JP2020034234A - Heat exchanger - Google Patents

Abstract

To provide a heat exchanger capable of efficiently progressing evaporation of low-temperature fluid in parallel to condensation of high-temperature fluid by arranging a heat exchange part combined with a plate in a proper direction in a shell so as to make the part surely perform heat exchange between gas phase high-temperature fluid and liquid phase low-temperature fluid.SOLUTION: A heat exchanger 10 serving as a condenser for heat exchanging between steam and working fluid of a steam power cycle and condensing steam, and an evaporator for evaporating working fluid employs a structure in which a heat exchange part 11 in which a plurality of heat exchanging plates are integrated in a parallel state is arranged in a shell 12. Flow channels through which steam and working fluid pass are alternately generated between the heat exchanging plates in parallel, steam and working fluid are circulated in the flow channels so as to be cross flow each other, and the working fluid is evaporated and the steam is condensed so as to downsize the heat exchange part 11 due to heat exchange via the heat exchanging plates, and achieve downsizing of the whole system including the heat exchanger 10.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a heat exchanger that can be used as an evaporator and a desalination condenser for a steam power cycle, for example, adapted to a hybrid cycle type ocean thermal energy conversion device.

Ocean temperature difference power generation, which generates power using the temperature energy of surface seawater and deep seawater in the ocean, is expected to be put to practical use, and research and development are being promoted in various countries.
As the method of the ocean temperature difference power generation, three types of open cycle, closed cycle and hybrid cycle are widely known. Of these, the hybrid cycle employs a steam power cycle that uses a low-boiling-point medium as the working fluid, as in the closed cycle, thereby eliminating the need for a special turbine as in the case of the open cycle, and the use of steam as a high-temperature heat source. As in the case of closed cycle, in the evaporator of the working fluid, the surface seawater as a high-temperature heat source and the evaporator heat transfer surface come into contact with each other, and the heat transfer surface is corroded by biological dirt and seawater. It is not necessary to worry about the generation of seawater, and the water condensed with water vapor derived from seawater used for heat exchange with the working fluid in the evaporator can be used for drinking, etc. Practical application in areas that require desalination is desired.

  In such an ocean temperature difference power generation system using a hybrid cycle, an evaporator that evaporates the working fluid evaporates the working fluid by exchanging heat with the steam that evaporates the seawater and at the same time condenses the steam and condensate. As freshwater, and also serves as a condenser for seawater desalination equipment.

As a heat exchanger that functions as both an evaporator and a condenser, the use of a shell-and-tube heat exchanger has been considered.However, in an ocean thermal energy conversion system, the temperature difference between each heat exchange medium is small. As a result, it is inevitable to increase the scale of the heat exchanger.Therefore, as a heat exchanger for such an application, a plate-type heat exchanger that is easy to achieve compactness by using a plate as a heat transfer element, Improved applications have been proposed.
An example of such a conventional plate-type heat exchanger is described in Japanese Patent No. 3100371.

Japanese Patent No. 3100371

  The conventional plate-type heat exchanger can be made compact by using a plate as a main component as shown in the patent document. In the case of a heat exchanger mainly used as an evaporator as shown in the above-mentioned patent document, evaporation, that is, a phase change from a liquid phase to a gas phase occurs in a flow path on the working fluid side. Has a configuration in which evaporation is efficiently performed, that is, a flow path of a working fluid to be evaporated extends in a vertical direction.

  Considering the application of such a conventional evaporator to an evaporator for evaporating a working fluid in a hybrid cycle ocean temperature difference power generation system, an evaporator that evaporates a working fluid in a hybrid cycle system simultaneously condenses water vapor. Thus, a condensate of fresh water is obtained, and the steam side can be regarded as a condenser.

  If the flow path on the water vapor side (high-temperature fluid side) of the conventional evaporator shown in the above-mentioned patent document is made to be in the vertical direction so that the condensation is efficiently performed on the water vapor side, the conventional evaporator will have a heat Since the fluids to be exchanged have a cross-flow configuration, the flow path on the working fluid side in the evaporator is horizontal. In this case, when the liquid-phase working fluid that flows laterally into the heat exchanger evaporates by heat exchange, the evaporated gas-phase working fluid flows upward with respect to the liquid-phase working fluid. The problem is that the working fluid does not stay in the upper part of the flow path and does not come out of the heat exchanger, and the remaining gas phase inhibits the contact between the liquid working fluid and the heat transfer surface, and As the efficiency of evaporation decreases, the stagnant portion becomes thermal resistance, and the efficiency of heat exchange with steam through the heat transfer surface decreases at this portion, so that the liquid phase operation through the heat transfer surface as a whole heat exchanger The heat exchange between the fluid and the steam does not proceed well, and there is a problem that the efficiency of condensation cannot be increased as expected.

  Further, in the conventional evaporator, as in the case of a general evaporator, if the flow path on the side of the working fluid to be evaporated is set to be in the vertical direction so that the evaporation is performed efficiently, The flow path on the (high-temperature fluid side) is horizontal. In this case, when the steam flowing laterally into the heat exchanger is condensed by heat exchange, the condensate after condensation flows downward with respect to the vapor in the gas phase, and the condensate in which the water vapor is condensed flows into the flow path. Collected in the lower part, it is difficult to discharge from the horizontal opening, there is a problem that it stays inside and re-evaporates or generates thermal resistance as a supercooled liquid part, and the amount of steam and working fluid As described above, there is a problem that the efficiency of evaporation of the heat exchanger as a whole cannot be increased as expected due to a decrease in the efficiency of heat exchange.

  The present invention has been made in order to solve the above-mentioned problem, and a heat exchange unit in which plates are combined is arranged in an appropriate direction in a shell, and heat exchange between a gas-phase high-temperature fluid and a liquid-phase low-temperature fluid is reliably performed. It is an object of the present invention to provide a heat exchanger in which evaporation of a low-temperature fluid and condensation of a high-temperature fluid can efficiently and concurrently proceed in a heat exchange section.

