576902 A7 _____B7___ 五、發明說明（） 【發明所屬之技術領域】 本發明，係關於減壓裝置與使用該減壓裝置之冷熱水 供應系統，以及用於該系統之減壓裝置之選擇方法。 【習知技術】 以往，加壓供水式冷熱水供應系統利用冷熱水混合龍 頭將冷水配管與熱水配管予以相連’從位於各戶（房間）供 水末端的水龍頭或淋浴用或沐浴用龍頭等來供應一設定溫 度之水。 【發明欲解決之課題】 然而上述系統中，冷水配管與熱水配管內的壓力由於 冷水或熱水用量之變動而會改變，使各戶水龍頭之水溫也 跟著改變。 於冷水管與熱水管分別設有泵，上述問題之原因在於 以配管連接於該泵吐出側之直動式減壓閥° 因泵之吐出壓力係高壓，爲了能降低至在各戶之冷水 管或熱水管末端所使用之壓力，而於冷水配管與熱水配管 分別設置減壓閥.，減壓閥會直接偵知二次側壓力來調整閥 開度而控制二次側壓力。 上述減壓閥因二次側壓力隨著冷熱水用量之不同而變 動大，故冷熱水的用量由於各水龍頭之使用一旦改變時， 冷水配管與熱水配管兩者之二次側壓力均會有大的變動， 使來自冷水配管之的冷水及來自熱水配管之的熱水之兩者 流量均會改變，因此用水中，冷水側或熱水側之壓力會忽 (請先閱讀背面之注意事項再填寫本頁) ^^1 ^^1 n νϋ 1 βϋ β ϋ —ϋ ϋ— ι_ϋ n ϋ— n I 線丨,---- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 ____ Β7 _ 五、發明說明（之） 下或忽上’造成所提供之水溫比溫度設定値爲低或爲高。 對於追種減壓閥’爲確保熱水或冷水之流量，須增加 膜片有效徑對減壓閥閥口徑的比値，這樣的話，減壓閥會 變得太大而不實用。 本發明之目的在於提供一種減壓裝置與使用該裝置之 冷熱水供應系統，以及用於該系統之減壓裝置之選擇方法 ，即用水量改變也能以穩定的壓力來供水。 【用以解決課題之手段】 本發明，係有鑒於上述課題，設有總閥，其透過閥口 將一次側壓力室及二次側壓力室予以連通，利用彈簧對開 閉該閥口之主閥施加開閥方向之彈壓，利用與主閥相連之 膜片區劃成位於本體內部膜片背面側之膜片室及一次側壓 力室，設置一嚮導管路，其在前述一次側壓力室與二次側 壓力室之間有減壓閥，在該嚮導管路中，將位於減壓閥一 次側之分岐管路連接於前述膜片室，並於分岐點起上游處 設置節流機構，利用該節流機構將把從本體一次側壓力室 流到減壓閥一次側壓力室及膜片室之通水量加以限制，當 要使用水而打開減壓閥時，可促使膜片室之壓力下降，使 本體呈開閥狀態。 亦即，當二次側壓力由於使用水而變得比其設定値爲 低時，因與用水量相同之水量通過本體，使二次側壓力不 會大幅下降，故即用水量改變也能以穩定的壓力來供水。 又，藉著把依某一定條件所選出之減壓裝置安裝於冷 熱水供應系統，能穩定地供應所需溫度之冷熱水而解決上 _____5_____ 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) -· I 丨 — 111— ^ . I — II---· » 576902 B7 五、發明說明（；） 述課題。 【發明之實施形態】 以下根據圖式說明本發明之一實施例。 在圖1表示嚮導作動式減壓裝置之截面圖。此減壓裝 置1主要係以總閥之本體2(設置於冷水配管與熱水配管）’ 以及減壓閥4(以嚮導管路連接於該本體2)所構成。 設在本體2之閥箱5，係開設流入口 6與流出口 7於 其左右側部，在閥箱5之內部，設置一次側壓力室8及二 次側壓力室9 (分別連通於流入口 6與流出口 7)，一次側壓 力室8及二次側壓力室9係在閥箱5內部以隔壁10區劃成 爲外側與內側，在隔壁10開口形成閥口 11(與流入口 6成 直交方向且向上），透過該閥口 11來連通一次側壓力室8 及二次側壓力室9。 又，在閥箱5之上部設置開口部5a，連通於一次側壓 力室8及閥口 11，該開口部5a則被位於閥箱5上部與蓋 住該閥箱5之閥帽12兩者間之膜片13所封閉。 閥帽12 ’係在其內側設置一^由膜片13區劃閥箱5內 部而成之凹狀空間，把此膜片13背面側之空間作爲膜片室 14，在該膜片室14之上部(相當於閥帽12)中心設置一連接 於嚮導管路3之口 15。 一主閥17，係與位於膜片13下方且設於閥口 11周圍 之閥座16相對應，膜片13下面呈近似環條狀突出；因主 閥17和膜片13形成爲一體，使主閥17與膜片13相連。 在主閥17內側之膜片13下面、與對應主閥17之膜 (請先閱讀背面之注意事項再填寫本頁) ;0 訂---------線」 表纸張尺度適用中國國家標準（CNS)A4規格（21〇 X 2976公爱 1 " 576902 A7 一___B7 __ 五、發明說明（^ ) 片13上面，分別接合近似圓板狀之壓膜片構件18、18a。 而且，在膜片室14之上部與壓膜片構件18之間壓裝 一彈簧19，用該彈簧19對主閥17施加閉閥方向之彈壓。 嚮導管路3，係把口 15a、15b(分別設置於本體2之一 次側壓力室8及二次側壓力室9)連接至外部，在嚮導管路 3上之減壓閥4之一次側(上游)設置分岐管路3a並把該分 岐管路3a連接於設在膜片室14之口 15，在嚮導管路3分 岐點Μ上游與分岐管路3a上，分別設置由針閥製成之節 流機構20、21。 並且，當二次側壓力P4從其設定壓力Ps下降至容許( 能以穩定之壓力供應冷熱水)範圍之下限値Pi/時，把減壓 閥4之流量能力(流量Q!)設定成比被節流機構20所限制之 供應能力(流量Q2)爲大。 即，設定爲滿足Qi>Q2之條件。 藉此，減壓裝置1可在裝有該減壓裝置1之冷熱水供 應系統中受到控制，使得在所設定之最大使用量Fm以下 時二次側壓力P4會在容許範圍內。 減壓閥4，在其閥箱22之左右側部開設連接於嚮導管 路3之流入口 23與流出口 24，在閥箱22之內部，分別設 置一次側壓力室25及二次側壓力室26(連通於流入口 23 與流出口 24)，以隔壁27將閥箱22內部區劃左右分別爲 一次側壓力室25及二次側壓力室26，在隔壁27與流入口 23直交方向上形成向下之閥口 28，透過該閥口 28連通兩 壓力室25、26。 --------訂---------線 (請先閱讀背面之注意事項再填寫本頁) 木纸張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 ____B7 __ 五、發明說明（i：) 在閥箱22之上部設置近似向上開口碟狀之凹部29, 並且將該凹部29底部之一部分予以開口而連通於二次側壓 力室26，利用位於凹部29與蓋住凹部29之彈簧蓋30之 間的膜片31來封閉凹部29。 而且，在接合於膜片31上面之壓膜片構件32 ’以及 螺裝於筒狀母螺紋部33(從彈簧蓋30上端向其內部下垂)之 調節螺絲34之間，壓裝一調節彈簧35，上下移動調節螺 絲34來調整調節彈簧35之彈力。 又，在凹部29下部之對應閥口 28的中央，設置圓形 開口部36，連通於一次側壓力室8，在該開口部36下方緊 接著設置既定長度之筒狀部37。 另外，自膜片31中心下垂形成一穿過筒狀部37及閥 口 28之閥棒38，在該閥棒.38下端設置開閉閥口 28之閥 體39。 閥體39係可接觸分離自如地設置於閥座40，藉由膜 片31之位移能控制閥體39之開度。 又，在閥棒38中途部位，向外突設一在筒狀部37內 壁滑動之活塞41並於該活塞41環設〇環42 ’來水密閉狀 地區劃出一次側壓力室25與凹部29(二次側壓力室26)。 接合於膜片31下面之壓膜片構件32a ’有一比開口部 36爲大的口徑，在膜片31位移至最下限之狀態，該壓膜 片構件32a位於開口部36之周緣並封閉開口部36，以限 制上述狀態之閥體39上升。 又，減壓閥4不限定於上述構成’只要具有一般減壓 (請先閱讀背面之注意事項再填寫本頁)576902 A7 _____B7___ V. Description of the invention (Technical field to which the invention belongs) The present invention relates to a pressure reducing device, a hot and cold water supply system using the pressure reducing device, and a method for selecting a pressure reducing device for the system. [Know-how] In the past, pressurized water-supply hot and cold water supply systems used cold and hot water mixing faucets to connect cold water pipes to hot water pipes. 'From faucets or shower or bath faucets located at the water supply end of each household (room). Supply a set temperature of water. [Problems to be Solved by the Invention] However, in the above-mentioned system, the pressure in the cold water pipe and the hot water pipe will change due to changes in the amount of cold water or hot water, and the water temperature of the faucet will also change accordingly. There are pumps for the cold water pipe and the hot water pipe respectively. The reason for the above problem lies in the direct-acting pressure reducing valve connected to the discharge side of the pump by a pipe. The discharge pressure of the pump is high pressure, so that it can be reduced to the cold water pipe in each household. Or the pressure used at the end of the hot water pipe, and a pressure reducing valve is installed in the cold water pipe and the hot water pipe. The pressure reducing valve will directly detect the secondary pressure to adjust the valve opening degree and control the secondary pressure. The above-mentioned pressure reducing valve changes greatly due to the difference in the amount of cold and hot water. Therefore, once the use of cold and hot water is changed, the secondary pressure of both the cold water pipe and the hot water pipe will be changed. The large change will change the flow of both cold water from the cold water pipe and hot water from the hot water pipe. Therefore, the pressure on the cold water side or the hot water side will be ignored in the water (please read the precautions on the back first) Fill out this page again) ^^ 1 ^^ 1 n νϋ 1 βϋ β ϋ —ϋ ϋ— ι_ϋ n ϋ— n I line 丨, ---- This paper size applies to China National Standard (CNS) A4 (210 X 297 (Mm) 576902 A7 ____ Β7 _ V. Description of the invention (of) Down or abruptly 'causes the provided water temperature to be lower or higher than the temperature setting 値. In order to ensure the flow of hot or cold water, the ratio of the effective diameter of the diaphragm to the valve diameter of the pressure reducing valve must be increased. In this case, the pressure reducing valve will become too large and impractical. The purpose of the present invention is to provide a decompression device, a hot and cold water supply system using the device, and a method for selecting a decompression device for the system, which can supply water at a stable pressure even when the amount of water is changed. [Means for solving the problem] The present invention is provided with a main valve in view of the above-mentioned problem. The main valve is connected to the primary pressure chamber and the secondary pressure chamber through a valve port, and the main valve of the valve port is opened and closed by a spring. Apply the spring pressure in the valve opening direction, and use the diaphragm area connected to the main valve to divide the diaphragm chamber and the primary pressure chamber located on the back side of the diaphragm inside the body. A guide pipe is provided. There is a pressure reducing valve between the secondary pressure chambers. In this guide line, a branch line on the primary side of the pressure reducing valve is connected to the diaphragm chamber, and a throttling mechanism is provided upstream from the branch point. The throttling mechanism will restrict the water flow from the primary pressure chamber of the body to the primary pressure chamber and diaphragm chamber of the pressure reducing valve. When water is used to open the pressure reducing valve, the pressure of the diaphragm chamber can be reduced. Make the body open. That is, when the secondary pressure becomes lower than its setting due to the use of water, because the same amount of water passes through the body, the secondary pressure does not decrease significantly, so the water consumption can be changed even if the water consumption is changed. Stable pressure to supply water. In addition, by installing a decompression device selected according to a certain condition on the hot and cold water supply system, it can solve the problem of _____5_____. The paper size applies the Chinese National Standard (CNS) A4 specification ( 210 X 297 mm) (Please read the notes on the back before filling out this page)-· I 丨 — 111— ^. I — II --- · »576902 B7 V. Description of the invention (;) The subject mentioned above. [Embodiment of the Invention] An embodiment of the present invention will be described below with reference to the drawings. A cross-sectional view of a guided decompression device is shown in FIG. 1. This pressure reducing device 1 is mainly composed of a main body 2 (installed in the cold water piping and hot water piping) 'and a pressure reducing valve 4 (connected to the main body 2 through a guide pipe). The valve box 5 provided in the main body 2 is provided with an inflow port 6 and an outflow port 7 on the left and right sides thereof. Inside the valve box 5, a primary pressure chamber 8 and a secondary pressure chamber 9 are respectively connected to the inlet. 