TWI617342B - Vacuum evaporation water generator - Google Patents
Vacuum evaporation water generator Download PDFInfo
- Publication number
- TWI617342B TWI617342B TW101140980A TW101140980A TWI617342B TW I617342 B TWI617342 B TW I617342B TW 101140980 A TW101140980 A TW 101140980A TW 101140980 A TW101140980 A TW 101140980A TW I617342 B TWI617342 B TW I617342B
- Authority
- TW
- Taiwan
- Prior art keywords
- seawater
- water
- condenser
- cooling
- preheater
- Prior art date
Links
Classifications
-
- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F1/00—Treatment of water, waste water, or sewage
- C02F1/02—Treatment of water, waste water, or sewage by heating
- C02F1/04—Treatment of water, waste water, or sewage by heating by distillation or evaporation
- C02F1/046—Treatment of water, waste water, or sewage by heating by distillation or evaporation under vacuum produced by a barometric column
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63J—AUXILIARIES ON VESSELS
- B63J1/00—Arrangements of installations for producing fresh water, e.g. by evaporation and condensation of sea water
-
- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F1/00—Treatment of water, waste water, or sewage
- C02F1/02—Treatment of water, waste water, or sewage by heating
- C02F1/04—Treatment of water, waste water, or sewage by heating by distillation or evaporation
- C02F1/043—Details
-
- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F2103/00—Nature of the water, waste water, sewage or sludge to be treated
- C02F2103/08—Seawater, e.g. for desalination
-
- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F2201/00—Apparatus for treatment of water, waste water or sewage
- C02F2201/001—Build in apparatus for autonomous on board water supply and wastewater treatment (e.g. for aircrafts, cruiseships, oil drilling platforms, railway trains, space stations)
-
- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F2201/00—Apparatus for treatment of water, waste water or sewage
- C02F2201/002—Construction details of the apparatus
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A20/00—Water conservation; Efficient water supply; Efficient water use
- Y02A20/124—Water desalination
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Hydrology & Water Resources (AREA)
- Environmental & Geological Engineering (AREA)
- Water Supply & Treatment (AREA)
- Organic Chemistry (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Heat Treatment Of Water, Waste Water Or Sewage (AREA)
- Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
Abstract
本發明係提供一種熱效率優異之真空蒸發式造水裝置。真空蒸發式造水裝置係具備:加熱器,係藉由來自熱源的熱將被供給之原料海水加熱而生成蒸氣者;容器本體,係將加熱器所產生之蒸氣導入者;減壓機構(水噴射器),係將容器本體內減壓者;冷凝器,係藉由冷卻用海水將容器本體內的蒸氣冷卻並生成淡水者;與預熱器,係藉由容器本體內之蒸氣將自冷凝器所排出之冷卻用海水的一部分加熱而作為原料海水供給至加熱器者。冷凝器及預熱器之至少一者的各傳熱管係內面或外面經凹凸加工。 The present invention provides a vacuum evaporation type water generating device excellent in thermal efficiency. The vacuum evaporating water generator includes a heater that heats the supplied raw material seawater by heat from a heat source to generate steam; the container body introduces steam generated by the heater; and the pressure reducing mechanism (water The ejector is a person who decompresses the inside of the container; the condenser cools the vapor in the container body by cooling seawater to generate fresh water; and the preheater is self-condensing by the vapor in the container body A part of the seawater for cooling discharged from the apparatus is heated and supplied to the heater as raw material seawater. The inner surface or the outer surface of each heat transfer tube of at least one of the condenser and the preheater is processed by the concavities and convexities.
Description
本發明係有關於一種用於從海水製造淡水的真空蒸發式造水裝置,特別是有關於一種具備預熱器之真空蒸發式造水裝置。 The present invention relates to a vacuum evaporation type water generating device for producing fresh water from seawater, and more particularly to a vacuum evaporation type water generating device having a preheater.
一般在海上運行的船舶,利用來自船舶所搭載之鍋爐的蒸氣或來自柴油機或其他機械的廢熱作為熱源,使汲取自海中的海水在高真空下蒸發來製造淡水,一直以來都是藉此來進行。該種真空蒸發式造水裝置,一般而言,係具備:加熱器,係藉由將所供給之原料海水與柴油機之冷卻等所使用的溫水之熱交換來加熱而使其蒸發者;與容器本體,係藉由減壓機構使內部保持在減壓(真空)狀態,並將所產生之蒸氣凝結而淡水化者。在容器本體內,係內藏有具複數傳熱管之冷凝器,藉由將蒸氣與流過傳熱管內部之冷卻用海水的熱交換使其冷卻/凝結來淡水化。又,將從冷凝器所排出之冷卻用海水之一部分,作為原料海水供給至加熱器。 Generally, ships operating at sea use steam from boilers carried by ships or waste heat from diesel engines or other machinery as a heat source to evaporate seawater extracted from the sea under high vacuum to produce fresh water, which has been used for this purpose. . In general, the vacuum evaporation type water generator includes a heater that is heated by heat exchange between warm water used for cooling the supplied raw material seawater and a diesel engine, and the like; The container body is maintained in a reduced pressure (vacuum) state by a pressure reducing mechanism, and the generated steam is condensed and desalinated. In the container body, a condenser having a plurality of heat transfer tubes is housed, and is cooled and condensed by heat exchange with cooling seawater flowing through the inside of the heat transfer tubes to be desalinated. Further, a part of the seawater for cooling discharged from the condenser is supplied to the heater as raw material seawater.
供給至加熱器之原料海水藉由與冷凝器之蒸氣 的熱交換,其溫度多少會變高,但相較於海水的蒸發溫度仍然頗低。因此,在上述結構之真空蒸發式造水裝置中,就無法有效率地進行加熱器之原料海水的加熱/蒸發。緣此,提案有一真空蒸發式造水裝置(例如參照專利文獻1),其具備一預熱器,係將從冷凝器所排出之冷卻用海水(原料海水)在進一步加熱後,供給至加熱器者。 The raw material supplied to the heater, the seawater, and the vapor of the condenser The heat exchange, its temperature will become higher, but the evaporation temperature is still relatively low compared to seawater. Therefore, in the vacuum evaporation type water generator of the above configuration, heating/evaporation of the raw material seawater of the heater cannot be efficiently performed. Therefore, there is proposed a vacuum evaporation type water generator (see, for example, Patent Document 1), which is provided with a preheater for supplying cooling water (raw water) discharged from a condenser to a heater after further heating. By.
在專利文獻1之真空蒸發式造水裝置中,在冷凝器上方係設有與冷凝器相同結構之多管式預熱器。從冷凝器被導入預熱器之傳熱管內的冷卻用海水,係藉由與在容器本體內所產生之蒸氣的熱交換進一步被加熱,而在較高溫的狀態下作為原料海水被供給至加熱器。藉此,在專利文獻1之真空蒸發式造水裝置中,便可謀求加熱器之熱效率的提高,並能謀求裝置整體的小型化。 In the vacuum evaporation type water generator of Patent Document 1, a multi-tube type preheater having the same structure as that of the condenser is provided above the condenser. The seawater for cooling introduced into the heat transfer tube of the preheater from the condenser is further heated by heat exchange with the steam generated in the container body, and is supplied as raw material seawater to the higher temperature state. Heater. As a result, in the vacuum evaporation type water generator of Patent Document 1, it is possible to improve the thermal efficiency of the heater and to reduce the size of the entire apparatus.
專利文獻1:日本專利特開平6-254534號公報 Patent Document 1: Japanese Patent Laid-Open No. Hei 6-254534
然而,在專利文獻1之真空蒸發式造水裝置中,係為了謀求加熱器之熱效率的提高而構成如斯,即藉由設置預熱器,將供給至加熱器之原料海水的溫度較為提高;但因未特別針對構成預熱器(甚至冷凝器)之各傳熱管之傳熱性能的提高有所探討,故在該點上還有改良的餘地。 However, in the vacuum evaporation type water generator of Patent Document 1, in order to improve the thermal efficiency of the heater, the temperature of the seawater supplied to the heater is increased by providing a preheater; However, there is still room for improvement in this point because the heat transfer performance of each of the heat transfer tubes constituting the preheater (or even the condenser) is not particularly discussed.
本發明係著眼於上述課題而完成者,其目的在於提供一種熱效率優異之真空蒸發式造水裝置。 The present invention has been made in view of the above problems, and an object thereof is to provide a vacuum evaporation type water generator which is excellent in thermal efficiency.
