evaporation temperature. In order to enable the evaporator to improve the operating efficiency under partial load conditions of the ice water machine under the optimal cold duty temperature, it also has the advantages of low cost and accurate liquid level control. In order to achieve the above object, the technical means of the present invention is to provide a liquid level evaporator refrigerant liquid level control method, the steps of which include the following: 〃 A, setting basic conditions: setting a plurality of temperature difference values and a plurality of correction values. Measuring temperature and pressure: measuring the temperature of an ice water into the water, an ice water outlet, a refrigerant evaporation pressure value, a refrigerant condensation pressure value, and a cold discharge temperature value. 7 ' C. Calculated error value: Based on the data obtained in steps A and B, the error value is obtained. D. Controlling the opening degree of the electronic expansion valve: according to the error difference obtained in the step C, to control the opening degree of the electronic expansion valve. In 201219731, in the step μ, the temperature difference and the correction value are the temperature difference between the evaporator, the temperature difference between the rated ice water and the water, the arithmetic level = the arithmetic mean temperature difference, the vertical band and the discharge temperature correction value, and the average temperature of the abnormal operation. The correction value is between _〇·5~〇5, and the temperature correction ΐίΓ5 is: And the rated arithmetic mean temperature difference, the rated ice water in and out of the 7 two value three arithmetic mean temperature difference correction value and the discharge temperature correction value are set in - control $; and the electronic expansion valve is set in the initial opening of the compressor start operation The setting value can be 50 to 100%. In the step described above, the temperature of the forest water, the temperature of the ice water and the temperature of the refrigerant discharge are respectively measured by a plurality of temperature sensors, and the pressure is measured by a plurality of pressures (4) the inhalation of the machine (4) The refrigerant pressure drop value of the pipe and the refrigerant condensing pressure value of the discharge pipe of the condensate compressor. The temperature sensor and the pressure sensing H system measure the ice water water temperature, the ice water water temperature, and the refrigerant discharge temperature. The refrigerant evaporation pressure value and the refrigerant condensation force value are transmitted to the controller. Step C, as described above, further has: C1, calculating an expected value of the expected average discharge temperature of the compressor and the arithmetic mean temperature difference of the evaporator: the compression is obtained according to the refrigerant evaporation pressure value, the refrigerant condensation pressure value, and the discharge temperature correction value. The expected discharge temperature of the machine; and the temperature difference between the ice water inlet temperature and the ice water outlet temperature, the arithmetic mean difference correction value and the arithmetic mean temperature difference, and the (four) button period = the arithmetic mean temperature difference. C2. Calculate the evaporation temperature of the refrigerant: according to the evaporation pressure value of the refrigerant, a refrigerant evaporation temperature is obtained. C3. Calculate the actual arithmetic