6 and outflow port 7), the primary side pressure chamber 8 and the secondary side pressure chamber 9 are divided into the outside and the inside by the partition wall 10 inside the valve box 5, and a valve port 11 is formed in the partition wall 10 (orthogonal to the inlet 6) And upward), the primary pressure chamber 8 and the secondary pressure chamber 9 are communicated through the valve port 11. An opening 5a is provided on the upper part of the valve box 5, and communicates with the primary pressure chamber 8 and the valve port 11. The opening 5a is located between the upper part of the valve box 5 and the bonnet 12 covering the valve box 5. The diaphragm 13 is closed. The bonnet 12 ′ is provided with a concave space formed by dividing the inside of the valve box 5 by the diaphragm 13, and the space on the back side of the diaphragm 13 is used as the diaphragm chamber 14. (Corresponding to the bonnet 12) A port 15 connected to the guide pipe 3 is provided in the center. A main valve 17 corresponds to the valve seat 16 which is located below the diaphragm 13 and is arranged around the valve port 11. The lower portion of the diaphragm 13 protrudes in a ring-like shape. Because the main valve 17 and the diaphragm 13 are integrated into one, The main valve 17 is connected to the diaphragm 13. Under the diaphragm 13 on the inside of the main valve 17, and the corresponding diaphragm of the main valve 17 (please read the precautions on the back before filling this page); China National Standard (CNS) A4 Specification (21 × 2976 Public Love 1 " 576902 A7____B7 __ V. Description of the Invention (^) Sheets 13 are respectively joined to approximately circular plate-shaped pressing film members 18, 18a. A spring 19 is press-fitted between the upper part of the diaphragm chamber 14 and the diaphragm member 18, and the spring 19 is used to urge the main valve 17 in the valve closing direction. The guide pipe 3 is provided with the ports 15a and 15b ( The primary side pressure chamber 8 and the secondary side pressure chamber 9) are respectively installed in the main body 2 and connected to the outside. A branch line 3a is provided on the primary side (upstream) of the pressure reducing valve 4 on the guide line 3 and the branch line The path 3a is connected to the mouth 15 provided in the diaphragm chamber 14. On the upstream of the branch point M of the guide line 3 and on the branch line 3a, throttle mechanisms 20 and 21 made of needle valves are respectively provided. When the side pressure P4 drops from its set pressure Ps to the lower limit of the allowable range (capable of supplying hot and cold water at a stable pressure) 値 Pi /, the flow capacity of the pressure reducing valve 4 ( The flow rate Q!) Is set to be larger than the supply capacity (flow rate Q2) restricted by the throttle mechanism 20. That is, it is set to satisfy the condition of Qi> Q2. With this, the pressure reducing device 1 can be equipped with the pressure reducing device The hot and cold water supply system of No. 1 is controlled so that the secondary pressure P4 will be within the allowable range when the maximum used amount Fm is set below. The pressure reducing valve 4 is opened and connected to the guide on the left and right sides of its valve box 22. The inlet 23 and outlet 24 of the pipeline 3 are provided inside the valve box 22 with a primary pressure chamber 25 and a secondary pressure chamber 26 (connecting to the inlet 23 and the outlet 24), and the valve is separated by a partition wall 27 Inside and outside the box 22 are a primary pressure chamber 25 and a secondary pressure chamber 26. A downward valve port 28 is formed in a direction perpendicular to the partition wall 27 and the inlet 23, and the two pressure chambers 25 and 26 are communicated through the valve port 28. -------- Order --------- Line (Please read the precautions on the back before filling this page) Wood paper size applies to China National Standard (CNS) A4 (210 X 297 (Mm) 576902 A7 ____B7 __ 5. Description of the invention (i :) A dish-like recess with an upward opening is provided on the upper part of the valve box 22 29, and a part of the bottom of the recessed portion 29 is opened to communicate with the secondary pressure chamber 26, and the recessed portion 29 is closed by a diaphragm 31 located between the recessed portion 29 and a spring cover 30 covering the recessed portion 29. Between the pressure diaphragm member 32 ′ on the diaphragm 31 and the adjustment screw 34 screwed on the cylindrical female screw portion 33 (hanging down from the upper end of the spring cover 30 to the inside thereof), an adjustment spring 35 is press-fitted and moved up and down to adjust Screw 34 adjusts the spring force of the adjustment spring 35. A circular opening portion 36 is provided in the center of the corresponding valve port 28 in the lower portion of the recessed portion 29, and communicates with the primary pressure chamber 8. A cylindrical portion 37 having a predetermined length is provided immediately below the opening portion 36. In addition, a valve rod 38 passing through the cylindrical portion 37 and the valve port 28 is formed from the center of the diaphragm 31, and a valve body 39 for opening and closing the valve port 28 is provided at the lower end of the valve rod .38. The valve body 39 is disposed on the valve seat 40 so as to be freely contactable and separable. The opening of the valve body 39 can be controlled by the displacement of the diaphragm 31. In the middle of the valve rod 38, a piston 41 that slides on the inner wall of the cylindrical portion 37 is protruded outward, and a ring 42 'is provided around the piston 41 to draw a primary-side pressure chamber 25 and a concave portion. 29 (secondary pressure chamber 26). The diaphragm member 32a 'joined to the lower surface of the diaphragm 31 has a larger diameter than the opening portion 36. When the diaphragm 31 is displaced to the lower limit, the diaphragm member 32a is located on the periphery of the opening portion 36 and closes the opening portion. 36. The valve body 39 is restricted from rising in the above state. In addition, the pressure reducing valve 4 is not limited to the above structure, as long as it has a general pressure reduction (please read the precautions on the back before filling in this page)
衣纸張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 _ _SI------— 五、發明說明（έ ) 功能者均可，總之，能作爲本體2之嚮導閥即可。 其次，根據圖1說明減壓裝置1之作用。 如圖1所示，假設上游側(連接於本體2之一次側壓力 室8)之壓力爲一次側壓力Pi，下游側(連接於本體2之二 次側壓力室9)之壓力爲二次側壓力P4，連接於嚮導管路3 上減壓閥4之一次側壓力室25的上游側壓力爲嚮導一次側 壓力P2，本體2膜片室14內之膜片室壓力爲P3，本體2 一次側之設定壓力爲Pf (以下稱爲一次側壓力設定値Pf) ，並且減壓閥4二次側壓力P4之設定(壓力）値爲Ps (以下 稱爲二次側壓力設定値Ps)。 當本體2之二次側關閉時，本體2及減壓閥4均閉閥 ’圖1中各壓力保持在Pl=卩2= ?3= Pf ’ = Ps。 當二次側從上述關閉狀態開放時，因二次側壓力P4從 其設定壓力ps下降，故減壓閥4會打開，嚮導一次側壓力 p2就從一次側壓力設定値Pf下降，使得減壓閥4上產生流 動。 在這種狀態，因節流機構20限制從上游側(本體2之 一次側壓力室8)流至減壓閥4 一次側壓力室25及膜片室 14的通水量，若二次側壓力P4從其設定壓力Ps下降，開 閥狀態之減壓閥4之(嚮導)一次側壓力？2就會劇減，本體 2之膜片室壓力P3隨之而下降，主閥17會和膜片13 —起 向開閥方向位移而開閥，使一次側壓力室8與二次側壓力 室9連通，水經由本體2從一次側流至二次側。 又，因從膜片室14流至減壓閥4之一次側壓力室25 (請先閱讀背面之注意事項再填寫本頁) --------訂-------—線 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 ____ B7 _ 五、發明說明（7 ) 的通水量被節流機構21所限制，故上述膜片室壓力p3之 壓力下降進行得比在一次側壓力室25之情形爲平緩。 藉此，緩慢打開主閥Π，以免打開主閥17時造成在 本體2上游側產生水鎚等不良現象。 在此，當二次側壓力P4下降至容許範圍下限時， 以要滿足上述Ql>Q2之條件之方式來設定的理由，係因爲 假想：在減壓裝置1，二次側壓力P4下降至容許範圍下限 PL時，會供應最大使用量Fm之情形，此時，爲要從減壓 裝置1供應最大使用量Fm，而使本體2開放，減壓閥4之 流量能力(流量Qi)(二次側壓力P4下降至容許範圍下限PL 時)若不超過供應能力（流量Q2X從節流機構20流通），就 不能期待嚮導一次側壓力P2之下降，由於前述設定條件， 把減壓裝置1藉由減壓閥4在最大使用量Fm以下能穩定 地控制在二次側壓力設定値Ps與二次側壓力p4之容許範圍 下限Ρι之間。 圖6，係二次側壓力設定値Ps爲〇.30MPa之減壓閥(不 連接節流機構2〇)之流量特性圖(X軸爲用水量(流量），Y軸 爲二次側壓力）；假設二次側壓力P4之容許範圍下限Pl爲 0.27 MPa時，當需要供應最大使用量Fm時，因從圖6得 知二次側壓力P4爲〇·27 MPa時之減壓閥4之流量Qi爲8 L/min，故只要將以節流機構20所限制之流量Q2 §又定爲比 8 L/min少量即可。 如上所述，藉由二次側之水之使用，若二次側壓力 P4低於其設定壓力ps，本體2之閥口 11就打開，與用水 _______10 ------— 衣紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂·-------I 丨座 576902 A7 ____B7__ 五、發明說明（# ) 量相同之水量會通過閥口 11，用水量與閥口通過得水量大 致一致，因此二次側壓力P4不會顯著下降，使得其壓力變 動之幅度比習知減壓閥小很多。 該事實亦能從圖7之減壓裝置1的流量特性圖(X軸爲 用水量，Y軸是二次側壓力），以及圖13之習知直動式減 壓閥(以下稱爲習知品）的流量特性圖(X軸爲用水量，Y軸 爲二次側壓力）來了解。 在圖7、13所示之曲線圖之條件，係最大用水量爲 300 L/min、一次側壓力設定値Pf爲0.50 MPa、減壓裝置1 之減壓閥4與習知品之二次側壓力設定値Ps都爲0.30 MPa 〇 用水量0〜300 L/min間之二次側壓力P4變動幅度係 指 0 L/min 之二次側壓力 Ρ4(=0·30 MPa)，與 300 L/min 之 二次側壓力P4(=約0.27 MPa)的差，在減壓裝置1(圖7)的 情形爲約〇.