200912215 九、發明說明： 【發明所屬之技術領域】 本發明是關於一種藉由對閥門的開度進行調r 在空調機中所流過的冷熱水的流量之空調控制系=而控= 調控制方法。 二 【先前技術】 在習知技術中，關於以冷熱水為熱媒體的空, 統，提出有一種對該熱媒體的送水壓力進行 照例如專利文獻1、專利文獻2)。 上、糸統(茶 圖1所示為關於本發明的第i實施形態之空調控 統的構成的方塊圖，但由於在習知技術中其全體構^也二 同樣的，所以利用圖1對習知的空調控制系統進行戈明疋 附力3 If 2·卜2_2進行壓送並利用熱源機^、Μ 並利用二次泵9_卜9_2進行壓送，且2 被供給到送水管路4， 集g相 壓，達二_ :之偏差’而控制間門6-1〜《的開度。 閥門通、空調控制襄置Μ根據闊門Η〜《的開度和 ；!，’而_空調機控制狀態。 、工制裝置15根據空調機控制狀態而決定設定送 200912215 水壓力’並通過變流器9_la、9_2a而決定二次果M、 的變流器(inverter)轉速，以使壓力感測器！}所計^ 的送水壓力與設定送水壓力一致。 在 〔專利文獻1〕日本專利早期公開之特開平 號公報 223 〔專利文獻2〕日本專利早期公開之特開平 號公報 224 如利用專利文獻1、專利文獻2所揭示的空調控 統，則送水壓力可變，從而可實現能量的節省。 J糸 空 但是，在專利文獻i、專利文獻2所揭示的空調 系統中，存在當因溫濕度設定的錯誤(過度製冷、過度製^ 4而使超過設計最大流量的冷熱水流過空調機時，會、、 调控制糸統的耗能增加之問題。 通常，空調機的冷熱水盤管是依據供給熱量進行設 計，溫度㈣或濕度控假藉錄據溫度偏錢濕度偏^ 的回饋控制，而控制閥門的開度，以控制通過冷埶 的冷熱水的流量。 ^ i 另一方面，通常溫濕度設定是委託用戶或者大樓管理 負責人進行，如他們進行了超出設計條件的設定變更，則 會使超出了 δ又§十最大流量的冷熱水通過空調機的冷熱水盤 管。冷熱水鮮是轉輯溫度祕件和輯流 件而確定最大熱量條件。 ^ 這長，當如別述那樣在冷熱水盤管中流過超過設計最 大流量的冷熱水時，泵的搬運動力增加且耗能增加。而且， 200912215 因為在冷熱水盤管中 大致-定，所以，上進行交換的熱量 〆、/、仙·里成反比，空調機的入口和出口沾、人 的、耗能::差減少，結果是熱源機的效率變差，使熱源: 閥門=^;、!?間;，進行調整，以在 並不進行。八κ取大流1，但因為耗費工時而 而且，雖然也有將要求流 ，的判斷指標中移除，或者降低送==二 二法，但存在使現場作業的勞力或時間以及5;=^ 系统文獻1'專利文獻2所揭示的空調控制 的冷熱水、水ίΓ流過超出設計最大流量 tX〇„ ^ ^ ^祙的入口和出口也無法確保冷熱水的設 說h空調控制系統的耗能增加之問題。如前面所 龟、厂法確保設計溫度差的情況下，熱源機的效率 旦源機的耗能增加。儘管未流過超出設計最大流 ί#Ir、7 ’部無法確保設計溫度差之理由是，對空調負 何形成超限流量。 【發明内容】 本發日月的目的是提供—種為了解決上賴題而形成 …=使因'皿濕度設定的錯誤等而產生超出設計最大流量 控求’也可抑制耗能的增加之空調控制系統及空調 200912215 而且，本發明的目的是提供—種在對空調負荷 限流量的情況下’此夠抑制耗能的增加之空調控制系$ ° 空調控制方法。 ’ 本發明的空調控制系統包括：粟，送出 ^ 機，接受前述冷熱=供給；閥門，用於控制被供給= 空調機的冷熱水的μ ;流量相m置，祕制 ：： 述閥_冷齡的流量；㊆驗_置，根據從前述空二 機所送出的供氣的溫度和設定溫度之偏差，而控制= n的開度；閥_度限制裝置，在_前述流量計列= 所計測的閥門通過流量超出設計最大流量之情況下，對$ 述閥門開度進行限制，以使前述閥門通過流量小於等於: 計最大流量；以及送水壓力控制裝置，根據前述閥門開^ 和閥門通過流量所決定的空調機的控制狀態，而控制從^ 述泵被送出到前述空調機之冷熱水的壓力亦即送水壓^= 而且，本發明的空調控制系統包括：泵，送出冷熱水. 空調機，接受前述冷熱水的供給；閥門，用於控制被供給 到該空調機的冷熱水的流量；流量計測裝置，用於計測通 過前述閥門的冷熱水的流量；回流水溫度計測裝置，計測 通過了前述空調機的回流水的溫度；空調控制裝置，根據 從前述空調機所送出的供氣的溫度和設定溫度之偏差，而 控制前述閥門的開度；閥門開度限制裝置，在利用前述流 量計測裝置所計測的閥門通過流量小於等於設計最大流 量，且製冷運轉時由前述回流水溫度計測裝置所計測的計 測回流水溫度較設計回流水溫度低的情況下，對前述閥門 200912215 開度進行限制，以在製冷運轉時使前述計測回流水溫度大 於等於設計回流水溫度；或者在利用前述流量計測裝置所 計測的閥門通過流量小於等於設計最大流量，且製熱運轉 時前述計測回流水溫度較設計回流水溫度高的情況下，對 前述閥門開度進行限制，以在製熱運轉時使前述計測回流 水温度小於等於設計回流水溫度；以及送水壓力控制裝 置，根據前述閥門開度和閥門通過流量所決定的空調機的 控制狀態，而控制從前述泵被送出到前述空調機之冷熱水 的壓力亦即送水壓力。 而且，在具有泵、空調機和閥門的空調控制系統中， 本發明的空調控制方法包括：空調控制步驟，根據從前述 空調機所送出的供氣的溫度和設定溫度之偏差，而控制前 述閥門的開度；流量計測步驟，對通過前述閥門的冷熱水 的流量進行計測；閥門開度限制步驟，在利用該流量計測 步驟所計測的閥門通過流量超出設計最大流量之情況下， 對前述閥門開度進行限制，以使前述閥門通過流量小於等 於設計最大流量；以及送水壓力控制步驟，根據前述閥門 開度和閥門通過流量所決定的空調機的控制狀態，而控制 從前述泵被送出到前述空調機之冷熱水的壓力亦即送水壓 力。 而且，在具有泵、空調機和閥門的空調控制系統中， 本發明的空調控制方法包括：空調控制步驟，根據從前述 空調機所送出的供氣的溫度和設定溫度之偏差，而控制前 述閥門的開度；流量計測步驟，其對通過前述閥門的冷熱 200912215 水的流量進行計測；回流水溫度計測步驟，其計測通過了 箣述空5周機的回流水的温度，閥門開度限制步驟，在利用 前述流量計測步驟所計測的閥門通過流量小於等於設計最 大流量’且製冷運轉時由前述回流水溫度計測步驟所計測 的5十測回流水溫度較设计回流水溫度低的情況下，對前述 閥門開度進行限制，以在製冷運轉時使前述計測回流水溫 度大於等於設計回流水溫度；或者在利用前述流量計測步 驟所計測的閥門通過流量小於等於設計最大流量，且製熱 運轉時前述計測回流水溫度較設計回流水溫度高的情況 下’對前述閥門開度進行限制，以在製熱運轉時使前述計 測回流水溫度小於等於設計回流水溫度；以及送水壓力控 制步驟，根據前述閥門開度和闕門通過流量所決定的空調 機的控制狀態，而控制從前述泵被送出到前述空調機之冷 熱水的壓力亦即送水壓力。 如利用本發明，則藉由在所計測的閥門通過流量超出 設計最大流量的情況下，限制闕鬥的開，，從而即使因溫 濕度設定的錯誤(過度製冷、過度製熱）等^產生超出設計 最大流量的流量要求，也可將^流对卩制在設計最 大流量以下，能夠抑制因泵搬#力1加所導致的耗能 的增加。而且，在本發明中，藉②將闕F通過流量抑制在 設計最大流量以下，可在空調機的入口S5 口確保冷熱水 的溫度差，所以能夠使熱源機的逢轉效y提向，可抑制熱 源機的耗能的增加。另外，在本發明中’不需要採取將要 求流量大的系統的閥Η開度從送水控♦的判斷指標中移 200912215 除，或者降低送水控制上的權重等方法，能夠節省現場作 業的勞力或時間。200912215 IX. Description of the Invention: [Technical Field] The present invention relates to an air conditioning control system that regulates the flow rate of hot and cold water flowing through an air conditioner by adjusting the opening degree of the valve = control = control method. [Prior Art] In the prior art, a water supply pressure of the hot medium is proposed as an air conditioner using hot and cold water as a heat medium. For example, Patent Document 1 and Patent Document 2). The top view is a block diagram showing the configuration of the air conditioning control system according to the first embodiment of the present invention. However, since the overall configuration is the same in the prior art, the same applies to FIG. The conventional air conditioning control system performs the pressure feed of the Goming 疋 3 If 2· 2 2_2 and uses the heat source machine ^, Μ and uses the secondary pump 9_b 9_2 for pressure feeding, and 2 is supplied to the water supply line 4 , Set g phase pressure, up to two _: the deviation 'and control the door 6-1 ~ "opening degree. Valve pass, air conditioning control set Μ according to the wide door Η ~ "opening and;!, 'and air conditioning In the machine control state, the manufacturing device 15 determines to set the water pressure of 200912215 according to the air conditioner control state, and determines the inverter speed of the secondary fruit M through the converters 9_la, 9_2a to make the pressure sense. The water supply pressure of the tester is the same as the set water supply pressure. [Patent Document 1] Japanese Patent Laid-Open Publication No. 223 (Patent Document 2) Japanese Patent Laid-Open Publication No. 224 In the air conditioning control system disclosed in Document 1 and Patent Document 2, water is delivered. In the air conditioning system disclosed in Patent Document i and Patent Document 2, there is an error in setting the temperature and humidity (overcooling, over-manufacturing, etc.) When designing the maximum flow of hot and cold water flowing through the air conditioner, it will increase the energy consumption of the control system. Usually, the hot and cold water coil of the air conditioner is designed according to the heat supply, and the temperature (4) or humidity control data is biased. The humidity control of the humidity is