  The heat exchanger according to the present invention exchanges heat between the high-temperature fluid in the gas phase and the low-temperature fluid in the liquid phase flowing from the outside through the heat exchange section made of a heat-conductive material, thereby condensing the high-temperature fluid in the gas phase. In a heat exchanger for evaporating a low-temperature fluid in a liquid phase, a heat exchanger for evaporating a low-temperature fluid in a liquid phase has an internal space separated from the outside by a partition, and the high-temperature fluid in a gas phase can be introduced into the internal space from the outside and condensed from the internal space to the outside. A high-temperature fluid in a liquid phase can be taken out, and a hollow container-like shell provided with a flow path for inflow and outflow of the low-temperature fluid that penetrates a partition wall is provided.The high-temperature fluid in a gas phase is steam, The low-temperature fluid in the liquid phase is a working fluid of the steam power cycle and is in the liquid phase, and the heat exchange unit is configured to perform a plurality of heat exchange plates made of a substantially rectangular metal thin plate in a plurality of juxtaposed states by a predetermined substantially Adjacent heat exchange plugs at two parallel While being welded in a watertight state with the heat exchanger, the other adjacent heat exchange plates and the other substantially parallel two end portions substantially orthogonal to the two end sides are welded in a watertight state and all integrated, and A first flow path through which the steam and the condensed water condensed by the water vapor pass and a second flow path through which the working fluid passes are generated between the heat exchange plates, and the steam and the condensed water can flow in and out. An opening portion of the first flow passage and an opening portion of the second flow passage through which a working fluid can flow in and out are formed as a right-angled arrangement, and the heat exchange portion is provided in the internal space of the shell, A predetermined gap is interposed between the inner surface of the shell partition other than the opening of the two flow paths, and the opening of the first flow path is disposed vertically, and the inflow / outflow flow path and the second flow path are disposed. And the opening portion of the passage is connected to Heat exchange between the working fluid in the liquid phase flowing into the shell and the steam flowing from the inner space of the shell, and in the heat exchange, the steam is condensed to obtain fresh water as condensed water. And a vapor power cycle evaporator for vaporizing the working fluid to obtain a gas-phase working fluid.

  As described above, according to the present invention, heat exchange is performed between steam and a working fluid of a steam power cycle, and a condenser for desalination that obtains fresh water by condensing steam and a working fluid in a liquid phase is vaporized by evaporating a working fluid in a liquid phase. As a heat exchanger that also serves as an evaporator that obtains the working fluid, a structure in which a heat exchange unit in which a plurality of substantially rectangular heat exchange plates are integrated in a parallel state is arranged in a shell is adopted. Between each of the parallel heat exchange plates to be formed, every other flow path through which the steam to be heat-exchanged and the working fluid pass is generated, and the steam and the working fluid are separated in each of these flow paths by the heat exchange plate. The heat exchange section can be downsized by allowing heat to flow through the heat exchange plate by evaporating the working fluid and condensing the steam. , Desalination and steam power system with heat exchanger Cycle mechanisms unloading with size of the entire system and its included can be achieved. In addition, the steam can linearly and smoothly enter the first flow path between the parallel heat exchange plates of the heat exchange section from the internal space of the shell, and the pressure loss in the flow path can be suppressed, and the condensation can be smoothly progressed. The water can flow down and can be taken out efficiently. Furthermore, since the contact between the water vapor and the heat exchange plate and the resulting heat transfer occur smoothly without interruption, heat exchange between the water vapor and the liquid-phase working fluid flowing into the second flow path separating the plate also occurs. The working fluid can be smoothly advanced, and the working fluid can be efficiently evaporated.

  Further, in the heat exchanger according to the present invention, if necessary, the heat exchange portion may be provided in the shell internal space, and the opening of the second flow path on the working fluid outflow side may be provided with respect to the opening of the working fluid inflow side. The heat exchanging section is disposed so as to be inclined so as to be on the upper side.

  As described above, according to the present invention, the heat exchange unit is disposed in the shell internal space in an inclined state, the liquid-phase working fluid flows into the second flow passage of the heat exchange unit, and the liquid-phase working fluid is exchanged with steam for heat exchange. When evaporating in the second flow path, the gas-phase working fluid is directed toward the upper part and the opening part of the second flow path due to the property of moving upward to the generated gas-phase working fluid, so that the gas-phase working fluid is Even if the gas-phase working fluid continues to move upward in the second flow path, the working fluid does not stay in the upper part of the second flow path, and the accumulated gas-phase working fluid Prevents the liquid-phase working fluid from contacting the surface of the heat exchange plate with the liquid-phase working fluid, thereby reliably preventing heat exchange between the liquid-phase working fluid and steam and evaporation of the working fluid from being performed smoothly. Evaporation of working fluid and condensation of water vapor can be performed efficiently with a heat exchanger

  In addition, the water condensed in the first flow path gathers on the side where the heat exchange part is inclined, and flows down from the predetermined range, which is the lowermost part of the opening, to the outside of the heat exchange part, and receives the condensed water. As a result, the size of the water recovery section leading to the outside of the shell can be reduced, and the heat exchanger can be made more compact.

  Further, the heat exchanger according to the present invention has, as necessary, a hollow depressurized container having an evaporating space communicating with the inner space of the shell therein, and the evaporating space being in a depressurized state lower than the atmospheric pressure. And an injection unit that is disposed in the decompression container and that injects seawater introduced from the outside into the internal space of the decompression container, and is disposed at least in communication with the evaporation space of the decompression container, and the evaporating space And a pressure reducing device that adjusts the internal space of the shell to a pressure lower than the saturated vapor pressure of the seawater, wherein the seawater injected from the injection unit is flash-evaporated in the evaporation space of the pressure-reducing container, and the water vapor obtained by evaporation is provided. Is condensed in the heat exchange section.

  As described above, according to the present invention, an injection unit that injects seawater into the evaporation space of the decompression container communicating with the internal space of the shell is provided, and the seawater is sprayed, sprayed, water film-shaped, or water column-shaped from the injection unit. , Etc., and the evaporating space is depressurized by the decompression device, seawater is flash-evaporated in the evaporating space, and the obtained water vapor is guided to the inner space of the shell and condensed in the heat exchange part. By continuously introducing the water vapor evaporated from the seawater into the heat exchange section, seawater desalination can be performed efficiently, and energy consumption related to evaporation and condensation other than the pressure reducing device that lowers the pressure in the pressure reducing vessel can be suppressed. This means that fresh water can be obtained at low cost. Furthermore, if the seawater to be evaporated is obtained by recovering predetermined exhaust heat, heat energy corresponding to the temperature difference with the working fluid in the heat exchanger can be recovered by the steam power cycle, and the yield of condensed water can be secured. Waste heat can be used effectively, and energy use efficiency can be increased.

  Further, in the heat exchanger according to the present invention, if necessary, the decompression container is provided integrally with the shell below the shell, and one of the partition walls separating the evaporation space of the decompression container and the internal space of the shell. The part is a mist removal part that prevents the seawater of the liquid present in the evaporation space from proceeding to the interior space of the shell while allowing the movement of gas from the evaporation space to the interior space of the shell. is there.

  As described above, according to the present invention, the decompression container is integrated with the shell, the inner space of the shell and the evaporating space are brought close to each other, and the steam generated in the evaporating space is quickly passed through the inner space of the shell to form the heat exchange section. By flowing into one flow path, the pressure loss of the steam moving to the heat exchange section can be reduced, and the temperature drop of the steam and the accompanying decrease in the heat exchange performance can be prevented, and the condensation of the steam and the evaporation of the working fluid can be efficiently performed. Can proceed. In addition, the space for evaporation and the internal space of the shell are separated by the mist removing part, and while the water vapor is allowed to advance to the shell internal space, seawater is prevented from proceeding from the evaporation space to the shell internal space, Even if the evaporating space where seawater is present is located close to the shell internal space, seawater components will not accidentally flow into the heat exchange section, thus reliably preventing contamination and corrosion of the heat exchange section and reducing maintenance frequency. Can be suppressed.