mean temperature difference: based on the ice water inlet temperature, 201219731 ice water outlet temperature and refrigerant evaporation temperature, an actual arithmetic mean temperature difference is obtained. C4. Calculating the error value of the refrigerant discharge temperature and the arithmetic mean temperature difference: according to the refrigerant discharge temperature and the desired refrigerant discharge temperature, an actual and period temperature temperature error value is obtained; and the actual arithmetic temperature difference and the desired arithmetic mean temperature difference are obtained. The value is obtained, and an actual and expected arithmetic mean temperature difference error is obtained in step C1, βm ! knife value π, the medium condensation pressure value is referred to as RSCp, and the discharge temperature correction value is simply CSHDT, which is the abbreviation of the desired discharge temperature. For SHDTexp, the expected formula for the spit is: SHDTexp={a + b χ (RSCp)+c = + dx (RSEP) + Cshdt}, and &, b, c, d are constants. = in step Cl, the abbreviation of 'ice water water temperature' is CWrt ^ temperature is simply referred to as CWLT, and the rated ice water is the positive value of the arithmetic mean temperature.
2為~，.期望算術平均溫差值之簡稱為、（-，皿差= 望异術平均溫差值之計算公式 exp) J CWLT)/ ΔΤχ =(CWRT- 發中’冷媒蒸發溫度之簡稱為RSET，々媒吱 發酿度之計算公式為：RSET 冷媒蒸 (R，)°·5，其中al、bl、cl為常數。 實二驟C3中’實際算術平均溫差值之簡稱At 貫際开術平均溫差值之計算 m(real) »2 is ~,. The abbreviation of the expected arithmetic mean temperature difference is, (-, the difference of the difference = the average temperature difference of the difference in the formula exp) J CWLT) / ΔΤχ = (CWRT- hair in the 'refrigerated evaporation temperature is referred to as RSET The formula for calculating the brewing degree is: RSET refrigerant steaming (R,) °·5, where al, bl, and cl are constants. In the second step C3, the actual arithmetic mean temperature difference is referred to as At. Calculation of average temperature difference m (real) »
+ CWLT) / 2] _ RSET。 祆曷· Δ^(_) =[(CWRT 於步驟C4中，管f金甘。μ 貫際與期望吐出溫度誤差值簡稱為 201219731+ CWLT) / 2] _ RSET.祆曷· Δ^(_) = [(CWRT in step C4, tube f Jingan. μ Inter- and expected discharge temperature error value is abbreviated as 201219731
ErrASHDT，實際與期望吐出溫度誤差值之計算公式為： En^sHDT =SHDT - SHDTexp ;實際與期望算術平均溫差 誤差值簡稱為Err^tm，實際與期望算術平均溫差誤差值之 計算公式為：Err^tm = - △tmheap。 如上所述之步驟D，其進一步具有：ErrASHDT, the actual and expected discharge temperature error value is calculated as: En^sHDT =SHDT - SHDTexp ; actual and expected arithmetic mean temperature difference error value is abbreviated as Err^tm, the actual and expected arithmetic mean temperature difference error value is calculated as: Err ^tm = - Δtmheap. Step D as described above, further having:
D1、判斷該實際與期望吐出溫度誤差值是否小於等於 或大於一設定值：設定值為零，若實際與期望吐出溫产誤 差值小於等於設定值時，開啟一液壓縮保護旗標，該 電子式膨脹閥之開度；若實際與期望吐出溫度誤差值大^ 設定值時，關閉該液壓縮保護旗標，並進入下一步驟。' D2、判斷該實際與期望算術平均溫差誤差值是否大於 或小於等於算術平均溫差值中立帶：若小於等於算術平均 溫差值中立冑’則電子式膨脹閥維持現有的開度，並回 步驟B;若大於算術平均溫錄巾立帶，職整 脹閥之開度，並回到步驟B。 》y 如上所述，步驟B與步驟C1之間進一步具有 機是否運狀㈣，若壓縮機未運轉，則結束；若撼 運轉，則進行步驟C1。 如上所述，步驟C4與步驟D1之間進一步具有 機是否運轉大於或小於等於一特定時間之步驟，特定問 為3〜5分鐘，若壓縮機運轉小於等於特定時間，電子式賸 脹閥的開度係為50〜1〇0%，則回到步驟B ;若壓縮^鏟 大於特定時間，則進行步驟D1。 如上所述之步驟’電子式膨脹閥係於一固定出力 期逐次減小5%開度，而電子式膨關最大開度限制等於電 201219731 子式膨脹閥現在開度。 當關閉該液壓縮保護旗標時，電子式膨脹閥最大開度 解除，並進入該步驟D2。 如上所述之步驟D2,於大於算術平均溫差值中立帶 時，控制器計算電子式膨脹閥之期望開度與動作步數，以 調整電子式膨脹閥之開度。 動作步數為正值時則增加電子式膨脹閥之開度，並回 到該步驟B ;動作步數為負值時則減少電子式膨脹閥之開 度，並回到該步驟B。 如上所述之步驟A及步驟B中進一步具有一修正該額 定冰水入出水溫差值的方法，其步驟包括有： 一、 設定額定滿載之冰水入出水溫差值：設定一額定 冰水入出水溫差值，額定冰水入出水溫差值等於步驟A中 之額定冰水入出水溫差值。 二、 壓縮機是否運轉：若壓縮機未運轉，即結束；若 壓縮機運轉則進行下一步驟。 三、 壓縮機是否達到全載條件：若壓縮機運轉未達全 載條件，則不修正，則至步驟二；若壓縮機運轉達全載條 件，則進行下一步驟。 