本發明之上述目的係藉由下述真空蒸發式造水裝置來達成;該真空蒸發式造水裝置係利用來自搭載於船舶之熱源的熱,從取進船舶之海水製造淡水,且該真空蒸發式造水裝置係具備:加熱器,係藉由來自熱源的熱將被供給之原料海水加熱而生成蒸氣者;容器本體,其係密閉型,且係使以前述加熱器所產生之蒸氣被導入者;減壓機構,係將前述容器本體內減壓者;冷凝器,係具有複數傳熱管,藉由冷卻用海水將前述容器本體內之蒸氣冷卻而生成淡水者;與預熱器,係具有複數的傳熱管,藉由前述容器本體內之蒸氣將自前述冷凝器所排出之冷卻用海水的一部分加熱,而作為原料海水供給至前述加熱器者;且前述冷凝器及前述預熱器之至少一者的前述各傳熱管係內面或外面經凹凸加工者。 The above object of the present invention is achieved by a vacuum evaporation type water generator which uses fresh heat from a heat source mounted on a ship to produce fresh water from seawater taken into the ship, and the vacuum evaporation The water generator includes a heater that heats the supplied raw material seawater by heat from a heat source to generate steam, and the container body is sealed, and the steam generated by the heater is introduced. The pressure reducing mechanism is a body for decompressing the inside of the container; the condenser has a plurality of heat transfer tubes, and the steam in the container body is cooled by cooling seawater to generate fresh water; and the preheater is a plurality of heat transfer tubes that are heated by a portion of the cooling seawater discharged from the condenser by the vapor in the container body, and supplied to the heater as raw material seawater; and the condenser and the preheater At least one of the heat transfer tubes on the inner surface or the outer surface of the heat transfer tube is processed by a concavo-convex process.
在本發明之較佳實施態樣中,在前述冷凝器與前述預熱器之間,設有將從前述冷凝器所排出之冷卻用海水之一部分升壓以供給至前述預熱器的輔助泵。 In a preferred embodiment of the present invention, between the condenser and the preheater, an auxiliary pump that boosts a portion of the cooling seawater discharged from the condenser to be supplied to the preheater is provided. .
在本發明之更佳的實施態樣中,備有用於將冷卻用海水供給至前述冷凝器之泵,前述泵係用於將從海所汲取之海水供給至包含柴油機之船舶的各海水使用處的海水泵。 In a further preferred embodiment of the present invention, there is provided a pump for supplying cooling seawater to the condenser, wherein the pump is used for supplying seawater extracted from the sea to each seawater use vessel of a diesel engine. Sea water pump.
在本發明之較佳的其他實施態樣中,備有用於將 冷卻用海水供給至前述冷凝器之泵,前述減壓機構係受海水所驅動之水噴射器,且前述泵係用於將驅動用海水供給至前述水噴射器之噴射泵,將由前述水噴射器所排出之驅動用海水作為冷卻用海水而供給至前述冷凝器。 In other preferred embodiments of the present invention, a pump for supplying cooling water to the condenser, wherein the pressure reducing mechanism is a water ejector driven by seawater, and the pump is used to supply a driving seawater to an injection pump of the water ejector, and the water ejector The discharged driving seawater is supplied to the condenser as cooling seawater.
在上述實施態樣之真空蒸發式造水裝置中,前述傳熱管係宜由波形管所構成。或者,前述傳熱管係宜藉由在內面或外面以一體的方式設有突起或溝來進行凹凸加工。 In the vacuum evaporation type water generator of the above embodiment, the heat transfer tube is preferably composed of a corrugated tube. Alternatively, it is preferable that the heat transfer tube is provided with a projection or a groove integrally formed on the inner surface or the outer surface to perform uneven processing.
又,在本發明之較佳的其他實施態樣中,前述減壓機構係受海水所驅動之水噴射器,並進一步具備係用於朝前述水噴射器供給驅動用海水之噴射泵;前述噴射泵係將自前述冷凝器所排出之冷卻用海水的一部分升壓以供給至前述水噴射器且供給至前述預熱器。在該實施態樣中,係進一步具備用於將冷卻用海水供給至前述冷凝器之泵,前述泵宜為海水泵,係用於將汲取自海上的水供給至包含柴油機在內之船舶的各海水使用處。又,前述傳熱管更宜藉由在內面或外面以一體的方式設有突起或溝來進行凹凸加工。 Further, in another preferred embodiment of the present invention, the pressure reducing mechanism is a water ejector driven by seawater, and further includes an injection pump for supplying driving seawater to the water ejector; The pump system boosts a part of the cooling seawater discharged from the condenser to be supplied to the water injector and to the preheater. In this embodiment, a pump for supplying cooling seawater to the condenser is further provided, and the pump is preferably a sea water pump for supplying water extracted from the sea to each of ships including a diesel engine. Sea water use. Further, it is preferable that the heat transfer tube is provided with a projection or a groove integrally formed on the inner surface or the outer surface to perform the uneven processing.
進一步,在上述之所有實施態樣之真空蒸發式造水裝置中,前述加熱器具有內部可導入原料海水之複數加熱管;前述各加熱管係以內面或外面經凹凸加工者為佳。 Further, in the vacuum evaporating water-making apparatus of all the above-described embodiments, the heater has a plurality of heating tubes into which the raw material seawater can be introduced, and each of the heating tubes is preferably an inner surface or an outer surface.
依據本發明之真空蒸發式造水裝置,由於係將冷凝器及預熱器之至少一者的各傳熱管之內面或外面凹凸加工之故,可提高各傳熱管的傳熱性能。因此,從預熱器被供給至加熱器之原料海水的溫度,相較於以平滑管來構成 各傳熱管之已有的真空蒸發型造水裝置,較能達到高溫。 According to the vacuum evaporating water-making apparatus of the present invention, since the inner surface or the outer surface of each of the heat transfer tubes of at least one of the condenser and the preheater is processed, the heat transfer performance of each heat transfer tube can be improved. Therefore, the temperature of the seawater of the raw material supplied from the preheater to the heater is compared with that of the smooth tube The existing vacuum evaporation type water generating device of each heat transfer tube can reach a high temperature.
1‧‧‧真空蒸發式造水裝置 1‧‧‧Vacuum evaporative water generator
2‧‧‧容器本體 2‧‧‧ container body
3‧‧‧加熱器 3‧‧‧heater
4‧‧‧冷凝器 4‧‧‧Condenser
5‧‧‧預熱器 5‧‧‧Preheater
6‧‧‧裝置本體 6‧‧‧ device body
7‧‧‧減壓機構(水噴射器) 7‧‧‧Relief mechanism (water jet)
8‧‧‧噴射泵 8‧‧‧jet pump
9‧‧‧輔助泵 9‧‧‧Auxiliary pump
9A‧‧‧第1管集箱 9A‧‧‧1st tube header
9B‧‧‧第2管集箱 9B‧‧‧2nd tube header
10‧‧‧船舶船體 10‧‧‧Ship hull
11‧‧‧海水泵 11‧‧‧ sea water pump
12‧‧‧海水供給通道 12‧‧‧Seawater supply channel
13‧‧‧冷卻水供給通道 13‧‧‧Cooling water supply channel
14‧‧‧分支通道 14‧‧‧ branch channel
15、19‧‧‧給水通道 15, 19‧‧‧ water supply channel
16‧‧‧原料海水供給通道 16‧‧‧ Raw material seawater supply channel
17‧‧‧氣體通道 17‧‧‧ gas passage
18‧‧‧鹽水排出通道 18‧‧‧ brine discharge channel
30‧‧‧加熱室 30‧‧‧heating room
31‧‧‧加熱管 31‧‧‧heat pipe
32‧‧‧海水供給室 32‧‧‧Seawater supply room
33‧‧‧原料海水導入口 33‧‧‧ Raw material seawater inlet
34‧‧‧溫水導入口 34‧‧‧Warm water inlet
35‧‧‧溫水排出口 35‧‧‧Warm water discharge
40、50‧‧‧傳熱管 40, 50‧‧‧ heat transfer tube
41、51‧‧‧管壁 41, 51‧‧‧ wall
42、52‧‧‧凸部 42, 52‧‧ ‧ convex
43、53‧‧‧凹部 43, 53‧‧ ‧ recess
90A、90B、93A、93B、98A、98B‧‧‧隔板 90A, 90B, 93A, 93B, 98A, 98B‧‧ ‧ partition
91A、91B‧‧‧預熱用管集箱室 91A, 91B‧‧‧ Preheating tube box room
92A、92B‧‧‧凝結用管集箱室 92A, 92B‧‧‧Condensation tube box room
94a‧‧‧冷卻水入口室 94a‧‧‧Cooling water inlet room
94b、99e‧‧‧近側折返室 94b, 99e‧‧‧ proximal reentry room
94c、99c‧‧‧內側折返室 94c, 99c‧‧‧ inside reentry room
94d‧‧‧冷卻水出口室 94d‧‧‧Cooling water outlet room
95‧‧‧冷卻水入口 95‧‧‧Cooling water inlet
96‧‧‧淡水出口 96‧‧‧ Freshwater exports
97‧‧‧冷卻水出口 97‧‧‧Cooling water outlet
99a‧‧‧原料海水入口室 99a‧‧‧ Raw seawater entrance room
99b、99d‧‧‧中央折返室 99b, 99d‧‧‧ Central Reentry Room
100‧‧‧原料海水入口 100‧‧‧ Raw seawater inlet
101‧‧‧原料海水出口 101‧‧‧ Raw seawater exports
102‧‧‧排氣管 102‧‧‧Exhaust pipe
103‧‧‧鹽水出口 103‧‧‧Salt outlet
圖1係本發明之一實施型態的真空蒸發式造水裝置的概略圖。 BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic view showing a vacuum evaporation type water generator according to an embodiment of the present invention.