〇3 MPa。 習知品（圖13)的情形則爲約0.20 MPa，亦即0 L/min 之二次側壓力Ρ4(=0·30 MPa)，與300 L/min之二次側壓力 P4(=約0.10 MPa)的差，因此，減壓裝置1比習知品二次側 壓力P4之變動幅度爲狹小。 而且，若把二次側從上述通水狀態變成不開放狀態， 通水時比二次側壓力設定値Ps爲低之二次側壓力P4由於來 自本體2之供水而上升，達到其設定値Ps並且關閉減壓閥 4之閥體39，藉著關閉閥，嚮導一次側壓力P2就會上升至 一次側壓力設定値Pf。 — _11 ____ 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) #--------^---------f费------——------------- 576902 A7 _ — _ B7__ 五、發明說明（7 ) 此時，因藉由分岐路3a中之節流機構21，來限制流 至膜片室14之通水量，故膜片室壓力P3就緩慢上升，主 閥Π伴隨該壓力上升而與膜片13 一起向閉閥方向緩慢位 移’當膜片室壓力P3達到一次側壓力設定値Pf時，主閥 17就關閉而停止通水。 在圖4表示使用減壓裝置1之冷熱水供應系統Z的配 管略圖。 該冷熱水供應系統Z，係將裝有減壓裝置1之冷水配 管路X與熱水配管路Y，在減壓裝置1之下游，分岐爲複 數條冷水管XI與熱水管Y1，將來自冷水配管路X之冷水 管XI與來自熱水配管路Y之熱水管Y1，以冷熱水混合龍 頭C予以連結並連接於水龍頭W。 冷水配管路X，係在儲水槽X2之供水側並聯定速與 變速之泵XP1、XP2，或連接兩定速或兩變速之泵XP1、 XP2，在該泵XP1、XP2之吐出側連接減壓裝置1本體2 之流入口 6，把流出口 7連接於冷水配管路X之下游側。 熱水配管路Y亦以與上述大致相同之方式來配管，從 儲水槽Y2之供水側(具備電熱水器、鍋爐等加熱裝置H)起 依序，裝入並聯之定速與變速之泵YP1、YP2，或兩定速 或兩變速之泵YP1、YP2、及減壓裝置1。 又，在冷水配管路X與熱水配管路Y，設置偵知壓力 或流量變化之裝置(未圖示)於泵XP1、XP2、YP1、YP2之 吐出側且在本體2上游，藉由該裝置來決定須運轉泵XP1 、XP2、YP1、YP2的台數，或者是改變泵XP1、XP2、 ____ 12 _________ ΐ、紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） n n I n n I i I n ϋ n I · I ϋ n n n n n=-OJI I n ϋ 1 I ϋ ϋ I (請先閱讀背面之注意事項再填寫本頁) 576902 A7 ______Β7 __ 五、發明說明（丨。） YP1、YP2之運轉次數而改變流量或壓力。 其次，根據圖1、4說明冷熱水供應系統z減壓裝置} 之作用。 該冷熱水供應系統Z上所使用之減壓裝置1，係根據 後述之選擇方法所選出者，使得所設定冷熱水之最大使用 量在Fm以下且二次側壓力P4在容許範圍(能以穩定之壓力 供水）內。 在此，假設冷熱水之最大使用量Fm爲300 L/min，一 次側壓力設定値爲0.50 MPa，二次側壓力設定値爲0.30 MPa，並使用具有圖7所示流量能力的減壓裝置1。 若使用具有上述能力之減壓裝置1，則當冷熱水之最 大使用量Fm低於300 L/min時，就能將相對於冷熱水使用 量之二次側壓力P4之變動幅度充分維持在容許範圍（約 0.03 MPa)內(參閱圖7)。 因此，若打開該冷熱水供應系統Z之水龍頭W，藉由 與上述相同的作用，按照設定溫度從冷水配管X與熱水配 管Y分別供應適當流量之冷水與熱水並在冷熱水混合龍頭 C混合。 此時，即使其他水龍頭C之使用造成冷熱水使用量(在 最大使用量Fm 300 L/min以下)改變，因與其使用量大致 相同之流量會通過本體2，來維持二次側壓力P4之變動幅 度(約〇·〇3 MPa)，故對應設定溫度之來自冷水配管X之冷 水與來自熱水配管γ之熱水之兩者流量均不會改變，能從 水龍頭W供應一設定溫度之冷熱水。 ____13 ____ 本纸張尺度適闬中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) # 576902 A7 五、發明說明（"） 接著，把各水龍頭W從上述通水狀態變成止水狀態， 主閥17就與上述相同會關閉而停止通水，水栗χρι、χρ2 、YP1、YP2則由於未圖示之壓力或流量偵知裝置而停止 運轉。 其次，根據圖5說明冷熱水供應系統Z之變形例(冷熱 水供應系統Z1)。 該冷熱水供應系統Z1，係將上述冷熱水供應系統z之 冷水配管X及熱水配管γ之各下游端部連接於儲水槽χ2 、Υ2之返回側，而構成冷水循環路Xa及熱水循環路Ya， 對與冷熱水供應系統Z相同或相當部分使用同一符號且省 略說明。 又，冷水循运路Xa及熱水循環路Ya之兩者均係連接 流量調節機構X3、Y3於儲水槽X2、Y2之返回側附近。 圖5(a)所示之流量調節機構X3、Υ3，係針閥N，構成 爲經常使設定之流量流回儲水槽X2、Y2。 圖5(b)所示之流量調節機構X3、Υ3，係以針閥N(與 上述相同設置），及放洩閥R(設置於在該針閥N之下游從 循環路Xa、Ya分岐而連接於儲水槽X2、Y2之返回側的 旁管路中）所構成，作用爲：不能以針閥N消化返回儲水槽 X2、Y2之流量，當循環路Xa、Ya末端側之壓力升至設定 値時，打開放洩閥R，經常使所設定之一定流量返回儲水 槽 X2、Y2。 又，各在圖（5a)及（5b)所示之冷熱水供應系統Ζι，流 量調節機構X3、Y3並不限定於上述者，只要使所設定之 ______14_____ 衣紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------1T---------^IAW------------------------ 576902 A7 _____ B7_ 五、發明說明（θ) 流量經常從冷水循環路Xa及熱水循環路Ya返回儲水槽 X2、Y2即可。 又，亦可不設置壓力或流量之偵知裝置(裝備於冷熱水 供應系統Z)。 其次，根據圖1、5說明冷熱水供應系統Ζι之減壓裝 置1之作用。 在冷熱水供應系統Z1，因以流量調節機構χ3、Y3設 定返回儲水槽X2、Y2之流量(以下，稱之循環流量），在 冷水循環路Xa及熱水循環路Ya中，時常(不論水龍頭w 之開閉)循環所設定之熱水或冷水。 使用在該冷熱水供應系統Z1之各減壓裝置1，係以後 述之選擇方法所選擇者，即使超過熱水或冷水之最大使用 量Fm仍使二次側壓力P4在容許範圍(能以穩定之壓力供應 冷熱水之範圍）內，在從根據此容許範圍之界限使用量Fs 與所設定之最大使用量Fm的差所導出之流量範圍內，來 設定冷水循環路Xa及熱水循垣路Ya之各別循環流量。 在此，假設最大使用量Fm爲300 L/min，一次側壓力 設定値爲〇.5〇MPa，二次側壓力設定値爲0.30MPa，使用 具有圖7所示之流量能力之減壓裝置1。 若使用具有上述能力之減壓裝置1，就得知：要是超 過最大使用量Fm 300 L/min之約420 L/min (界限使用量 Fs)，即使將其界限使用量Fs與最大使用量Fm的差約120 L/min以下爲循環流量，能將對使用量之二次側壓力P4之 變動幅度仍維持在容許範圍(約〇.〇3 MPa)內（參閱圖7)。 _15 —___ 拿、纸張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） - -- -------费--------訂·！丨線和 (請先閱讀背面之注意事項再填寫本頁) 576902 A7 ___B7____ 五、發明說明（Π ) 在此，若設定冷水循環路Xa及熱水循環路Ya之各別 循環流量爲50 L/min，因該時之二次側壓力P4，係如圖7 所示約0.29 MPa，故冷熱水供應系統Z1之冷熱水使用量0 〜300 L/min間之二次側壓力P4之變動幅度，在減壓裝置1 ，就成爲約0.02 MPa(0 L/min時之二次側壓力P4(=約 0.29MPa)，與 300 L/min 時之二次側壓力 P4(=約 0.27MPa) 的差），比上述冷熱水供應系統Z，更能使二次側壓力P4之 變動幅度狹小。 其次，說明減壓裝置1之選擇方法。 該選擇方法，係決定··使用減壓裝置1之冷熱水供應 系統Z、Z1之最大使用量Fm，〜次側與二次側之設定壓 力Pf、Ps及對冷熱水使用量之二次側壓力P4之變動幅度( 容許之下限値PL)後，根據這些決定事項，依照以下選擇作 業順序進行。 在此，爲說明之方便上，選擇：冷熱水之最大使用量 Fm爲300 L/min，設定一次側壓力1>£爲0.5〇MPa ’二次側 壓力設定値Ps爲0.30MPa，二次側壓力P4由其設定壓力Ps 所容許之範圍下限爲0.27 MPa。 1.減壓閥之選擇 (1) 選擇··所決定之設定ps在於調廳範圍(表示能設 定之二次側壓力範圍的減壓閥規範之一)之減壓閥4 ° (2) 接著，準備：表示減壓閥4之流纛與二次側壓力 之關係的流量特性圖1(在該減壓閥4上游側連接節流機構 20，將流量能力(流量（^)(二次側壓力P4由其設定壓力Ps ___16 ---- 拿、纸張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） --------訂---------線 (請先閱讀背面之注意事項再填寫本頁) 576902 A7 _ ____B7____ 五、發明說明（#) 下降至所容許之範圍下限PL時的減壓閥4)，設定於超過供 應能力（流量Q2)(以節流機構2〇限制)的狀態）。 流量特性圖I，係先在流量爲0時設定二次側壓力’ 其後邊增加著流量，邊來測定該時之二次側壓力’將其結 果畫成曲線圖者，分別表示流量與二次側壓力於圖1之x 軸及γ軸。 然後，圖I中之流量特性曲線A(在節流機構20之上 述條件(Qi> Q2)下，測量減壓閥4之流量特性），由於減壓 閥4本身之特性，關閉升壓雖各別不同’然而所設定之最 大使用量Fm以下之二次側壓力P4 ’就成爲稍微向右降下（ 從其設定壓力PS下降至所容許之範圍下限PL)之斜度(通過 所容許之壓力値pL的略水平線），以實測確認，此斜度在 任何減壓閥4均成爲一定。 因此，上述條件下之減壓閥4之流量特性曲線A，即 使不予測量，不拘二次側壓力設定値Ps多少，係具有大致 接近水平(平行於X軸）且稍微向右降下之一定之斜度(參閱 圖8)，要選擇後述之總閥時，不妨可將通過容許範圍下限 値(所容許之壓力値)Pl之略平行於X軸之直線，作爲流量 特性曲線A(圖9中之一點鏈線）。 在圖8所示之上述斜度之流量特性曲線A，雖表示複 數個對應流量0之二次側壓力P4之設定値Ps〔 〇·40、0·3〇 、0·2〇、0·10 (MPa)〕，並且表示根據各設定値Ps之相同 斜度之流量特性曲線A，然而在此因冷熱水供應系統Z、 Z1所決定之二次側壓力設定値匕爲0.3〇MPa，故使用轉記 S-—-— 17__— —_____-— 表紙張尺度適用中國國家標準（CNS)A4 ϋΓΓ2ι〇 x 297公H'' --------tT---------線 (請先閱讀背面之注意事項再填寫本頁) 576902 A7 ____ B7___ 五、發明說明（β ) 〇.30MPa爲二次側壓力設定値Ps之流量特性曲線A的流 量特性圖I。 2.總閥之選擇 (1) 適當尋找複數種總閥候補（基本構成係與上述者 相同，但主要閥口 11之口徑則不相同）。 (2) 然後，準備流量特性圖Π (表示各候補之一次側 壓力Pi(及與二次側壓力P4之壓差)與流量之關係）（圖10) 〇 流量特性圖Π，係以二次側壓力爲〇(即閥口之開放狀 態），邊漸漸增加著一次側壓力，邊來測量該時之流量，將 其結果畫成圖表者，分別表示一次側壓力（因二次側壓力爲 0，故相當於一次側壓力與二次側壓力之壓差）與流量於其 圖Π之X軸及Y軸。 在圖10所示之流量特性圖π，分別表示對應總閥候補 之流量特性曲線a〜c。 (3) 轉換表示流量特性圖Π之流量特性曲線a〜c於流 量特性圖1(表示流量特性曲線A)。 在流量特性圖Π，例如所謂一次側壓力爲〇.20MPa， 係表示一次側壓力Pi爲0.20MPa，且二次側壓力P4爲0時 之流量，換言之，這流量即是一次側壓力Pl與二次側壓力 P4之壓差爲〇.20MPa時的流量。 因此’在流量特性曲線A，壓差0.20MPa，即一次側 壓力Pi 0.5 OMPa ’二次側壓力p4 〇時之流量爲440 L/min 〇 _____—----——18_ 拿、纸張尺度適用中國國豕標準（CNS)A4規格（21〇 X 297公釐） -------费--------訂---------$· (請先閱讀背面之注意事項再填寫本頁) 576902 A7 ------_B7____ 五、發明說明（ft) 在圖11表示以此要領換算二次側壓力p4(在流量特性 曲線A將設定一次側壓力Pf爲0.50MPa時)與流量的表。 在圖11之換算表， ^，係表示圖Π所示之壓力（一次側壓力？1與二次側 壓力之壓差）， /5 ’係表示設定一次側壓力pf爲〇.5〇MPa時之二次側 壓力 P4，即，/3 = Pf-α， Τ ’係表不在圖Π對應α之流量(能力）。 將上述換算表所示之Θ與r標在圖I，來轉換表示流 量能力曲線a。 问樣’就圖Π之流量特性曲線b、c，亦製作換算表( 未圖示)而轉換表示於圖I。 圖9，係表示：在表示流量特性曲線A之圖I，表示 如上述所轉換之流量特性曲線a〜c者。 (4)在流量特性圖I，流量特性曲線A，與轉換表示 之各流量特性曲線a〜c的交點Ra〜Rc之座標，係 Ra(0_27,420)、Rb(0.26,605)、Rc(0.26,680)，該交點座標 Ra〜Rc，係在將所選擇之減壓閥4與各總閥候補分別配合 而使用爲上述決定事項之基礎時，即使使用流量變化，仍 能以穩定之壓力（二次壓)供水的界限點。 並且，在圖9所示之圖I，流量特性曲線A與流量特 性曲線a〜c分別連接之曲線，就相當於配合減壓閥4與本 體2之減壓裝置1的流量特性曲線。 在各主閥候補之界限點Ra〜Rc中，因超過上述最大 ____19_____ 拿、紙張尺度適用中國國家標準（CNS)A4規格（2忉x四7公釐） --------訂---------線 (請先閱讀背面之注意事項再填寫本頁) 576902 A7 ___ B7__ —__ 五、發明說明（丨Ί) 使用量Fm=300 L/min，且與二次側壓力設定値 Ps=0.30MPa之差最少，係通過交點座標Ra(0·27、420)之 流量特性曲線a，故選擇爲對應此曲線之總閥2。 藉由使用減壓裝置1(配合如上述所選擇之減壓閥4與 總閥2)於冷熱水供應系統Z、Z1，即使用水量變化亦能以 穩定之壓力供應冷熱水。 在圖12，表示··根據實測値（分別配合如上述所選擇 之減壓閥4與各總閥候補，設定：冷熱水之最大使用量爲 300 L/min，設定一次側壓力Pf爲〇.5〇MPa，二次側壓力設 定値？3爲〇.3〇MPa，而測量流量與二次側壓力？4)的流量 特性曲線。 圖12所示之各減壓裝置1之流量特性曲線Jl、J2、J3 ，係描寫與圖9所示之各減壓裝置1之流量特性曲線(A〜 a)、（A〜b)、（A〜c)各別大致相同的曲線，根據上述方法， 能確認不需要一一測量藉此配合減壓閥4與總閥候補各減 壓裝置1。 【發明之效果】 申請專利範圍第1項之發明，因在上述構成之總閥2 之〜次側壓力室8與二次側壓力室9間，設置含有減壓閥 4之嚮導管路3，在該嚮導管路3，將設於減壓閥4 一次側 之分岐管路3a連接於膜片室14，在分岐點Μ起上游處設 置節流機構20，故藉著在本體2二次側使用水，使得當二 次側壓力Ρ4低於設定壓力Ps時，減壓閥4就會開閥，此時 ’從本體2之一次側壓力室8流至減壓閥4 一次側壓力室 -------20____ 衣紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 丨丨I»---------f--------訂——I!線_ (請先閱讀背面之注意事項再填寫本頁) A7 ---- B7 ___— — 友、發明說明（丨R ) ，當該壓力p3改變時可讓會開閉的本體2主閥17緩慢動 作而防止水鎚（當主閥17急遽開閉閥時發生於本體2之上 游側之現象)等不良現象。 在申請專利範圍第2項之發明，係一種冷熱水供應系 統z，其分別在上述冷水配管路X與熱水配管路Y，以冷 熱水混合龍頭來連結減壓裝置1下游分岐之冷水管XI及 熱水管Y1，並且連接於水龍頭W，各減壓裝置1係當二次 側壓力P4在所設定之熱水或冷水之最大使用量爲Fm以下 時仍在容許範圍內，故即使使用各水龍頭W而致冷熱水之 使用量改變，二次側壓力P4僅會在其容許範圍內變動，使 得按照冷熱水設定溫度之來自冷水配管X之冷水及來自熱 水配管Y之熱水之流量不會改變，因此能從水龍頭W穩定 地供應一設定溫度之冷熱水。 存申請專利範圍第3項之發明，係一種冷熱水供應系 統Z1，其在上述冷水循環路Xa與熱水循環路Ya，以冷熱 水混合龍頭C來連結分別從減壓裝置1與流量調節機構 X3、Y3間分岐出之冷水管XI及熱水管Y1，並連接於水 龍頭W，各減壓裝置1係即使超過所設定之熱水或冷水之 最大使用量Fm，二次側壓力P4也會在容許範圍內，另外 ，從基於前述容許範圍之界限使用量Fs與所設定之最大使 用量Fm的差値來導出一流量範圍，並在該流量範圍內分 別設定冷水循環路Xa與熱水循環路Ya之循環流量，因此 ，若是在超過冷熱水之最大使用量Fm並在界限使用量Fs 以下，即使將界限使用量Fs與最大使用量Fm之差以下的 _ ___22_——— 本紙張尺度適用中國國家標準（CNS)A4規格（210 x 297公釐） ---------------------訂---------^ —^wi (請先閱讀背面之注意事項再填寫本頁) 576902 . A7 _____B7____ 五、發明說明（20) 量當作循環流量，也能把相對於使用量之二次側壓力P4的 變動幅度維持於容許範圍內。 藉此，因二次側壓力之起始値僅減少了與所設定之 循環流量相對應的壓力’故能減少二次側壓力的變動幅 度，讓按照冷熱水之設定溫度之來自冷水配管X之冷水及 來自熱水配管Y之熱水的流量更加穩定，而能較穩定地供 應設定溫度之冷熱水。 又，在冷熱水供應系統Z之冷水配管X與熱水配管Y ，一旦各水龍頭W均停止使用時，即使嚮導一次側壓力P2 由於閉閥之減壓閥4而上升，膜片室14之壓力藉由節流機 構21也不會立即上升而使主閥17緩慢閉閥，因此，雖在 閥關閉之前本體2二次側由於有水從本體2 —次側流至二 次側，而有可能會上升至一次側壓力設定値Pf，但因在冷 熱水供應系統Z1之冷水循環路Xa與熱水循環路Ya，讓 所設定之（循環）流量不斷地循環，故即使有前述之情形’ 本體2之二次側也不會上升至一次側壓力設定値Pf。 如此一來，因不斷地有一定量之水流過本體2 ’故能 防止當水龍頭W之水用量減少時所產生之顫動(chattering) ，因冷水及熱水分別循環於冷水循環路Xa與熱水循環路 Ya，故打開水龍頭W即可使用一設定溫度之冷熱水，對於 整天均使用冷熱水之醫院、旅館等來說非常方便。 3 存申諝軎利範圍第4項之發明，藉由根據冷熱水供應 系統Z、Z1之決定事項(冷熱水之最大使用量Fm、一次側 壓力設定値Pf、二次側壓力設定値ps、相對冷熱水使用量 _____22___- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ---I----訂---------i^wl (請先閱讀背面之注意事項再填寫本頁) 576902 A7 _______B7_;___ 五、發明說明（W ) 之二次側壓力P4之變動幅度），將表示於流量特性圖Π之 各候補總閥之流量特性曲線a〜c轉換表示於，表示減壓閥 4(上游連接有節流機構)流量特性曲線A之流量特性圖I， 其中前述減壓閥4之流量特性曲線A與候補總閥之流量特 性曲線a〜c的交點座標爲Ra〜Rc，從中選擇流量特性曲 線爲a之總閥2，其交點座標超過前述最大使用量Fm，且 與二次側壓力設定値Ps的差最少，在此藉由流量特性圖I ，即可簡單地選出符合各種設定條件的總閥2，並且能掌 握減壓裝置1之能力。 