controlled by the feedback control, and the opening of the valve is controlled to control the flow rate of the cold and hot water passing through the cold. ^ i On the other hand, the usual temperature and humidity setting is performed by the entrusting user or the person in charge of the building management, as they have carried out If the setting changes beyond the design conditions, the hot and cold water that exceeds the δ and §10 maximum flow rate will pass through the hot and cold water coil of the air conditioner. The hot and cold water is used to reproduce the temperature secrets and the flow parts to determine the maximum heat condition. Long, when the hot and cold water exceeding the designed maximum flow rate flows through the hot and cold water coil as described above, the pumping power is increased and the energy consumption is increased. Moreover, 20091 2215 Because it is roughly fixed in the hot and cold water coils, the heat exchanged on the upper and/or lower sides of the air conditioner is inversely proportional to the entrance and exit of the air conditioner, and the energy consumption of the person is reduced: the result is the heat source machine. The efficiency is worse, so that the heat source: valve = ^;, !?;, adjust, to not carry out. Eight κ take a large flow 1, but because of the labor and also, although there will be a request for flow, the judgment The indicator is removed, or the delivery == two-two method is reduced, but there is labor or time for on-site work and 5;=^ The air-conditioning control of the hot and cold water and the water flow disclosed in the patent document 1' patent document 2 exceeds the design. The inlet and outlet of the maximum flow rate tX〇„^^^祙 also fail to ensure the problem of increased energy consumption of the air conditioning control system. As in the previous turtle and factory methods to ensure the design temperature difference, the efficiency of the heat source machine increases the energy consumption of the source machine. Although the reason why the design temperature difference cannot be ensured beyond the design maximum flow ί#Ir, 7 ′ is that the air conditioner is subjected to an over-flow. SUMMARY OF THE INVENTION The purpose of the present day and the month is to provide an air conditioner that can be formed in order to solve the problem of the above problem, and that can cause an increase in energy consumption due to an error in the setting of the humidity of the dish. Control System and Air Conditioning 200912215 Moreover, it is an object of the present invention to provide an air conditioning control system that is capable of suppressing an increase in energy consumption in the case of limiting the flow rate of an air conditioner. The air conditioning control system of the present invention comprises: millet, delivery machine, accepting the aforementioned hot and cold = supply; valve for controlling the supplied μ = the hot and cold water of the air conditioner; the flow phase is set, the secret:: the valve _ cold The flow rate of the age; the seven test_set, according to the deviation of the temperature of the air supply sent from the second air machine and the set temperature, and control the opening degree of n; the valve_degree limit device, in the aforementioned flow meter column = When the measured valve exceeds the designed maximum flow rate, the valve opening degree is limited, so that the aforementioned valve passage flow rate is less than or equal to: the maximum flow rate; and the water supply pressure control device, according to the aforementioned valve opening and valve passage flow rate The control state of the air conditioner is determined, and the pressure of the hot and cold water sent from the pump to the air conditioner is controlled, that is, the water supply pressure is controlled. Further, the air conditioning control system of the present invention includes: a pump, which sends out hot and cold water. a machine for receiving the supply of the hot and cold water; a valve for controlling the flow rate of the hot and cold water supplied to the air conditioner; and a flow measuring device for measuring the flow rate of the hot and cold water passing through the valve; The flowing water temperature measuring device measures the temperature of the return water passing through the air conditioner; and the air conditioning control device controls the opening degree of the valve according to the deviation of the temperature of the air supply sent from the air conditioner and the set temperature; the valve opening degree The limiting device, when the flow rate of the valve measured by the flow measuring device is less than or equal to the designed maximum flow rate, and the temperature of the measured return water measured by the reflux water temperature measuring device during the cooling operation is lower than the temperature of the designed return water, The opening degree of the valve 200912215 is limited to make the measured return water temperature equal to or higher than the designed return water temperature during the cooling operation; or the valve passing flow rate measured by the flow measuring device is less than or equal to the designed maximum flow rate, and the heating operation is performed. When the temperature of the reflux water is higher than the temperature of the designed reflux water, the valve opening degree is limited to make the measured reflux water temperature equal to or lower than the designed return