JP6524298B2 - Vacuum evaporation type fresh water generator - Google Patents

Description

  The present invention relates to a vacuum evaporation type water producing apparatus for producing fresh water from seawater, and more particularly to a vacuum evaporation type water producing apparatus provided with a preheater.

  Generally, in ships operating on the sea, fresh water is produced by evaporating seawater pumped up from the sea under high vacuum using steam from a boiler mounted on the vessel or waste heat from a diesel engine or the like as a heat source That is conventionally done. In this type of vacuum evaporation type water producing apparatus, generally, the inside of the raw material seawater to be supplied is reduced in pressure by a heater that heats and evaporates by heat exchange with warm water used for cooling of a diesel engine, etc. And a sealed container body which is held in a vacuum state and condenses and desalinates the generated vapor. A condenser having a plurality of heat transfer tubes is built in the container body, and the steam is desalinated by cooling and condensing by heat exchange with the cooling seawater flowing inside the heat transfer tubes. Further, part of the cooling seawater discharged from the condenser is supplied to the heater as raw material seawater.

  The temperature of raw material seawater supplied to the heater is somewhat higher due to heat exchange with steam in the condenser, but it is considerably lower than the evaporation temperature of seawater. Therefore, in the vacuum evaporation type water producing apparatus of the said structure, a heating and evaporation of the raw material seawater in a heater were not performed efficiently. Therefore, a vacuum evaporation type water producing apparatus has been proposed that includes a preheater that supplies heat to the heater after further heating the cooling seawater (raw material seawater) discharged from the condenser (see, for example, Patent Document 1) .

  In the vacuum evaporation type water producing apparatus of Patent Document 1, a multitubular preheater having a configuration similar to that of the condenser is provided above the condenser. The cooling seawater introduced from the condenser into the heat transfer tube of the preheater is further heated by heat exchange with the steam generated in the vessel body, and is supplied to the heater as raw seawater under higher temperature conditions. It has become so. Thus, in the vacuum evaporation type water producing apparatus of Patent Document 1, the thermal efficiency of the heater is improved, and the overall size of the apparatus is reduced.

Unexamined-Japanese-Patent No. 6-254534

  However, the vacuum evaporation type water producing apparatus of Patent Document 1 is configured to improve the thermal efficiency of the heater by providing a preheater to further increase the temperature of the raw material seawater supplied to the heater. However, since the heat transfer performance of the heat transfer tubes constituting the preheater (and the condenser) has not been particularly studied, there is room for further improvement in this respect.

  This invention is made | formed paying attention to the above-mentioned subject, and an object of this invention is to provide the vacuum evaporation type fresh-water-making apparatus excellent in thermal efficiency.

The above object of the present invention is to heat raw material seawater supplied by heat from a heat source in a vacuum evaporation type water producing apparatus for producing fresh water from seawater taken into a ship using heat from a heat source mounted on a ship. And a sealed vessel body into which the steam generated by the heater is introduced, decompression means for decompressing the inside of the vessel body, and a plurality of heat transfer tubes, the vessel body It has a condenser that cools the internal steam with cooling seawater to produce freshwater, and a plurality of heat transfer tubes, and a part of the cooling seawater discharged from the condenser with the steam in the container body And a preheater that heats and supplies the material as raw material seawater to the heater, wherein each heat transfer tube of at least one of the condenser and the preheater has an inner surface or an outer surface that is roughened. Achieved by a water device.

  In a preferred embodiment of the present invention, between the condenser and the preheater, there is an auxiliary pump for pressurizing the part of the cooling seawater discharged from the condenser and supplying the pressure to the preheater. It is characterized by being provided.

  In a further preferred embodiment of the present invention, a pump for supplying cooling seawater to the condenser is provided, and the pump supplies seawater pumped from the sea to each seawater using point of a ship including a diesel engine. It is characterized by being a seawater pump.