四、 計算壓縮機於全載條件運轉的冰水入出水溫差 值：控制器依據冰水入水溫度與冰水出水溫度，得出壓縮 機於全載條件時之冰水入出水溫差值； 五、 自動判定是否重新調整額定冰水入出水溫差設定 值：依據額定冰水入出水溫差與冰水入出水溫差值，而得 出一誤差值，若誤差值的絕對值小於等於一設定值時，則 10 201219731 不動作，則至步驟二，設定值為5%;若絕對值大於該設定 值，則進行下一步驟； 六、判斷連續發生的次數是否等於或小於一固定次 -f :該固定次數為五〜十次，若絕對值大於該設定值之發生 人數等於該固定次數，則冰水入出水溫差值取代額定冰水 ^出水溫差，並回到步驟二；若絕對值大於設定值之發生 人數j於°亥固定次數，則不修正，並至步驟二。 冰水入出水溫差值之簡稱ATreai，冰水入出水溫差值 •之計算f式為：ΔΤ— = CWRT- CWLT;額定冰水入出水溫 差值之簡稱為，誤差值之計算公式為：娜（Δτ⑽ —^Tsetpoint) / △丁沾卬以加 ^ 5%。 綜合上述之方法，其主要係依據實際與期望吐出溫度 $差值及實際與難算術平均溫差誤差值，以調整電子式 ^閥之開度’進而控制冷媒流量，而可有效發揮蒸發器 之熱交換面積’並能提升蒸發溫度，以絲發器之冷媒可 .位於最佳液位，而使蒸發器於最佳的冷媒蒸發溫度 •=本發明具有費用較低、液位解析精準度佳、可控制部分 負載條件時冷媒於最佳液位之優點。 【實施方式】 以下係藉由特定的具體實施例說明本發明之實施方 ^ ’所屬技術領域巾具有通常知識者可由本說明書所揭示 之内容輕易地瞭解本發明之其他優點與功效。 請參閱圖一、二„ H ^ 一 B所不，本發明係一種滿液式 〇發益冷媒液位控制方法，其步驟包括有： 201219731 A、設定基本條件2〇:於—控制器 U ’於額定滿載運轉條件時之财算術平均二差值 Mm)與-額定冰水人出水溫差 ； CW、〜術平均溫差值中立帶（以下簡稱，祕响 與-吐出&度修正值（以下簡稱’Cshdt)，其令c細在 -0.5〜0.5之間，CsHDT在〇〜5之間；該額定冰水入出水 /ΠΙ·差係可依冰水流量而改變，該額定冰水入出水溫差的改 變设疋方式’睛見後述。並且電子式膨服閥14在壓縮機 12啟動運轉的初始開度所設定之設定值可為50〜1〇〇〇/〇。 B、量測溫度與壓力21 :使用一溫度感測器11〇量測 蒸發器11之冰水入水溫度（以下簡稱，CWRT)，另使用 一溫度感測器111量測蒸發器11之冰水出水溫度（以下簡 稱，CWLT);使用一壓力感測器112量測蒸發器11或壓縮 機的吸氣管121之冷媒蒸發壓力值（以下簡稱，RSEP); 使用一溫度感測器120量測壓縮機12之冷媒吐出溫度（以 下簡稱’ SHDT);使用一壓力感測器130量測冷凝器13或 壓縮機的吐出管122之冷媒冷凝壓力值（以下簡稱， RSCP);將 CWRT、CWLT、RSEP、SHDT 與 RSCP 傳送給 控制器10。 c、壓縮機12是否運轉22 :若壓縮機12未運轉，則 電子式膨脹閥14開度為〇% 220 ’並結束221 ;倘若，壓縮 機12運轉’則持續至下一步驟。D1, determining whether the actual and desired discharge temperature error value is less than or equal to or greater than a set value: the set value is zero, and if the actual and desired discharge temperature error value is less than or equal to the set value, turning on a liquid compression protection flag, the electron The opening degree of the expansion valve; if the actual and desired discharge temperature error value is greater than the set value, the liquid compression protection flag is turned off, and the next step is entered. ' D2, determine whether the actual and expected arithmetic mean temperature difference error value is greater than or less than the arithmetic mean temperature difference neutral band: if less than or equal to the arithmetic mean temperature difference neutral 胄 'the electronic expansion valve maintains the existing opening degree, and returns to step B If it is greater than the arithmetic mean temperature recording towel stand, the opening of the full expansion valve, and return to step B. 》y As described above, between step B and step C1, there is further whether or not the machine is in operation (4), and if the compressor is not running, it ends; if 撼 is operated, step C1 is performed. As described above, between step C4 and step D1, there is further a step of whether the machine is operated for more than or less than or equal to a specific time, and the specific question is 3 to 5 minutes. If the compressor operation is less than or equal to a specific time, the electronic expansion valve is opened. If the degree is 50~1〇0%, then return to step B; if the compression is larger than the specific time, proceed to step D1. The electronic expansion valve as described above is successively reduced by 5% opening during a fixed output period, and the electronic opening maximum opening limit is equal to the current opening degree of the 201219731 sub-expansion valve. When the liquid compression protection flag is turned off, the maximum opening degree of the electronic expansion valve is released, and the process proceeds to step D2. In step D2 as described above, when the neutral band is greater than the arithmetic mean temperature difference, the controller calculates the desired opening degree and the number of action steps of the electronic expansion valve to adjust the opening degree of the electronic