water temperature during the heating operation; and the water supply pressure control device according to the foregoing Valve opening and valve flow The control state of the air conditioner determined by the amount is controlled, and the pressure of the hot and cold water sent from the pump to the air conditioner is controlled, that is, the water supply pressure. Moreover, in an air conditioning control system having a pump, an air conditioner, and a valve, the air conditioning control method of the present invention includes: an air conditioning control step of controlling the valve based on a deviation of a temperature of the air supply sent from the air conditioner and a set temperature The opening degree; the flow measuring step, measuring the flow rate of the hot and cold water passing through the valve; the valve opening limit step, in the case where the flow rate measured by the flow measuring step exceeds the designed maximum flow rate, the valve is opened Limiting, so that the valve passing flow rate is less than or equal to the designed maximum flow rate; and the water supply pressure control step, according to the valve opening degree and the control state of the air conditioner determined by the valve passing flow, and the control is sent from the pump to the air conditioner The pressure of the hot and cold water of the machine is also the water supply pressure. Moreover, in an air conditioning control system having a pump, an air conditioner, and a valve, the air conditioning control method of the present invention includes: an air conditioning control step of controlling the valve based on a deviation of a temperature of the air supply sent from the air conditioner and a set temperature The opening degree; the flow measuring step, which measures the flow rate of the hot and cold water through the aforementioned valve 200912215; the measuring step of the reflux water thermometer, the measuring step passes through the temperature of the return water of the empty 5 week machine, and the valve opening limit step, In the case where the flow rate of the valve measured by the flow metering step is less than or equal to the designed maximum flow rate and the temperature of the measured reflux water measured by the aforementioned reflux water temperature measuring step is lower than the temperature of the designed return water, The opening degree of the valve is limited to make the measured reflux water temperature equal to or higher than the designed return water temperature during the cooling operation; or the measured flow rate of the valve measured by the flow metering step is less than or equal to the designed maximum flow rate, and the foregoing measurement is performed during the heating operation When the temperature of the return water is higher than the temperature of the designed return water, 'right The valve opening degree is limited to make the measured return water temperature less than or equal to the designed return water temperature during the heating operation; and the water supply pressure control step, the air conditioner control state determined according to the valve opening degree and the trick passage flow rate. And controlling the pressure of the hot and cold water sent from the pump to the air conditioner, that is, the water supply pressure. According to the present invention, the opening of the bucket is restricted by the flow rate of the measured valve exceeding the designed maximum flow rate, so that even the error due to the temperature and humidity setting (overcooling, excessive heating) By designing the flow rate of the maximum flow rate, it is also possible to control the flow rate below the designed maximum flow rate, and it is possible to suppress the increase in energy consumption caused by the pumping force #1. Further, in the present invention, by suppressing the flow rate of 阙F by the flow rate below the design maximum flow rate, the temperature difference between the hot and cold water can be ensured at the inlet S5 of the air conditioner, so that the heat transfer effect of the heat source machine can be raised. The increase in energy consumption of the heat source machine is suppressed. In addition, in the present invention, it is not necessary to adopt a method of shifting the valve opening degree of the system requiring a large flow rate from the judgment index of the water supply control ♦ to 200912215, or reducing the weight on the water supply control, thereby saving the labor of the field work or time.
而且，在本發明中，在所計測的閥鬥通過流量小於等 於設計最大流量，且製冷運轉時所計測的計測回流水溫度 低於設計回流水溫度之情況下，或製熱蓮轉時的計測回流 水μ度向於設計回流水溫度的情況下，藉由限制閥門的開 ，，可在對空調負載形成過度流量的情況下抑制閥門通過 流量。結果使本發明可在空調機的入口和出口確保冷熱水 的溫度差，所以能夠使熱源機的運轉效率提高，可抑^熱 源機的耗能的增加。 … 【實施方式】 〔第1實施形態〕 一以下，參照圖式對本發明的實施形態進行說明。圖工 :::關於本發明的第1實施形態之空調控制系統的構成 圖1的空調控制系統的構成包括：熱源機Μ、^ 2， 1生成冷熱水的冷熱水產生器、熱泵、冷械 其作為該熱源機叫 :專路 =官箱Μ、3-2,其將來自多個熱源機Μ、 =: ==合；送水管路4;空調機^3;閥門 給到空調機M〜5，冷熱水的流量進行 ；；^路7;回路集管箱8,其將在空調機5-M3中進 仃熱父換並通過回流水管路7 甲進 泉一，其設置在去:=?=送回;二次 吩市s相3-1和3-2之間；旁通 200912215 闕ίο ’其設置在去路集督箱3心和3_2之間；壓力感測器 η，其用於相配r系統^的送水壓力；供氣溫度感測 态12-1〜12-3 ’其用於計剛從空調機^丨〜^^所送出的供 .氣的溫度；回流水溫度感蜊器（回流水溫度計測裝置）13， .其用於計麟過了空調機5_1〜5_3的回流水的溫度；空調 控制裝置14’其藉由調整閥門6_丨〜6_3的開度而控制對空 調機5-1〜5-3的冷熱水的供給量；送水控制裝置15，其對 (將冷熱水向空調機5-1〜5-3送出之泵9-卜9-2等進行控制。 閥門6-1〜6-3分別具有流量感測器（流量計測裝置）， 對通過閥門6_1〜6-3的冷熱水的流量進行計測。二次泵 9-1、9-2分別具有變流器9-ia、。 由一次泵2-；1、2_2壓送並由熱源機M、1-2附加熱量 之冷水或熱水等熱媒（送水），是被送至去路集管箱， 並利用二次泵9-1、9-2壓送而經由去路彎管3_2被供給到 送水管路4，且通過空調機5_1〜5-3而利用回流水管'ς 7 广作為回流水到達回路集管箱8，再利用泵^、2_2進行壓 V. 送。运樣，冷熱水就在以上的路徑中進行循環。 另外’在上述說明中所說的配管系統末端，是指在建 築物的最高處所設置的閥門的附近，或者從泵開始的拉繞 距離最長之閥門的附近中的某一個。