  In the heat exchanger according to the present invention, if necessary, the liquid level position of the liquid-phase working fluid in the working fluid circulation flow path of the steam power cycle is set above the heat exchange unit, and the heat exchange unit The working fluid in the liquid phase exists in the entire second flow path, and can exchange heat with the steam in the first flow path via the heat exchange plate of the heat exchange unit.

  As described above, according to the present invention, the level of the liquid phase working fluid in the working fluid flow path of the steam power cycle is adjusted so that the level of the liquid phase working fluid is above the heat exchange unit, and the working fluid is steam When evaporating in the second flow path by heat exchange with, the generated gas-phase working fluid travels upward as bubbles while traveling in the liquid phase working fluid that has not evaporated toward the opening of the second flow path, By flowing out from the opening to the outside, even if the gas-phase working fluid continues to move upward in the second flow path, the working fluid does not stay at the upper part of the second flow path, and the accumulated gas-phase working fluid is in the liquid phase. It is possible to reliably prevent a state in which heat exchange between the liquid-phase working fluid and steam and evaporation of the working fluid are not performed smoothly by preventing contact between the working fluid and the surface of the heat exchange plate. To efficiently evaporate the working fluid and condense water vapor Kill.

  In addition, the heat exchanger according to the present invention, if necessary, of at least one of the upper and lower openings of the first flow path in the heat exchange section, on the cooling fluid inflow side in the second flow path. A substantially box-shaped non-condensable gas collecting portion, which is disposed so as to cover a predetermined range portion close to the opening portion, and has one open end communicating with an inner region of the non-condensing gas collecting portion, and an outer portion of the shell. And a substantially tubular non-condensable gas discharge portion that is disposed with the other open end positioned at the other end thereof and that can discharge the non-condensable gas collected in the non-condensable gas collection portion to the outside of the shell.

  As described above, according to the present invention, the condensation easily proceeds at a low temperature near the entrance of the second flow path in the first flow path, and the non-condensable gas is collected along the area where the non-condensable gas contained in the steam is likely to stay. A non-condensable gas discharge section is provided to connect the non-condensable gas discharge section, and the non-condensable gas can be discharged to the outside of the flow path through the non-condensable gas collection section and the non-condensable gas discharge section. It can be drawn to the condensed gas collecting part and removed from the first flow path to the outside, and it is possible to prevent the uncondensed gas accumulated in the first flow path from interfering with the contact between the water vapor and the heat exchange plate and preventing the condensation from proceeding. Can be efficiently condensed

  In the heat exchanger according to the present invention, heat exchange is performed between the gaseous high-temperature fluid and the liquid-phase low-temperature fluid flowing from the outside through the heat exchange unit made of a heat conductive material, and the gaseous high-temperature fluid is condensed. In the heat exchanger for evaporating the low-temperature fluid in the liquid phase, the heat exchanger has an internal space separated from the outside by the partition, and the high-temperature fluid in the gas phase can be introduced into the internal space from the outside, and can be introduced from the internal space to the outside. A high-temperature fluid in a condensed liquid phase can be taken out, and a hollow container-like shell provided with a low-temperature fluid inflow / outflow passage that penetrates a partition wall is provided, and the plurality of heat exchange units are substantially in parallel. Each of the heat exchange plates made of a rectangular metal sheet is welded in a predetermined substantially parallel two end portions to one adjacent heat exchange plate and in a watertight state, while another adjacent heat exchange plate is The other substantially parallel two ends substantially orthogonal to the two end sides The parts are welded in a watertight state at the site and are all integrated, and a first flow path through which the high-temperature fluid passes and a second flow path through which the low-temperature fluid passes between the respective heat exchange plates are generated alternately, and the high-temperature fluid is generated. An opening portion of the first flow path that can flow in and out and an opening portion of the second flow path that can flow in and out of the low-temperature fluid are formed so as to form a right angle, and the heat exchange portion is provided in an inner space of the shell. An opening on the low-temperature fluid outflow side in the second flow path while interposing a predetermined gap between the second flow path and the inner surface of the shell partition other than the opening part, and positioning the opening part of the first flow path up and down. The entire heat exchange unit is disposed to be inclined so that the portion is located above the opening portion on the low temperature fluid inflow side, and the low temperature fluid inflow / outflow channel and the opening portion of the second channel are connected, Liquid-phase cryogenic fluid flowing through the cryogenic fluid inflow / outflow channel A gas phase hot fluid flowing from the shell inner space is intended to heat exchange.

  As described above, according to the present invention, a heat exchange unit in which a plurality of substantially rectangular heat exchange plates are integrated in a parallel state is disposed in an inclined state in the shell internal space, and each of the parallel heat exchange units is formed. Between the heat exchange plates, first and second passages are alternately generated through which a gas-phase high-temperature fluid and a liquid-phase low-temperature fluid to be subjected to heat exchange are generated. The low-temperature fluid is passed through the heat exchange plate so as to form a cross-flow, and the high-temperature fluid in the gas phase is condensed and the low-temperature fluid in the liquid phase is evaporated. By exchanging heat between the heat exchanger and the low-temperature fluid, the heat exchange unit can be downsized, so that the entire system including the heat exchanger can be downsized and the load can be reduced accordingly. Also, when the liquid-phase low-temperature fluid flows into the second flow path of the heat exchange section with respect to the inclined heat exchange section, and evaporates in the second flow path by heat exchange with the high-temperature fluid, the generated gas phase Due to the nature of the low-temperature fluid, which tends to move upward, toward the upper part of the second flow path and toward the opening of the second flow path, the gas-phase low-temperature fluid flows from the upper part of the opening part of the second flow path. Even if the gas-phase low-temperature fluid continues to move upward in the second flow path, the low-temperature fluid does not stay at the upper part of the second flow path, and the accumulated gas-phase low-temperature fluid and the liquid-phase low-temperature fluid are heated. The heat exchange between the liquid-phase low-temperature fluid and the gas-phase high-temperature fluid and the evaporation of the liquid-phase low-temperature fluid do not occur smoothly by preventing the contact with the surface of the exchange plate, thereby ensuring the heat exchange. It is possible to efficiently evaporate the liquid-phase low-temperature fluid and condense the gas-phase high-temperature fluid in the vessel.