  In another preferred embodiment of the present invention, a pump for supplying cooling seawater to the condenser, the pressure reducing means is a water ejector driven by seawater, and the pump is It is an ejector pump for supplying driving seawater to the water ejector, and the driving seawater discharged from the water ejector is supplied to the condenser as cooling seawater.

  In the vacuum evaporation type water producing apparatus according to the above embodiment, the heat transfer tube is preferably configured by a corrugated tube. Alternatively, it is preferable that the heat transfer tube is roughened by integrally providing a protrusion or a groove on the inner surface or the outer surface.

  Further, in another preferred embodiment of the present invention, the pressure reducing means is a water ejector driven by seawater, and further comprises an ejector pump for supplying driving seawater to the water ejector, the ejector pump Is characterized in that a portion of the cooling seawater discharged from the condenser is pressurized and supplied to the water ejector and supplied to the preheater. In this embodiment, the system further comprises a pump for supplying cooling seawater to the condenser, wherein the pump is a seawater pump for supplying seawater pumped up from the sea to each seawater using point of a ship including a diesel engine. Is preferred. Further, it is further preferable that the heat transfer tube is formed of a corrugated tube, or the heat transfer tube is processed to be uneven by integrally providing a protrusion or a groove on an inner surface or an outer surface.

  Furthermore, in the vacuum evaporation type water producing apparatus according to all the embodiments described above, the heater has a plurality of heating pipes into which raw material seawater can be introduced, and each of the heating pipes has an uneven inner or outer surface. Is preferred.

  According to the vacuum evaporation type water producing apparatus according to the present invention, the heat transfer performance of each heat transfer tube is improved because the inner surface or the outer surface of each heat transfer tube of at least one of the condenser and the preheater is roughened. it can. Therefore, the temperature of the raw material seawater supplied from the preheater to the heater can be made higher than that of the existing vacuum evaporation type water producing apparatus in which each heat transfer tube is constituted by a smooth tube. Thus, the thermal efficiency of the heater can be further improved.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic block diagram of the vacuum evaporation type fresh-water-generation apparatus which concerns on one Embodiment of this invention. It is a longitudinal cross-sectional view of the apparatus main body of FIG. It is sectional drawing in alignment with the II line of FIG. It is sectional drawing in alignment with the II-II line of FIG. It is sectional drawing of a heat exchanger tube. It is a longitudinal cross-sectional view of the apparatus main body of other embodiment. It is sectional drawing of a heating pipe. It is a schematic block diagram of the vacuum evaporation type water-creation apparatus based on other embodiment of this invention. It is a schematic block diagram of the vacuum evaporation type water-creation apparatus based on other embodiment of this invention. It is a schematic block diagram of the vacuum evaporation type water-creation apparatus based on other embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the attached drawings. FIG. 1 is a schematic configuration view of a vacuum evaporation type water producing apparatus 1 according to an embodiment of the present invention, and FIG. 2 is a longitudinal sectional view of an apparatus main body 6 of FIG. As shown in FIGS. 1 and 2, the vacuum evaporation type water producing apparatus 1 of the present embodiment includes an apparatus main body 6 including a closed container main body 2, a heater 3, a condenser 4 and a preheater 5, and a container The pressure reducing means 7 which holds the main body 2 in a pressure reducing (vacuum) state is provided. In addition, in FIG. 1, the code | symbol 10 is a hull of a ship, the code | symbol 11 is a seawater pump provided in the ship and for pumping up seawater from the sea. The seawater pumped up by the seawater pump 11 is supplied as a jacket cooling water for cooling the various seawater use locations, for example, a diesel engine mounted on the ship, and vacuum evaporation to the condenser 4 It is supplied as cooling water for water production by the water production apparatus 1.

  The container body 2 is connected to the heater 3 at the lower portion, and incorporates the condenser 4 and the preheater 5 at the upper portion. Moreover, while the degassing pipe 102 is provided in the upper part of the container main body 2, the brine exit 103 is provided in the position higher than the heater 3 of the lower part.