選擇其中的哪—個可 根據建築物而酌情決定。測定送水壓力的位置只要是果和 閥門之間的配管，在哪裡都可以，但是最好是在配管系統 末端進行測定。亦即，由於配管系統末端是最容易受到因 配管的破損所導致的送水壓下降之影響的位置，所以如進 13 200912215 行控制而使這裏的送水壓力滿足規定的值，則在全部的配 管系統中都可滿足規定的送水壓力。 圖2所示為空調控制裝置14的構成例的方塊圖。空調 控制裝置14包括：供氣溫度接收部14〇，其用於接收供氣 溫度感測态12-1〜12-3所計測之供氣溫度的值；流量接收 部141，其用於接收閥門6-1〜6-3的流量感測器所計測之 流里的值，回流水溫度接收部142 ’其用於接收回流水溫 度感測器13所计測之回流水溫度的值；設定部143，其用 於接收由用戶或建築物的管理負責人所設定的溫度設定值 (或濕度设疋值）’記憶部144，其預先記憶在空調機5·ι〜 5-3中所流過之冷熱水的設計最大流量的值，和設計回流 水溫度的值；運算部145，其決定向空調機5_丨〜5_3所供 給的冷熱水的設定流量，且決定空調機5_丨〜5_3的控制狀 態（空調機控制狀態）；閥門控制部146，其根據運算部145 所決J的設定流量而控制閥門6_丨〜6_3的開度；空調機控 制狀態發送部147,其將空調機控制狀態向送水控制裝置 15進行發送。 運算部145和閥門控制部146構成空調控制裝置和閥 門開度限制裝置。 圖3所示為送水控制裝置15的構成例的方塊圖。送水 控制，置15包括：送水壓力接收部15()，其用於接收壓力 感測為11所計測之送水壓力白勺值；空調機控制狀態接收部 151&其用於接收從空調控制裝置14所發送的空調機控制 狀心’運异部152，其根據空調機控制狀態而決定設定送 14 200912215 水壓力，泵控制部153，其根據運算部152所決定的設定 送水壓力，而通過變流器9-ia、9-2a控制二次泵9-1、9-2 的轉速(以下稱作變流器轉速）。 • 接著，對本實施形態的空調控制系統的動作進行說 明。圖4所示為空調控制裝置14的動作的流程圖，圖5 所示為利用空調控制裝置14的空調機控制狀態的決定方 法之流程圖，圖6所示為送水控制襞置15的動作的流程 广 圖，圖7所示為利用送水控制裝置15的綜合送水狀態的決 "定方法之流程圖。 空調機5-1〜5-3從熱源機1-1、1_2接收冷水或熱水的 供給’並將從作為空調控制區域的室内所返回的空氣(返回 氣體)和外部氣體之混合氣體進行冷卻或加熱，且將冷卻或 加熱了的供氣送入到室内。 空調控制裝置14的供氣溫度接收部140接收表示供氣 溫度的供氣溫度信號(圖4的步驟S1)，其中供氣溫度是利 用供氣溫度感測12-1〜12-3進行計測。 Ο 運异部145計算閥門6-1〜6-3的設定流量，以使設定 部143所設定的溫度設定值和供氣溫度接收部14〇所接收 的供氣溫度的值一致(步驟S2)。亦即，運算部145根據溫 度設定值和供氣溫度的偏差，而利用例如 PID(Prop〇rtional-Integral-Derivative，比例積分微分)運算求 取設定流量。運算部145在每一空調機和與其對應的供氣 溫度感測器的組中，進行這種設定流量的計算。 另外，也可利用濕度感測器計測供氣的濕度，並根據 15 200912215 濕度設定值和現在的供氣濕度之偏差，㈣^定#。 另-方面’流量接收部141接收表示冷;二二通 其中，冷熱水的閥門通過流 罝疋由閥Η 6_1〜6-3的流量感測器進行計測。 f算部145將流量接收部⑷所接㈣現在的閥Π通 過流里的值和記憶部144所記憶的設計最大流量的值進行 通過流量超出設計最大流量(在步驟 中^為疋），則對閥門6_1〜6·3的開度進行限制，以 使閥門通過流量小於等於設計最大流量(步驟吻。 - H6·1〜6·3的開度限制的具體方法，是例如以下所 ^主7 Π卩145在現在㈣門通過流量超出設計最大流量 及 步，S2所算出的設定流量較現在的設定流量 里小的情況下，藉由將步驟S2所算出的設 、、*旦於Φ、新的设定流量進行更新，並將該更新後的設定 到間門控制部146，而限制闕門6·1〜6·3的開度 1而且，運算部145在現在的閥門通過流量超出 二現在、:量的情況，及步驟S2所算出的設定流量大於 計最大炉息设定流量或設計最大流量的情況下，藉由使設 輸出C新的設定流量，並將該更新後的設定流量 S5)。句門控制部146，而限制閥門6-1〜6_3的開度(步驟 使現閥門6-1〜6-3的開度進行控制’以 流量的值~ 1通過流量的值與從運算部145所輸出的設定 致。這樣’可對閥門6-1〜6-3的開度進行限制。 16 200912215 運算部145在每-閥門w〜6_3進行步驟§4、§5的處理。 在記憶部144巾預先存儲的設計最大流量#然可為全 部的空調機5·1〜5·3共同的值，也可為對每—空調機5] ' 〜5-3的確定的值。 接著，在現在的閥門通過流量小於等於設計最大流量 的情況下(在步驟S4中判定為否），回流水溫度接收部142 接受表示回流水溫度的回流水溫度信號(步驟S6)，其中， 回流水溫度是由回流水溫度感測器13進行計測。 運算部145對回流水溫度接收部I42所接收的現在的 =流水溫度的值和記憶部144所記憶的設計回流水溫度的 U行比較，並在現在的回流水温度較設計回流水溫度低 、鱼二兄下(在步驟S7中判定為是）’對閥門w〜6_3的開度 加订限制(步，驟S8) ’以使回流水溫度大於等於設計回流水 且，閥2 6-1〜6-3的開度限制的具體方法與上述相同。而 异部I45在步驟S7中，如現在的回流水溫度大於 量作叹计回流水溫度，則藉由將步驟S2所算出的設定流 =為新的設定流量，並將該更新後的設定流量輸出到閥 沾广制部146,而對閥門6_1〜6·3的開度進行控制(步驟 步驟另外，如現在的回流水溫度較設計回流水溫度低而在 運轉中判定為是的情況，為製冷運轉的情況。在製熱 言萨的情況下，是當現在的回流水溫度較設計回流水溫度 门了在步驟S7中判定為是，當現在的回流水溫度小於等 17 200912215 於設計回流水溫度時判定為否，如在步驟S7中判定為是， 可對閥門6-1〜6-3的開度進行限制，以使回流水度於 等於設計回流水溫度。設計回流水溫度在冷水(製；^運轉） 的情況和熱水(製熱運轉)的情況下當然可分別進彳^ ^定。 在步驟S5、S8、S9的處理結束後，運算部據 閥門6 -1〜6 - 3的流量控制狀態而決定空調機5 〜3的栌 調機控制狀態)(步驟_，並將該空調機控制^ 嫌域魏料7向送林難置15進行 i利二')。步驟S1。*的空調機控制狀態的決定方 次矛〗用圖5進行說明。 持規運算部145賴⑽〜6相全態是否保 如不保持^T；5分鐘）進行檢查（圖5的步驟S21)， 為「送水壓:Γ:Γ=機!空調機控制狀態判定 門6-1〜6=、 ）。而且，運算部145在閥 不足狀離卜全開狀雜持規定時_情況下，檢測流量 過流量不足)是否保持規定時間 刀鐘）（步驟S23)。 空調機二： 的處理。 3)進行步驟S10、S11 18 200912215 為是）。 助作(在圖4的步驟S12中 ㈣接^利用圖6、圖7對送水控制裝置15的動作進行 收從；7控制裝置15的空調機控制狀態接收部15卜接 送來的空調機控制狀態（圖6中的Further, in the present invention, when the measured valve bucket passage flow rate is less than or equal to the design maximum flow rate, and the measured return water temperature measured during the cooling operation is lower than the design return water temperature, or when the heating water is turned, the measurement is performed. When the reflux water μ degree is designed to the reflux water temperature, by restricting the opening of the valve, the valve passage flow rate can be suppressed in the case where an excessive flow rate is formed to the air conditioning load. As a result, the temperature difference between the hot and cold water can be ensured at the inlet and the outlet of the air conditioner, so that the operation efficiency of the heat source machine can be improved, and the energy consumption of the heat source machine can be suppressed. [Embodiment] [First Embodiment] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Fig.:: Configuration of the air conditioning control system according to the first embodiment of the present invention The air conditioning control system of Fig. 1 includes a heat source unit, a hot water generator for generating hot and cold water, a heat pump, and a cold machine. As the heat source machine is called: special road = official box Μ, 3-2, which will come from multiple heat source machines =, =: == combined; water supply line 4; air conditioner ^3; valve to air conditioner M~ 5, the flow of hot and cold water is carried out;; ^ Road 7; the circuit header box 8, which will be replaced in the air conditioner 5-M3, the hot father is replaced by the return water pipeline 7 A spring, it is set to go: ?