expansion valve. When the number of action steps is positive, the opening of the electronic expansion valve is increased, and the process returns to step B; when the number of action steps is negative, the opening of the electronic expansion valve is decreased, and the process returns to step B. Step A and step B as described above further have a method for correcting the temperature difference between the rated ice water and the inlet water, the steps of which include: 1. setting the temperature difference of the ice water in and out of the rated full load: setting a rated ice water into the water The temperature difference, the rated ice water inlet and outlet water temperature difference is equal to the rated ice water inlet and outlet water temperature difference in step A. 2. Whether the compressor is running: If the compressor is not running, it will end; if the compressor is running, proceed to the next step. 3. Whether the compressor reaches the full load condition: if the compressor does not reach the full load condition, if it is not corrected, go to step 2; if the compressor runs to the full load condition, proceed to the next step. 4. Calculate the temperature difference between the inlet and outlet water of the compressor under full load conditions: the controller determines the temperature difference between the inlet and outlet of the ice water according to the ice water inlet temperature and the ice water outlet temperature; Automatically determine whether to re-adjust the rated ice water inlet and outlet water temperature difference setting value: according to the difference between the rated ice water inlet and outlet water temperature difference and the ice water inlet and outlet water temperature difference, and obtain an error value, if the absolute value of the error value is less than or equal to a set value, then 10 201219731 does not work, then to step 2, the set value is 5%; if the absolute value is greater than the set value, proceed to the next step; 6. Determine whether the number of consecutive occurrences is equal to or less than a fixed number of times -f: the fixed number of times For five to ten times, if the absolute value is greater than the set value, the number of occurrences is equal to the fixed number of times, then the ice water inlet and outlet water temperature difference replaces the rated ice water and water temperature difference, and returns to step two; if the absolute value is greater than the set value If the number of people in j is fixed at ° Hai, it will not be corrected and will go to step 2. The abbreviation of ice water inlet and outlet water temperature is referred to as ATreai, the difference between ice water and water temperature is calculated as: ΔΤ— = CWRT- CWLT; the nominal ice water temperature difference is the abbreviation for the error value: Na ( Δτ(10) —^Tsetpoint) / △丁卬卬 to add ^ 5%. In combination with the above method, the main method is based on the difference between the actual and desired discharge temperature, and the actual and difficult arithmetic mean temperature difference error value, to adjust the opening degree of the electronic valve, thereby controlling the flow rate of the refrigerant, and effectively exerting the heat of the evaporator. Exchange area 'and can increase the evaporation temperature, the refrigerant of the hair dryer can be located at the optimal liquid level, and the evaporator is at the optimal refrigerant evaporation temperature.