  The degassing pipe 102 is connected to the pressure reducing means 7 via a gas line 17. In the present embodiment, the pressure reducing means 7 is constituted by a water ejector, and the noncondensable gas in the inside of the container body 2 is sucked by the water ejector 7 from the degassing pipe 102 and the inside of the container body 2 is at atmospheric pressure. The low pressure reduction (vacuum) state is maintained, and in the container main body 2, evaporation / condensation of raw material seawater described later is performed in the pressure reduction (vacuum) state. Further, the brine outlet 103 is connected to the water ejector 7 via the brine discharge line 18, and brine (seawater) after evaporation in the container body 2 described later is sucked from the brine outlet 103 by the water ejector 7 And then discharged out of the vessel.

  The heater 3 includes a closed-type heating chamber 30 and a plurality of heating tubes 31 provided in the heating chamber 30. The plurality of heating tubes 31 are disposed to extend in the vertical direction, and both ends 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 the lower part of the heating chamber 30, and the seawater supply chamber 32 is provided with a raw material seawater inlet 33 for introducing the raw material seawater into each heating pipe 31. A hot water inlet 34 and a hot water outlet 35 for introducing and discharging hot water such as jacket cooling water used for cooling a diesel engine are provided on the side wall surface of the heating chamber 30. The raw material seawater introduced into each heating pipe 31 from the raw material seawater inlet 33 is heated by heat exchange with the warm water introduced into the heating chamber 30 from the warm water inlet 34 and is evaporated to become steam as the container main body 2 Supplied inside.

  The condenser 4 is for cooling the steam supplied into the container body 2 to generate fresh water, and a plurality of heat transfer tubes 40 and both ends of a heat transfer tube group obtained by bundling the plurality of heat transfer tubes 40. And a first header 9A and a second header 9B in communication with each other. Each heat transfer tube 40 is disposed to extend in the horizontal direction, and both ends thereof are connected to the left wall surface and the right wall surface of the container body 2.

Above the condenser 4, a plurality of heat transfer pipes 50 constituting the preheater 5 are provided. The plurality of heat transfer tubes 50 are also arranged to extend in the horizontal direction, and both ends thereof are connected to the left wall surface and the right wall surface of the container body 2 and communicate with the first header 9A and the second header 9B. .

  In the first and second headers 9A and 9B, partition plates 90A and 90B are provided, respectively. The insides of the two headers 9A and 9B are partitioned by the partition plates 90A and 90B into an upper preheating header chamber 91A and 91B and a lower condensing header chamber 92A and 92B. The preheating header chambers 91A and 91B are in communication with the respective heat transfer pipes 50 constituting the preheater 5, while the condensing header chambers 92A and 92B are in communication with the respective heat transmission pipes 40 constituting the condenser 4. There is.

  In each of the condensing header chambers 92A and 92B, partition plates 93A and 93B are provided as shown in FIG. The inside of the condensation header 92A of the first header 9A is partitioned by a partition plate 93A into a cooling water inlet chamber 94a on the back side and a folding chamber 94b on the front side. Further, the inside of the condensation header 92B of the second header 9B is divided by the partition plate 93B into a cooling water outlet chamber 94d on the front side and a folding chamber 94c on the rear side.

  The cooling water inlet chamber 94 a is provided with a cooling water inlet 95 for introducing cooling seawater for cooling and condensing the vapor in the container body 2. The cooling water inlet 95 is connected to a cooling water supply pipe 13 connected to the seawater supply pipe 12 from the seawater pump 11 to each seawater use point in the ship (see FIG. 1). Sea water is introduced as cooling water by operation. The cooling seawater introduced into the cooling water inlet chamber 94a relays the folding chambers 94b and 94c as shown by the arrows in FIG. 3 in the respective heat transfer pipes 40, and cools the other second header 9B. It flows toward the water outlet chamber 94d. The steam supplied into the container body 2 is condensed by being cooled by heat exchange with the cooling seawater flowing in each heat transfer pipe 40, and the fresh water generated by the condensation is the fresh water provided in the container body 2 It is taken out from the outlet 96.