圖2係圖1之裝置本體的縱截面圖。 Figure 2 is a longitudinal sectional view of the apparatus body of Figure 1.
圖3係沿圖2 I-I線之截面圖。 Figure 3 is a cross-sectional view taken along line I-I of Figure 2.
圖4係沿圖2 Ⅱ-Ⅱ線之截面圖。 Figure 4 is a cross-sectional view taken along line II-II of Figure 2.
圖5(A)~(C)係傳熱管的截面圖。 5(A) to (C) are cross-sectional views of the heat transfer tubes.
圖6係其他實施型態之裝置本體的縱截面圖。 Fig. 6 is a longitudinal sectional view showing the apparatus body of another embodiment.
圖7(A)~(C)係加熱管的截面圖。 7(A) to (C) are cross-sectional views of a heating pipe.
圖8係本發明之其他實施型態之真空蒸發式造水裝置的概略結構圖。 Fig. 8 is a schematic block diagram showing a vacuum evaporation type water generator according to another embodiment of the present invention.
圖9係本發明之其他實施型態之真空蒸發式造水裝置的概略結構圖。 Fig. 9 is a schematic block diagram showing a vacuum evaporation type water generator according to another embodiment of the present invention.
圖10係本發明之其他實施型態之真空蒸發式造水裝置的概略結構圖。 Fig. 10 is a schematic block diagram showing a vacuum evaporation type water generator according to another embodiment of the present invention.
以下,針對本發明之實施型態,一邊參照附加圖示一邊說明。圖1係本發明之一實施型態之真空蒸發式造水裝置1概略結構圖,圖2係圖1之裝置本體6的縱截面圖。本實施型態之真空蒸發式造水裝置1係如圖1及圖2所示,具備裝置本體6,其係由密閉型的容器本體2、加熱器3、冷凝器4及預熱器5所構成者;與減壓機構7,其係將容器本體2保 持在減壓(真空)狀態者。再者,在圖1中,符號10係船舶的船體,符號11係設置於船舶內,用於將海水從海中汲取上來的海水泵。以海水泵11所汲取上來的海水,係被供給至各種海水使用處,例如除了供給至搭載於船舶內之柴油機,作為用於冷卻柴油機的缸套冷卻水之外,還會供給至冷凝器4,作為利用真空蒸發式造水裝置1來造水用的冷卻水。 Hereinafter, the embodiments of the present invention will be described with reference to the accompanying drawings. 1 is a schematic structural view of a vacuum evaporation type water generator 1 according to an embodiment of the present invention, and FIG. 2 is a longitudinal sectional view of the apparatus body 6 of FIG. As shown in FIGS. 1 and 2, the vacuum evaporating water-making apparatus 1 of the present embodiment includes an apparatus main body 6, which is composed of a sealed container main body 2, a heater 3, a condenser 4, and a preheater 5. a constituting body; and a pressure reducing mechanism 7, which protects the container body 2 Hold in the state of decompression (vacuum). Further, in Fig. 1, reference numeral 10 denotes a ship's hull, and reference numeral 11 is provided in a ship for extracting seawater from the sea. The seawater pumped up by the sea water pump 11 is supplied to various seawater use places. For example, it is supplied to the diesel engine mounted in the ship, and is supplied to the condenser 4 as cooling water for cooling the diesel engine. It is used as cooling water for water generation by the vacuum evaporation type water generator 1.
容器本體2係於下部連接有加熱器3,且於上部內藏有冷凝器4及預熱器5。又,在容器本體2的上部,設有排氣管102,且在較下部加熱器3高的位置,設有鹽水出口103。 The container body 2 has a heater 3 connected to the lower portion, and a condenser 4 and a preheater 5 are housed in the upper portion. Further, an exhaust pipe 102 is provided in the upper portion of the container body 2, and a brine outlet 103 is provided at a position higher than the lower heater 3.
排氣管102係透過氣體通道17連接至減壓機構7。減壓機構7在本實施形態中係由水噴射器所構成,容器本體2內部之不凝結性氣體係自排氣管102受到水噴射器7所吸引,使容器本體2內保持在較大氣壓低的減壓(真空)狀態,在容器本體2中,在減壓(真空)狀態下進行後述之原料海水的蒸發/凝結。又,鹽水出口103係透過鹽水排出通道18連接至水噴射器7,在後述的容器本體2內,已蒸發後之鹽水(海水)自鹽水出口103受水噴射器7所吸引後,排出至船舶外。 The exhaust pipe 102 is connected to the pressure reducing mechanism 7 through the gas passage 17. In the present embodiment, the pressure reducing mechanism 7 is constituted by a water ejector, and the non-condensable gas system inside the container body 2 is sucked by the water ejector 7 from the exhaust pipe 102, so that the inside of the container body 2 is kept at a relatively low gas pressure. In the reduced pressure (vacuum) state, evaporation/condensation of the raw material seawater described later is performed in the container main body 2 under reduced pressure (vacuum). Further, the brine outlet 103 is connected to the water ejector 7 through the brine discharge passage 18, and the evaporated brine (seawater) is sucked from the brine outlet 103 by the water ejector 7 in the container body 2 to be described later, and then discharged to the vessel. outer.
加熱器3係具備密閉型的加熱室30與設於加熱室30內之複數的加熱管31。複數的加熱管31係以朝沿垂直方向延伸的方式來配置,其兩端部係連接於加熱室30的上壁面及下壁面。在加熱室30的下部,連接有海水供給室32,在海水供給室32係設有用於將原料海水導入各加熱管31之 原料海水導入口33。在加熱室30的側壁面,係設有溫水導入口34及溫水排出口35,係將用於柴油機卻等缸套冷卻水等的溫水分別導入及排出。自原料海水導入口33導入至各加熱管31之原料海水,係藉由與從溫水導入口34被導入加熱室30內的溫水之熱交換來加熱而蒸發,形成蒸氣後被供給至容器本體2內。 The heater 3 includes a sealed heating chamber 30 and a plurality of heating tubes 31 provided in the heating chamber 30. The plurality of heating pipes 31 are arranged to extend in the vertical direction, and both end portions thereof are connected to the upper wall surface and the lower wall surface of the heating chamber 30. A seawater supply chamber 32 is connected to a lower portion of the heating chamber 30, and a seawater supply chamber 32 is provided with a raw material seawater for introducing the heating pipes 31. Raw material seawater introduction port 33. The warm water inlet port 34 and the warm water discharge port 35 are provided on the side wall surface of the heating chamber 30, and the warm water such as the cylinder liner cooling water for the diesel engine is introduced and discharged. The raw material seawater introduced into the heating pipes 31 from the raw material seawater inlet 33 is heated by heat exchange with warm water introduced into the heating chamber 30 from the warm water inlet 34, and is vaporized to be supplied to the vessel. Inside the body 2.
冷凝器4係用於將供給至容器本體2內的蒸氣冷卻而生成淡水者,其具備複數的傳熱管40,與第1管集箱9A及第2管集箱9B,其係與將前述複數傳熱管40捆束而成之傳熱管群的兩端分別連通者。各傳熱管40係以朝水平方向延伸的方式配置,其兩端部係連接至容器本體2之左壁面及右壁面。 The condenser 4 is for cooling the steam supplied into the container main body 2 to generate fresh water, and includes a plurality of heat transfer tubes 40, and the first tube header 9A and the second tube header 9B. The two ends of the heat transfer tube group bundled by the plurality of heat transfer tubes 40 are respectively connected. Each of the heat transfer tubes 40 is disposed to extend in the horizontal direction, and both end portions thereof are connected to the left wall surface and the right wall surface of the container body 2.
在冷凝器4的上方,設有構成預熱器5之複數的傳熱管50。該複數的傳熱管50係以朝水平方向延伸的方式配置,其兩端部係連接至容器本體2的左壁面及右壁面,並與第1管集箱9A及第2管集箱9B連通。 Above the condenser 4, a plurality of heat transfer tubes 50 constituting the preheater 5 are provided. The plurality of heat transfer tubes 50 are arranged to extend in the horizontal direction, and both end portions are connected to the left wall surface and the right wall surface of the container body 2, and are connected to the first tube header 9A and the second tube header 9B. .