It is a front view of the heat exchanger concerning a 1st embodiment of the present invention. It is a schematic structure explanatory view of the heat exchange part in the heat exchanger concerning a 1st embodiment of the present invention. 1 is a schematic explanatory diagram of an ocean temperature difference power generation system to which a heat exchanger according to a first embodiment of the present invention is applied. It is a longitudinal section of the heat exchanger concerning a 1st embodiment of the present invention. It is a longitudinal section of the heat exchanger concerning a 2nd embodiment of the present invention. It is a front view of the heat exchanger concerning a 3rd embodiment of the present invention. It is a schematic perspective view of a heat exchange part and a non-condensable gas collection part in a heat exchanger concerning a 3rd embodiment of the present invention. FIG. 13 is a schematic perspective view of another heat exchange unit and a non-condensable gas collection unit in the heat exchanger according to the third embodiment of the present invention. It is a schematic front view of a heat exchange part and a non-condensable gas collection part in a heat exchanger concerning a 4th embodiment of the present invention. It is a partially cutaway perspective view of the non-condensable gas collection part in the heat exchanger concerning a 4th embodiment of the present invention. It is an explanatory view of the attachment state to the plate for heat exchange of the non-condensable gas collection part in the heat exchanger concerning a 4th embodiment of the present invention.

(First embodiment of the present invention)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. In this embodiment, an example in which the present invention is applied to a hybrid cycle type ocean thermal energy conversion system will be described.

  In each of the drawings, the heat exchanger 10 according to the present embodiment is formed by integrating a plurality of heat exchange plates 15 made of a plurality of substantially rectangular metal thin plates in a parallel state, and is provided with a gas-phase high-temperature fluid flowing in from the outside. A hollow container-like shell having a heat exchange unit 11 for exchanging heat with a low-temperature fluid in a liquid phase, and an internal space separated from the outside by a partition, and arranged so as to house the heat exchange unit 11 in this internal space. 12 is provided.

  The heat exchange unit 11 is disposed in the internal space of the shell 12 and exchanges heat between a high-temperature fluid flowing from the outside and a liquid-phase working fluid as a low-temperature fluid to condense the vapor and condense liquid. In addition, at least a part of the liquid-phase working fluid is evaporated to obtain a gas-phase working fluid.

  The heat exchange unit 11 is configured such that each of the plurality of heat exchange plates 15 made of a substantially rectangular metal thin plate is arranged in a watertight state with one heat exchange plate adjacent at two predetermined end portions that are substantially parallel to each other. On the other hand, the other heat exchange plates adjacent to each other and the other substantially parallel two end sides substantially orthogonal to the two end sides are welded in a watertight state, and all are integrally formed. (See FIG. 2).

  The heat exchange unit 11 has one first passage 15b between the heat exchange plates 15 through which the steam and the condensate condensed by the steam pass, and one second passage 15c through which the working fluid passes. The opening of the first flow passage 15b, which is generated every other time, and through which the vapor and the condensate can flow, and the opening of the second flow passage 15c, through which the working fluid can flow, are arranged at a right angle. Configuration. That is, the heat exchange section 11 has a so-called cross-flow heat exchanger structure in which the steam flowing through each of the first flow paths 15b and the working fluid flowing through each of the second flow paths 15c form a cross flow. .

  In addition, the heat exchange unit 11 tilts the entire heat exchange unit into the inner space of the shell 12 such that the opening on the working fluid outflow side of the second flow path 15c is above the opening on the working fluid inflow side. Is arranged.

  The arrangement of the heat exchange unit 11 at an angle is not limited to a mode in which the heat exchange unit 11 is attached to the shell 12 in an inclined state (see FIG. 1), but the heat exchange unit is arranged inside. The inclined shell may be installed at an angle to obtain a state in which the heat exchange unit integrated with the shell is inclined.

  The shell 12 is formed in the shape of a hollow container having an internal space isolated from the outside, is capable of introducing steam from the outside to the internal space, and capable of taking out condensate from the internal space to the outside, and penetrates the partition. This is a configuration in which a working fluid inflow / outflow channel is provided.

  The heat exchanging portion 11 that is tilted and accommodated in the shell 12 connects the inflow / outflow passage of the working fluid and the opening of the second passage 15c, and also connects the opening other than the opening of the second passage 15c. A working fluid that is arranged so as to interpose a predetermined gap between the inner surface of the shell partition wall and the opening of the first flow path 15b so as to face up and down, and flows into each second flow path 15c through the inflow / outflow flow path; Heat is exchanged with the steam flowing into each first flow path 15b from the shell internal space.

  In addition, in the internal space of the shell 12, in response to the condensed liquid flowing down from the heat exchange unit 11 disposed at an angle, a water recovery unit 12b for receiving the condensed liquid is provided near the side surface of the shell 12. Provided.

  On the outside of the shell 12, there is provided a pipe 13 serving as a working fluid circulation flow path of a steam power cycle for allowing a working fluid to flow into and out of each of the second flow paths 15c of the heat exchange section 11 through the inflow / outflow flow path. It is a configuration to be connected. Further, outside the shell 12, a storage unit 19 for collecting the condensed liquid that flows down from the heat exchange unit 11, reaches the inner space of the shell 12, and is finally discharged out of the shell is also connected.

  The ocean temperature difference power generation system 1 to which the heat exchanger 10 according to the present embodiment is applied includes a steam power cycle unit 50 that converts heat energy obtained from a working fluid into power, and the steam power cycle unit 50 converts heat energy from heat energy. It is configured to include a power generation device 55 that generates power using the generated power, and a flash evaporator 61 that obtains water vapor by evaporating a part of seawater.

  The heat exchanger 10 is supplied with steam derived from the surface seawater generated by the flash evaporator 61 as the high-temperature fluid, and flows in through the internal space of the shell 12 and the steam flowing through the inner space of the shell 12. The heat exchange unit 11 exchanges heat with the liquid-phase working fluid to form a fresh water (seawater desalination) condenser that condenses water vapor to obtain fresh water as condensed water, and operates the liquid phase. It forms an evaporator of the steam power cycle unit 50 that evaporates the fluid to obtain a gas-phase working fluid.

  The steam power cycle unit 50 exchanges heat between a working fluid composed of a low-boiling medium such as ammonia and water vapor as the high-temperature fluid, and evaporates the working fluid to produce a vapor-phase working fluid. The exchanger 10, a turbine 52 that operates by introducing a gas-phase working fluid, and converts thermal energy possessed by the working fluid into power, and converts the gas-phase working fluid that has exited the turbine 52 into a deep seawater or the like. The condenser 53 is condensed by exchanging heat with the cooling fluid to form a liquid phase, and a pump 54 for sending the liquid-phase working fluid extracted from the condenser 53 to the evaporator 31. Among them, the turbine 52 and the pump 54 are known devices similar to those used in a general steam power cycle, and the description is omitted.

  The power generation device 55 generates power using the power converted from the thermal energy in the steam power cycle unit 50, and specifically, is driven by the turbine 52 to generate power. The power generator 55 is the same as that used for power generation using a known turbine as a drive source, and a detailed description thereof will be omitted. The steam power cycle unit 50 and the power generator 55 constitute a temperature difference power generator that generates power in a steam power cycle.