在用於冷熱水供應系統Z之各減壓裝置1之選擇中， 尤其是當選擇一即使超過熱水或冷水之最大使用量Fm，二 次側壓力P4也會在容許範圍內之總閥2時，從其圖I得知 :根據容許範圍之界限使用量Fs與所設定之最大使用量 Fm的差，係分別爲冷水循環路Xa與熱水循環路Ya之循 環流量的範圍，在其範圍內可決定循環流量。 又，在一二次側壓力設定値？3在於調壓範圍內之減壓 閥4的上游連接有節流機構20，於流量特性圖I所示之這 種減壓閥4之流量特性曲線A，係在當二次側壓力P4達到 容許範圍下限PlJ寺，保持在Q K減壓閥4之流量)>Q2 (被 節流機構20所限制之供應流量)之狀態下所測量之結果； 在Q Θ Q2之條件下，流量特性曲線A係梯度稍微向右下 降之近似直線，其大致平行於X軸，任何的減壓閥4因其 梯度爲一定，故在流量特性圖I中，以與流量0相對應之 二次側壓力P4之設定値Ps爲起點，僅表示出具有上述梯度 __24____ 拿、紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 . A7 _ B7 _The size of the clothing paper is applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 576902 A7 _ _SI ---------- V. Description of the invention (hand) Any function, in short, can be used as the body 2 The pilot valve is sufficient. Next, the operation of the pressure reducing device 1 will be described with reference to FIG. 1. As shown in Fig. 1, it is assumed that the pressure on the upstream side (connected to the primary pressure chamber 8 of the body 2) is the primary pressure Pi, and the pressure on the downstream side (connected to the secondary pressure chamber 9 of the body 2) is the secondary side Pressure P4, the pressure on the upstream side of the primary pressure chamber 25 connected to the pressure reducing valve 4 on the pilot line 3 is the pilot primary pressure P2, and the diaphragm chamber pressure in the diaphragm chamber 14 of the body 2 is P3, and the primary side of the body 2 The set pressure is Pf (hereinafter referred to as the primary pressure setting 値 Pf), and the setting (pressure) 压力 of the secondary pressure P4 of the pressure reducing valve 4 is Ps (hereinafter referred to as the secondary pressure setting 値 Ps). When the secondary side of the main body 2 is closed, both the main body 2 and the pressure reducing valve 4 are closed. The pressure in FIG. 1 is maintained at Pl = 卩 2 =? 3 = Pf ′ = Ps. When the secondary side is opened from the above-mentioned closed state, because the secondary side pressure P4 decreases from its set pressure ps, the pressure reducing valve 4 is opened, and the primary pressure p2 decreases from the primary side pressure setting 値 Pf, so that the pressure is reduced. Flow is generated on the valve 4. In this state, because the throttle mechanism 20 restricts the flow of water from the upstream side (the primary pressure chamber 8 of the main body 2) to the pressure reducing valve 4, the primary pressure chamber 25 and the diaphragm chamber 14, if the secondary pressure P4 From its set pressure Ps, is the primary pressure of the (guide) pressure reducing valve 4 in the open state? 2 will decrease sharply, the diaphragm chamber pressure P3 of the main body 2 will decrease accordingly, and the main valve 17 and the diaphragm 13 will be displaced toward the valve opening direction to open the valve, so that the primary pressure chamber 8 and the secondary pressure chamber 9 communicates, and water flows from the primary side to the secondary side via the body 2. In addition, because it flows from the diaphragm chamber 14 to the primary pressure chamber 25 of the pressure reducing valve 4 (please read the precautions on the back before filling in this page) -------- Order ----------- The size of the paper is applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 576902 A7 ____ B7 _ 5. The water flow of the invention description (7) is restricted by the throttle mechanism 21, so the above-mentioned diaphragm chamber pressure p3 The pressure drop progresses more gently than in the case of the primary pressure chamber 25. Thereby, the main valve Π is opened slowly, so as to avoid the occurrence of a water hammer and the like on the upstream side of the main body 2 when the main valve 17 is opened. Here, when the secondary pressure P4 drops to the lower limit of the allowable range, the reason for setting is to satisfy the above-mentioned conditions of Ql> Q2, because it is assumed that in the decompression device 1, the secondary pressure P4 drops to the allowable At the lower limit of the range PL, the maximum use amount Fm will be supplied. At this time, in order to supply the maximum use amount Fm from the pressure reducing device 1 and the body 2 is opened, the flow capacity (flow rate Qi) of the pressure reducing valve 4 (secondary When the side pressure P4 drops to the lower limit of the allowable range PL) If the supply capacity is not exceeded (the flow rate Q2X flows from the throttle mechanism 20), the decrease in the pilot side pressure P2 cannot be expected. Due to the aforementioned setting conditions, the pressure reducing device 1 is passed through The pressure reducing valve 4 can be stably controlled between the secondary pressure setting 値 Ps and the lower limit P1 of the allowable range of the secondary pressure p4 below the maximum usage amount Fm. Figure 6 shows the flow characteristics of a pressure reducing valve with a secondary pressure setting 値 Ps of 0.30 MPa (without a throttle mechanism 20) (X-axis is the water consumption (flow), Y-axis is the secondary pressure) ; Assuming that the lower limit P1 of the allowable range of the secondary pressure P4 is 0.27 MPa, when the maximum use amount Fm needs to be supplied, the flow rate of the pressure reducing valve 4 when the secondary pressure P4 is 0.27 MPa is known from FIG. 6. Qi is 8 L / min, so it is sufficient to set the flow rate Q2 § restricted by the throttling mechanism 20 to be smaller than 8 L / min. As mentioned above, with the use of water on the secondary side, if the secondary side pressure P4 is lower than its set pressure ps, the valve port 11 of the main body 2 is opened, and the water is _______10. Applicable to China National Standard (CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before filling out this page) -------- Order · ------- I 丨 Block 576902 A7 ____B7__ 5. Description of the Invention (#) The same amount of water will pass through the valve port 11, and the water consumption is approximately the same as the water amount passed through the valve port. Therefore, the secondary pressure P4 will not decrease significantly, making the pressure fluctuation amplitude larger than the conventional one. The pressure reducing valve is much smaller. This fact can also be obtained from the flow characteristic diagram of the pressure reducing device 1 in FIG. 7 (the X-axis is the water consumption and the Y-axis is the secondary pressure), and the conventional direct-acting pressure reducing valve (hereinafter referred to as the conventional product) of FIG. 13 To understand the flow characteristics chart (X-axis is water consumption, Y-axis is secondary pressure). The conditions in the graphs shown in Figures 7 and 13 are the maximum water consumption of 300 L / min, the primary pressure setting 値 Pf of 0.50 MPa, the pressure reducing valve 4 of the pressure reducing device 1, and the secondary pressure setting of the conventional product.値 Ps are all 0.30 MPa. 0 The secondary side pressure P4 between 0 and 300 L / min of water consumption refers to the secondary side pressure P4 (= 0 · 30 MPa) of 0 L / min, and 300 L / min. The difference in the secondary pressure P4 (= about 0.27 MPa) was about 0.03 MPa in the case of the decompression device 1 (FIG. 7). In the case of conventional products (Figure 13), it is about 0.20 MPa, that is, the secondary side pressure P4 (= 0.30 MPa) at 0 L / min, and the secondary side pressure P4 (= about 0.10 MPa) at 300 L / min. Therefore, the pressure reducing device 1 has a narrower fluctuation range of the secondary side pressure P4 than the conventional product. Furthermore, if the secondary side is changed from the above-mentioned water-passing state to the non-open state, the secondary-side pressure P4, which is lower than the secondary-side pressure setting 値 Ps when the water is passed, rises due to the water supply from the body 2, and reaches its setting 値 Ps Then, the valve body 39 of the pressure reducing valve 4 is closed, and by closing the valve, the primary pressure P2 on the pilot side rises to the primary pressure setting 値 Pf. — _11 ____ This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) # -------- ^ ----- ---- f fee ----------------------- 576902 A7 _ — _ B7__ V. Description of the invention (7) At this time, because of the branch road 3a The throttle mechanism 21 restricts the amount of water flowing to the diaphragm chamber 14. Therefore, the pressure P3 of the diaphragm chamber rises slowly, and the main valve