在第1及第2管集箱9A、9B內,分別設有隔板90A、90B。兩管集箱9A、9B內係由各隔板90A、90B,劃分為上方的預熱用管集箱室91A、91B與下方的凝結用管集箱室92A、92B。預熱用管集箱室91A、91B係與構成預熱器5之各傳熱管50連通,而凝結用管集箱室92A、92B係與構成冷凝器4之各傳熱管40連通。 Separators 90A and 90B are provided in the first and second tube headers 9A and 9B, respectively. The two pipe headers 9A and 9B are divided into upper preheating pipe header chambers 91A and 91B and lower condensation pipe header chambers 92A and 92B by the respective partition plates 90A and 90B. The preheating tube header chambers 91A and 91B communicate with the respective heat transfer tubes 50 constituting the preheater 5, and the condensation tube header chambers 92A and 92B communicate with the respective heat transfer tubes 40 constituting the condenser 4.
在各凝結用管集箱室92A、92B內,如圖3所示,係分別設有隔板93A、93B。第1管集箱9A之凝結用管集箱 92A內係由隔板93A劃分為內側的冷卻水入口室94a與近側的折返室94b。又,第2管集箱9B之凝結用管集箱92B內係由隔板93B劃分為近側的冷卻水出口室94d與內側的折返室94c。 In each of the condensation tube header chambers 92A and 92B, as shown in Fig. 3, partition plates 93A and 93B are provided, respectively. Condensation tube header box of the first tube header box 9A The inside of the 92A is divided into a cooling water inlet chamber 94a on the inner side and a folding chamber 94b on the side in the inner side by the partition plate 93A. Further, the inside of the condensation header 92B of the second header 9B is partitioned by the partition plate 93B into a proximal cooling water outlet chamber 94d and an inner folded chamber 94c.
在冷卻水入口室94a,設有用於導入冷卻用海水之冷卻水入口95,該冷卻用海水係用於將容器本體2內之蒸氣冷卻/凝結者。在冷卻水入口95係連接有冷卻水供給通道13,其係連接於從海水泵11至船舶內各海水使用處之海水供給通道12者(參照圖1),藉由海水泵11之作動而將海水導入作為冷卻水。在冷卻水入口室94a所導入之冷卻用海水係將在各傳熱管40內,如圖3之箭頭所示,中繼通過各折返室94b、94c,往另側的第2管集箱9B之冷卻水出口室94d的方向流動。被供給至容器本體2內的蒸氣,係利用與各傳熱管40所流動之冷卻用海水的熱交換被冷卻而凝結,藉由凝結而產生的淡水係自設於容器本體2之淡水出口96取出。 The cooling water inlet chamber 94a is provided with a cooling water inlet 95 for introducing cooling seawater for cooling/condensing the steam in the container body 2. A cooling water supply passage 13 is connected to the cooling water inlet 95, and is connected to the seawater supply passage 12 from the sea water pump 11 to the seawater use point in the ship (refer to FIG. 1), and is activated by the sea water pump 11 Seawater is introduced as cooling water. The seawater for cooling introduced in the cooling water inlet chamber 94a is relayed in each of the heat transfer tubes 40, as indicated by the arrows in Fig. 3, through the respective folded-back chambers 94b and 94c, and to the other second header box 9B. The cooling water outlet chamber 94d flows in the direction. The steam supplied into the container main body 2 is cooled and condensed by heat exchange with the cooling seawater flowing through the respective heat transfer tubes 40, and the fresh water generated by the condensation is supplied from the fresh water outlet 96 of the container body 2. take out.
在冷卻水出口室94d,係設有用於將冷卻用海水排出之冷卻水出口97。從冷卻水出口97所排出的冷卻用海水,一部分係透過分支通道14供給至噴射泵8,另外一部分係透過給水通道15供給至預熱器5,剩餘的則被排出至船舶外(參照圖1)。噴射泵8係用於驅動水噴射器7者,與裝置本體6以一體的方式設置。供給至噴射泵8的冷卻用海水係利用噴射泵8來升壓後,被供給至水噴射器7,驅動水噴射器7後,被排出至船舶外。 A cooling water outlet 97 for discharging the seawater for cooling is provided in the cooling water outlet chamber 94d. A part of the seawater for cooling discharged from the cooling water outlet 97 is supplied to the jet pump 8 through the branch passage 14, and the other part is supplied to the preheater 5 through the water supply passage 15, and the rest is discharged to the outside of the ship (refer to Fig. 1). ). The jet pump 8 is for driving the water jet 7 and is provided integrally with the apparatus body 6. The seawater for cooling supplied to the jet pump 8 is boosted by the jet pump 8, and then supplied to the water ejector 7, and the water ejector 7 is driven, and then discharged to the outside of the ship.
接著,在各預熱用管集箱室91A、91B內,係如 第4圖所示,分別設有2枚隔板98A、98B。在第1管集箱9A之預熱用管集箱91A內,係由隔板98A劃分成內側的原料海水出口室99f與中央及近側的折返室99d、99e。又,在第2管集箱9B之預熱用管集箱91B內,係由隔板98B劃分成近側的原料海水入口室99a與中央及內側的折返室99b、99c。 Next, in each of the preheating tube header chambers 91A and 91B, As shown in Fig. 4, two partition plates 98A and 98B are provided, respectively. In the preheating pipe header 91A of the first header 9A, the raw material seawater outlet chamber 99f and the center and proximal folding chambers 99d and 99e are defined by the partition plate 98A. In the preheating pipe header 91B of the second header 9B, the partition 98B is divided into a raw material seawater inlet chamber 99a and a center and inner folding chambers 99b and 99c.
在原料海水入口室99a,係設有用於將自冷凝器4所排出之冷卻用海水的一部分導入之原料海水入口100。在原料海水入口100係連接有給水通道15;在給水通道15,設有輔助泵9(參照圖1)。從冷凝器4所排出的冷卻用海水之一部分係在經輔助泵9升壓的狀態下,被導入原料海水入口室99a。接著,將構成預熱器5的各傳熱管50內,如第4圖的箭頭所示,通過各折返室99b~99e,往另側的第1管集箱9A之原料海水出口室99f的方向流動。此時,冷卻用海水在各傳熱管50內流動時,一邊藉由與供給至容器本體2內之蒸氣的熱交換而被加熱,一邊被導入原料海水出口室99f。 In the raw material seawater inlet chamber 99a, a raw material seawater inlet 100 for introducing a part of the cooling seawater discharged from the condenser 4 is provided. A feed water passage 15 is connected to the raw material seawater inlet 100; and an auxiliary pump 9 is provided in the water supply passage 15 (see Fig. 1). A part of the seawater for cooling discharged from the condenser 4 is introduced into the raw material seawater inlet chamber 99a while being pressurized by the auxiliary pump 9. Next, in each of the heat transfer tubes 50 constituting the preheater 5, as shown by the arrows in Fig. 4, the raw material seawater outlet chambers 99f of the first header header 9A of the other side are passed through the respective folding chambers 99b to 99e. The direction flows. At this time, when the seawater for cooling flows in each of the heat transfer tubes 50, it is introduced into the raw material seawater outlet chamber 99f while being heated by heat exchange with the steam supplied into the container main body 2.
在原料海水出口室99f,設有用於排出冷卻用海水的原料海水出口101。原料海水出口101所排出之冷卻用海水係透過原料海水供給通道16,被供給至海水供給室32作為原料海水。 A raw material seawater outlet 101 for discharging the seawater for cooling is provided in the raw material seawater outlet chamber 99f. The seawater for cooling discharged from the raw material seawater outlet 101 passes through the raw material seawater supply passage 16 and is supplied to the seawater supply chamber 32 as raw material seawater.
如此,因上述結構之預熱器5的存在,從冷凝器所排出之冷卻用海水的一部分,再藉由與被供給至容器本體2內之較高溫的蒸氣之熱交換而升溫後,再做為原料海水供給至加熱器3。因此,可較為提高供給至加熱器3之原料海水的溫度,因而能提高加熱器3的熱效率。 As described above, due to the presence of the preheater 5 having the above configuration, a part of the seawater for cooling discharged from the condenser is further heated by heat exchange with the higher temperature steam supplied into the container main body 2, and then The raw material seawater is supplied to the heater 3. Therefore, the temperature of the seawater of the raw material supplied to the heater 3 can be relatively increased, so that the thermal efficiency of the heater 3 can be improved.
