201235304 六、發明說明： 【發明戶斤屬之技術領域3 發明領域 本發明係有關於一種造水裝置及造水方法。 【先前技術3 背景技術 迄今，在從蒸氣得到動力之蒸氣渦輪設備中，係利用 從渦輪群排出並在復水器冷凝之蒸氣冷凝水而進行造水。 例如，專利文獻1所揭示之蒸氣渦輪設備係如第5圖所示， 由渦輪91導入復水器92之蒸氣藉由與冷海水93進行熱交 換，成為冷凝水94而導入冷凝器95。存積於冷凝器95之蒸 氣冷凝水在再度作為鋼爐供水而使用的過程中作為造水裝 置之冷卻水而使用，藉此可達到熱回收的效果，並且可作 為渦輪系統而達成省能源化。在第5圖之構造中，冷海水93 在復水器92成為溫海水96而一部份導入至蒸發器97，所生 成之蒸氣被導入冷凝器95與冷凝水94進行熱交換，藉此產 生淡水98。 先行技術文獻 專利文獻 專利文獻1 :日本專利公報特開昭61-161189號 【發明内容】 發明揭示 發明欲解決之課題 但是，對於如今之蒸氣渦輪設備而言，由於因應更上 201235304 一層的省能源化潮流需求，須要求因蒸氣條 導致之高效率化，導入至冷凝器95而利用於:上円壓化而 凝水94的溫度會高溫化、且蒸氣冷凝水會有凝之冷 向。因此’在上述習知構造中’並無法處理適=匕的傾 水量之冷凝水溫度與流量，習知之造水裝置 ；所需造 等限制，會有難以確保所需造水量之虞: 於蒸發溫度 因此 ’本發明之目的在於提供1可達 且可提升造水效率之造水裝置及造水方法。 取*源化並 用以解決課題之手段 、本發明之前述目的可藉由下述之造水裝置來達成’該 造水裝置具有：加熱器，係加熱原料水而生成水 及復水器，料卻社从水蒸氣^成㈣水者1前 述復水器具有將水·與冷卻水進行熱域的第丨㈣換 器、及將水洛氣與原料水進行熱交換的第2熱交換器並構 造成使通過前述第2熱交換器之原料水可導入前述加轨^ 在該造水裝置中，前述第1熱交換器及第2熱交換器可 構造成一體化而使冷卻水及原料水不會混合。 前述復水器可構造成具有積層^ 複數之傳熱板，複數之前述傳熱板由接人其中之分隔構件 分。在該構造中’前述第i熱交換器係構成為 從一=前述端板導人冷卻水，透過—方之前述板群進行 與水減之熱交換，將熱交換後之冷卻水從—方之前述端 板排出；而前述第2熱交換器係構成為從另一方之前述端板 導入原料水’透過另-方之前述板群進行與水蒸氣之熱交 201235304 換，將熱交換後之原料水從另一方之前述端板排出。根據 該構成，可達到小型化且可提升復水器的能力。 又，更具備蒸氣渦輪設備，該蒸氣渦輪設備係構成有 循環路徑而可使鍋爐所產生之蒸氣在渦輪驅動後以渦輪冷 凝器冷凝而流回前述鋼爐，藉此，使前述第1熱交換器介於 前述循環路徑中而可使前述渦輪冷凝器所生成之渦輪冷凝 水成為冷卻水。 又，本發明之前述目的可藉由下述之造水方法來達 成，該造水方法包含以下步驟：加熱步驟，以加熱器加熱 原料水而生成水蒸氣；及冷凝步驟，藉由冷卻水及原料水 冷卻所生成之水蒸氣而生成蒸德水，且前述加熱步驟將前 述冷凝步驟中與水蒸氣熱交換後之原料水導入前述加熱 器。 發明效果 根據本發明，可提供一種可達到省能源化並且可提升 造水效率之造水裝置及造水方法。 圖式簡單說明 第1圖係本發明之一實施型態之造水裝置的系統圖。 第2圖係第1圖所示之造水裝置的重要部份系統圖。 第3圖係第1圖所示之造水裝置的重要部份立體圖。 第4圖係本發明之其他實施型態之造水裝置的重要部 份立體圖。 第5圖係習知之造水裝置的系統圖。 【實施方式3 201235304 用以實施發明之形態 以下，參照附加圖式說明本發明之一實施形態。第i圖 係本發明之一實施型態之造水裝置的系統圖。如第1圖所 示，造水裝置1係於蒸氣渦輪設備50之系統組裝造水裝置本 體100而構成。蒸氣渦輪設備50之一例為具備鍋爐51、渦輪 群52、屬輪冷凝益53、基礎冷凝器（ground condenser)54、 供水加熱器55及脫氣機56，且該等構成要素係藉由循環路 徑60而連接。 鍋爐51使重油 '液化天然氣等燃料燃燒而由供給水產 生蒸氣，並供給至渦輪群52。渦輪群52係由例如高壓渦輪 及低壓渦輪所構成之蒸氣渦輪群，可產生用以使船舶之推 進器等旋轉的動力。渦輪冷凝器53可藉由海水等來冷卻從 渦輪群52排出之蒸氣而生成渦輪冷凝水。所生成之渦輪冷 凝水藉由泵61的動作，通過基礎冷凝器54及供水加熱器 55，利用導入於渴輪群52之蒸氣的一部份進行加熱後，導 入至脫氣器56而除去氧等。貯存在脫氣器56之渦輪冷凝水 藉由泵62的動作，供給至鍋爐51再成為蒸氣，並循環於循 環路徑60。蒸氣渦輪設備50宜舉例如搭載於蒸氣渦輪船 者，但用途並無特別限定，例如也可為發電用。 造水裝置本體100在具備上述構造之蒸氣渦輪設備5〇 中，經過分歧路徑63而夾在泵61與基礎冷凝器54之間的循 環路徑60，並如後所述，將通過循環路徑6〇之渦輪冷凝水 作為造水用之冷部水來使用。供給至造水裝置本體1〇〇之渦 輪冷凝水的流量可藉由操作設置於循環路徑6 〇之調整閥6 4 6 201235304 而進行調整。造水裝置本體100也可直接安插在循環路徑60 中間，來代替如本實施形態之從循環路徑60分流者。 第2圖係造水裝置本體100的系統圖。如第2圖所示，造 水裝置本體100具備：加熱器10，係將做為原料水之海水加 熱而生成水蒸氣者；蒸發器20，係將水蒸氣與鹽水(濃縮海 水）等濃縮原料水分離者；及復水器30，係冷卻水蒸氣而生 成蒸顧水者。 加熱器10具有可分別導入及排出原料水之原料水導入 口 11及水蒸氣•鹽水出口 12、及分別導入及排出船舶用引 擎水套冷卻水等溫水之溫水導入口 13及溫水排出口 14，從 原料水導入口 11所導入之原料水藉由從溫水導入口 13所導 入之溫水加熱而蒸發，再從水蒸氣•鹽水出口 12排出。加 熱器10宜舉例如與後述之復水器30同樣具有板式熱交換器 者，但熱交換器之種類並無特別限定。又，水蒸氣之加熱 源也無限定須為溫水，例如也可為蒸氣、燃燒式加熱器或 電熱器等。 蒸發器20具有：加熱原料水導入口 21，係可導入由水 蒸氣•鹽水出口 12所排出之加熱後的原料水者；蒸氣排出 口 22，係排出由原料水所生成之水蒸氣者；及鹽水排出口 23，係排出殘留之鹽水者。 復水器30包含有：蒸氣導入口 31，係導入由蒸氣排出 口 22所排出之水蒸氣者；蒸餾水排出口 32，係排出冷卻水 蒸氣所得之蒸餾水者；分別導入及排出用以冷卻蒸氣之冷 卻水的冷卻水導入口 33及冷卻水排出口 34 ;及分別導入及 7 201235304 排出同樣可冷卻蒸氣之原料水的原料水導入口 35及原料水 排出口 36。 在冷卻水導入口 3 3，將第丨圖所示之蒸氣渦輪設備5 〇之 渦輪冷凝水導入而作為冷卻水，由冷卻水排出口 34排出之 冷卻水再度回到蒸氣渦輪設備5〇之循環路徑60。成為冷卻 水之渦輪冷凝水通常為高純度的清水，故在復水器3〇設有 分隔構件37以使冷卻水與原料水不會混合。復水器3〇藉由 戎分隔構件37，分離成將水蒸氣與冷卻水進行熱交換之第j 熱父換器310、及將水蒸氣與原料水進行熱交換之第2熱交 換器320。冷卻水不一定須為清水，也可為與原料水不同之 其他冷卻液。 又，在原料水導入口 35，藉由其他系統或喷射泵41的 動作，導入海水作為原料水，由原料水排出口 36排出之原 料水導入至加熱器1〇之原料水導入口 11。原料水除了本實 轭型態之海水外，可使用自來水、雨水、地下水、河水、 工業排水、生活排水等。由噴射泵41所供給之原料水也可 利用為水喷射器40之驅動水，蒸發器20及復水器3〇藉由連 接於水噴射器40之最大負壓部而使非冷凝氣體被吸引，而 維持真空狀態。由蒸餾水排出口 32排出之蒸餾水 條水純^清水槽(未目和。 本實施型態之復水器30係由板式熱交換器所構成。如 第3圖之重要部分立體圖所示，復水器30在2個端板lu、112 之間’構成為分別複數交互地積層配置2種傳熱板113&、 U3b ’而邊緣部藉由連結棒30a、30b結合。另外，在第3圖 8 201235304 中，為了容易理解構造，以虛線顯示一方之端板111。各傳 熱板113a、113b形成為矩形，在鄰接配置於積層方向之中 央附近之2片傳熱板113b、113b之間，設有上述之分隔構件 37。各傳熱板113a、113b由該分隔構件37分離成2個板群。 本實施型態之分隔構件37係構成為藉由口栓37a密封住較 傳熱板113a、113b之厚度厚的板之開口，即使是冷卻水為 高壓之渦輪冷凝水的情況下，也可發揮高度的耐壓性能， 可確實地防止冷卻水與原料水混合。但是，分隔構件37之 構成並不限定於本實施型態者，例如，可如第4圖所示，也 可藉由鄰接配置之2片傳熱板113a、113b構成分隔構件37。 構成第4圖所示之分隔構件37的2個傳熱板113a、113b具有 後述之蒸餾流通口 114、115，另一方面，該等以外的開口 皆藉由口栓37a密封住。另外，在第4圖中，對於第4圖中與 第1圖同樣的構成部分，附加同樣符號。 蒸氣導入口 31及蒸餾水排出口 32分別形成於一方之端 板111中之一方之對角。