Π is slowly displaced with the diaphragm 13 in the valve closing direction along with the pressure rise. When the chamber pressure P3 reaches the primary pressure setting 値 Pf, the main valve 17 is closed and the water flow is stopped. Fig. 4 is a schematic view showing the piping of the hot and cold water supply system Z using the pressure reducing device 1. The cold and hot water supply system Z is a cold water distribution pipe X and a hot water distribution pipe Y equipped with a pressure reducing device 1, and downstream of the pressure reducing device 1, it is divided into a plurality of cold water pipes XI and hot water pipes Y1. The cold water pipe XI with the pipe X and the hot water pipe Y1 from the hot water pipe Y are connected with the hot and cold water mixing faucet C and connected to the faucet W. The cold water distribution line X is connected to the fixed-speed and variable-speed pumps XP1 and XP2 on the water supply side of the water storage tank X2, or connected to two fixed-speed or two-speed pumps XP1 and XP2, and connected to the pump XP1 and XP2 to discharge pressure. The inlet 6 of the main body 2 of the device 1 connects the outlet 7 to the downstream side of the cold water distribution line X. The hot water piping line Y is also piped in approximately the same manner as above, and is sequentially installed from the water supply side of the water storage tank Y2 (equipped with heating devices H such as electric water heaters and boilers) to the fixed-speed and variable-speed pump YP1 in parallel. YP2, or two fixed speed or two variable speed pumps YP1, YP2, and pressure reducing device 1. Furthermore, a device (not shown) for detecting a change in pressure or flow rate is provided in the cold water distribution line X and the hot water distribution line Y on the discharge side of the pumps XP1, XP2, YP1, and YP2, and upstream of the main body 2. To determine the number of pumps XP1, XP2, YP1, YP2 that must be operated, or to change the pumps XP1, XP2, ____ 12 _________ ΐ, paper size applies Chinese National Standard (CNS) A4 (210 X 297 mm) nn I nn I i I n ϋ n I · I ϋ nnnnn = -OJI I n ϋ 1 I ϋ ϋ I (Please read the precautions on the back before filling out this page) 576902 A7 ______ Β7 __ 5. Description of the invention (丨.) YP1, YP2 The number of operations changes the flow or pressure. Next, the operation of the hot and cold water supply system z decompression device} will be described with reference to FIGS. 1 and 4. The decompression device 1 used in the hot and cold water supply system Z is selected according to the selection method described later, so that the maximum used amount of hot and cold water is set below Fm and the secondary pressure P4 is within an allowable range (can be stabilized Pressure water supply). Here, it is assumed that the maximum use amount Fm of cold and hot water is 300 L / min, the primary pressure is set to 0.50.50 MPa, the secondary pressure is set to 00.30 MPa, and a pressure reducing device 1 having a flow capacity shown in FIG. 7 is used. . If the pressure reducing device 1 with the above capability is used, when the maximum amount of hot and cold water Fm is less than 300 L / min, the fluctuation range of the secondary pressure P4 relative to the amount of hot and cold water can be maintained to a sufficient level. Range (about 0.03 MPa) (see Figure 7). Therefore, if the faucet W of the hot and cold water supply system Z is turned on, the cold water and hot water with appropriate flows are respectively supplied from the cold water pipe X and the hot water pipe Y according to the set temperature, and the hot and cold water faucet C is mixed according to the set temperature. mixing. At this time, even if the use of other faucets C changes the amount of hot and cold water (below the maximum usage Fm 300 L / min), the flow that is approximately the same as the usage will pass through the body 2 to maintain the change in the secondary pressure P4. Range (approximately 0.03 MPa), so the flow of cold water from the cold water pipe X and hot water from the hot water pipe γ will not change corresponding to the set temperature, and can supply a set of cold hot water from the faucet W . ____13 ____ This paper is suitable for Chinese National Standards (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling out this page) # 576902 A7 5. Description of the Invention Each faucet W is changed from the above-mentioned water-passing state to the water-stop state, and the main valve 17 is closed as above to stop water flow, and the water chestnuts χρι, χρ2, YP1, and YP2 are stopped due to a pressure or flow detection device not shown Running. Next, a modified example of the hot and cold water supply system Z (the hot and cold water supply system Z1) will be described with reference to FIG. 5. The cold and hot water supply system Z1 connects the cold water pipes X and hot water pipes γ of the cold and hot water supply system z to the return sides of the water storage tanks χ2 and Υ2 to form the cold water circulation path Xa and the hot water circulation. In the road Ya, the same reference numerals are used for the same or corresponding parts of the hot and cold water supply system Z, and the description is omitted. Both the cold water circulation path Xa and the hot water circulation path Ya are connected to the flow adjustment mechanisms X3 and Y3 near the return sides of the water storage tanks X2 and Y2. The flow rate adjusting mechanisms X3 and Υ3 shown in Fig. 5 (a) are needle valves N and are configured to always return the set flow rate to the water storage tanks X2 and Y2. The flow rate adjusting mechanisms X3 and Υ3 shown in FIG. 5 (b) are divided by a needle valve N (same arrangement as described above) and a relief valve R (installed downstream of the needle valve N and divided from the circulation paths Xa and Ya). Connected to the return side of the water storage tanks X2 and Y2), the function is: the flow returned to the water storage tanks X2 and Y2 cannot be digested by the needle valve N, and when the pressure on the end of the circulation path Xa, Ya rises to the setting At the moment, open the drain valve R to return the set flow to the water storage tanks X2 and Y2. In addition, each of the cold and hot water supply systems Zil shown in Figures (5a) and (5b), the flow adjustment mechanisms X3 and Y3 are not limited to the above, as long as the set _____14_____ clothing and paper standards are set to Chinese National Standards (CNS ) A4 size (210 X 297 mm) (Please read the notes on the back before filling out this page) -------- 1T --------- ^ IAW ------- ----------------- 576902 A7 _____ B7_ 5. Description of the invention (θ) The flow rate can often return to the water storage tanks X2 and Y2 from the cold water circulation path Xa and the hot water circulation path Ya. It is not necessary to provide a pressure or flow detection device (equipped with the hot and cold water supply system Z). Next, the function of the decompression device 1 of the hot and cold water supply system Z1 will be described with reference to Figs. In the hot and cold water supply system Z1, because the flow adjustment mechanisms χ3 and Y3 are used to set the return flow to the water storage tanks X2 and Y2 (hereinafter, referred to as the circulating flow), in the cold water circulation path Xa and the hot water circulation path Ya, w open and close) cycle hot or cold water set. Each decompression device 1 used in the hot and cold water supply system Z1 is selected by a selection method described later. Even if the maximum amount of hot water or cold water Fm is exceeded, the secondary side pressure P4 is within the allowable range (can be stabilized in a stable manner). Pressure supply range of cold and hot water), set the cold water circulation path Xa and hot water circulation path within the flow range derived from the difference between the limit usage amount Fs and the set maximum usage amount Fm of this allowable range Individual circulating flows of Ya. Here, it is assumed that the maximum use amount Fm is 300 L / min, the primary pressure is set to 0.50 MPa, and the secondary pressure is set to 0.30 MPa. A pressure reducing device 1 having a flow capacity shown in FIG. 7 is used. . If the pressure reducing device 1 with the above capability is used, it will be known that if the maximum use amount Fm exceeds 300 L / min, about 420 L / min (limit use amount Fs), even if the limit use amount Fs and the maximum use amount Fm are exceeded The difference below about 120 L / min is the circulating flow rate, which can maintain the fluctuation range of the secondary side pressure P4 to the used amount within the allowable range (about 0.03 MPa) (see Figure 7). _15 —___ The dimensions of the paper and the paper are applicable to the Chinese National Standard (CNS) A4 (210 X 297 mm)--------- Fee -------- Order ·!