構成冷凝器4之各傳熱管40及構成預熱器5的各傳熱管50係如圖5所示,其內面及外面經凹凸加工。在本實施型態中,各傳熱管40、50係由波形管所構成,於其管壁41、51上,有多數的凸部42、52及凹部43、53交互地連接。凸部42、52及凹部43、53的截面視形狀係可形成如圖5(A)所示之山形狀之外,還有如圖5(B)、(C)所示之矩形狀或波形狀等各種形狀。 As shown in FIG. 5, each of the heat transfer tubes 40 constituting the condenser 4 and the heat transfer tubes 50 constituting the preheater 5 are subjected to uneven processing on the inner surface and the outer surface. In the present embodiment, each of the heat transfer tubes 40, 50 is constituted by a corrugated tube, and a plurality of convex portions 42, 52 and concave portions 43, 53 are alternately connected to the tube walls 41, 51. The cross-sectional shapes of the convex portions 42, 52 and the concave portions 43, 53 can be formed in a mountain shape as shown in Fig. 5(A), and a rectangular shape or a wave shape as shown in Figs. 5(B) and (C). And so on.
再者,作為各傳熱管40、50,除波形管之外,亦可使用經凹凸加工之加工管,該凹凸加工係對管壁41、51平滑的平滑管,在管壁41、51的內面及外面沿軸方向以預定的間隔一體地設置在周方向上延伸之複數的環狀突起。又,作為加工管,亦可藉由在平滑管的管壁41、51的內面及外面以螺旋狀的方式一體地設置突起來進行凹凸加工;又,亦可為以溝來取代突起,在平滑管的管壁41、51之內面及外面,與突起同樣地一體地設置來進行凹凸加工。再者,亦可為藉由對平滑管在管壁41、51之內面及外面,沿周方向以預定的間隔一體地設置在軸方向上延伸之複數的突起或溝來進行凹凸加工。像這樣,只要是能使各傳熱管40、50的表面積增大,則將管壁41、51之內面及外面進行凹凸加工的方法可無特別限定。 Further, as the heat transfer tubes 40 and 50, in addition to the corrugated tube, a processing tube which is subjected to concavo-convex processing, which is a smooth tube which is smooth to the tube walls 41 and 51, is formed on the tube walls 41 and 51. The inner surface and the outer surface are integrally provided with a plurality of annular projections extending in the circumferential direction at predetermined intervals in the axial direction. Further, as the processing tube, the protrusions may be integrally formed by spirally providing the protrusions on the inner surface and the outer surface of the tube walls 41 and 51 of the smooth tube. Alternatively, the protrusion may be replaced by a groove. The inner surface and the outer surface of the tube walls 41 and 51 of the smoothing tube are integrally provided in the same manner as the protrusions to perform the uneven processing. Further, it is also possible to perform the concavo-convex processing by integrally providing a plurality of protrusions or grooves extending in the axial direction at predetermined intervals in the circumferential direction on the inner surface and the outer surface of the tube walls 41 and 51. As described above, the method of performing the uneven processing on the inner surface and the outer surface of the tube walls 41 and 51 is not particularly limited as long as the surface area of each of the heat transfer tubes 40 and 50 is increased.
在本實施型態之真空蒸發行造水裝置1中,由於冷凝器4及預熱器5之各傳熱管40、50的內面及外面經凸凹加工之故,其外徑相較於幾乎相同的平滑管,各傳熱管40、50的表面積較大,亦即,因在傳熱管內外之熱交換時可確保較大的傳熱面積,且凹凸將傳熱管內所流動的冷卻用海 水係經攪拌,而提高在傳熱面(管壁41、51)之蒸氣及冷卻用海水間的傳熱效率,造成各傳熱管40、50的熱交換量增大。因此,藉由將各傳熱管40、50的內面及外面進行凸凹加工,相較於使用平滑管的情況,可使各傳熱管40、50內所流動的冷卻用海水藉由與蒸氣的熱交換而進一步加熱至高溫,這樣的結果可更加提高供給至加熱器3之原料海水的溫度。因此,可進一步提高加熱器3的熱效率。 In the vacuum evaporation line water generating device 1 of the present embodiment, since the inner surface and the outer surface of each of the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5 are subjected to convex and concave processing, the outer diameter is relatively small. The same smoothing tube has a large surface area of each of the heat transfer tubes 40, 50, that is, a large heat transfer area is ensured during heat exchange between the inside and outside of the heat transfer tube, and the unevenness causes cooling in the heat transfer tube. Use the sea The water system is stirred to increase the heat transfer efficiency between the steam on the heat transfer surfaces (tube walls 41, 51) and the sea water for cooling, and the heat exchange amount of each of the heat transfer tubes 40, 50 is increased. Therefore, by performing the convex-concave processing on the inner surface and the outer surface of each of the heat transfer tubes 40 and 50, the cooling seawater flowing in each of the heat transfer tubes 40 and 50 can be made to be vaporized by steam compared to the case where the smooth tube is used. The heat exchange is further heated to a high temperature, and as a result, the temperature of the raw material seawater supplied to the heater 3 can be further increased. Therefore, the thermal efficiency of the heater 3 can be further improved.
另一方面,將各傳熱管40、50之內面及外面進行凸凹加工,會因凹凸而增大管摩擦係數,而使傳熱管內所流動的冷卻用海水之壓力損失變大。因此,為了防止冷卻用海水之流動性變差,加大傳熱管的尺寸,或是提高海水泵的容量/揚程等對策便成為必要。就冷凝器4而言,由於係被供給經海水泵11升壓後的海水,不易受到壓力損失增大的影響,但就預熱器5而言,由於係被供給由冷凝器4排出之冷卻用海水,且預熱器5本身的壓力損失亦增大,故在預熱器5之出口的原料海水出口101之海水的壓力,相較於使用平滑管的情況係大幅降低。壓力損失變大,若來自原料海水出口101的海水供給壓力變低,對加熱器3而言將有無法充分地供給原料海水的疑慮。為了消除此疑慮,一般雖會考慮提高海水泵11的容量/揚程,但要進一步提高對船舶內之各海水使用處供給海水之大型的海水泵11之容量等,會有泵本身的成本及耗費電量等運轉經費大幅地高漲等問題。緣此,在本實施型態之真空蒸發型造水裝置1中,在冷凝器4與預熱器5之間的給水通道15設有小型的輔助泵9,將 自冷凝器4所排出之冷卻用海水利用輔助泵9升壓之後,供給至預熱器5。藉此,即便在預熱器5亦可促進與蒸氣間的熱交換,且能應付冷卻用海水之壓力損失的增大,因此可充分地確保對加熱器3之原料海水的給水量。 On the other hand, when the inner surface and the outer surface of each of the heat transfer tubes 40 and 50 are subjected to the convex-concave processing, the tube friction coefficient is increased by the unevenness, and the pressure loss of the cooling seawater flowing in the heat transfer tube is increased. Therefore, in order to prevent the fluidity of the seawater for cooling from deteriorating, it is necessary to increase the size of the heat transfer tube or to increase the capacity/lift of the sea water pump. In the case of the condenser 4, since the seawater pressurized by the sea water pump 11 is supplied, it is less likely to be affected by the increase in pressure loss, but the preheater 5 is supplied with cooling by the condenser 4 With seawater, and the pressure loss of the preheater 5 itself is also increased, the pressure of the seawater at the raw material seawater outlet 101 at the outlet of the preheater 5 is greatly reduced as compared with the case of using a smooth tube. When the pressure loss from the raw material seawater outlet 101 is lowered, the pressure of the seawater from the raw material seawater outlet 101 is lowered, and there is a fear that the raw material seawater cannot be sufficiently supplied to the heater 3. In order to eliminate this concern, although the capacity/head of the sea water pump 11 is generally considered to be increased, the cost and cost of the pump itself may be increased by further increasing the capacity of the large sea water pump 11 that supplies seawater to each seawater use location in the ship. There are problems such as a large increase in operating expenses such as electricity. Therefore, in the vacuum evaporation type water generating device 1 of the present embodiment, the water supply passage 15 between the condenser 4 and the preheater 5 is provided with a small auxiliary pump 9, which will The seawater for cooling discharged from the condenser 4 is boosted by the auxiliary pump 9, and then supplied to the preheater 5. Thereby, even in the preheater 5, heat exchange with the steam can be promoted, and the pressure loss of the seawater for cooling can be increased, so that the amount of water supplied to the raw material seawater of the heater 3 can be sufficiently ensured.
依據上述結構的真空蒸發型造水裝置1,因係在容器本體2之多管式的冷凝器4上方設置多管式的預熱器5,來將供給至加熱器3的原料海水加熱,故不再需要用於將預熱器5與冷凝器4分離設置的空間,而可謀求裝置的小型化。 According to the vacuum evaporation type water generator 1 of the above configuration, since the multi-tube type preheater 5 is provided above the multi-tube type condenser 4 of the container body 2, the seawater supplied to the heater 3 is heated. A space for separating the preheater 5 from the condenser 4 is no longer required, and the device can be miniaturized.