  The flash evaporator 61 has a hollow depressurized container 61a having therein an evaporating space communicating with the inner space of the shell 12 of the heat exchanger 10, and the evaporating space being in a depressurized state lower than the atmospheric pressure. An injection unit 61b disposed in the decompression container 61a and injecting seawater introduced from the outside into the evaporation space of the decompression container 61a into a mist, a water droplet, a water film, a water column, or the like; In this configuration, the seawater injected from the injection unit 61b is flash-evaporated in the evaporation space in the decompression container 61a to obtain water vapor.

  The decompression container 61 a of the flash evaporator 61 communicates with the shell 12 of the heat exchanger 10 so that the steam generated by the flash evaporator 61 can be introduced into the inner space of the shell 12.

  Further, a decompression exhaust device 16 is connected to the shell 12 of the heat exchanger 10 through a pipe or the like, and the evaporating space in the decompression container 61a of the flash evaporator 61 communicating with the inner space of the shell 12 is reduced by the decompression container. The pressure is adjusted to be lower than the saturated vapor pressure of water at the same temperature as the seawater to be evaporated in 61a, the temperature at which the water in the seawater changes (evaporates) from the liquid phase to the gaseous phase in the decompression vessel 61a, and In the heat exchange unit 11 in the shell 12, the temperature at which the vapor changes from the gaseous phase to the liquid phase (condensation) is maintained to be lower than the respective temperatures at the atmospheric pressure.

  As a result, a part of the seawater introduced into the depressurized container 61a changes from a liquid phase to a gas phase, and the temperature of the seawater remaining in the liquid phase decreases. The seawater not evaporated in the decompression container 61a is drained from the decompression container 61a and discharged to the sea.

  The seawater introduced into the flash evaporator 61 to be evaporated is, for example, warm seawater on the surface of the ocean, and the seawater taken from the sea is once led to a deaerator (not shown) to remove air in the seawater. It is led to the flash evaporator 61.

  As described above, the combination of the flash evaporator 61 for obtaining the water vapor by flash-evaporating the seawater in the decompression vessel 61a and the heat exchanger 10 for condensing the water vapor evaporated by the flash evaporator 61 is the seawater. A seawater desalination apparatus 60 for obtaining fresh water containing no salt from the seawater is provided.

  Next, an operation state of the heat exchanger based on the above configuration will be described. As a premise, both the steam power cycle unit 50 and the seawater desalination device 60 of the ocean temperature difference power generation system 1 including the heat exchanger 10 are in the operating state, and the heat exchanger 10 exchanges heat between steam and the working fluid. It is assumed that it is performed continuously.

  In the heat exchanger 10, steam derived from seawater as a high-temperature fluid flows through the first flow path 15 b of the heat exchange section 11 in the shell, and a steam power cycle as a low-temperature fluid flows through the second flow path 15 c of the heat exchange section 11. The liquid-phase working fluid in the section 50 is circulated, and heat exchange is performed between the steam passing through each of the first flow paths 15b and the working fluid passing through each of the second flow paths 15c.

  Here, focusing on the second flow path 15c through which the working fluid passes, the liquid-phase working fluid flowing into each of the second flow paths 15c of the heat exchange section 11 through the inflow / outflow flow path of the shell 12 is a heat exchange plate. The heat exchange with the water vapor in the first flow path 15b is performed via the heat pipe 15, and a part of the heat is evaporated. When the working fluid evaporates in the second flow path 15c, the gas-phase working fluid that is generated as air bubbles tends to move upward in the liquid-phase working fluid. As it goes to the upper part of the flow path 15c, it goes to the opening part on the outflow side of the second flow path 15c located on the upper side.

  As described above, since the heat exchange unit 11 is arranged at an angle such that the opening on the working fluid outflow side in the second flow path 15c is located at the top, the vapor-phase working fluid is allowed to evaporate as the evaporation proceeds. Even if the state of ascending the flow path 15c continues, the gas-phase working fluid can escape from the upper part of the opening of the second flow path 15c to the outside of the second flow path 15c, and the gas-phase working fluid can flow out of the second flow path 15c. There is no stay at the top of the.

  For this reason, when the working fluid in the liquid phase evaporates by heat exchange, as in the case where the conventional evaporator is simply provided with the working fluid flow path in the horizontal direction, the vaporized working fluid in the vaporized state flows out of the flow path. The gaseous working fluid stays at the top of the flow path without exiting, and the accumulated gas-phase working fluid prevents contact between the liquid-phase working fluid and the surface of the heat exchange plate, thereby reducing the efficiency of heat exchange between the working fluid and steam. Can be prevented.

  In this way, the heat exchanger 10 exchanges the heat of the working fluid in the liquid phase with the water vapor, raises the temperature of the working fluid, and evaporates the working fluid. The activated working fluid operates the turbine 52, and the turbine 52 drives the power generator 55 to generate power. The working fluid that has exited the turbine 52 is introduced into the condenser 53, and is condensed by heat exchange with the cooling fluid separately introduced into the condenser 53 to become a liquid phase. The working fluid in the liquid phase returns to the inside of the heat exchanger 10 after being pressurized by the pump 54, and each process after the evaporation is repeated.

  On the other hand, on the seawater desalination apparatus 60 side, first, seawater withdrawn from the sea is once led to a deaerator (not shown) to remove air in the seawater, and then introduced into the flash evaporator 61. You.

The seawater is jetted from the jetting portion 61b into the space inside the depressurized container 61a in the form of a mist, a water droplet, a water film, or a water column in the depressurized container 61a of the flash evaporator 61. Most of the water in the seawater changes into gaseous water containing no impurities, that is, water vapor by flash evaporation in the decompression vessel 61a whose pressure is reduced to about 10 to 60 mmHg, and at the same time, the temperature of the seawater drops I do.
The water vapor obtained by evaporation of the water travels in the decompression vessel 61a together with the surrounding gas, and reaches the heat exchanger 10 in a state separated from the liquid (mist).

  In the heat exchanger 10, the steam enters the internal space from the opening at the top of the shell 12. Then, the steam proceeds through the inner space of the shell 12 and flows in from the upper and lower openings in the first flow path 15b of the heat exchange unit 11. That is, the steam flows from the inner space of the shell 12 into the first flow path 15b from the upper opening portion of the first flow path 15b in the heat exchange section 11, and proceeds downward in the first flow path 15b. And heat exchange with the working fluid via the heat exchanger, condenses on the surface of the heat exchange plate 15 facing the first flow path 15b, and becomes liquid water. Further, the steam proceeds downward in the internal space of the shell 12, passes beside the heat exchange unit 11, reaches below the heat exchange unit 11, and then turns upward to be below the first flow path 15 b in the heat exchange unit 11. Also flows into the first flow path 15b from the opening portion on the side of the first flow path, and heat-exchanges with the working fluid via the heat exchange plate 15 while traveling upward through the first flow path 15b, so that the heat exchange flow faces the first flow path 15b. It condenses on the surface of the plate 15 and becomes liquid water.