  The cooling water outlet chamber 94 d is provided with a cooling water outlet 97 for discharging the cooling seawater. The cooling seawater discharged from the cooling water outlet 97 is partially supplied to the ejector pump 8 via the branch line 14, and the other is supplied to the preheater 5 via the water supply line 15, and the remainder is Is discharged out of the ship etc. (see Figure 1). The ejector pump 8 is for driving the water ejector 7 and is provided integrally with the apparatus main body 6. The seawater for cooling supplied to the ejector pump 8 is pressurized by the ejector pump 8 and then supplied to the water ejector 7, and after driving the water ejector 7, it is discharged out of the ship.

  Next, as shown in FIG. 4, two partition plates 98A and 98B are provided in each of the preheating header chambers 91A and 91B. The inside of the preheating header 91A of the first header 9A is partitioned by a partition plate 98A into a raw material seawater outlet chamber 99f on the back side and turning chambers 99d and 99e on the center side and the front side. Further, the inside of the preheating header 91B of the second header 9B is divided by the partition plate 98B into the raw material seawater inlet chamber 99a on the front side and the folding chambers 99b and 99c on the center and the rear side.

The raw material seawater inlet chamber 99 a is provided with a raw material seawater inlet 100 for introducing a part of the cooling seawater discharged from the condenser 4. A feed water pipe 15 is connected to the raw material seawater inlet 100, and an auxiliary pump 9 is provided in the feed water pipe 15 (see FIG. 1). A portion of the cooling seawater discharged from the condenser 4 is introduced into the raw material seawater inlet chamber 99 a in a state of being pressurized by the auxiliary pump 9. Then, as shown by the arrows in FIG. 4, the insides of the heat transfer tubes 50 constituting the preheater 5 are relayed to the folding chambers 99b to 99e, and headed toward the raw material seawater outlet chamber 99f of the other first header 9A. Flow. At this time, the cooling seawater is introduced into the raw material seawater outlet chamber 99 f while being heated by heat exchange with the steam supplied into the container body 2 when flowing through the heat transfer tubes 50.

  The raw material seawater outlet chamber 99f is provided with a raw material seawater outlet 101 for discharging cooling seawater. The cooling seawater discharged from the raw material seawater outlet 101 is supplied as raw material seawater to the seawater supply chamber 32 through the raw material seawater supply pipeline 16.

  Thus, due to the presence of the preheater 5 configured as described above, a portion of the cooling seawater discharged from the condenser 4 is warmed by heat exchange with the relatively high temperature steam supplied into the container body 2 Then, the heater 3 is supplied as raw material seawater. Therefore, the temperature of the raw material seawater supplied to the heater 3 can be further raised, and the thermal efficiency of the heater 3 can be improved.

  As shown in FIG. 5, the inner and outer surfaces of each of the heat transfer tubes 40 that constitute the condenser 4 and the heat transfer tubes 50 that constitute the preheater 5 are roughened. In the present embodiment, each heat transfer tube 40, 50 is formed of a corrugated tube, and the tube wall 41, 51 has a large number of convex portions 42, 52 and concave portions 43, 53 alternately and continuously. There is. The cross-sectional shapes of the convex portions 42 and 52 and the concave portions 43 and 53 are not only mountain shapes as shown in FIG. 5A, but also rectangular shapes and waves as shown in FIGS. 5B and 5C. It can be formed into various shapes such as a shape.