進一步,由於冷凝器4及預熱管5之各傳熱管40、50的內面及外面係經加工,固可提高各傳熱管40、50的傳熱性能。因此,可將從冷凝器4透過預熱器5供給至加熱器3的原料海水的溫度,與以平滑管構成各傳熱管40、50之既存的真空蒸發型造水裝置相比,提高至較高的溫度,因此可進一步提高加熱器3的熱效率。又,在冷凝器4與預熱器5之間的給水通道15設置輔助泵9,將自冷凝器4所排出之冷卻用海水利用輔助泵9升壓後供給至預熱器5,因此可應付流動於預熱器5的各傳熱管50內之冷卻用海水(原料海水)之壓力損失的增大。因此,可對加熱器3充分地供給原料海水。其結果,可增加在真空蒸發型造水裝置1所製造之淡水的製造量,提高裝置之造水性能。另一方面,與各傳熱管40、50由平滑管所構成之既存的真空蒸發型造水裝置相比,藉由裝置之造水性能的提高,即便減少冷凝器4及預熱器5之各傳熱管40、50的數量,也能製造大致同量的淡水。 因此,可謀求裝置的精簡化。 Further, since the inner surface and the outer surface of each of the heat transfer tubes 40 and 50 of the condenser 4 and the preheating tube 5 are processed, the heat transfer performance of each of the heat transfer tubes 40 and 50 can be improved. Therefore, the temperature of the raw material seawater supplied from the condenser 4 to the heater 3 through the preheater 5 can be increased to be higher than that of the existing vacuum evaporation type water generating device in which the heat transfer tubes 40 and 50 are formed by the smooth tubes. The higher the temperature, the further the thermal efficiency of the heater 3 can be further increased. Further, an auxiliary pump 9 is provided in the water supply passage 15 between the condenser 4 and the preheater 5, and the cooling seawater discharged from the condenser 4 is boosted by the auxiliary pump 9 and supplied to the preheater 5, thereby coping with The pressure loss of the cooling seawater (raw material seawater) flowing in each of the heat transfer tubes 50 of the preheater 5 is increased. Therefore, the raw material seawater can be sufficiently supplied to the heater 3. As a result, the amount of fresh water produced in the vacuum evaporation type water generator 1 can be increased, and the water generation performance of the apparatus can be improved. On the other hand, compared with the existing vacuum evaporation type water generating device in which each of the heat transfer tubes 40 and 50 is composed of a smooth tube, even if the water generation performance of the device is improved, even the condenser 4 and the preheater 5 are reduced. The amount of each of the heat transfer tubes 40, 50 can also produce approximately the same amount of fresh water. Therefore, the simplification of the device can be achieved.
又,由於僅須在各傳熱管40、50由平滑管所構成之既存的真空蒸發型造水裝置中,將平滑管以內面及外面經凹凸加工之波形管或加工管等替代,就能提高裝置的造水性能,故能簡易且低成本地將既存的真空蒸發型造水裝置進行版本升級。 Further, in the existing vacuum evaporation type water generating device in which each of the heat transfer tubes 40 and 50 is composed of a smooth tube, the smooth tube can be replaced by a corrugated tube or a processing tube which is subjected to uneven processing on the inner surface and the outer surface. By improving the water-generating performance of the device, it is possible to upgrade the existing vacuum evaporation type water-making device in a simple and low-cost manner.
以上雖係針對本發明之一實施型態進行說明,但本發明非受上述實施型態限定者,只要是在不脫離本發明旨趣的範圍內,可有各種的變更。例如,在上述圖1之實施型態中,是將各傳熱管40、50的內面及外面進行凹凸加工,但亦可僅在內面或外面其中一者進行凹凸加工。 The above is a description of the embodiments of the present invention, and the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention. For example, in the embodiment of Fig. 1, the inner surface and the outer surface of each of the heat transfer tubes 40 and 50 are subjected to uneven processing, but the concave and convex processing may be performed only on one of the inner surface and the outer surface.
又,雖對冷凝器4及預熱器5之各傳熱管40、50施以凹凸加工,但亦可僅對冷凝器4之各傳熱管40或預熱器5之各傳熱管50之一者施予凹凸加工。 Further, although the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5 are subjected to the uneven processing, the heat transfer tubes 50 of the heat transfer tubes 40 or the preheaters 5 of the condenser 4 may be used only. One of them is subjected to concave and convex processing.
又,對加熱器3之各加熱管31,亦可與冷凝器4及預熱器5之各傳熱管40、50同樣地施予凹凸加工。第6圖係表示在除了冷凝器4及預熱器5之各傳熱管40、50以外,針對加熱器3之各加熱管31亦施予凹凸加工之實施型態(圖2的變形例)。各加熱管31係與冷凝器4及預熱器5之各傳熱管40、50同樣,如圖7所示,在管壁31A上,具有多數的凸部31B及凹部31C交互地連接,對其內面及外面施予凹凸加工。凸部31B及凹部31C的截面視形狀係可形成如圖7(A)所示之山形狀外,還可形成如圖7(B)、(C)所示之矩形狀或波形狀等各種形狀。作為上述結構的加熱管31,雖可適宜地 使用波形管,但在波形管之外,亦可使用經凹凸加工的加工管,該凹凸加工係對管壁31A平滑之平滑管,在管壁31A的內面及外面,將在周方向上延伸之複數的環狀突起,沿軸方向以預定的間隔一體地設置。又,作為加工管,亦可將突起在平滑管的管壁31A內面及外面螺旋狀地以一體的方式設置藉以進行凹凸加工,又,亦可以溝來取代突起,在平滑管的管壁31A的內面及外面,以與突起同樣的方式一體的設置,藉以進行凹凸加工。進一步,亦可對平滑管,將在軸方向上延伸之複數的突起或溝,在管壁31A的內面及外面,在周方向上以預定的間隔一體地設置,藉以進行凹凸加工。如此,只要能使各加熱管31的表面積變大,則將管壁31A內面及外面凹凸加工的方法係不受限。 Further, the heating pipes 31 of the heater 3 may be subjected to uneven processing in the same manner as the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5. Fig. 6 shows an embodiment in which the heat transfer tubes 31 of the heater 3 are also subjected to uneven processing in addition to the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5 (variation of Fig. 2) . Similarly to the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5, each of the heating tubes 31 has a plurality of convex portions 31B and recessed portions 31C alternately connected to each other on the tube wall 31A. The inner surface and the outer surface are subjected to concave and convex processing. The cross-sectional shape of the convex portion 31B and the concave portion 31C can be formed into a mountain shape as shown in Fig. 7(A), and various shapes such as a rectangular shape or a wave shape as shown in Figs. 7(B) and (C) can be formed. . The heating pipe 31 having the above configuration may be suitably used A corrugated tube is used, but a processing tube which is processed by concavo-convex processing may be used in addition to the corrugated tube. The concavo-convex processing is a smooth tube which is smooth to the tube wall 31A, and extends in the circumferential direction on the inner surface and the outer surface of the tube wall 31A. The plurality of annular projections are integrally provided at predetermined intervals in the axial direction. Further, as the processing tube, the protrusion may be integrally provided in a spiral shape on the inner surface and the outer surface of the tube wall 31A of the smooth tube to perform the uneven processing, or the groove may be replaced by the groove, and the tube wall 31A of the smooth tube may be used. The inner surface and the outer surface are integrally provided in the same manner as the protrusions, thereby performing the uneven processing. Further, in the smooth tube, a plurality of projections or grooves extending in the axial direction may be integrally provided at a predetermined interval in the circumferential direction on the inner surface and the outer surface of the tube wall 31A, thereby performing uneven processing. As described above, as long as the surface area of each of the heating pipes 31 can be increased, the method of processing the inner and outer surfaces of the pipe wall 31A is not limited.
藉由將加熱器3之各加熱管31的內面及外面凹凸加工,與其外徑大致相同的平滑管相較之下,各加熱管30的表面積變大,亦即,可確保在加熱管內外之熱交換時較大的傳熱面積。進一步,利用凹凸來攪拌加熱管內所流動的原料海水,藉此提高在傳熱面(管壁31A)之溫水及原料海水間的傳熱效率。其結果,各加熱管31的熱交換量增大。因此,如圖6所示之實施型態,藉由將各加熱管31之內面及外面進行凸凹加工,相較於使用平滑管的情況,各加熱管31內所流動之原料海水變得能與溫水高效率地進行熱交換,各加熱管31之加熱效率提高,結果使原料海水的蒸發效率良好,而能充分地將蒸氣供給至容器本體2內。 By processing the inner surface and the outer surface of each of the heating tubes 31 of the heater 3, the surface area of each of the heating tubes 30 is larger than that of the smooth tubes having substantially the same outer diameter, that is, ensuring the inside and outside of the heating tubes. Large heat transfer area for heat exchange. Further, the raw material seawater flowing in the heating pipe is stirred by the unevenness, thereby improving the heat transfer efficiency between the warm water on the heat transfer surface (the pipe wall 31A) and the raw material seawater. As a result, the amount of heat exchange between the respective heating tubes 31 increases. Therefore, in the embodiment shown in Fig. 6, by performing the convex and concave processing on the inner surface and the outer surface of each of the heating tubes 31, the raw material seawater flowing in each of the heating tubes 31 can be made as compared with the case where the smooth tubes are used. The heat exchange is efficiently performed with warm water, and the heating efficiency of each heating pipe 31 is improved. As a result, the evaporation efficiency of the raw material seawater is good, and the vapor can be sufficiently supplied into the container body 2.