丨 Xinhe (Please read the precautions on the back before filling this page) 576902 A7 ___B7____ V. Description of the Invention (Π) Here, if the circulation flow of the cold water circulation path Xa and the hot water circulation path Ya are set to 50 L / min, because the secondary pressure P4 at this time is about 0.29 MPa as shown in Fig. 7, the cold and hot water supply system Z1's cold and hot water consumption 0 ~ 300 L / min changes in the secondary pressure P4, In the decompression device 1, the difference is about 0.02 MPa (secondary pressure P4 (= about 0.29 MPa) at 0 L / min), and the difference between the secondary pressure P4 (= about 0.27 MPa) at 300 L / min ), Compared with the hot and cold water supply system Z, it can make the fluctuation range of the secondary pressure P4 narrower. Next, a method for selecting the decompression device 1 will be described. This selection method determines the maximum use amount Fm of the hot and cold water supply systems Z and Z1 using the pressure reducing device 1, the set pressures Pf, Ps of the secondary and secondary sides, and the secondary side of the hot and cold water usage. After the fluctuation range of the pressure P4 (lower allowable limit 値 PL), based on these decisions, follow the selection procedure below. Here, for the convenience of explanation, choose: the maximum amount of cold and hot water Fm is 300 L / min, set the primary side pressure 1 > £ 0.50 MPa 'secondary side pressure setting 値 Ps 0.30 MPa, secondary side The lower limit of the allowable range of the pressure P4 from its set pressure Ps is 0.27 MPa. 1. Selection of pressure reducing valve (1) Selection ... The determined setting ps is a pressure reducing valve 4 ° in the hall adjustment range (indicating one of the pressure reducing valve specifications of the secondary pressure range that can be set) (2) Next Preparation: Flow rate characteristics showing the relationship between the flow rate of the pressure reducing valve 4 and the pressure on the secondary side. Figure 1 (The throttle mechanism 20 is connected to the upstream side of the pressure reducing valve 4, and the flow capacity (flow rate (^) (secondary side The pressure P4 is set by the pressure Ps ___16 ---- The size of the paper and the paper are applicable to the Chinese National Standard (CNS) A4 (210 X 297 mm) -------- Order -------- -Line (please read the precautions on the back before filling this page) 576902 A7 _ ____B7____ V. Description of the invention (#) The pressure reducing valve 4 when the pressure drops to the lower limit of the allowable range PL), set to exceed the supply capacity (flow Q2 ) (With the throttle mechanism 20 limited). The flow characteristic diagram I is to set the secondary pressure when the flow is 0, and then increase the flow to measure the secondary pressure at that time. The results are plotted as graphs showing the flow rate and the secondary side pressure on the x-axis and γ-axis of Fig. 1. Then, the flow characteristic curve A in Fig. 1 (in the throttle mechanism 2) 0 under the above conditions (Qi> Q2), the flow characteristics of the pressure reducing valve 4 are measured). Due to the characteristics of the pressure reducing valve 4 itself, the closed boost pressures are different, but the maximum used amount is twice below the Fm. The side pressure P4 'becomes the slope (from its set pressure PS to the lower limit of the allowable range PL) which is slightly lowered to the right (through the horizontal line of the allowable pressure 値 pL). It is confirmed by actual measurement that this slope is at any The pressure reducing valves 4 are all constant. Therefore, even if the flow characteristic curve A of the pressure reducing valve 4 under the above conditions is not measured, the secondary side pressure setting 二次 Ps is approximately close to the level (parallel to the X axis). And a certain slope that descends to the right slightly (refer to Figure 8), when selecting the master valve described later, it may be a straight line that passes the lower limit of the allowable range 値 (allowable pressure 値) Pl slightly parallel to the X axis as Flow characteristic curve A (one point chain line in FIG. 9). The flow characteristic curve A of the above-mentioned slope shown in FIG. 8 shows the setting of a plurality of secondary-side pressures P4 corresponding to a flow rate of 0, Ps [0 · 40 , 0.30, 0.20, 0.10 (MPa)], and It shows the flow characteristic curve A with the same slope of each setting 値 Ps. However, the secondary side pressure set by the hot and cold water supply systems Z and Z1 is set to 0.30MPa, so the transfer note S ---- — 17 __— —_____-— The paper size of the table applies to Chinese National Standard (CNS) A4 ϋΓΓ2ι〇x 297 male H '' -------- tT --------- line (please read the back first) Please pay attention to this page and fill in this page again) 576902 A7 ____ B7___ V. Description of the Invention (β) 0.30MPa is the flow characteristic diagram I of the flow characteristic curve A of the secondary pressure setting 値 Ps. 2. Selection of main valve (1) Appropriately search for multiple types of main valve candidates (the basic structure is the same as the above, but the diameter of the main valve port 11 is different). (2) Next, prepare a flow rate characteristic diagram Π (representing the relationship between the primary side pressure Pi (and the pressure difference from the secondary side pressure P4) and the flow rate of each candidate) (Figure 10) 〇 Flow rate characteristic diagram Π The side pressure is 0 (that is, the open state of the valve port). While gradually increasing the primary side pressure, measure the flow rate at that time, and draw the results as graphs, which respectively indicate the primary side pressure (because the secondary side pressure is 0). Therefore, it is equivalent to the pressure difference between the primary pressure and the secondary pressure) and the flow rate on the X and Y axes of the graph Π. The flow characteristic diagram π shown in FIG. 10 shows the flow characteristic curves a to c corresponding to the master valve candidates, respectively. (3) The flow characteristic curves a to c showing the flow characteristic map Π are converted to the flow characteristic chart 1 (showing the flow characteristic curve A). In the flow characteristic diagram Π, for example, the so-called primary pressure is 0.20 MPa, which means the flow when the primary pressure Pi is 0.20 MPa and the secondary pressure P4 is 0. In other words, this flow is the primary pressure Pl and two The flow rate when the differential pressure of the secondary pressure P4 is 0.20 MPa. Therefore, in the flow characteristic curve A, the pressure difference is 0.20MPa, that is, the primary pressure Pi 0.5 OMPa 'The flow rate at the secondary pressure p4 〇 is 440 L / min 〇 _____—----—— 18_ Take the paper The standard is applicable to China National Standard (CNS) A4 (21〇X 297 mm) ------- fee -------- order --------- $ · (please first Read the notes on the back and fill in this page again) 576902 A7 ------_ B7____ V. Description of the invention (ft) In Figure 11, the secondary pressure p4 is converted in this way (the primary pressure will be set in the flow characteristic curve A) (When Pf is 0.50 MPa) and flow rate table. In the conversion table of FIG. 11, ^ indicates the pressure (the differential pressure between the primary pressure? 