  As the heat transfer tubes 40 and 50, in addition to the corrugated tube, a plurality of annular projections extending in the circumferential direction are provided on the inner and outer surfaces of the tube walls 41 and 51, as opposed to the smooth tube in which the tube walls 41 and 51 are smooth. Alternatively, it is possible to use a processed pipe that is unevenly formed by integrally providing at a predetermined interval in the axial direction. In addition, as a processed pipe, projections may be integrally formed on the inner and outer surfaces of the pipe walls 41 and 51 of the smooth pipe in a spiral shape, and uneven processing may be performed. The inner and outer surfaces of the tube walls 41 and 51 may be processed integrally by providing them in the same manner as the protrusions. Furthermore, a plurality of projections or grooves extending in the axial direction may be integrally formed on the inner and outer surfaces of the tube walls 41 and 51 at predetermined intervals in the circumferential direction with respect to the smooth tube. As described above, as long as the surface area of each of the heat transfer tubes 40 and 50 is increased, the method for forming the inner and outer surfaces of the tube walls 41 and 51 is free.

  In the vacuum evaporation type water producing apparatus 1 of the present embodiment, the inner and outer surfaces of the heat transfer tubes 40, 50 of the condenser 4 and the preheater 5 are roughened, so that the outer diameter is compared with the smooth tube having substantially the same As a result, the surface area of each heat transfer tube 40, 50 is increased, that is, a larger heat transfer area can be secured during heat exchange inside the heat transfer tube, and the cooling seawater flowing in the heat transfer tube is agitated by the unevenness. As a result, the heat transfer efficiency between the steam and the cooling seawater on the heat transfer surface (the pipe walls 41 and 51) is improved, and as a result, the amount of heat exchange of the heat transfer pipes 40 and 50 is increased. Therefore, by processing the inner and outer surfaces of each heat transfer tube 40, 50 to be uneven, the temperature of the cooling seawater flowing in each heat transfer tube 40, 50 is further increased by heat exchange with steam, as compared with the case where smooth tubes are used. As a result of being able to heat, the temperature of the raw material seawater supplied to the heater 3 can be made higher. Therefore, it is possible to further improve the thermal efficiency of the heater 3.

On the other hand, when the inner and outer surfaces of the heat transfer tubes 40 and 50 are roughened, the tube friction coefficient is increased due to the unevenness, and the pressure loss of the cooling seawater flowing in the heat transfer tube is increased. Therefore, in order to prevent the deterioration of the flow of the seawater for cooling, it is necessary to take measures such as increasing the size of the heat transfer tube or increasing the capacity and lift of the seawater pump. The condenser 4 is supplied with seawater after being pressurized by the seawater pump 11, so it is unlikely to be affected by the increase in pressure loss, but the cooling water discharged from the condenser 4 is not affected by the preheater 5. Since the pressure loss of the preheater 5 itself is also increased, the pressure of seawater at the raw material seawater outlet 101, which is the outlet of the preheater 5, is greatly reduced compared to when a smooth tube is used. When the pressure loss increases and the seawater supply pressure from the raw material seawater outlet 101 decreases, the raw material seawater may not be sufficiently supplied to the heater 3. In order to solve this, it is conceivable to increase the capacity and lift of the seawater pump 11. However, if the capacity etc. of the large seawater pump 11 for supplying seawater to each seawater using point in the ship is increased, There is a problem that the operating cost is greatly increased, such as the cost of itself and the amount of power consumption. Therefore, in the vacuum evaporation type water producing apparatus 1 of the present embodiment, the small auxiliary pump 9 is provided in the water supply pipe line 15 between the condenser 4 and the preheater 5, and the cooling pump discharged from the condenser 4 is provided. Seawater is pressurized by the auxiliary pump 9 and then supplied to the preheater 5. Thereby, also in the preheater 5, it is possible to cope with the increase in pressure loss of the cooling seawater while promoting heat exchange with the steam, so that the feed water amount of the raw material seawater to the heater 3 is sufficiently ensured. Is possible.

  According to the vacuum evaporation type water producing apparatus 1 of the above configuration, the multi-tube type preheater 5 is provided above the multi-tube type condenser 4 of the container body 2 to heat the raw material seawater supplied to the heater 3 Therefore, the device can be miniaturized without requiring a space for separately providing the preheater 5 with the condenser 4.