又,在上述圖1之實施型態中,作為在加熱器3 用於使原料海水加熱/蒸發的熱源,係利用來自柴油機的廢熱,但除此之外,亦可利用來自會產生廢熱之裝置的廢熱,如利用來自鍋爐的蒸氣,在加熱器3使原料海水加熱/蒸發亦可。 Moreover, in the above embodiment of FIG. 1, as the heater 3 The heat source for heating/evaporating the raw material seawater utilizes waste heat from the diesel engine, but in addition, waste heat from a device that generates waste heat may be utilized, such as using steam from the boiler to make the raw material seawater in the heater 3. Heating/evaporation is also possible.
又,在述圖1之實施型態中,自冷凝器4所排出之冷卻用海水,其一部分係利用輔助泵9來升壓並透過給水通道15供給至預熱器5,但亦可省略該輔助泵9。圖8係圖1之實施型態的變形例,表示輔助泵9經省略之真空蒸發式造水裝置1的概略結構圖。再者,基本的結構係與上述圖1之實施型態的結構相同,在此因將對應的結構標上相同符號故省略說明。 Further, in the embodiment of Fig. 1, part of the cooling seawater discharged from the condenser 4 is boosted by the auxiliary pump 9 and supplied to the preheater 5 through the water supply passage 15, but the cooling water may be omitted. Auxiliary pump 9. Fig. 8 is a schematic view showing a modification of the embodiment of Fig. 1 and showing a schematic configuration of the vacuum evaporation type water generator 1 in which the auxiliary pump 9 is omitted. In addition, the basic structure is the same as that of the above-mentioned embodiment of FIG. 1, and since the corresponding structure is attached with the same code|symbol, description is abbreviate|omitted.
在圖8的實施型態中,自冷凝器4所排出的冷卻用海水,一部分係透過分支通道14,供給至噴射泵8,剩下的被排出至船舶外。供給至噴射泵8之冷卻用海水,在經噴射泵8升壓後,一部分供給至水噴射器7,而剩下的則透過通道19供給至預熱器5。接著,供給至預熱器5之冷卻用海水係利用與供給至容器本體2內之蒸氣的熱交換來加熱後,作為原料海水,透過原料海水供給通道16供給至加熱器3。如此,在圖8的實施型態中,使噴射泵8之噴出側的通道分支,將利用噴射泵8升壓後的冷卻用海水透過給水通道19供給至預熱器5,藉此可應付預熱器5之各傳熱管50內所流動之冷卻用海水之壓力損失的增大,而能對加熱器3充分地供給原料海水。其結果,不僅可實現與圖1之實施型態相同的作用/效果,更由於不需輔助泵9,也能將裝置簡略化。 In the embodiment of Fig. 8, a part of the seawater for cooling discharged from the condenser 4 is partially supplied to the jet pump 8 through the branch passage 14, and the rest is discharged to the outside of the ship. The seawater for cooling supplied to the jet pump 8 is supplied to the water injector 7 after being pressurized by the jet pump 8, and the remaining is supplied to the preheater 5 through the passage 19. Then, the seawater for cooling supplied to the preheater 5 is heated by heat exchange with the steam supplied into the container main body 2, and then supplied as raw material seawater to the heater 3 through the raw material seawater supply passage 16. In the embodiment of FIG. 8, the passage on the discharge side of the jet pump 8 is branched, and the seawater for cooling boosted by the jet pump 8 is supplied to the preheater 5 through the water supply passage 19, thereby coping with the preheating The pressure loss of the seawater for cooling flowing in each of the heat transfer tubes 50 of the heat exchanger 5 is increased, and the raw material seawater can be sufficiently supplied to the heater 3. As a result, not only the same action/effect as the embodiment of Fig. 1 but also the auxiliary pump 9 can be realized, and the device can be simplified.
又,在上述圖1之實施型態中,雖是將噴射泵8與裝置本體6以一體的方式設置,但如圖9所示,亦可將噴射泵8設置於較裝置本體6下方的位置。在圖1的實施型態中,噴射泵8係被供給有自冷凝器4所排出之冷卻用海水的一部分,但在圖9的實施型態中,噴射泵8係將從海中汲取上來的海水作為驅動水供給至水噴射器7。 Further, in the embodiment of Fig. 1, the jet pump 8 and the apparatus main body 6 are integrally provided. However, as shown in Fig. 9, the jet pump 8 may be disposed below the apparatus main body 6. . In the embodiment of Fig. 1, the jet pump 8 is supplied with a part of the seawater for cooling discharged from the condenser 4, but in the embodiment of Fig. 9, the jet pump 8 is seawater extracted from the sea. The drive water is supplied to the water injector 7.
又,在圖1、圖8及圖9之實施型態中,雖使用水噴射器作為減壓機構7,但其並非必定受限於此者,亦可為真空泵等。 Further, in the embodiment of FIGS. 1, 8, and 9, a water ejector is used as the pressure reducing mechanism 7, but it is not necessarily limited thereto, and may be a vacuum pump or the like.
進一步,圖10係表示本發明之其他實施型態的真空蒸發式造水裝置1的概略結構圖。再者,基本的結構係與上述圖1的實施型態相同,在此因將對應的結構標上相同符號故省略說明。 Further, Fig. 10 is a schematic configuration view showing a vacuum evaporation type water generator 1 according to another embodiment of the present invention. In addition, the basic structure is the same as that of the above-mentioned embodiment of FIG. 1, and the description is abbreviate|omitted by the same code|symbol.
在圖10的實施型態中,從噴射泵8作為驅動水而被供給至噴射器7之海水,係透過冷卻水供給回路13,作為利用真空蒸發式造水裝置1來造水用的冷卻水供給至冷凝器4。作為噴射泵8,係使用自海中汲取海水,並僅將之供給至水噴射器7之小型泵。 In the embodiment of FIG. 10, the seawater supplied to the ejector 7 from the jet pump 8 as the driving water is transmitted through the cooling water supply circuit 13 as the cooling water for water generation by the vacuum evaporation type water generator 1. It is supplied to the condenser 4. As the jet pump 8, a small pump that draws seawater from the sea and supplies it only to the water injector 7 is used.
即便在該圖10之實施型態中,被供給至冷凝器4的冷卻用海水,在將被供給至容器本體2內之蒸氣冷卻/凝結而生成淡水後,從冷凝器4被排出,但其中一部分係被供給至預熱器5而藉由與被供給至容器本體2內之蒸氣的熱交換被加熱後,作為原料海水,透過原料海水供給通道16被供給至海水供應室32。在此,藉由將預熱器5之各傳熱管50(進 一步則是冷凝器4之各傳熱管40)的內面及外面凹凸加工,可使供給至加熱器3之原料海水的溫度更高,而能提高加熱器3之熱效率。另一方面,在圖10之實施型態中,藉由提高噴射泵8的容量等,就不需要輔助泵9,又,或許因為提高了海水泵11的容量等而能以低成本來應付流動於預熱器5之各傳熱管50(甚至是冷凝器4之各傳熱管40)內的冷卻用海水之壓力損失的增大,故可對加熱器3充分地供應原料海水。其結果,可實現與圖1之實施型態相同的作用/效果。 In the embodiment of FIG. 10, the cooling seawater supplied to the condenser 4 is cooled and condensed in the container body 2 to generate fresh water, and then discharged from the condenser 4, but A part is supplied to the preheater 5 and heated by heat exchange with the steam supplied into the container main body 2, and then supplied as raw material seawater to the seawater supply chamber 32 through the raw material seawater supply passage 16. Here, by the heat transfer tubes 50 of the preheater 5 In one step, the inner surface and the outer surface of each heat transfer tube 40) of the condenser 4 are subjected to uneven processing, so that the temperature of the seawater supplied to the heater 3 can be made higher, and the thermal efficiency of the heater 3 can be improved. On the other hand, in the embodiment of Fig. 10, the auxiliary pump 9 is not required by increasing the capacity and the like of the jet pump 8, and the flow can be coped with a low cost because the capacity of the sea water pump 11 is increased or the like. Since the pressure loss of the seawater for cooling in each of the heat transfer tubes 50 of the preheater 5 (even the heat transfer tubes 40 of the condenser 4) is increased, the raw material seawater can be sufficiently supplied to the heater 3. As a result, the same action/effect as the embodiment of Fig. 1 can be achieved.