•=The invention has low cost and accurate liquid level resolution. It can control the advantages of the refrigerant at the optimum liquid level under partial load conditions. [Embodiment] The following is a description of the embodiments of the present invention by way of specific embodiments. The technical scope of the present invention can be easily understood by those of ordinary skill in the art. Please refer to Fig. 1 and 2 „H ^一B. The present invention is a full liquid type 〇发益冷液液位控制方法, the steps including: 201219731 A, setting basic conditions 2〇: ——controller U ' The arithmetic mean two difference Mm) at the rated full load operating condition and the temperature difference of the rated ice water effluent; CW, ~ average temperature difference neutral band (hereinafter referred to as the secret and spit & degree correction value (hereinafter referred to as 'Cshdt), which makes c fine between -0.5 and 0.5, and CsHDT between 〇 and 5; the rated ice water in/out water/ΠΙ·difference can be changed according to the ice water flow rate, and the rated ice water inlet and outlet water temperature difference The change setting method will be described later, and the set value of the electronic expansion valve 14 set at the initial opening degree of the compressor 12 start operation may be 50 to 1 〇〇〇 / 〇 B. Measuring temperature and pressure 21: The temperature of the ice water in the evaporator 11 is measured using a temperature sensor 11 (hereinafter referred to as CWRT), and the temperature of the ice water of the evaporator 11 is measured using a temperature sensor 111 (hereinafter referred to as CWLT). Measuring the evaporator 11 or the suction pipe 121 of the compressor using a pressure sensor 112 The refrigerant evaporation pressure value (hereinafter referred to as RSEP); the refrigerant discharge temperature of the compressor 12 (hereinafter referred to as 'SHDT) is measured using a temperature sensor 120; the condenser 13 or the compressor is measured using a pressure sensor 130 The refrigerant condensation pressure value of the discharge pipe 122 (hereinafter referred to as RSCP); the CWRT, CWLT, RSEP, SHDT, and RSCP are transmitted to the controller 10. c. Whether the compressor 12 is operating 22: if the compressor 12 is not operating, the electrons The expansion valve 14 has an opening of 〇% 220' and ends 221; if the compressor 12 is running, it continues to the next step.
D、計算壓縮機12之期望冷媒吐出溫度與蒸發器11 之期望算術平均溫差值23 :控制器10根據RSEP、rSCP 12 201219731 與Cshdt，而得出壓縮機12之期望冷媒吐出溫度（以下 簡稱 ’ SHDTexp)，計算公式為：SHDTexp ={a + b χ (RSCP)+ c x (RSCP)2 + d X (RSEP) + CSHDT}，其中 a、b、c、d為常數。控制器i〇依據CWRT、CWLT、ΔΤ、 CAtm與Atm，而得出蒸發器u之期望算術平均溫差值（以 下簡稱，〜（㈣）’計算公式為：爲^冲）=(cwrt CWLT)/ ΔΤ x 。 E、 計算冷媒蒸發溫度24 :控制器1〇依據RSEp，而 • 得出一冷媒蒸發溫度（以下簡稱，RSET)，計算公式為： RSET = al+bl X (RSEP) + Cl X (RSEP)05，其中 a卜b卜 cl為常數。 ” 、 F、 計算實際的算術平均溫差值25 :控制器1〇在依 CWRT、CWLT與RSET’而得出一實際算術平均溫差值（以 下簡稱，△tmkai))，計算公式為：Μιη(Γ^) CWLT) / 2] - RSET。 - G、計算冷媒吐出溫度與算術平均溫差值之誤差值 • %:控制器10依據SHDT與SHDTexp，而得出一實際與期 望吐出溫度誤差值（以下簡稱，ErrASHDT )，計算公為： En^SHDT =SHDT _ SHDTexp ;控制器 1〇 依據… 與Atm(real)’而得出一實際與期望算術平均溫差誤1值 下簡稱，Err^tm ) ’計算公式為：Err^tm = At ,D. Calculating the desired refrigerant average temperature difference of the compressor 12 and the desired arithmetic mean temperature difference 23 of the evaporator 11: The controller 10 derives the desired refrigerant discharge temperature of the compressor 12 based on RSEP, rSCP 12 201219731 and Cshdt (hereinafter referred to as ' SHDTexp), the calculation formula is: SHDTexp = {a + b χ (RSCP) + cx (RSCP) 2 + d X (RSEP) + CSHDT}, where a, b, c, d are constant. The controller i 〇 according to CWRT, CWLT, ΔΤ, CAtm and Atm, and obtains the expected arithmetic mean temperature difference of the evaporator u (hereinafter referred to as ~((4))' is calculated as: ^冲)=(cwrt CWLT)/ ΔΤ x . E. Calculate the evaporation temperature of the refrigerant 24: The controller 1〇 derives a refrigerant evaporation temperature (hereinafter referred to as RSET) according to RSEp, and the calculation formula is: RSET = al + bl X (RSEP) + Cl X (RSEP) 05 , where a b b cl is a constant. ”, F, calculate the actual arithmetic mean temperature difference 25: controller 1 得出 according to CWRT, CWLT and RSET' to obtain an actual arithmetic mean temperature difference (hereinafter referred to as Δtmkai), the calculation formula is: Μιη (Γ ^) CWLT) / 2] - RSET - G, calculate the error value of the refrigerant discharge temperature and the arithmetic mean temperature difference • %: The controller 10 derives an actual and expected discharge temperature error value based on SHDT and SHDTexp (hereinafter referred to as , ErrASHDT), the calculation is: En^SHDT = SHDT _ SHDTexp; the controller 1 〇 according to ... and Atm (real)' to obtain an actual and expected arithmetic mean temperature difference error 1 under the abbreviation, Err^tm) 'calculation The formula is: Err^tm = At ,
Atm Atm (exp) _ M (real” H、壓縮機12是否運轉大於或小於等於一特定時 27:若壓縮機12運轉小於等於-特定時間，電子式膨服 14的開度係為5(M00% 270，則回到上述之步驟β ， 13 201219731 重新整個步驟，該特定時間為3〜5分鐘；倘若，壓縮機12 運轉大於該特定時間時，則進行下一步驟。 1、判斷Err^sHDT是否小於等於或大於一設定值28 : 控制器ίο針對ErrASHDT進行判斷，是否ErrASHDT大於 或小於專於一設定值，該設定值可為零，若Err^SHDT小於 等於零時’開啟液壓縮保護旗標280，電子式膨脹閥14於 一固定出力週期逐次減小5%的開度281，以進行一液壓縮 的保護流程，直至SHDT大於SHDTexp，即電子式膨脹閥 14最大開度限制等於電子式膨脹閥14現在開度282,並回 到步驟B 283 ; 倘若’ Eh^shdt大於零時，則關閉液壓縮保護旗標 284，電子式膨脹閥最大開度限制解除285，並進入下一步 驟。 J判斷ErrAtm的絕對值是否小於等於或大於dead band 29 :若為小於等於deadband時，電子式膨脹閥14維 持現有的開度290，並回到步驟b 283 ; 若為大於dead band時，控制器1〇計算電子式膨脹閥 14之期望開度與動作步數291，以調整電子式膨脹閥丨4之 開度，若動作步數為正值時則增加電子式膨脹閥14之開度 292 ’並回到步驟b 283 ; 若動作步數負值時則減少電子式膨脹閥14之開度 293 ’並再回到上述之步驟b 283。 回到步驟B之目的，在於重複整個步驟，以避免液壓 縮的保護流程反覆發生的情況。 雖可藉由上述之設定溫度、量測實際壓力並轉換為溫 201219731 度與量測實際溫度後，控制器10依前述之數據與修正值， 再決定是否要調整電子式膨脹閥14之開度，以有效提升冰 水機於部分負載條件下的運轉效率與最佳的冷媒液位。但 冰水流量變化會改變冰水入出水溫差值，其會導致最初所 設定之ΔΤ可能存有極大的誤差值，並會造成電子式膨脹 " 閥14之開度調整不當，故AT必須依實際冰水入出溫差值 自動進行修正，該修正方法係應用於上述之步驟A與B 中，該修正法之步驟如下： φ 一、設定額定滿載運轉條件之冰水入出水溫差值30 : 如上述步驟A，設定一額定冰水入出水溫差值（以下簡稱， △Tsetpoint) ’於此步驟中所述之△Tsetpoint係專於上述之 ΔΤ ° 二、壓縮機12是否運轉31 :若壓縮機12未運轉，即 結束310 ;若壓縮機12運轉進行下一步驟。 - 三、壓縮機是否達到全載條件32 :若壓縮機12運轉 . 未達全載條件，即100%，則不修正320，並至步驟二351 ; Φ 若壓縮機12運轉達全載條件，則進行下一步驟。 四、 計算壓縮機12於全載條件運轉的冰水入出水溫差 值33 :控制器10依據CWRT與CWLT，而得出壓縮機12於 全載條件運轉時之冰水入出水溫差值（以下簡稱，A T r e a丨）， 計算公式為：ATreal = CWRT- CWLT。 五、 自動判定是否重新調整額定冰水入出水溫差設定 值34 .控制益1 〇依據△Tsetpoint與ATreal ’而付出·知差 值，若該誤差值之絕對值小於等於一設定值時，該設定值 可為5%，則不修正320，並至步驟二351，計算公式為： 15 201219731 ABS(ATreal - △Tsetpoint) / △Tsetpoint 2 5%，若該絕對 值大於該設定值，則進行下一步驟。 六、判斷連續發生的次數是否等於或小於一固定次數 35 :該固定次數可為五〜十次，若步驟五之絕對值大於該設 定值，但發生次數小於該固定次數，則不修正320，並至 步驟二351 ;若發生次數等於該固定次數，則ATsetp〇int 等於MVea丨350，即MVeai取代於步驟一所設定之ΔΤ，並 再回到步驟二351，以重複整個步驟。 综合上述，本發明係依據ΔΤ、Atm、C^tm、dead band、 CsHDT、CWRT、CWRT、RSEP、SHDT、RSCP、SHDTexp、 △tm (exp)、RSET、Atm (reai)、Err^SHDT、Err^tm，而決定 是否要調整電子式膨脹閥14之開度，以提升冰水機之運轉 效率，並且ΔΤ可隨實際狀態，而進行修正，以使電子式 膨脹閥14的開度可因應實際狀態而調整，進而控制冷媒流 量’以使蒸發器11之冷媒可位於最佳液位，而可有效發揮 蒸發器11之熱交換面積，並能提升蒸發溫度，並使蒸發器 11於最佳的冷媒蒸發溫度運轉。 惟以上所述之具體實施例，僅係用於例釋本發明之特 點及功效，而非用於限定本發明之可實施範疇，於未脫離 本發明上揭之精神與技術範疇下，任何運用本發明所揭示 内容而完成之等效改變及修飾，均仍應為下述之申請專利 範圍所涵蓋。 16 201219731 【圖式簡單說明】 圖一係應用本發明之滿液式蒸發器冷媒液位控制方法 之冰水機之示意圖。 . 圖二A及二B係本發明之滿液式蒸發器冷媒液位控制 方法之流程示意圖。 圖三係本發明之修正設定額定滿載之冰水出水溫差值 之流程示意圖。 