=return; second quotation between the s phase 3-1 and 3-2; bypass 200912215 阙ίο 'It is set between the 3rd and 3_2 of the depot, the pressure sensor η, which is used The water supply pressure of the matching r system ^; the gas supply temperature sensing state 12-1~12-3 'it is used to calculate the temperature of the gas supplied from the air conditioner ^丨~^^; the reflux water temperature sensor (return water temperature measuring device) 13, which is used to calculate the temperature of the return water of the air conditioners 5_1 to 5_3; the air conditioning control device 14' controls the air conditioner by adjusting the opening degree of the valves 6_丨~6_3 Machine 5-1 The supply amount of the hot and cold water of ～5-3; the water supply control device 15 controls the pump 9-b-9-2 that sends the cold and hot water to the air conditioners 5-1 to 5-3. Valve 6-1~ 6-3 each has a flow sensor (flow rate measuring device) for measuring the flow rate of the hot and cold water passing through the valves 6_1 to 6-3. The secondary pumps 9-1 and 9-2 respectively have a current transformer 9-ia, The hot medium (water supply), such as cold water or hot water, which is pumped by the primary pump 2; 1, 2_2 and is heated by the heat source machine M, 1-2, is sent to the bypass header box, and the secondary pump 9 is used. -1, 9-2 are sent to the water supply line 4 via the outward bend 3_2, and are returned to the loop header 8 by the air conditioners 5_1 to 5-3 using the return water pipe 'ς7' as the return water. Pressing the pump ^, 2_2 for pressure V. Sending, the hot and cold water is circulated in the above path. In addition, the end of the piping system mentioned in the above description refers to the valve installed at the highest point of the building. In the vicinity, or one of the vicinity of the valve with the longest distance from the pump. Which one of them can be selected at the discretion of the building. The position of the pressure may be any place as long as it is a pipe between the fruit and the valve, but it is preferably measured at the end of the piping system, that is, since the end of the piping system is most susceptible to water supply pressure due to breakage of the piping. Since the position of the influence of the descent is controlled so that the water supply pressure here satisfies the predetermined value, the predetermined water supply pressure can be satisfied in all the piping systems. Fig. 2 shows the configuration of the air conditioning control device 14. The block diagram of the air conditioning control unit 14 includes: an air supply temperature receiving unit 14〇 for receiving a value of the supply air temperature measured by the supply air temperature sensing states 12-1 to 12-3; and a flow rate receiving unit 141, It is used to receive the value in the flow measured by the flow sensor of the valves 6-1 to 6-3, and the return water temperature receiving portion 142' is configured to receive the reflux water temperature measured by the reflux water temperature sensor 13. The setting unit 143 is configured to receive a temperature setting value (or a humidity setting value) set by the management person in charge of the user or the building, and the memory unit 144 is pre-stored in the air conditioner 5·1 to 5- The cold that flows through 3 The value of the designed maximum flow rate of the hot water and the value of the designed return water temperature; the calculation unit 145 determines the set flow rate of the hot and cold water supplied to the air conditioners 5_丨 to 5_3, and determines the air conditioners 5_丨~5_3 Control state (air conditioner control state); valve control unit 146 controls opening degree of valves 6_丨 to 6_3 based on set flow rate determined by calculation unit 145; air conditioner control state transmitting unit 147, which controls air conditioner The state is transmitted to the water supply control device 15. The calculation unit 145 and the valve control unit 146 constitute an air-conditioning control device and a valve opening degree restriction device. FIG. 3 is a block diagram showing a configuration example of the water supply control device 15. The water supply control unit 15 includes: a water supply pressure receiving portion 15 () for receiving a value of the water supply pressure measured by the pressure sensing 11; and an air conditioner control state receiving portion 151 & for receiving the slave air conditioning control device 14 The transmitted air conditioner control center "transmission unit 152" determines the water pressure of the setting and delivery 14 200912215 based on the air conditioner control state, and the pump control unit 153 passes the variable flow according to the set water supply pressure determined by the calculation unit 152. The switches 9-ia, 9-2a control the rotational speeds of the secondary pumps 9-1, 9-2 (hereinafter referred to as converter speeds). • Next, the operation of the air conditioning control system of the present embodiment will be described. 4 is a flowchart showing the operation of the air conditioning control device 14, and FIG. 5 is a flowchart showing a method of determining the air conditioner control state by the air conditioning control device 14, and FIG. 6 is a view showing the operation of the water supply control device 15. The flow chart is broad, and FIG. 7 is a flow chart showing the method of determining the integrated water supply state by the water supply control device 15. The air conditioners 5-1 to 5-3 receive the supply of cold water or hot water from the heat source units 1-1 and 1_2 and cool the air (return gas) returned from the room as the air-conditioning control area and the mixed gas of the outside air. Or heating, and the cooled or heated supply air is sent to the room. The supply air temperature receiving unit 140 of the air conditioning control device 14 receives the supply air temperature signal indicating the supply air temperature (step S1 of Fig. 4), wherein the supply air temperature is measured by the supply air temperature sensing 12-1 to 12-3. The different flow portion 145 calculates the set flow rate of the valves 6-1 to 6-3 so that the temperature set value set by the setting unit 143 matches the value of the supply