  Furthermore, since the inner and outer surfaces of the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5 are processed to be uneven, the heat transfer performance 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 via the preheater 5 can be compared to that of the existing vacuum evaporation type water producing apparatus in which the heat transfer pipes 40, 50 are formed of smooth pipes. Because the temperature can be increased, the thermal efficiency of the heater 3 can be further improved. In addition, the auxiliary pump 9 is provided in the water supply line 15 between the condenser 4 and the preheater 5, and the seawater for cooling discharged from the condenser 4 is pressurized by the auxiliary pump 9, and Since it supplies, it can respond to the increase in the pressure loss of the seawater for cooling (raw material seawater) which flows through the inside of each heat exchanger tube 50 of preheater 5. Therefore, 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 producing apparatus 1 can be increased, and the water producing performance of the apparatus can be improved. On the other hand, the heat transfer tubes of the condenser 4 and the preheater 5 are improved by the improvement of the water production performance of the apparatus compared to the existing vacuum evaporation type water production apparatus in which the heat transfer pipes 40, 50 are constituted by smooth tubes Even if the number of 40, 50 is reduced, it is possible to produce almost the same amount of fresh water. Therefore, the apparatus can be made compact.

  Further, in the existing vacuum evaporation type water producing apparatus in which each heat transfer pipe 40, 50 is constituted by a smooth pipe, the smooth pipe is replaced with a corrugated pipe or a processed pipe whose inner and outer surfaces are roughened. Since the water production performance is improved, it is possible to upgrade the existing vacuum evaporation type water production system simply and at low cost.

  As mentioned above, although one Embodiment of this invention was described, this invention is not limited to above-mentioned embodiment, A various change is possible unless it deviates from the meaning of this invention. For example, in the embodiment of FIG. 1 described above, the inner surface and the outer surface of each heat transfer tube 40, 50 are unevenly processed, but only one of the inner surface or the outer surface may be unevenly processed.

  In addition, although each heat transfer pipe 40, 50 of the condenser 4 and the preheater 5 is subjected to uneven processing, each heat transfer pipe 40 of the condenser 4 or each heat transfer pipe 50 of the preheater 5 is only You may make it uneven process.

Further, as in the case of the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5, uneven processing may be performed on the heating tubes 31 of the heater 3. FIG. 6 shows an embodiment (a modified example of FIG. 2) in which each heating tube 31 of the heater 3 is also subjected to uneven processing in addition to the heat transfer tubes 40 and 50 of the condenser 4 and the preheater 5. There is. Each heating pipe 31 is, like the heat transfer pipes 40 and 50 of the condenser 4 and the preheater 5, as shown in FIG. 7, a large number of convex portions 31B and concave portions 31C alternately and continuously on the pipe wall 31A. The surface and the surface are roughened. The cross sectional shapes of the convex portion 31B and the concave portion 31C are not limited to the mountain shape as shown in FIG.
It can be formed into various shapes such as a rectangular shape and a wave shape as shown in the above. Although a corrugated pipe can be used suitably as heating pipe 31 of the above-mentioned composition, in addition to a corrugated pipe, a plurality of annular projections which extend in the circumferential direction with respect to a smooth pipe in which pipe wall 31A is smooth It is also possible to use a processed pipe that is roughened by integrally providing the inner surface and the outer surface of the wall 31A at predetermined intervals in the axial direction. In addition, as a processed pipe, projections may be integrally formed on the inner surface and the outer surface of the smooth pipe in a spiral shape, and uneven processing may be performed, and instead of the projections, grooves are formed in the pipe wall of the smooth pipe Uneven processing may be performed by integrally providing the inner surface and the outer surface of 31 A in the same manner as the protrusions. Further, a plurality of projections or grooves extending in the axial direction may be integrally formed on the inner and outer surfaces of the pipe wall 31A at predetermined intervals in the circumferential direction with respect to the smooth pipe. As described above, as long as the surface area of each heating tube 31 is increased, the method for forming the inner and outer surfaces of the tube wall 31A is free.