φ 【主要元件符號說明】 10 控制器 11 蒸發器 110 溫度感測器 111 溫度感測器 112 壓力感測器 12 壓縮機 120 溫度感測器 • 121 壓縮機吸氣管 122 壓縮機吐出管 13 冷凝器 130 壓力感測器 14 電子式膨脹閥 20〜293 步驟 30〜351 步驟 17Atm Atm (exp) _ M (real) H, whether the compressor 12 is running greater than or less than or equal to a specific time 27: If the compressor 12 is operated less than or equal to - a specific time, the opening degree of the electronic expansion device 14 is 5 (M00 % 270, return to the above step β, 13 201219731 to repeat the whole step, the specific time is 3 to 5 minutes; if the compressor 12 is operated more than the specific time, proceed to the next step. 1. Determine Err^sHDT Whether it is less than or equal to a set value of 28: The controller ίο judges whether ErrASHDT is greater than or less than a set value, and the set value can be zero. If Err^SHDT is less than or equal to zero, the liquid compression protection flag is turned on. 280, the electronic expansion valve 14 is successively reduced by 5% of the opening degree 281 in a fixed output force cycle to perform a liquid compression protection process until the SHDT is greater than SHDTexp, that is, the maximum expansion limit of the electronic expansion valve 14 is equal to the electronic expansion. The valve 14 is now open 282 and returns to step B 283; if 'Eh^shdt is greater than zero, the liquid compression protection flag 284 is closed and the electronic expansion valve maximum opening limit is released 285 and proceeds to the next step. Whether the absolute value of the ErrAtm is less than or equal to dead band 29: if it is less than or equal to deadband, the electronic expansion valve 14 maintains the existing opening degree 290 and returns to step b 283; if it is greater than the dead band, the controller 1 〇 calculating the desired opening degree and the number of operating steps 291 of the electronic expansion valve 14 to adjust the opening degree of the electronic expansion valve 丨4, and increasing the opening degree 292' of the electronic expansion valve 14 if the number of operating steps is positive Going back to step b 283; if the number of action steps is negative, reducing the opening degree 293' of the electronic expansion valve 14 and returning to the above step b 283. The purpose of returning to step B is to repeat the entire step to avoid liquid The compression protection process occurs repeatedly. Although the actual temperature can be measured and converted to the temperature 201219731 degree and the actual temperature is measured, the controller 10 determines whether or not to use the above data and the correction value. Adjusting the opening degree of the electronic expansion valve 14 to effectively improve the operating efficiency of the ice water machine under partial load conditions and the optimal refrigerant liquid level. However, the change of ice water flow rate will change the temperature difference between the ice water and the water, which will result in The initial setting of ΔΤ may have a large error value, and will cause the electronic expansion " the opening degree of the valve 14 is improperly adjusted, so the AT must automatically correct according to the actual ice water inlet and outlet temperature difference, the correction method is applied to the above In steps A and B, the steps of the correction method are as follows: φ 1. Set the ice water inlet and outlet water temperature difference 30 of the rated full load operation condition: as in the above step A, set a nominal ice water inlet and outlet water temperature difference (hereinafter referred to as △) Tsetpoint) 'The ΔTsetpoint described in this step is specific to the above ΔΤ ° 2. Whether the compressor 12 is running 31: If the compressor 12 is not running, the end 310; if the compressor 12 is running, the next step is performed. - 3. Whether the compressor reaches full load condition 32: If the compressor 12 is running. If the full load condition is reached, that is, 100%, then 320 is not corrected, and step 2 is 351; Φ If the compressor 12 is operated to the full