1 and the secondary pressure) shown in FIG. Π, and / 5 ′ indicates when the primary pressure pf is set to 0.5 MPa. The secondary side pressure P4, that is, / 3 = Pf-α, T ′ is the flow rate (capacity) corresponding to α in FIG. Θ and r shown in the above conversion table are marked in Fig. 1 to convert and express the flow capacity curve a. Question sample 'is also shown in Figure I with a conversion table (not shown) for the flow characteristic curves b and c of Figure Π. Fig. 9 is a view showing a flow characteristic curve A as shown in Fig. I, which shows the flow characteristic curves a to c converted as described above. (4) In the flow characteristic diagram I, the flow characteristic curve A, and the coordinates of the intersection points Ra to Rc of each flow characteristic curve a to c indicated by the conversion are Ra (0_27,420), Rb (0.26,605), Rc ( 0.26,680), the coordinates of the intersection point Ra ~ Rc, when the selected pressure reducing valve 4 and each main valve candidate are used separately as the basis of the above-mentioned decision, even if the flow rate is changed, the pressure can still be stable. (Secondary pressure) Boundary point of water supply. Moreover, in the graph I shown in FIG. 9, the curve in which the flow characteristic curve A and the flow characteristic curves a to c are respectively connected is equivalent to the flow characteristic curve of the pressure reducing device 1 that cooperates with the pressure reducing valve 4 and the main body 2. In the limit points Ra ~ Rc of each main valve candidate, because it exceeds the maximum ____19_____ mentioned above, the paper size applies the Chinese National Standard (CNS) A4 specification (2 忉 x 4 7 mm) -------- Order --------- Line (Please read the precautions on the back before filling this page) 576902 A7 ___ B7__ —__ V. Description of the invention (丨 Ί) The amount of use Fm = 300 L / min, and The difference between the side pressure setting 値 Ps = 0.30 MPa is the smallest, because it passes through the flow characteristic curve a of the intersection coordinates Ra (0 · 27, 420), so the total valve 2 corresponding to this curve is selected. By using the pressure reducing device 1 (in conjunction with the pressure reducing valve 4 and the main valve 2 selected as above) in the hot and cold water supply systems Z and Z1, the hot and cold water can be supplied at a stable pressure even if the water consumption varies. In FIG. 12, it is shown that according to the actual measurement (in accordance with the pressure reducing valve 4 and the main valve candidates selected as described above, setting: the maximum use of hot and cold water is 300 L / min, and the primary pressure Pf is set to 0. 50 MPa, the secondary pressure setting 値? 3 is 0.30 MPa, and the flow rate characteristic curve of the measured flow rate and the secondary pressure? 4). The flow characteristic curves J1, J2, and J3 of each pressure reducing device 1 shown in FIG. 12 describe the flow characteristic curves (A ~ a), (A ~ b), ( A ~ c) Each curve is approximately the same. According to the method described above, it can be confirmed that one-by-one measurement is not required to cooperate with the pressure reducing valve 4 and the main valve candidate each pressure reducing device 1. [Effects of the invention] The invention of the first scope of the application for the patent, because a guide line 3 including a pressure reducing valve 4 is provided between the main valve 2 to the secondary pressure chamber 8 and the secondary pressure chamber 9 of the above structure. In this guide line 3, a branch line 3a provided on the primary side of the pressure reducing valve 4 is connected to the diaphragm chamber 14, and a throttle mechanism 20 is provided upstream from the branch point M. Therefore, the secondary side of the main body 2 is used. Use water so that when the secondary pressure P4 is lower than the set pressure Ps, the pressure reducing valve 4 will open. At this time, 'flow from the primary pressure chamber 8 of the main body 2 to the pressure valve 4 primary pressure chamber- ----- 20____ Applicable to China National Standard (CNS) A4 size (210 X 297 mm) for clothing paper size 丨 丨 I »--------- f -------- Order—— I! Line _ (Please read the precautions on the back before filling this page) A7 ---- B7 ___ — — Friends, invention description (丨 R), when the pressure p3 is changed, the main valve of the body 2 that can be opened and closed can be opened The 17 is operated slowly to prevent the water hammer (a phenomenon that occurs on the upstream side of the main body 2 when the main valve 17 suddenly opens and closes the valve) and other undesirable phenomena. The invention in item 2 of the scope of patent application is a cold and hot water supply system z, which is connected to the cold water pipe XI downstream of the pressure reducing device 1 with a cold and hot water mixing faucet in the cold water pipe X and hot water pipe Y, respectively And hot water pipe Y1, and connected to the faucet W, each pressure reducing device 1 is within the allowable range when the secondary side pressure P4 is below the set maximum hot or cold water usage Fm, so even if each faucet is used W and the amount of cold and hot water changes, the secondary pressure P4 will only change within its allowable range, so that the flow of cold water from cold water pipe X and hot water from hot water pipe Y will not change according to the set temperature of the hot and cold water Therefore, a set temperature of hot and cold water can be stably supplied from the faucet W. The invention with the third scope of the patent application is a cold and hot water supply system Z1. The cold and hot water circulation path Xa and the hot water circulation path Ya are connected with a hot and cold water mixer faucet C to connect the pressure reducing device 1 and the flow regulating mechanism respectively. The cold water pipe XI and hot water pipe Y1 divided between X3 and Y3 are connected to the faucet W. Even if the pressure reducing device 1 exceeds the set maximum amount of hot water or cold water Fm, the secondary side pressure P4 will be at Within the allowable range, in addition, a flow range is derived from the difference between the limit usage amount Fs and the set maximum use amount Fm based on the aforementioned allowable range, and the cold water circulation path Xa and the hot water circulation path are respectively set within the flow range. The circulation flow of Ya, therefore, if it exceeds the maximum use amount Fm of cold and hot water and is below the limit use amount Fs, even if the difference between the limit use amount Fs and the maximum use amount Fm is _ ___ 22 _———— This paper scale applies to China National Standard (CNS) A4 Specification (210 x 297 mm) --------------------- Order --------- ^-^ wi ( (Please read the notes on the back before filling this page) 576902. A7 _____B7____ V. Invention Ming amount (20) as the circulation flow rate, can be used in an amount relative to the secondary-side pressure fluctuation amplitude of P4 is maintained within an allowable range. Thereby, because the initial pressure of the secondary side pressure only reduces the pressure corresponding to the set circulation flow rate, the fluctuation range of the secondary side pressure can be reduced, and the temperature from the cold water pipe X according to the set temperature of the hot and cold water can be reduced. The flow of cold water and hot water from the hot water pipe Y is more stable, and cold and hot water at a set temperature can be supplied more stably. Moreover, in the cold water piping X and hot water piping Y of the hot and cold water supply system Z, once the faucets W are stopped, even if the pilot pressure P2 rises due to the closed-valve pressure reducing valve 4, the pressure of the diaphragm chamber 14 Even if the throttle mechanism 21 does not rise immediately, the main valve 17 is slowly closed. Therefore, it is possible that the secondary side of the body 2 may flow from the secondary side to the secondary side of the body 2 before the valve is closed. It will rise to the primary pressure setting 値 Pf, but because the cold water circulation path Xa and hot water circulation path Ya of the cold and hot water supply system Z1, the set (circulated) flow rate is continuously circulated, so even if there is the aforementioned situation The secondary side of 2 does not rise to the primary side pressure setting 値 Pf. In this way, because a certain amount of water continuously flows through the body 2 ', chattering can be prevented when the water consumption of the faucet W is reduced, because cold water and hot water are circulated in the cold water circulation path Xa and hot water circulation, respectively. Road Ya, so you can use a set temperature of hot and cold water by turning on the faucet W, which is very convenient for hospitals and hotels that use hot and cold water all day. 3 The invention of item 4 of the claim scope is based on the decision items of the hot and cold water supply system Z and Z1 (the maximum amount of hot and cold water Fm, the primary pressure setting 値 Pf, the