  In this way, while the steam flowing into the first flow path 15b from the upper and lower openings condenses by exchanging heat with the working fluid via the heat exchange plate 15 while traveling inside the heat exchange section 11, particularly the lower opening Can quickly come into contact with the lower part of the heat exchange plate 15, the heat exchange accompanying the contact of the water vapor with each part of the heat exchange plate 15 proceeds smoothly, and uncondensed water flowing toward the inside of the heat exchanger Is sequentially condensed.

  The water condensed on the surface of the heat exchange plate 15 flows down to the lower opening portion of the first flow path 15b in the heat exchange unit 11, but the heat exchange unit 11 is disposed at an inclined position, Water condensed in the one flow path 15b flows on the surface of the heat exchange plate 15 toward the inflow side opening portion of the second flow path 15c in the lower heat exchange section 11, and gathers there. From the lowermost part of the lower opening portion to the outside of the heat exchange section 11.

Thereby, when the water recovery part 12b which receives the water condensed in the internal space of the shell 12 and guides it to the outside is provided, such a water recovery part 12b is a part that can flow down the condensed water in the lower opening portion of the first flow path 15b. The heat exchanger can be reduced to a size corresponding to the range, and the heat exchanger can be made compact.
The water flowing down from the heat exchange unit 11 goes out of the shell 12 and is collected in the storage unit 19, and is sent out to the outside as a mass of water.

  As described above, in the heat exchanger according to the present embodiment, the heat exchange is performed between the steam and the working fluid of the steam power cycle, and the condenser that condenses the steam to obtain fresh water and the working fluid in the liquid phase are evaporated. As the heat exchanger 10 also serving as an evaporator for obtaining a gas-phase working fluid, a structure in which a heat exchange unit 11 in which a plurality of substantially rectangular heat exchange plates 15 are integrated in a parallel state is disposed in a shell 12. Adopted, every other flow path through which the steam to be heat-exchanged and the working fluid pass is generated between the parallel heat exchange plates 15 constituting the heat exchange section 11, and the steam and the working flow Since the fluid and the fluid are circulated through the heat exchange plate so as to form a cross-flow, and the working fluid is evaporated and the steam is condensed, the heat exchange between the steam and the working fluid is performed via the heat exchange plate 15. Heat exchange unit 11 Can, the heat exchanger of the entire system that includes the desalination and mechanism of the steam power cycle having a 10 size and load reduction associated therewith can be reduced. In addition, steam can linearly and smoothly enter the first flow path 15b between the parallel heat exchange plates 15 of the heat exchange unit 11 from the internal space of the shell 12, and the pressure loss in the flow path is suppressed to smoothly promote condensation. The condensed water is allowed to flow down and can be taken out efficiently. Further, the contact between the steam and the heat exchange plate 15 and the resulting heat transfer occur smoothly without interruption, so that the heat between the steam and the liquid-phase working fluid flowing into the second flow path 15c separating the plate is generated. The replacement can be smoothly advanced, and the working fluid can be efficiently evaporated.

  In the heat exchanger according to the embodiment, when the liquid-phase working fluid is evaporated in the second flow path 15c of the heat exchange unit 11 to obtain the gas-phase working fluid, the liquid phase in the heat exchanger 10 is changed. The working fluid and the gas-phase working fluid are separated from each other, and only the gas-phase working fluid is caused to flow out to the working-fluid flow path on the outlet side. However, in addition to this, a gas-liquid separator is provided on the downstream side of the heat exchanger in the steam power cycle, and the liquid-phase working fluid and the gas-phase working fluid can be separated by this gas-liquid separator. Then, the liquid level of the liquid phase working fluid in the working fluid flow path of the steam power cycle may be adjusted so that the liquid level of the liquid phase working fluid is positioned above the heat exchange section.

  In this case, when the working fluid is evaporated in the second flow path by heat exchange with steam, the generated gas-phase working fluid travels upward as bubbles, and the opening of the second flow path together with the non-evaporated liquid-phase working fluid. Part, and flows out from the opening part, so that the working fluid does not stay at the upper part of the second flow path even if the vapor-phase working fluid continues to move upward in the second flow path, and the accumulated gas remains. To prevent the phase working fluid from interfering with the contact between the liquid phase working fluid and the surface of the heat exchange plate, thereby preventing heat exchange between the liquid phase working fluid and steam and evaporation of the working fluid from being performed smoothly. Thus, the working fluid can be efficiently evaporated and the water vapor condensed by the heat exchanger.

  When the liquid level is higher than the heat exchange part of the heat exchanger as described above, it is not necessary to dispose the heat exchange part in the inner space of the shell as in the above-described embodiment. In the second flow path, the opening portion on the working fluid outflow side and the opening portion on the working fluid inflow side may have the same vertical position.

  Further, in the heat exchanger according to the embodiment, the present invention is applied to a hybrid cycle type ocean temperature difference power generation system, in which heat exchange is performed between steam derived from seawater and a working fluid, and steam is condensed to obtain fresh water. And the role of an evaporator that evaporates a liquid-phase working fluid to obtain a gas-phase working fluid, but is not limited thereto. And a heat exchanger that condenses a high temperature fluid in a gas phase and evaporates a low temperature fluid in a liquid phase.

(Second embodiment of the present invention)
In the heat exchanger according to the first embodiment, the seawater desalination device 60 is formed in combination with the flash evaporator 61, and the internal space of the shell 12 is communicated with the decompression container 61 a of the flash evaporator 61. However, the present invention is not limited to this. As shown in FIG. 5, the shell 22 of the heat exchanger 20 has a predetermined size, and the shell 22 also serves as a depressurizing container of the flash evaporator and serves as an injection unit 65b of the flash evaporator 65. Alternatively, a configuration may be adopted in which the evaporating portion and the condensing portion of the seawater desalination apparatus are collectively disposed in a common shell, by accommodating the heat exchange section 21 and the introduction flow path of the seawater.

  In this case, the flash evaporator 65 includes a shell 22 of the heat exchanger 20 which also serves as a decompression vessel for reducing the internal space to the atmospheric pressure or less, an injection unit 65b for seawater injection disposed in the shell 22, A mist removing unit 65c for capturing and removing minute water droplets (mist) of seawater mixed in the steam flow toward the heat exchange unit 21 in the shell 22 is provided. In the flash evaporator 65, the seawater is guided to the injection unit 65b and is injected upward into the inner space of the shell 22. As in the previous embodiment, the inside of the shell 22 is depressurized by a decompression exhaust device (not shown) to a pressure equal to or lower than the saturated vapor pressure of water at the same temperature as the seawater injected from the injection portion 65b.

  The seawater is sprayed upward from a large number of spraying parts 65b arranged in the shell 22 so as to be in the form of mist, water droplets, a water film, or a water column, and part of the water is converted into steam by flash evaporation. The phase changes and at the same time the temperature of the seawater drops. Water vapor obtained by evaporation of water passes through the mist removing section 65c and flows into the heat exchange section 21 in the same shell 22. Since the evaporating portion and the condensing portion are integrally accommodated in the shell 22, the pressure loss in the flow of steam from the evaporating side to the condensing side can be reduced.