  By subjecting the inner surface and the outer surface of each heating tube 31 of the heater 3 to unevenness, the surface area of each heating tube 30 is increased as compared to a smooth tube having substantially the same outer diameter. A large heat transfer area can be secured at the time of replacement. Furthermore, the raw material seawater flowing in the heating pipe is agitated by the unevenness, so that the heat transfer efficiency between the hot water and the raw material seawater on the heat transfer surface (the pipe wall 31A) is improved. As a result, the heat exchange amount of each heating tube 31 is increased. Therefore, as in the embodiment shown in FIG. 6, by roughing the inner and outer surfaces of each heating tube 31, the raw material seawater flowing in each heating tube 31 efficiently with warm water as compared to the case where a smooth tube is used. As a result of heat exchange being performed and the heating efficiency by each heating tube 31 being enhanced, the evaporation efficiency of the raw material seawater can be made favorable, and steam can be sufficiently supplied into the container main body 2.

  Further, in the embodiment of FIG. 1 described above, waste heat from the diesel engine is used as a heat source for heating and evaporating the raw material seawater in the heater 3, but in addition, waste from the engine generating waste heat Heat may be used, or steam from the boiler may be used to heat and evaporate the raw material seawater in the heater 3.

  Further, in the embodiment of FIG. 1 described above, a portion of the cooling seawater discharged from the condenser 4 is pressurized by the auxiliary pump 9 and supplied to the preheater 5 via the water supply pipe 15. However, this auxiliary pump 9 can be omitted. FIG. 8 is a modification of the embodiment of FIG. 1 and shows a schematic configuration view of the vacuum evaporation type water producing apparatus 1 in which the auxiliary pump 9 is omitted. The basic configuration is the same as the configuration of the embodiment of FIG. 1 described above, and the description will be omitted by attaching the same reference numerals to the corresponding configurations.

  In the embodiment of FIG. 8, part of the cooling seawater discharged from the condenser 4 is supplied to the ejector pump 8 through the branch conduit 14, and the rest is discharged out of the ship or the like. The seawater for cooling supplied to the ejector pump 8 is boosted by the ejector pump 8 and then partially supplied to the water ejector 7 while the rest is supplied to the preheater 5 via the water supply conduit 19 . Then, the seawater for cooling supplied to the preheater 5 is heated by heat exchange with the vapor supplied to the inside of the container body 2, and then is supplied to the heater 3 as the raw material seawater via the raw material seawater supply pipeline 16. Supplied. Thus, in the embodiment of FIG. 8, the pipe line on the discharge side of the ejector pump 8 is branched, and the pressurized seawater for cooling by the ejector pump 8 is supplied to the preheater 5 through the water supply pipe 19. Accordingly, it is possible to cope with the increase in the pressure loss of the cooling seawater flowing in the heat transfer pipes 50 of the preheater 5, and the raw material seawater can be sufficiently supplied to the heater 3. As a result, the same operation and effect as the embodiment of FIG. 1 can be realized, and since the auxiliary pump 9 is not necessary, the apparatus can be simplified.

Further, although the ejector pump 8 is provided integrally with the apparatus main body 6 in the embodiment of FIG. 1 described above, the ejector pump 8 may be installed below the apparatus main body 6 as shown in FIG. Good. In the embodiment of FIG. 1, a part of the cooling seawater discharged from the condenser 4 was supplied to the ejector pump 8. However, in the embodiment of FIG. The pump is supplied to the water ejector 7 as driving water.

  Further, although the water ejector is used as the pressure reducing means 7 in the embodiments of FIGS. 1, 8 and 9, the invention is not necessarily limited to this, and a vacuum pump or the like may be used.

  Furthermore, FIG. 10 shows a schematic configuration diagram of a vacuum evaporation type water producing apparatus 1 according to another embodiment of the present invention. The basic configuration is the same as that of the embodiment shown in FIG. 1 described above, and the detailed description will be omitted by attaching the same reference numerals to the corresponding configurations.