air temperature received by the supply air temperature receiving unit 14 (step S2). . In other words, the calculation unit 145 calculates the set flow rate by, for example, PID (Prop〇rtional-Integral-Derivative) calculation based on the deviation between the temperature set value and the supply air temperature. The calculation unit 145 performs calculation of such a set flow rate in each of the air conditioners and the group of supply air temperature sensors corresponding thereto. In addition, the humidity sensor can also be used to measure the humidity of the air supply, and according to the deviation of the humidity setting value of 15 200912215 and the current supply air humidity, (4) ^定#. On the other hand, the flow receiving unit 141 receives the indication of cold; the second and second passages, wherein the valves of the hot and cold water are measured by the flow sensors of the valves Η 6_1 to 6-3 through the flow. The calculation unit 145 passes the flow rate of the current valve Π through the flow rate receiving unit (4) and the value of the designed maximum flow rate memorized by the storage unit 144 to exceed the designed maximum flow rate (in the step ^ 疋), The opening degree of the valves 6_1~6·3 is limited so that the valve passing flow rate is less than or equal to the designed maximum flow rate (step kiss. - The specific method of opening limit of H6·1~6·3 is, for example, the following main 7 Π卩 145, when the current flow rate exceeds the designed maximum flow rate and the step, and the set flow rate calculated by S2 is smaller than the current set flow rate, the setting calculated in step S2, * is Φ, new The set flow rate is updated, and the updated setting is set to the door control unit 146, and the opening degree 1 of the tips 6·1 to 6·3 is restricted, and the calculation unit 145 passes the current flow rate of the valve now. In the case of the amount, and when the set flow rate calculated in step S2 is greater than the maximum furnace set flow rate or the design maximum flow rate, the new set flow rate is outputted by C, and the updated set flow rate S5 is set. ). The sentence gate control unit 146 limits the opening degree of the valves 6-1 to 6_3 (the step of controlling the opening degrees of the current valves 6-1 to 6-3) to the value of the flow rate to the flow rate value and the slave operation unit 145. The output is set such that the opening degree of the valves 6-1 to 6-3 can be limited. 16 200912215 The calculation unit 145 performs the processing of steps § 4 and § 5 for each valve w to 6_3. The maximum flow rate of the design of the towel pre-stored may be a common value of all the air conditioners 5·1 to 5·3, or may be a certain value for each of the air conditioners 5]' to 5-3. Next, now When the flow rate of the valve passage is less than or equal to the design maximum flow rate (NO in step S4), the return water temperature receiving portion 142 receives a return water temperature signal indicating the return water temperature (step S6), wherein the return water temperature is determined by The calculation unit 145 compares the value of the current = flowing water temperature received by the return water temperature receiving unit I42 with the U line of the designed reflow temperature memorized by the memory unit 144, and now The temperature of the reflux water is lower than the temperature of the designed reflux water, and the fish is under the second brother (in step S7) The judgment is YES) 'Add limit to the opening degree of the valve w~6_3 (step, step S8) 'to make the reflux water temperature greater than or equal to the designed return water and the opening limit of the valve 2 6-1~6-3 The method is the same as above. In step S7, if the current reflux water temperature is greater than the amount of the backflow water temperature, the set flow calculated in step S2 is set to the new set flow rate, and the The updated set flow rate is output to the valve squeezing portion 146, and the opening degrees of the valves 6_1 to 6·3 are controlled (step step, if the current reflux water temperature is lower than the design return water temperature, it is determined during operation as In the case of cooling operation, in the case of heating, it is determined that the current return water temperature is lower than the design return water temperature threshold in step S7, and the current return water temperature is less than or equal to 17 200912215 When the design of the reflux water temperature is judged as NO, if it is determined as YES in step S7, the opening degree of the valves 6-1 to 6-3 can be restricted so that the reflux water level is equal to the designed return water temperature. Flowing water temperature in cold water (system; ^ operation) In the case of the hot water (heating operation), it is of course possible to determine the air conditioning. After the processing of steps S5, S8, and S9 is completed, the computing unit determines the air conditioning according to the flow control state of the valves 6-1 to 6-3. The machine control state of the machine 5 to 3) (step _, and the air conditioner control ^ 域 魏 魏 7 向 向 送 送 进行 进行 进行 进行 进行 ' 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 The determination of the spear is described with reference to Fig. 5. The holding calculation unit 145 checks whether the (10) to 6 phase states are not maintained (T) for 5 minutes; (step S21 of Fig. 5), which is "sending water pressure: Γ: Γ = machine! Air conditioner control state determination gates 6-1 to 6 =, ). Further, the calculation unit 145 detects whether or not the flow rate excessive flow rate is maintained for a predetermined time (in the case of a valve shortage) when the valve is insufficiently closed (step S23). Air conditioner 2: The treatment. 3) Steps S10, S11 18 200912215 are performed). In the step S12 of FIG. 4, the operation of the water supply control device 15 is performed by using FIG. 6 and FIG. 7; and the air conditioner control state receiving unit 15 of the control device 15 controls the air conditioner control state. (in Figure 6