各傳熱板113a、113b在對應於蒸氣 導入口 31及蒸餾水排出口 3 2的位置分別形成有蒸餾流通口 114、115，於藉由各蒸餾流通口 114而形成之流路連接有蒸 氣導入口 31，於藉由各蒸餾流通口 115而形成之流路則連接 有蒸餾水排出口 32。 冷卻水導入口 33及冷卻水排出口 34分別形成於一方之 端板111中之另一方之對角。構成配置於一方之端板111與 分隔構件37之間之一方之板群的各傳熱板113a、113b，在 對應於冷卻水導入口 33及冷卻水排出口 34的位置，分別形 9 201235304 成有冷卻水流通口 116、117， ⑴而形成之鱗騎财料水排出通口 山原料水以口35及原料水㈣叫分卿成於另-方 之化板、m中之另—方之對角。構成配置於另—方之端板 112與分隔構件37之間之另_方之板群的各傳熱板⑴a、 113b ’在對應於原料水導入口35及原料水排出口 的位 置’分別形成有原料水流通π118、119，於藉由各原料水 流通口 m㈣紅流路連接有原料水導人σ35，於藉由各 原料流通卩119而形成之流路則連接有原料水排出口36。分 隔構件37具有蒸館流通口114、115，另一方面則如上所述， 藉由口栓37a密閉住對應於冷卻水流通口 116、117及原料水 流通口 118、119的開口。 各傳熱板113a、113b皆於一方面形成有溝部120a、 120b，傳熱板U3a之溝部i2〇a連通2個蒸飽流通口 114、115 間’另一方面’ 2個冷卻水流通口116、in間或2個原料水 流通口 118、119間則係隔離。又，傳熱板113b之溝部120b 隔離2個蒸德流通口 114、115間，另一方面，2個冷卻水流 通口 116、117間或2個原料水流通口 us、119間則係連通。 鄰接之各傳熱板113a、113b之間，藉由墊片（未圖示）而密 封。另外，在第3圖中為了易於理解，形成於傳熱板U3a、 113b之積層方向的流路，以虛線顯示與溝部120a、120b連 通的部分，以實線顯示與溝部120a、120b隔離的部分。 藉由復水器30之上述構造，在一方之端板111與分隔構 201235304 件37之間，由蒸氣導入口 31及冷卻水導入口 33所導入之水 蒸氣及冷卻水分別流通於傳熱板113a之溝部i2〇a及傳熱板 113b之溝部120b，因此，以傳熱板113a、113b之積層方向 來看，水蒸氣及冷卻水交互通過鄰接之傳熱板113a、113b 間。結果，在水蒸氣與冷卻水之間，透過傳熱板113a、113b 進行熱交換’此部分作為第1熱交換器31〇而產生機能。結 束熱交換而生成之蒸餾水及冷卻水分別由蒸餾水排出口 32 及冷卻水排出口 34排出。 在復水器30之另一方之端板112與分隔構件37之間，由 原料水導入口 35所導入之原料水流通於傳熱板113b之溝部 120b，因此’以傳熱板113a、113b之積層方向來看，水蒸 氣及原料水交互通過鄰接之傳熱板n3a、113b間。結果， 在水蒸氣與原料水之間，透過傳熱板113a、113b進行熱交 換，此部分作為第2熱交換器320而產生機能。結束熱交換 而被加熱之原料水由原料水排出口 36排出。 根據具備上述構造之造水裝置卜從復水器30之一方之 端板111透過冷卻水導入口 33所導入的冷卻水、與從另一方 之端板112透過原料水導入口 35所導入的原料水，分別在第 1熱交換器310及第2熱交換器320與水蒸氣進行熱交換，藉 此，構成為可生成蒸顧水’因此，較習知之僅使冷卻水與 水蒸氣進行熱交換之構造更易於進行水蒸氣的冷凝，可提 高復水器30的效率。又，由於在加熱器1〇，導入在第2熱交 換器320中因為與水蒸氣之熱交換而升溫的原料水，故可使 導入加熱器1 〇之原料水在初期階段蒸發而提升熱交換效 11 201235304 率，可達到省能源化。導入加熱器10之原料水的溫度可藉 由選擇設置於復水器3〇之傳熱板ii3a、113b片數、或分隔 構件37的位置來進行適當調整。 造水裝置1可達成之上述效果，在如本實施蜇態般將蒸 氣渦輪設備50之渦輪冷凝水作為冷卻水的情況下會特別顯 著’即使隨著蒸氣條件之高溫化而使渦輪冷凝水較為高 溫，也可易於確保所需之造水量。但是，導入復水器30之 冷卻水並不一定須限定於蒸氣渦輪設備5〇之渦輪冷凝水， 例如’也可使用其他蒸氣循環系統所生成之冷凝水、或藉 由使用蒸氣作為熱源或動力源而生成、保持高溫而利用於 其他用途的排泄水等。 又，在本實施型態中，由於第1熱交換器310及第2熱交 換器320係一體化以使冷卻水及原料水不會產生混合，故可 達成構造之小型化’並且可提升復水器30之效率。具體而 言’可將第1熱交換器310及第2熱交換器320沿著傳熱板 113a、113b之積層方向並列配置。本實施型態之構成係導 入於復水器3〇之水蒸氣最初其一部份會導入至第1熱交換 器310，然後’剩下的水蒸氣會導入至第2熱交換器320。但 是，第1熱交換器310及第2熱交換器320之配置並不限定於 本實施塑態者，例如，也可構成為將冷卻水導入口 33及冷 卻水排出口 34設置於另一方之端板in，將原料水導入口 35 及原料水排出口 36設置於一方之端板iu。 並且，第1熱交換器310及第2熱交換器320宜如本實施 型態般藉由板式熱交換器而形成，但也可使用殼管式等之 12 201235304 其他熱交換器。又，第1熱交換器310及第2熱交換器320也 無須一定要一體化，也可為互相分離的構造。第1熱交換器 310及第2熱交換器320也可構成為使水蒸氣氣流分歧而分 別導入至第1熱交換器310及第2熱交換器320。 I：圖式簡單說明3 第1圖係本發明之一實施型態之造水裝置的系統圖。 第2圖係第1圖所示之造水裝置的重要部份系統圖。 第3圖係第1圖所示之造水裝置的重要部份立體圖。 第4圖係本發明之其他實施型態之造水裝置的重要部 份立體圖。 第5圖係習知之造水裝置的系統圖。 【主要元件符號說明】 1...造水裝置 31...蒸氣導入口 10...加熱器 32…蒸餾水排出口 11...原料水導入口 33...冷卻水導入口 12...水蒸氣•鹽水出口 34...冷卻水排出口 13...溫水導入口 35...原料水導入口 14...溫水排出口 36...原料水排出口 20…蒸發器 37...分隔構件 21…加熱原料水導入口 37a·.· 口栓 22...蒸氣排出口 40...水喷射器 23...鹽水排出口 41...喷射泵 30...復水器 42...蒸餾水泵 30a、30b...連結棒 50...蒸氣渦輪設備 13 201235304 51...鍋爐 95...冷凝器 52...渦輪群 96...溫海水 53...渦輪冷凝器 97...蒸發器 54...基礎冷凝器 98...淡水 55...供水加熱器 100...造水裝置本體 56...脫氣機 111、112...端板 60...循環路徑 113a、113b...傳熱板 61、62···泵 114、115…蒸餾流通口 91...渴輪 120a、HOb.··溝部 92...復水器 310…第1熱交換器 93...冷海水 320...第2熱交換器 94...冷凝水 14201235304 VI. Description of the Invention: [Technical Field of Invention] 3 Field of the Invention The present invention relates to a water generating device and a water producing method. [Prior Art 3] Heretofore, in a steam turbine plant that receives power from steam, water is produced by vapor condensed water discharged from a turbine group and condensed in a rehydrator. For example, as shown in Fig. 5, the steam turbine apparatus disclosed in Patent Document 1 is introduced into the condenser 95 by the heat exchange with the cold seawater 93 by the steam introduced into the rehydrator 92 by the turbine 91. The vapor condensed water stored in the condenser 95 is used as the cooling water of the water generating device in the process of being used again as a water supply to the