  As described above, in the heat exchanger according to the present embodiment, the components forming the flash evaporator 65 and the heat exchange unit 21 are accommodated in the shell 22 of the heat exchanger 20, and the evaporator and the condenser are integrally arranged. Since the steam obtained by the flash evaporator 65 can enter the heat exchange unit 21 as it is, it is easy to maintain the reduced pressure, and it is ensured that the steam reaches the heat exchange unit 21 in the gas phase and is condensed. As a result, a series of processes from evaporation to condensation can be smoothly performed in the shell 22, the efficiency of the condensation can be increased, and the exhaust from the inside of the shell 22 can be directly guided to the decompression exhaust device and discharged. The entire apparatus has a simple and compact structure, so that the cost can be reduced.

(Third embodiment of the present invention)
A third embodiment of the present invention will be described with reference to FIGS.
In each of the drawings, the heat exchanger according to the present embodiment includes a heat exchange unit 11 and a shell 12, similarly to the first embodiment, except that the opening of the first flow path 15b in the heat exchange unit 11 is different. A substantially box-shaped non-condensable gas collecting portion 17 disposed over a predetermined range of the portion, and communicating with an inner region of the non-condensing gas collecting portion 17 so that the non-condensable gas can be discharged out of the shell 12. And a substantially tubular non-condensable gas discharge portion 18.

  The non-condensable gas collecting unit 17 is formed of a substantially box-like body that is partially open, and includes a second flow path of at least one of the upper and lower openings of the first flow path 15 b in the heat exchange unit 11. 15c is provided so as to cover a predetermined range portion near the opening portion on the working fluid inflow side in 15c.

  The non-condensable gas discharge unit 18 is formed in a substantially tubular shape, and has one open end communicating with the inside region of the non-condensable gas collection unit 17 and the other open end located outside the shell 12. A decompression device (not shown) is connected to the other open end so that the non-condensable gas collected in the non-condensable gas collection unit 17 can be discharged to the outside of the shell 12. It is.

  Next, the removal of non-condensable gas in the heat exchanger based on the above configuration will be described. As a premise, as in the first embodiment, seawater taken from the sea is once guided to a deaerator (not shown) to remove air in the seawater, and then introduced into a flash evaporator 61, It is assumed that most of the water in the seawater injected into the space in the depressurized vessel 61a of the flash evaporator 61 whose pressure has been reduced becomes steam by flash evaporation, and this steam flows into the heat exchanger 10.

  In the heat exchanger 10, as in the first embodiment, the steam enters the internal space from the opening at the top of the shell 12. Then, the steam proceeds in the internal space of the shell 12 and flows in from the upper and lower openings in the first flow path 15b of the heat exchange unit 11.

  Of the steam, the steam that has flowed into the first flow path 15b from the upper opening portion exchanges heat with the working fluid through the heat exchange plate 15 while traveling downward through the first flow path 15b, and is transferred to the first flow path 15b. It condenses on the surface of the heat exchange plate 15 facing it, and becomes water in the liquid phase. Further, the steam that has flowed into the first flow path 15b from the lower opening portion exchanges heat with the working fluid via the heat exchange plate 15 while traveling upward through the first flow path 15b. And condenses on the surface of the heat exchange plate 15 to become liquid water.

  When the vapor condenses, the non-condensable gas that has flowed into the first flow path 15b together with the vapor is separated from the water that has condensed into a liquid phase. This non-condensable gas normally naturally exits outside the first flow path 15b, and is discharged to the outside of the shell 12 by the vacuum exhaust device 16 through the internal space of the shell 12. However, in the portion of the first flow path 15b of the heat exchange unit 11 near the opening on the working fluid inflow side in the second flow path 15c separating the heat exchange plate, the temperature of the working fluid on the second flow path 15c side Is lower than that of the other parts, the condensation of the vapor proceeds easily, and the amount of the non-condensable gas to be separated increases. Since the amount of the non-condensable gas is increased in this way, the discharge of the non-condensable gas tends to be stagnant in this portion, and the accumulated non-condensable gas hinders the contact between the steam and the heat exchange plate 15 and the steam does not flow. May not be able to condense.

  On the other hand, the non-condensable gas collecting unit 17 is arranged so as to cover a predetermined range near the opening on the working fluid inflow side in the second flow path 15c, of the upper opening of the first flow path 15b in the heat exchange unit 11. The non-condensable gas can be sucked from the first flow path 15b through the non-condensable gas collection unit 17 and the non-condensable gas discharge unit 18 to remove the remaining non-condensable gas, and the steam and heat in the first flow path 15b can be removed. Contact with the surface of the exchange plate and condensation of the vapor by heat exchange can be continued without being hindered by the non-condensable gas.

  As described above, in the heat exchanger according to the present embodiment, in the region near the second flow passage inlet in the first flow passage 15b, condensation easily proceeds at a low temperature, and the non-condensable gas contained in the steam is likely to stay in the region. Along with this, an uncondensable gas collecting unit 17 is provided, and an uncondensable gas discharging unit 18 is connected to the uncondensable gas collecting unit 17. Since the shell can be discharged from the first channel 15b to the outside of the shell, the non-condensable gas remaining in a part of the first channel 15b can be attracted to the non-condensable gas collection unit 17 and removed, and the non-condensable gas accumulated in the first channel 15b can be removed. The gas can be prevented from contacting the steam with the heat exchange plate 15 to prevent the steam from being condensed, so that the gas can be efficiently condensed.

  In the heat exchanger according to the embodiment, the non-condensable gas collecting unit is provided in the upper opening, but the operation in the second flow passage 15c of the first flow passage 15b of the heat exchange unit 11 is performed. As long as the opening portion corresponds to a predetermined range portion close to the opening portion on the fluid inflow side, the non-condensable gas collecting portion 17 may be provided on the lower side as shown in FIG.

(Fourth embodiment of the present invention)
In the heat exchanger according to the third embodiment, the non-condensable gas collecting portion is formed in a box shape and is arranged so as to cover a part of the opening portion. As shown in FIG. 11, the end of the non-condensable gas collecting unit 17 has a shape in which a plurality of projecting protrusions 17b are arranged in a tooth shape, and the protrusion 17b at this end is inserted into the first flow path 15b to a predetermined depth. At the same time, a partition fixed to each heat exchange plate 15 sandwiching the first flow path 15b and dividing the portion near the opening of the first flow path into a part communicating with the internal space of the shell and a part communicating with the non-condensable gas collecting part 17 It can also be configured to function as.

  In this case, the end portion of the non-condensable gas collecting section 17 partitions the first flow path 15b as a partition, and even if steam flows into a position near the non-condensable gas collecting section 17 in the first flow path opening, the partition section does not. Since it is prevented from proceeding toward the non-condensable gas collection unit 17, the steam that has flowed into the opening portion does not go to the non-condensable gas collection unit 17 but proceeds to the first flow path 15 b as far as possible, and The flow into the condensed gas collecting unit 17 can be suppressed, and the vapor can be prevented from being erroneously discharged through the non-condensable gas collecting unit 17, so that the vapor can be surely condensed without any leakage.