  In the embodiment of FIG. 10, seawater supplied from the ejector pump 8 to the water ejector 7 as driving water is supplied to the condenser 4 through the cooling water supply circuit 13 for water production by the vacuum evaporation type water producing apparatus 1 It is supplied as cooling water. As the ejector pump 8, a small pump that pumps up seawater from the sea and supplies this to only the water ejector 7 is used.

  Also in the embodiment of FIG. 10, the cooling seawater supplied to the condenser 4 cools and condenses the vapor supplied in the container main body 2 to generate fresh water, and then is discharged from the condenser 4. However, after being partially heated by heat exchange with the steam supplied to the preheater 5 and supplied into the container main body 2, a seawater supply chamber as the raw material seawater via the raw material seawater supply pipe 16 Supplied to 32 Here, by subjecting at least one of the inner surface and the outer surface of each heat transfer pipe 50 of the preheater 5 (and further each heat transfer pipe 40 of the condenser 4) to uneven, the temperature of the raw material seawater supplied to the heater 3 By making it high, 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 unnecessary by raising the capacity of the ejector pump 8 and the cost of the preheater 5 is lower than raising the capacity of the seawater pump 11. As it is possible to cope with the increase in the pressure loss of the cooling seawater flowing in the heat transfer tubes 50 (and the heat transfer tubes 40 of the condenser 4), the raw seawater can be sufficiently supplied to the heater 3. As a result, the same operation and effect as the embodiment of FIG. 1 can be realized.

DESCRIPTION OF SYMBOLS 1 Vacuum evaporation type water production apparatus 2 Container main body 3 Heater 4 Condenser 5 Preheater 7 Water ejector 8 Ejector pump 9 Auxiliary pump 11 Seawater pump 31 Heating tube 40, 50 Heat transfer tube

Claims (6)

In a vacuum evaporation type water producing apparatus that produces fresh water from seawater taken into a ship using heat from a heat source mounted on the ship,
A heater that generates steam by heating supplied raw seawater with heat from a heat source;
A closed container body into which steam generated by the heater is introduced;
Decompression means for decompressing the inside of the container body;
A condenser having a plurality of heat transfer tubes and cooling the steam in the container body with cooling seawater to generate fresh water;
And a preheater having a plurality of heat transfer tubes and heating a part of the cooling seawater discharged from the condenser with the steam in the container body to supply the heater with raw water.
The heat transfer tubes of at least one of the condenser and the preheater are roughened on the inner surface or the outer surface,
Between the condenser and the preheater, there is provided an auxiliary pump which pressurizes part of the cooling seawater discharged from the condenser and supplies it to the preheater. apparatus. A pump for supplying cooling seawater to the condenser;
The vacuum evaporation type water producing apparatus according to claim 1 , wherein the pump is a seawater pump for supplying seawater pumped from the sea to each seawater use point of the ship. The heat transfer tubes, vacuum evaporative desalination apparatus according to claim 1 or 2 is constituted by a corrugated tube. The vacuum evaporation type water producing apparatus according to any one of claims 1 to 3 , wherein the heat transfer tube is roughened by integrally providing a protrusion or a groove on an inner surface or an outer surface. The decompression means is a water ejector driven by seawater,
An ejector pump for supplying driving seawater to the water ejector is integrally provided in an apparatus body including the container body, the heater, the condenser, and the preheater.
The vacuum evaporation type water producing apparatus according to claim 1 , wherein the ejector pump pressurizes a part of the cooling seawater discharged from the water condenser and supplies the pressurized seawater to the water ejector. The decompression means is a water ejector driven by seawater,
An ejector pump for supplying driving seawater to the water ejector is disposed below an apparatus body including the container body, the heater, the condenser, and the preheater,
The vacuum evaporation type water producing apparatus according to claim 1 , wherein the ejector pump pressurizes seawater pumped from the sea and supplies the pressurized seawater to the water ejector.

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