steel furnace, thereby achieving the effect of heat recovery and saving energy as a turbine system. . In the configuration of Fig. 5, the cold seawater 93 is introduced into the evaporator 97 in the rehydrator 92 as the warm seawater 96, and the generated vapor is introduced into the condenser 95 to exchange heat with the condensed water 94, thereby generating Fresh water 98. The present invention discloses a problem to be solved by the invention. However, for today's steam turbine equipment, since it is more energy-efficient in the 201235304 layer In order to increase the efficiency of the steam flow, it is required to be introduced into the condenser 95 to be used for the upper pressure, and the temperature of the condensation water 94 is increased, and the vapor condensation water is cooled. Therefore, in the above-mentioned conventional structure, it is impossible to deal with the condensed water temperature and flow rate of the appropriate amount of water, and the conventional water-making device; the required manufacturing limit, it is difficult to ensure the required amount of water production: evaporation Temperature Therefore, the object of the present invention is to provide a water generating device and a water generating method which are capable of improving water production efficiency. The above-described object of the present invention can be achieved by the following water-making device. The water-making device has a heater that generates water and a rehydrator by heating raw material water. The first rehydrator has a second (four) converter that performs water and cooling water in the hot zone, and a second heat exchanger that exchanges water and raw water in the hot water. The raw material water passing through the second heat exchanger can be introduced into the water supply device, and the first heat exchanger and the second heat exchanger can be configured to be integrated to form cooling water and raw material water. Will not mix. The foregoing water reconstitutor may be constructed to have a plurality of heat transfer plates, and the plurality of heat transfer plates are divided by the partition members. In the above configuration, the "i-th heat exchanger" is configured to guide the cooling water from the one end plate to the front plate, and to exchange heat with the water after the plate group is passed through, and to remove the cooling water after the heat exchange. The second heat exchanger is configured to introduce raw material water from the other end plate and pass through the other plate group to perform heat exchange with water vapor 201235304, and heat exchange The raw material water is discharged from the other end plate of the other side. According to this configuration, the miniaturization can be achieved and the capacity of the rehydrator can be improved. Further, the steam turbine apparatus further includes a circulation path configured to allow the steam generated by the boiler to be condensed by the turbine condenser after the turbine is driven to flow back to the steel furnace, thereby causing the first heat exchange The turbine is condensed in the circulation path to make the turbine condensate generated by the turbine condenser into cooling water. Moreover, the above object of the present invention can be attained by a water-making method comprising the steps of: heating a step of heating a raw material water with a heater to generate water vapor; and a condensation step by cooling water and The raw material water cools the generated steam to form steamed water, and the heating step introduces the raw material water that has been subjected to heat exchange with the steam in the condensation step into the heater. EFFECT OF THE INVENTION According to the present invention, it is possible to provide a water generating device and a water generating method which can achieve energy saving and can improve water generating efficiency. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a system diagram of a water-making apparatus of one embodiment of the present invention. Fig. 2 is a system diagram showing an important part of the water generator shown in Fig. 1. Fig. 3 is a perspective view of an important part of the water generating device shown in Fig. 1. Fig. 4 is a perspective view showing an important part of a water generating device of another embodiment of the present invention. Figure 5 is a system diagram of a conventional water making device. [Embodiment 3] 201235304 Mode for Carrying Out the Invention Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings. Figure i is a system diagram of a water-making device of one embodiment of the present invention. As shown in Fig. 1, the fresh water generator 1 is constructed by assembling the water generating device body 100 in the system of the steam turbine device 50. One example of the steam turbine device 50 is provided with a boiler 51, a turbine group 52, a genus wheel condensing profit 53, a ground condenser 54, a water supply heater 55, and a degasser 56, and these constituent elements are by a circulation path. 60 and connected. The boiler 51 burns a fuel such as heavy oil 'liquefied natural gas, and generates steam from the supply water, and supplies it to the turbine group 52. The turbine group 52 is a group of steam turbines composed of, for example, a high pressure turbine and a low pressure turbine, and generates power for rotating a ship's pusher or the like. The turbine condenser 53 can cool the steam discharged from the turbine group 52 by seawater or the like to generate turbine condensate. The generated turbine condensate is heated by a part of the steam introduced into the thirsty wheel group 52 by the operation of the pump 61 through the base condenser 54 and the water supply heater 55, and then introduced into the deaerator 56 to remove oxygen. Wait. The turbine condensate stored in the degasser 56 is supplied to the boiler 51 by the operation of the pump 62 to be vaporized, and circulated to the circulation path 60. The steam turbine device 50 is preferably mounted on a steam turbine ship, for example, but the application is not particularly limited, and for example, it may be used for power generation. The fresh water generator body 100 is sandwiched between the pump 61 and the base condenser 54 via the branch path 63 in the steam turbine device 5 having the above configuration, and will pass through the circulation path 6 as will be described later. Turbine condensate is used as cold water for water production. The flow rate of the turbulent water supplied to the main body of the fresh water generator unit 1 can be adjusted by operating the regulating valve 6 4 6 201235304 provided in the circulation path 6 。. The fresh water generator body 100 may be directly inserted in the middle of the circulation path 60 instead of being diverted from the circulation path 60 as in the present embodiment. Fig. 2 is a system diagram of the water generator body 100. As shown in Fig. 2, the fresh water generator main body 100 includes a heater 10 that heats seawater as raw material water to generate steam, and the evaporator 20 is a concentrated raw material such as steam and brine (concentrated seawater). The water separator; and the rehydrator 30 are those that cool the water vapor to generate steam. The heater 10 has a raw material water inlet port 11 and a water vapor/salt water outlet 12 that can respectively introduce and discharge raw material water, and a warm water inlet port 13 and a warm water drain that respectively introduce and discharge warm water such as cooling