secondary pressure setting 値 ps, Relative cold and hot water consumption _____ 22 ___- This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) --- I ---- Order --------- i ^ wl (Please Read the precautions on the back before filling this page) 576902 A7 _______ B7 _; ___ 5. The variation range of the secondary side pressure P4 of the description of the invention (W) will be shown in the flow characteristic diagram of the flow characteristics of each candidate master valve The conversion from a to c is shown in the flow characteristic diagram I showing the flow characteristic curve A of the pressure reducing valve 4 (the throttle mechanism is connected upstream), wherein the flow characteristic curve A of the pressure reducing valve 4 and the flow characteristic curve a of the alternate master valve a The coordinates of the intersection point of ~ c are Ra ~ Rc, from which the total valve 2 whose flow characteristic curve is a is selected. Its intersection point exceeds the aforementioned maximum use amount Fm, and the difference from the secondary pressure setting 値 Ps is the smallest. Here, the flow rate is used. Characteristic map I, you can simply select the main valve 2 that meets various setting conditions, and It means the ability to be able to grasp a reduced pressure. In the selection of each pressure reducing device 1 for the hot and cold water supply system Z, especially when selecting a total valve 2 where the secondary side pressure P4 will be within the allowable range even if the maximum use amount Fm of hot or cold water is selected According to Figure I, the difference between the allowable range limit Fs and the set maximum use amount Fm is the range of the circulating flow rates of the cold water circulation path Xa and the hot water circulation path Ya, respectively. The internal flow rate can be determined. What about the primary and secondary pressure setting? 3, a throttle mechanism 20 is connected upstream of the pressure reducing valve 4 in the pressure regulating range, and the flow characteristic curve A of the pressure reducing valve 4 shown in the flow characteristic diagram I is when the secondary pressure P4 reaches the allowable Lower limit of the range PlJ Temple, maintained at the flow rate of QK pressure reducing valve 4) > Q2 (supply flow rate restricted by the throttling mechanism 20); the measurement result under the condition of Q Θ Q2 The gradient is an approximate straight line that drops slightly to the right, which is approximately parallel to the X axis. Because any gradient of the pressure reducing valve 4 is constant, in the flow characteristic diagram I, the pressure of the secondary side pressure P4 corresponding to the flow 0 is Setting 値 Ps as the starting point only indicates that it has the above gradient __24____. The paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 576902. A7 _ B7 _
五、發明說明（Z2J 之流量特性曲線A即可。 在申請專利範圍第項之發明，於流量特性圖I所示 之減壓閥4流量特性曲線A，因與通過二次側壓力p4之容 許範圍下限値PL之水平(於圖I平行於表示流量之X軸)直 線大致相同，故即使將流量特性曲線A以圖9之一點鏈線 來替代，對於總閥2之選擇沒有任何妨礙，而能容易地製 作用來選擇總閥之圖I，故本發明之實用效果很大。 【圖式之簡單說明】 圖1係減壓裝置之截面圖。 圖2係總閥之放大截面圖。 ________________________________________麗^係減壓麗之^截面___ 圖4係使用減壓裝置之冷熱水供應系統的配管略圖。 圖5係使用減壓裝置之循環式冷熱水供應系統的配管 略圖，⑷係流量調節機構爲針閥之配管略圖，⑻係流量調 節機構爲針閥及放洩閥之配管略圖。 圖6係減壓裝置中所使用之減壓閥單體的流量特性曲 線。 圖7係減壓裝置之流量特性圖。 圖8係連接有節流機構之減壓閥之流量特性圖I ’顯 示二次側壓力設定値不相同時之各流量特性曲線。 圖9係流量特性圖I，其把圖8所示之流量特性曲線 1中之一轉記過來並把如圖10所示之各流量特性曲線換算而 成者。 圖10係顯示各候補總閥之流量特性曲線的流量特性圖 ______75 —__—---- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) • --------貧---------線. 576902 A7 _B7_ 五、發明說明（/) Π。 圖11係換算表。 圖12係根據減壓裝置(組合各候補總閥)實測値的流量 特性圖。 圖13係習知品之流量特性圖。 【符號說明】 (請先閱讀背面之注意事項再填寫本頁) --------IT---------^ —^w---- 1 減壓裝置 2 本體 3 嚮導管路 3a 分岐管路 4 減壓閥 6 流入口 7 流出口 8 一次側壓力室 9 二次側壓力室 11 閥口 13 膜片 14 膜片室 17 主閥 19 彈簧 20 節流機構 21 節流機構 A 流量特性曲線 癱 a 流量特性曲線 26 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 B7 五、發明說明（ b 流量特性曲線 C 流量特性曲線 C 冷熱水混合龍頭 Fm 最大使用量 Η 加熱裝置 Pf 一次側壓力設定値 Ps 二次側壓力設定値 P4 二次側壓力 Pl 容許範圍下限 Qi 流量 q2 流量 Ra 交點座標 Rb 交點座標 Rc 交點座標 X 冷水配管路 Xa 冷水循環路 XI 冷水管 X2 儲水槽 X3 流量調節機構 XP1 泵 XP2 泵 Y 熱水配管路 Ya 熱水循環路 Y1 熱水管 27 (請先閱讀背面之注意事項再填寫本頁) # 訂·丨 •線丨-- 木紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 576902 A7 _B7 五、發明說明（A) Y2 儲水槽 Y3 流量調節機構 W 水龍頭 I 流量特性圖 Π 流量特性圖 (請先閱讀背面之注意事項再填寫本頁) # 一-5J·!1111 _28 I紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐iV. Explanation of the invention (The flow characteristic curve A of Z2J is sufficient. For the invention in the scope of the patent application, the flow characteristic curve A of the pressure reducing valve 4 shown in the flow characteristic chart I is due to the permissibility of passing the secondary side pressure p4. The lower limit of the range 値 the level of PL (parallel to Figure X parallel to the X-axis indicating flow) is approximately the same straight line, so even if the flow characteristic curve A is replaced by a point chain line in Figure 9, there is no obstacle to the selection of the main valve 2, and The diagram I used to select the master valve can be easily produced, so the practical effect of the present invention is great. [Simplified description of the diagram] Fig. 1 is a sectional view of the pressure reducing device. Fig. 2 is an enlarged sectional view of the master valve. _______________________________________ _ 丽 ^ is a pressure-reducing ^ cross section ___ Figure 4 is a schematic diagram of the piping of the hot and cold water supply system using a pressure reducing device. Figure 5 is a schematic diagram of the piping of the circulating cold and hot water supply system using a pressure reducing device, and ⑷ is a flow adjustment The mechanism is a schematic diagram of the piping of the needle valve, and the series flow adjustment mechanism is a schematic diagram of the piping of the needle valve and the relief valve. Figure 6 shows the flow characteristic curve of the pressure reducing valve used in the pressure reducing device. Figure 7 is the pressure reducing device Figure 8 is a flow characteristic diagram of a pressure reducing valve connected to a throttling mechanism. I 'shows each flow characteristic curve when the secondary pressure setting is different. Figure 9 is a flow characteristic diagram I. One of the flow characteristic curve 1 shown in 8 is transferred and converted into each flow characteristic curve shown in Fig. 10. Fig. 10 is a flow characteristic chart showing the flow characteristic curve of each candidate master valve ______75 — __—---- This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) • -------- Poor-- ------- Line. 576902 A7 _B7_ V. Description of the invention (/) Π. Figure 11 is the conversion table. Figure 12 is the flow rate characteristic diagram of the measured radon based on the pressure reducing device (combined with the alternate main valves). Figure 13 It is the flow characteristic diagram of conventional products. [Symbol Description] (Please read the precautions on the back before filling this page) -------- IT --------- ^ — ^ w ---- 1 Pressure reducing device 2 Body 3 Guide line 3a Dividing line 4 Pressure reducing valve 6 Inlet 7 Outlet 8 Primary pressure chamber 9 Secondary pressure chamber 11 Valve port 13 Membrane 14 Diaphragm chamber 17 Main valve 19 Spring 20 Throttling mechanism 21 Throttle mechanism A Flow characteristic curve a Flow characteristic curve 26 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) 576902 A7 B7 5 Description of the invention (b Flow rate characteristic curve C Flow rate characteristic curve C Hot and cold water mixing faucet Fm Maximum usage Η Heating device Pf Primary pressure setting 値 Ps Secondary pressure setting 値 P4 Secondary pressure Pl Allowable range lower limit Qi Flow q2 Flow Ra Intersection coordinate Rb Intersection coordinate Rc Intersection coordinate X Cold water distribution line Xa Cold water circulation path XI Cold water tube X2 Water storage tank X3 Flow adjustment mechanism XP1 Pump XP2 Pump Y Hot water distribution line Ya Hot water circulation path Y1 Hot water pipe 27 (Please read the back first Please pay attention to this page before filling in this page) # Order · 丨 • Line 丨-The size of the wood paper is applicable to the Chinese National Standard (CNS) A4 (210 X 297 mm) 576902 A7 _B7 V. Description of the invention (A) Y2 Water storage tank Y3 Flow adjustment mechanism W Faucet I Flow characteristic diagram Π Flow characteristic diagram (Please read the precautions on the back before filling P) # a -5J ·! 1111 _28 I paper scale applicable Chinese National Standard (CNS) A4 size (210 X 297 mm i