送水控制裝的運算部152根據所接收的空調機控 制狀態而決定綜合送水狀態（综合送水status)(步驟％2)。 步驟S32的综合送水狀態的決定方法利用圖7進行說明。 首先，運算部152檢查各空調機54^-3的空調機# 制狀態中是否存在「送水壓不足」的情況（圖7的步ς S41) ’且只要有1個「送水壓不足」，即決定综合送^狀 態為「送水壓不足」（步驟S42)。運算部152在各空調機 5-1〜5-3的空調機控制狀態不存在「送水壓不足」的情、、兄 下，檢查「送水壓過多」的個數(步驟S43)，如「送水壓過 多」的個數大於等於設定個數(在本實施例中為1個），則 決定綜合送水狀態為「送水壓過多」（步驟S44)。而且，運 算部152在「送水壓過多」的個數不足設定個數的情况下， 決定綜合送水狀態為「最佳送水壓」（步驟S45)。這樣，結 束步驟S32的處理。 接著，運算部152根據綜合送水狀態，決定設定送水 壓力（圖6的步驟S33)。設定送水壓力的決定方法是例如以 下那樣。運算部152在綜合送水狀態為「最佳送水壓」的 19 200912215 0不變更現在的設定送水壓力而予以維持（步驟 1[ 運算部152在綜合送水狀態為「送水壓不 ΐΐϋρ 定送水壓力上加上規定的設定值 里Α 之值，作為新的設定送水壓力（步驟S33)。 且運卩152在綜合送水狀態為「送水壓過多」的 下，將從現在的設定送水壓力減去規定的設定值變更 Ρ之值，作為新的設定送水壓力（步驟S33)。 "Δ 严二水ΪΪ裝置15的送水壓力接收部15〇接收表示送水 Τ]7㈣信號(步驟S34)，其中，送水壓力是由壓力 感測器11進行計測。 刀 水麼== 算部152在藉由將步驟S33所決定的設定送 t 泵控制部153而控制送水壓力（步驟 )。泵控制部153透過變流器9七、9_2a，對二次果9卜 9-2的變㈣魏進行控制’喊壓力麵器u所計測的 現在的达水壓力與設定送水壓力一致。 S3i二=!!裝置1f反復騎以上那樣的圖6所示的步驟 中為是）。、处理’直至系統停止動作（在圖6的步驟S36 =上所述二在本實施形態中，藉由在計測的闕門通 超過以取大流量的情況下，對閥門6]〜6_3的開 丁、^制,而即使因溫濕度設定的錯誤(過度製冷、過 歧熱)麵產生了咖設計最大流量的流量要求，也可抑 制閥門通過流量以使其小於等於設計 泵搬運動力的增加所導致的耗能的增加。而且，在本實施 20 200912215 形態中’藉由抑制閥門通過流量以使其小於等於設計最大 流量’可在空調機5-1〜5-3的入口和出口確保冷熱水的溫 度差’因此’能夠使熱源機1-1、1-2的運轉效率提高’可 抑制熱源機Μ、1_2的耗能的增加。而且，在本實施形態 中’不需要採取將要求流量大的系統的閥門開度從送水控 制的判斷指標中移除，或者降低送水控制上的權重等方 法’能夠節省現場作業的人力和時間。 而且’在本實施形態中，在所計測的閥門通過流量小 於等於設計最大流量，且製冷運轉時所計測的計測回流水 溫度低於設計回流水溫度之情況下，或製熱運轉時的計測 回流水溫度高於設計回流水溫度的情況下，藉由限制閥門 6-1〜6-3的開度’可在對空調負載形成過度流量的情況下 抑制闕門通過流量。結果使本實施形態可在空調機5-1〜 5-3的入口和出口確保冷熱水的溫度差，所以能夠使熱源 機1-1、1-2的運轉效率提高，可抑制熱源機1-1、1-2的耗 能的增加。 ，且，如本實施形態所示，藉由在閥門6_〗〜6_3中内 置流1感測器，從而不需要為了流量感測器而在配管進行 施工，可增加本發明的適用對象。 丁 另外，在本實施形態中，是作為在具有二次泵、 9-2的系統中應用的例子進行了說明，但在只具有一次泵 2-1〜2-3的系統中，也可與本實施形態同樣地對一次泵/ 〜2-3進行控制。 而且，在本實施形態中所說明的空調控制裝置14、送 21 200912215 水控制裝置15，可分別益丄 她，中央處理單元）错由具有cpu (central p麗ssing 些硬體資_程式而^錢裝置及介面的電腦和控制這 置中所存放的程i貫現。這些電腦的CPU是依據記憶裝 ϋ 叫行本實細彡祕制的處理。 !_屋業上之可利用性] ^明可適用於空調 【圖式簡單說明】 f 统的二成方塊i ^於本發明的第1實施形態之空調控制系 圖2所示為圖1的办 成例的方塊圖。 § 周控制系統的空調控制裝置之構 成例：方塊圖：θ的工凋控制系統的送水控制裝置之構 :所示為圖2的空調控制裝 圖5所示為利用圖2 之机私圖。 態的決定方法的流程圖。一工1衣置之空調機控制狀 =6所不為圖3的送水控制裝置的動 圖7所示為利用闰q &、、， 乍之流程圖。 的決定枝的餘圖:1水控織以综合送水狀態 【主要元件符號說明】The calculation unit 152 of the water supply control device determines the integrated water supply state (combined water delivery status) based on the received air conditioner control state (step %2). The method of determining the integrated water supply state in step S32 will be described with reference to Fig. 7 . First, the calculation unit 152 checks whether or not the "water supply pressure is insufficient" in the air conditioner #4 state of each of the air conditioners 54^-3 (step S41 of Fig. 7), and only one "water supply pressure is insufficient" That is, it is determined that the integrated delivery state is "the water supply pressure is insufficient" (step S42). In the air conditioner control state of each of the air conditioners 5-1 to 5-3, the calculation unit 152 does not have the "supplement of the water supply pressure", and checks the number of "too much water supply pressure" (step S43). When the number of the "several water supply pressures" is equal to or greater than the set number (one in the present embodiment), it is determined that the integrated water supply state is "too much water supply pressure" (step S44). Further, when the number of "too much water supply pressure" is less than the set number, the operation unit 152 determines that the integrated water supply state is "optimal water supply pressure" (step S45). Thus, the processing of step S32 is ended. Next, the calculation unit 152 determines the water supply pressure to be set based on the integrated water supply state (step S33 in Fig. 6). The method of determining the water supply pressure is as follows. The calculation unit 152 maintains the current set water supply pressure without changing the current set water supply pressure at 19 200912215 0 in which the integrated water supply state is "optimal water supply pressure" (step 1 [the calculation unit 152 sets the water supply pressure to "the water supply pressure is not set to the water supply pressure". The value of the predetermined set value is added as the new set water supply pressure (step S33). And the operation 152 is subtracted from the current set water supply pressure when the integrated water supply state is "too much water supply pressure". The value of the predetermined set value change Ρ is set as the new set water supply pressure (step S33). The water supply pressure receiving unit 15 of the Δ 二 ΪΪ 15 15 15 receives the signal indicating the water supply Τ 7 (4) (step S34), wherein The water supply pressure is measured by the pressure sensor 11. Knife water == The calculation unit 152 sends the water supply pressure to the pump control unit 153 by the setting determined in step S33 (step). The pump control unit 153 transmits the pressure. The flow device 9 7 and 9_2a control the change of the second fruit 9 9 9-2 (four) Wei. The current water pressure measured by the pressure pressure device u is consistent with the set water supply pressure. S3i 