Claims (7)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012006182 | 2012-01-16 | ||
JP2012193025A JP6041584B2 (en) | 2012-01-16 | 2012-09-03 | Vacuum evaporative fresh water generator |
Publications (2)
Publication Number | Publication Date |
---|---|
TW201330915A TW201330915A (en) | 2013-08-01 |
TWI617342B true TWI617342B (en) | 2018-03-11 |
Family
ID=49177021
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
TW101140980A TWI617342B (en) | 2012-01-16 | 2012-11-05 | Vacuum evaporation water generator |
Country Status (3)
Country | Link |
---|---|
JP (3) | JP6041584B2 (en) |
CN (1) | CN106277116A (en) |
TW (1) | TWI617342B (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6041584B2 (en) * | 2012-01-16 | 2016-12-14 | 株式会社ササクラ | Vacuum evaporative fresh water generator |
ES2953957T3 (en) * | 2015-04-23 | 2023-11-17 | Dan Alexandru Hanganu | Condenser-evaporator tube |
JP7229599B2 (en) * | 2017-08-02 | 2023-02-28 | 株式会社ササクラ | Multi-effect fresh water generator |
TWI757508B (en) * | 2017-08-02 | 2022-03-11 | 日商笹倉機械工程股份有限公司 | Fresh water generation device |
JP7026939B2 (en) * | 2017-08-02 | 2022-03-01 | 株式会社ササクラ | Multi-effect water production equipment |
JP7129041B2 (en) * | 2018-05-08 | 2022-09-01 | 株式会社ササクラ | fresh water generator |
CN109437353B (en) * | 2018-12-17 | 2024-02-27 | 海汇集团有限公司 | Single-effect sea water desalination device |
CN110217847A (en) * | 2019-07-26 | 2019-09-10 | 哈尔滨汽轮机厂辅机工程有限公司 | A kind of small-sized Flash Type desalination plant |
US20220364721A1 (en) * | 2019-09-30 | 2022-11-17 | Yoshiaki Miyazato | Steam generation apparatus |
CN111099676A (en) * | 2020-02-19 | 2020-05-05 | 怡灏环境技术有限公司 | Device for synchronously recycling salt during seawater purification |
JP7396654B2 (en) * | 2020-02-25 | 2023-12-12 | 株式会社ササクラ | Control device, control method, and control program for controlling vacuum evaporation fresh water generator |
JP7431447B2 (en) * | 2020-06-08 | 2024-02-15 | 株式会社東洋製作所 | Distilled water production equipment |
TW202212268A (en) * | 2020-09-25 | 2022-04-01 | 日商笹倉機械工程股份有限公司 | Management device managing vacuum vaporization-type fresh water generation device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6243692A (en) * | 1985-08-21 | 1987-02-25 | 株式会社タツノ・メカトロニクス | Display for gasoline station |
CN2196772Y (en) * | 1994-07-15 | 1995-05-10 | 沈阳黎明发动机制造公司工程机械厂 | Tube-casing type high-efficiency vapour-liquid heat exchanger |
JPH08121991A (en) * | 1994-10-21 | 1996-05-17 | Sumitomo Metal Ind Ltd | High anti-corrosion type corrugated pipe |
JP2001279784A (en) * | 2000-03-31 | 2001-10-10 | Toto Ltd | Warm water device for bidet |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51125668A (en) * | 1975-04-25 | 1976-11-02 | Ebara Corp | A decdorizing arrangement |
JPS5512352A (en) * | 1978-07-12 | 1980-01-28 | Toshiba Corp | Direct contact type condenser |
SE423836B (en) * | 1980-07-10 | 1982-06-07 | Projectus Ind Produkter Ab | CONTAINER FOR PREPARING THE TAP WATER THROUGH HEATING BY A HEAT PUMP |
JPS5864493A (en) * | 1981-10-13 | 1983-04-16 | Babcock Hitachi Kk | Fresh water producing device attached with corrugated heat transfer pipe |
JPS5987580U (en) * | 1982-11-29 | 1984-06-13 | ヤンマーディーゼル株式会社 | Shell-and-tube heat exchanger |
JPH0335438Y2 (en) * | 1985-09-06 | 1991-07-26 | ||
JPS6266796U (en) * | 1985-10-15 | 1987-04-25 | ||
JPH0380981A (en) * | 1989-08-25 | 1991-04-05 | Kawanami Shunpei | Apparatus for desalting seawater or brine |
JP3183986B2 (en) * | 1993-03-03 | 2001-07-09 | 株式会社ササクラ | Vacuum evaporation type fresh water generator |
CN2252040Y (en) * | 1995-12-29 | 1997-04-16 | 孙红兵 | Spray-type direct evaporating seawater desalination apparatus |
JP3843066B2 (en) * | 2002-12-26 | 2006-11-08 | 日立ホーム・アンド・ライフ・ソリューション株式会社 | Heat pump water heater |
JP2005030521A (en) * | 2003-07-09 | 2005-02-03 | Osaka Gas Co Ltd | Corrugated pipe and its piping method and repairing method |
JP2008261566A (en) * | 2007-04-12 | 2008-10-30 | Sumitomo Light Metal Ind Ltd | Double-pipe heat exchanger |
JP2010112663A (en) * | 2008-11-10 | 2010-05-20 | Panasonic Corp | Heat exchanger |
JP5617213B2 (en) * | 2009-09-30 | 2014-11-05 | 三菱化学株式会社 | Plate reactor and reaction product production method |
JP2011106746A (en) * | 2009-11-18 | 2011-06-02 | Hitachi Cable Ltd | Heat transfer tube, heat exchanger, and processed product of heat transfer tube |
JP6041584B2 (en) * | 2012-01-16 | 2016-12-14 | 株式会社ササクラ | Vacuum evaporative fresh water generator |
-
2012
- 2012-09-03 JP JP2012193025A patent/JP6041584B2/en active Active
- 2012-11-05 TW TW101140980A patent/TWI617342B/en active
-
2013
- 2013-01-16 CN CN201610680720.6A patent/CN106277116A/en active Pending
-
2016
- 2016-08-08 JP JP2016155279A patent/JP6321736B2/en active Active
-
2018
- 2018-04-04 JP JP2018072347A patent/JP6524298B2/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6243692A (en) * | 1985-08-21 | 1987-02-25 | 株式会社タツノ・メカトロニクス | Display for gasoline station |
CN2196772Y (en) * | 1994-07-15 | 1995-05-10 | 沈阳黎明发动机制造公司工程机械厂 | Tube-casing type high-efficiency vapour-liquid heat exchanger |
JPH08121991A (en) * | 1994-10-21 | 1996-05-17 | Sumitomo Metal Ind Ltd | High anti-corrosion type corrugated pipe |
JP2001279784A (en) * | 2000-03-31 | 2001-10-10 | Toto Ltd | Warm water device for bidet |
Also Published As
Publication number | Publication date |
---|---|
JP6524298B2 (en) | 2019-06-05 |
JP6321736B2 (en) | 2018-05-09 |
JP2018114501A (en) | 2018-07-26 |
JP2013166141A (en) | 2013-08-29 |
JP2016193437A (en) | 2016-11-17 |
CN106277116A (en) | 2017-01-04 |
TW201330915A (en) | 2013-08-01 |
JP6041584B2 (en) | 2016-12-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
TWI617342B (en) | Vacuum evaporation water generator | |
JP5462939B2 (en) | Power generation and seawater desalination complex plant | |
US10099154B2 (en) | Multi-effects desalination system | |
CN102762501A (en) | Waste heat driven desalination process | |
JP2009097788A (en) | Multi-pressure condenser and condensate reheating method | |
KR101821660B1 (en) | Vacuum evaporation desalination system | |
JP5672450B2 (en) | Fresh water generator and fresh water generation method | |
CN106338056B (en) | A kind of horizontal side burning formula coil arrangement Quick steam generating system | |
JP5570433B2 (en) | Salt water desalination method and desalination plant using MSF desalination unit with steam recirculation system | |
US1555435A (en) | Feed-water heater | |
JP5979395B2 (en) | Fresh water generator and fresh water generation method | |
JP3879407B2 (en) | Fresh water generator | |
JP7129041B2 (en) | fresh water generator | |
KR101567655B1 (en) | TVC-MED having Non-condensible Gas Venting System | |
JP2019105251A (en) | Geothermal power generation system | |
AU2014231976B2 (en) | Methanol plant and gasoline synthesis plant | |
TW200821266A (en) | Desalting or purifying apparatus for sea water | |
US479454A (en) | Generation of steam-power | |
JP2006130380A (en) | Apparatus for producing distilled water and method for bleeding non-condensible gas in the apparatus | |
JPS61187985A (en) | Production of clear water |