DESCRIPTION OF SYMBOLS 1 Ocean temperature difference power generation system 10 Heat exchanger 11 Heat exchange part 12 Shell 12b Water recovery part 13 Pipeline 15 Heat exchange plate 15b First flow path 15c Second flow path 16 Decompression exhaust device 17 Non-condensable gas collection part 17b Convex part 18 Non-condensable gas discharge unit 19 Storage unit 20 Heat exchanger 21 Heat exchange unit 22 Shell 50 Steam power cycle unit 52 Turbine 53 Condenser 54 Pump 55 Power generation device 60 Seawater desalination device 61, 65 Flash evaporator 61a Decompression container 61b, 65b Injection unit 65c Mist removal unit

Claims (7)

The gas-phase high-temperature fluid and the liquid-phase low-temperature fluid flowing from the outside are heat-exchanged through a heat exchange part made of a heat-conductive material to condense the gas-phase high-temperature fluid and evaporate the liquid-phase low-temperature fluid. In the heat exchanger,
The partition has an internal space separated from the outside by the partition, and is capable of introducing the gas-phase high-temperature fluid from the outside into the internal space and taking out the condensed liquid-phase high-temperature fluid from the internal space to the outside. A hollow container-shaped shell provided with a flow path for inflow and outflow of the low-temperature fluid that penetrates the
The high temperature fluid in the gas phase is steam,
The liquid-phase cryogenic fluid is a working fluid of a steam power cycle and is in a liquid phase;
The heat exchange unit welds each heat exchange plate made of a substantially rectangular thin metal plate in a plurality of parallel states to one adjacent heat exchange plate at two predetermined end portions that are substantially parallel to each other in a watertight state. On the other hand, the other adjacent heat exchange plate and the other two substantially parallel two end sides substantially orthogonal to the two end sides are welded in a watertight state at a watertight state and all integrated, and the heat exchange plate is provided between the heat exchange plates. An opening portion of the first flow passage that generates alternately a first flow passage through which steam and condensed water condensed by the water vapor and a second flow passage through which the working fluid passes, and through which steam and condensed water can flow in and out. And the opening portion of the second flow path through which the working fluid can flow in and out is formed as a right-angled arrangement,
The heat exchange section, in the internal space of the shell, a predetermined gap between the shell partition inner surface other than the opening of the second flow path, and the opening of the first flow path is positioned vertically Disposed, the inflow / outflow channel and the opening of the second channel are connected,
The fresh water condenser that exchanges heat between the liquid-phase working fluid flowing through the inflow / outflow passage and steam flowing from the shell internal space, and condenses the steam to obtain fresh water as condensed water by the heat exchange. And a vapor power cycle evaporator for evaporating a liquid-phase working fluid to obtain a gas-phase working fluid. The heat exchanger according to claim 1,
The heat exchange unit is disposed in the shell internal space such that the entire heat exchange unit is inclined such that an opening on the working fluid outflow side of the second flow path is above the opening on the working fluid inflow side. A heat exchanger characterized in that: In the heat exchanger according to claim 1 or 2,
A hollow depressurized container having an evaporating space communicating with the inner space of the shell therein, and the evaporating space being in a depressurized state lower than the atmospheric pressure;
An injection unit that is disposed in the decompression container and injects seawater introduced from outside into the internal space of the decompression container,
A pressure reducing device disposed at least in communication with the evaporating space of the depressurizing vessel, and adjusting the evaporating space and the inner space of the shell to a pressure lower than the saturated vapor pressure of the seawater,
A heat exchanger, wherein seawater injected from an injection unit is flash-evaporated in an evaporation space of the decompression container, and steam obtained by evaporation is condensed in the heat exchange unit. The heat exchanger according to claim 3,
The decompression container is disposed integrally with the shell below the shell,
A part of the partition wall that separates the evaporation space of the decompression vessel from the inner space of the shell allows gas to move from the evaporation space to the inner space of the shell, while the seawater of liquid existing in the evaporation space A heat exchanger characterized by being a mist removal part that prevents it from proceeding to the internal space. The heat exchanger according to any one of claims 1 to 4,
The liquid level position of the liquid-phase working fluid in the working fluid circulation flow path of the steam power cycle is set above the heat exchange unit, and the liquid-phase working fluid is present in the entire second flow path of the heat exchange unit. A heat exchanger capable of exchanging heat with steam in the first flow path via a heat exchange plate of a heat exchange section. The heat exchanger according to claim 2,
Of at least one of the upper and lower openings of the first flow path in the heat exchange section, disposed over a predetermined range portion close to the opening on the cooling fluid inflow side in the second flow path, A substantially box-shaped non-condensable gas collecting unit;
One open end is communicated with the inner region of the non-condensable gas collection unit, and the other open end is located outside the shell, and the non-condensable gas collected in the non-condensable gas collection unit is disposed. A heat exchanger comprising: a substantially tubular non-condensable gas discharge portion capable of being discharged outside the shell. The gas-phase high-temperature fluid and the liquid-phase low-temperature fluid flowing from the outside are heat-exchanged through a heat exchange part made of a heat-conductive material to condense the gas-phase high-temperature fluid and evaporate the liquid-phase low-temperature fluid. In the heat exchanger,
The partition has an internal space separated from the outside by the partition, and is capable of introducing the gas-phase high-temperature fluid from the outside into the internal space and taking out the condensed liquid-phase high-temperature fluid from the internal space to the outside. A hollow container-like shell provided with a low-temperature fluid inflow / outflow passage that penetrates the
The heat exchange unit welds each heat exchange plate made of a substantially rectangular thin metal plate in a plurality of parallel states to one adjacent heat exchange plate at two predetermined end portions that are substantially parallel to each other in a watertight state. On the other hand, the other adjacent heat exchange plates and the other substantially parallel two end portions substantially orthogonal to the two end sides are welded in a watertight state and all integrated, and a high temperature is applied between the heat exchange plates. The first flow path through which the fluid flows and the second flow path through which the low-temperature fluid flows are generated alternately, and the opening of the first flow path through which the high-temperature fluid can flow in and the second flow path through which the low-temperature fluid can flow in and out. The opening of the two channels is formed as a right angle arrangement,
The heat exchange section, in the internal space of the shell, a predetermined gap between the shell partition inner surface other than the opening of the second flow path, and while positioning the opening of the first flow path up and down The low-temperature fluid outflow-side opening in the second flow path is disposed with the entire heat exchanging portion inclined such that the low-temperature fluid inflow-side opening is located above the low-temperature fluid inflow-side opening. A heat exchange characterized by connecting the opening of the second flow path and exchanging heat between the liquid-phase low-temperature fluid flowing through the low-temperature fluid inflow / outflow path and the gas-phase high-temperature fluid flowing from the shell internal space. vessel.

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