water for the engine water jacket of the ship. At the outlet 14, the raw material water introduced from the raw material water introduction port 11 is heated by the warm water introduced from the warm water introduction port 13 to be evaporated, and then discharged from the steam/salt outlet 12. The heater 10 is preferably a plate heat exchanger similarly to the water reclaimer 30 to be described later, but the type of the heat exchanger is not particularly limited. Further, the heating source of the water vapor is not limited to being warm water, and may be, for example, a vapor, a combustion heater or an electric heater. The evaporator 20 has a heating raw material water introduction port 21 for introducing the heated raw material water discharged from the steam/salt water outlet 12, and a vapor discharge port 22 for discharging the water vapor generated by the raw material water; The brine discharge port 23 is a person who discharges residual brine. The rehydrator 30 includes a vapor introduction port 31 for introducing water vapor discharged from the vapor discharge port 22, and a distilled water discharge port 32 for discharging distilled water obtained by cooling the steam; respectively, introducing and discharging the steam for cooling The cooling water introduction port 33 and the cooling water discharge port 34 of the cooling water are introduced, and the raw material water introduction port 35 and the raw material water discharge port 36 which discharge the raw material water of the same vapor are discharged, respectively, and 7 201235304. At the cooling water introduction port 33, the turbine condensate of the steam turbine device 5 shown in Fig. 导入 is introduced as cooling water, and the cooling water discharged from the cooling water discharge port 34 is returned to the circulation of the steam turbine device 5〇. Path 60. The turbine condensate which becomes the cooling water is usually high-purity water, so the partitioning member 37 is provided in the rehydrator 3 so that the cooling water and the raw material water do not mix. The water separator 3 is separated into a jth hot parent converter 310 for exchanging heat between water vapor and cooling water, and a second heat exchanger 320 for exchanging heat between water vapor and raw material water by the crucible partition member 37. The cooling water does not have to be clean water, and it may be other coolant than the raw water. In the raw material water introduction port 35, seawater is introduced as raw material water by the operation of the other system or the jet pump 41, and the raw material water discharged from the raw material water discharge port 36 is introduced into the raw material water introduction port 11 of the heater 1. In addition to the solid yoke type seawater, raw water can be used for tap water, rainwater, groundwater, river water, industrial drainage, and domestic drainage. The raw material water supplied from the jet pump 41 can also be used as the driving water of the water ejector 40, and the evaporator 20 and the rehydrator 3 使 attract the non-condensed gas by being connected to the maximum negative pressure portion of the water ejector 40. While maintaining a vacuum. The distilled water strip discharged from the distilled water discharge port 32 is purely clear (not shown. The rehydrator 30 of the present embodiment is constituted by a plate heat exchanger. As shown in the perspective view of the important part of Fig. 3, the rehydration In the case of the two end plates lu and 112, the two types of heat transfer plates 113 & U3b ' are arranged in a plurality of layers, and the edge portions are joined by the connecting rods 30a and 30b. In addition, in Fig. 3 In 201235304, in order to make the structure easy to understand, one end plate 111 