load condition, Then proceed to the next step. 4. Calculate the temperature difference between the ice water and the water flowing out of the compressor 12 under full load conditions: The controller 10 obtains the temperature difference between the ice water and the water when the compressor 12 is operated under full load conditions according to CWRT and CWLT (hereinafter referred to as , AT rea丨), the calculation formula is: ATreal = CWRT- CWLT. 5. Automatically determine whether to re-adjust the rated ice water inlet and outlet water temperature difference setting value 34. Control benefit 1 付出 pays the difference value according to △Tsetpoint and ATreal ', if the absolute value of the error value is less than or equal to a set value, the setting The value can be 5%, then the error is not corrected 320, and to step two 351, the calculation formula is: 15 201219731 ABS(ATreal - ΔTsetpoint) / ΔTsetpoint 2 5%, if the absolute value is greater than the set value, proceed to the next step. 6. Determine whether the number of consecutive occurrences is equal to or less than a fixed number of times 35: the fixed number of times may be five to ten times. If the absolute value of step 5 is greater than the set value, but the number of occurrences is less than the fixed number of times, 320 is not corrected. And step 2 351; if the number of occurrences is equal to the fixed number of times, ATsetp〇int is equal to MVea 丨 350, that is, MVeai is replaced by ΔΤ set in step 1, and then returns to step 351 to repeat the entire step. In summary, the present invention is based on ΔΤ, Atm, C^tm, dead band, CsHDT, CWRT, CWRT, RSEP, SHDT, RSCP, SHDTexp, Δtm (exp), RSET, Atm (reai), Err^SHDT, Err ^tm, and decide whether to adjust the opening degree of the electronic expansion valve 14 to improve the operating efficiency of the ice water machine, and ΔΤ can be corrected according to the actual state, so that the opening degree of the electronic expansion valve 14 can be adapted to the actual situation. The state is adjusted to control the refrigerant flow rate so that the refrigerant of the evaporator 11 can be located at the optimum liquid level, and the heat exchange area of the evaporator 11 can be effectively utilized, and the evaporation temperature can be raised, and the evaporator 11 can be optimized. The refrigerant evaporates at a temperature. However, the specific embodiments described above are merely used to exemplify the features and functions of the present invention, and are not intended to limit the scope of the present invention, and may be applied without departing from the spirit and scope of the present invention. Equivalent changes and modifications made to the disclosure of the present invention are still covered by the scope of the following claims. 16 201219731 [Simple description of the drawings] Fig. 1 is a schematic view of an ice water machine to which the liquid level control method of the flooded evaporator of the present invention is applied. Fig. 2A and Fig. 2B are schematic flow charts showing the method for controlling the liquid level of the flooded evaporator of the present invention. Fig. 3 is a schematic flow chart showing the difference between the ice water and water outlet temperature of the modified full rated load according to the present invention. Φ [Main component symbol description] 10 Controller 11 evaporator 110 temperature sensor 111 temperature sensor 112 pressure sensor 12 compressor 120 temperature sensor • 121 compressor suction pipe 122 compressor discharge pipe 13 condensation 130 Pressure sensor 14 Electronic expansion valve 20~293 Step 30~351 Step 17