2 =!! Device 1f repeated Ride the above as shown in Figure 6. The steps in the process are yes). "Processing until the system stops operating (in step S36 of Fig. 6 = the above two. In the present embodiment, the opening of the valves 6] to 6_3 is performed by the case where the measured slamming door passes over to take a large flow rate. Ding, ^ system, and even if the error set by the temperature and humidity (overcooling, overheating) surface creates the flow rate requirement of the maximum flow rate of the coffee design, it can also suppress the flow rate of the valve to be less than or equal to the increase of the pumping power of the design pump. The resulting increase in energy consumption. Moreover, in the embodiment of the present invention 20 200912215, 'by suppressing the flow rate of the valve to be equal to or less than the designed maximum flow rate', it is possible to ensure hot and cold water at the inlet and outlet of the air conditioners 5-1 to 5-3. The temperature difference 'so' can improve the operation efficiency of the heat source machines 1-1 and 1-2, and it is possible to suppress an increase in the energy consumption of the heat source unit Μ1 and 1-2. Moreover, in the present embodiment, it is not necessary to take a large flow rate. The method of removing the valve opening degree from the judgment index of the water supply control or reducing the weight on the water supply control can save the manpower and time of the field work. And in the present embodiment, the measured When the flow rate of the valve is less than or equal to the designed maximum flow rate, and the measured reflux water temperature measured during the cooling operation is lower than the designed return water temperature, or when the measured return water temperature during the heating operation is higher than the designed return water temperature, By restricting the opening degree of the valves 6-1 to 6-3, the flow rate of the card door can be suppressed in the case where an excessive flow rate is formed to the air conditioning load. As a result, the present embodiment can be at the entrance of the air conditioners 5-1 to 5-3. Since the temperature difference between the hot and cold waters is ensured at the outlet, the operation efficiency of the heat source machines 1-1 and 1-2 can be improved, and the increase in energy consumption of the heat source machines 1-1 and 1-2 can be suppressed. As shown in the figure, by incorporating the flow 1 sensor in the valves 6__6 to 6_3, it is not necessary to perform the construction of the pipe for the flow sensor, and the object to which the present invention is applied can be increased. In addition, in the present embodiment, Although it has been described as an example of application to a system having a secondary pump and 9-2, in a system having only one primary pump 2-1 to 2-3, a primary pump can be used in the same manner as in the present embodiment. ~2-3 for control. Moreover, in this implementation The air conditioning control device 14 described in the state, the delivery 21 200912215 water control device 15, respectively, can benefit her, the central processing unit) is wrong with the cpu (central p ssing some hardware _ program and money device and interface The computer and the control are stored in the middle of the process. The CPU of these computers is handled according to the memory of the device. The availability of the house is clearly applicable to the air conditioner. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 2 is a block diagram of an example of the air conditioning control system of the first embodiment of the present invention. § The air conditioning control device of the weekly control system Configuration example: Block diagram: Structure of the water supply control device of the θ control system: The air conditioner control device shown in Fig. 2 is shown in Fig. 5 as a private diagram using Fig. 2. Flow chart of the method of determining the state. The control of the air conditioner of the first work and the clothing is = 6 is not the movement of the water supply control device of Fig. 3. Fig. 7 is a flow chart using 闰q &,,, 乍. The remaining map of the decision branch: 1 water control weaving to the integrated water supply state [main component symbol description]
Ul ' 1-2 :熱源機 厶1、2-2 : -次泵 Li ' 3-2 :去路集管箱 4 :送水管路 22 200912215 5- 1〜5-3 :空調機 6- 1〜6-3 :閥門 7:回流水管路 8:回路集管箱 9-1、9-2 :二次泵 9-la、9-2a :變流器 10 :旁通閥 11 :壓力感測器 12-1〜12-3 :供氣温度感測器 13 :回流水溫度感測器 14 :空調控制裝置 15 :送水控制裝置 140 :供氣温度接收部 141 :流量接收部 142 :回流水溫度接收部 143 :設定部 144 :記憶部 145 :運算部 146 :閥門控制部 147 :空調機控制狀態發送部 150 :送水壓力接收部 151 :空調機控制狀態接收部 152 :運算部 153 :泵控制部 23Ul ' 1-2 : Heat source machine 厶 1, 2-2 : - Secondary pump Li ' 3-2 : Road header tank 4 : Water supply line 22 200912215 5- 1~5-3 : Air conditioner 6 - 1~6 -3 : Valve 7: Return water line 8: Circuit header box 9-1, 9-2: Secondary pump 9-la, 9-2a: Converter 10: Bypass valve 11: Pressure sensor 12- 1 to 12-3: supply air temperature sensor 13 : reflux water temperature sensor 14 : air conditioning control device 15 : water supply control device 140 : supply air temperature receiving unit 141 : flow rate receiving unit 142 : return water temperature receiving unit 143 : Setting unit 144 : Memory unit 145 : Calculation unit 146 : Valve control unit 147 : Air conditioner control state transmitting unit 150 : Water supply pressure receiving unit 151 : Air conditioner control state receiving unit 152 : Calculation unit 153 : Pump control unit 23