is shown by a broken line. Each of the heat transfer plates 113a and 113b is formed in a rectangular shape, and is disposed between two heat transfer plates 113b and 113b disposed adjacent to the center in the stacking direction. The partition member 37 is provided. The heat transfer plates 113a and 113b are separated into two plate groups by the partition member 37. The partition member 37 of the present embodiment is configured to seal the heat transfer plate 113a by the port plug 37a, The opening of the thick plate of 113b can exhibit a high pressure resistance even in the case where the cooling water is high-pressure turbine condensate, and can surely prevent the cooling water from mixing with the raw material water. However, the constitution of the partition member 37 Not limited to this embodiment For example, as shown in Fig. 4, the partition member 37 may be constituted by two heat transfer plates 113a and 113b disposed adjacent to each other. The two heat transfer plates 113a constituting the partition member 37 shown in Fig. 4, 113b has the distillation flow ports 114 and 115 which will be described later, and the openings other than these are sealed by the port plug 37a. In Fig. 4, the same components as those of the first figure in Fig. 4 are shown. The vapor inlet port 31 and the distilled water discharge port 32 are respectively formed on one of the opposite ends of one of the end plates 111. The heat transfer plates 113a and 113b correspond to the vapor introduction port 31 and the distilled water discharge port 32. Distillation flow ports 114 and 115 are formed at the respective positions, and a vapor introduction port 31 is connected to the flow path formed by each distillation flow port 114, and a distilled water discharge port is connected to the flow path formed by each distillation flow port 115. 32. The cooling water introduction port 33 and the cooling water discharge port 34 are respectively formed at opposite corners of the other one of the end plates 111. Each of the plate groups disposed between one of the end plates 111 and the partition member 37 is formed. Heat transfer plates 113a, 113b, at At the positions of the cooling water introduction port 33 and the cooling water discharge port 34, the cooling water circulation ports 116 and 117 are formed in the form of 2012, 2012, and the water is discharged from the mouth of the mountain. The water (4) is called the division of the other side of the square, and the other side of the square, which is disposed between the other side of the plate 112 and the partition member 37. The hot plates (1) a and 113b' are formed with raw material water flows π118 and 119 at positions corresponding to the raw material water introduction port 35 and the raw material water discharge port, respectively, and the raw material water is connected by the raw material water circulation port m (four) red flow path. Σ35, the raw material water discharge port 36 is connected to the flow path formed by the flow of the raw material 卩119. The partition member 37 has the steaming chamber circulation ports 114 and 115. On the other hand, as described above, the opening corresponding to the cooling water circulation ports 116 and 117 and the raw material water outlet ports 118 and 119 is sealed by the port plug 37a. Each of the heat transfer plates 113a and 113b is formed with a groove portion 120a and 120b on one hand, and a groove portion i2〇a of the heat transfer plate U3a communicates between the two steam supply ports 114 and 115, and on the other hand, two cooling water flow ports 116. In between, or between two raw material water outlets 118, 119 are isolated. Further, the groove portion 120b of the heat transfer plate 113b separates between the two steam flow ports 114 and 115, and the two cooling water flow ports 116 and 117 or the two raw material water flow ports us and 119 communicate with each other. The adjacent heat transfer plates 113a and 113b are sealed by a gasket (not shown). In addition, in FIG. 3, in order to make it easy to understand, the flow path formed in the lamination direction of the heat transfer plates U3a and 113b shows the part which communicates with the groove parts 120a and 120b by the broken line, and shows the part isolate|separated from the groove part 120a and 120b by the solid line. . By the above-described structure of the rehydrator 30, between the one end plate 111 and the partition structure 201235304, the water vapor and the cooling water introduced from the steam introduction port 31 and the cooling water introduction port 33 respectively flow through the heat transfer plates. Since the groove portion i2〇a of the 113a and the groove portion 120b of the heat transfer plate 113b, the water vapor and the cooling water alternately pass between the adjacent heat transfer plates 113a and 113b as viewed in the stacking direction of the heat transfer plates 113a and 113b. As a result, heat exchange between the water vapor and the cooling water is transmitted through the heat transfer plates 113a and 113b. This portion functions as the first heat exchanger 31. The distilled water and the cooling water which are formed by the heat exchange are discharged from the distilled water discharge port 32 and the cooling water discharge port 34, respectively. Between the other end plate 112 of the rehydrator 30 and the partition member 37, the raw material water introduced from the raw material water introduction port 35 flows through the groove portion 120b of the heat transfer plate 113b, so that the heat transfer plates 113a and 113b are used. In the direction of the lamination, the water vapor and the raw material water alternately pass between the adjacent heat transfer plates n3a, 113b. As a result, heat exchange is performed between the steam and the raw material water through the heat transfer plates 113a and 113b, and this portion functions as the second heat exchanger 320. The raw material water heated by the end of the heat exchange is discharged from the raw material water discharge port 36. According to the water-making device having the above-described structure, the cooling water introduced from the end plate 111 of one of the recirculation devices 30 through the cooling water introduction port 33 and the raw material introduced through the raw material water introduction port 35 from the other end plate 112 are introduced. The water exchanges heat with the steam in the first heat exchanger 310 and the second heat exchanger 320, whereby the water can be formed by steaming. Therefore, it is conventionally known that only the cooling water and the steam are exchanged. The configuration makes it easier to condense water vapor, which improves the efficiency of the rehydrator 30. In addition, since the raw material water heated by the heat exchange with the water vapor is introduced into the second heat exchanger 320, the raw material water introduced into the heater 1 can be evaporated in the initial stage to enhance the heat exchange. Efficiency 11 201235304 rate, can achieve energy saving. The temperature of the raw material water introduced into the heater 10 can be appropriately adjusted by selecting the number of the heat transfer plates ii3a, 113b provided in the rehydrator 3 or the position of the partition member 37. The above-described effects of the fresh water generator 1 can be particularly remarkable when the turbine condensate of the steam turbine device 50 is used as the cooling water as in the present embodiment, even if the steam condensate is higher than the steam temperature. High temperatures also make it easy to ensure the amount of water needed. However, the cooling water introduced into the rehydrator 30 does not necessarily have to be limited to the turbine condensate of the steam turbine unit 5, for example, 'the condensed water generated by other vapor circulation systems may be used, or by using steam as a heat source or power. The source generates and maintains high temperature and is used for drain water of other uses. Further, in the present embodiment, since the first heat exchanger 310 and the second heat exchanger 320 are integrated so that the cooling water and the raw material water are not mixed, the structure can be miniaturized and the complex can be improved. The efficiency of the water 30. Specifically, the first heat exchanger 310 and the second heat exchanger 320 may be arranged side by side in the stacking direction of the heat transfer plates 113a and 113b. In the embodiment, the water vapor introduced into the rehydrator 3 is initially introduced into the first heat exchanger 310, and the remaining water vapor is introduced into the second heat exchanger 320. However, the arrangement of the first heat exchanger 310 and the second heat exchanger 320 is not limited to the embodiment, and for example, the cooling water introduction port 33 and the cooling water discharge port 34 may be provided in the other. In the end plate in, the raw material water introduction port 35 and the raw material water discharge port 36 are provided in one end plate iu. Further, the first heat exchanger 310 and the second heat exchanger 320 are preferably formed by a plate heat exchanger as in the present embodiment, but other heat exchangers such as a shell tube type 12 201235304 may be used. Further, the first heat exchanger 310 and the second heat exchanger 320 do not have to be integrated, and may be separated from each other. The first heat exchanger 310 and the second heat exchanger 320 may be configured to introduce the water vapor streams into the first heat exchanger 310 and the second heat exchanger 320, respectively. I: BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a system diagram of a water-making apparatus according to an embodiment of the present invention. Fig. 2 is a system diagram showing an important part of the water generator shown in Fig. 1. Fig. 3 is a perspective view of an important part of the water generating device shown in Fig. 1. Fig. 4 is a perspective view showing an important part of a water generating device of another embodiment of the present invention. Figure 5 is a system diagram of a conventional water making device. [Description of main component symbols] 1...Water generator 31...Vapor introduction port 10...Heater 32...Distilled water discharge port 11...Material water inlet port 33...Cooling water inlet port 12.. Water vapor • Brine outlet 34... Cooling water discharge port 13... Warm water inlet 35... Raw material water inlet 14... Warm water outlet 36... Raw water outlet 20... Evaporator 37... partition member 21: heating raw material water introduction port 37a.. port plug 22... steam discharge port 40... water ejector 23... brine discharge port 41... jet pump 30... Rehydrator 42...distillation water pump 30a, 30b...connecting rod 50...vapor turbine equipment 13 201235304 51...boiler 95...condenser 52...turbine group 96...warm sea water 53 ... turbo condenser 97... evaporator 54... basic condenser 98... fresh water 55... water supply heater 100... water generator body 56... degasser 111, 112. .. end plate 60...circulation paths 113a, 113b...heat transfer plates 61, 62··· pumps 114, 115...distillation port 91...thirsty wheel 120a, HOb....groove 92... Rehydrator 310...first heat exchanger 93...cold seawater 320...second heat exchanger 94...condensate 14