JP2009180396A - Steam producing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a steam producing device capable of reducing water expense in producing steam. <P>SOLUTION: This steam producing device 1 comprises: an evaporator 2 having an environment water storing portion disposed on a position higher than a water level of the environment water for storing the environment water, reducing a pressure in the environment water storing portion by lowering the liquid level of the environment water filled in the environment water storing portion by hydraulic head pressure to evaporate the environment water; and a compression means 3 for compressing the steam generated by the evaporator 2. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a steam production apparatus.

2. Description of the Related Art Conventionally, as a steam production apparatus that produces steam, a configuration in which steam is generated using heat obtained by burning fuel in a boiler is generally known. Steam used in a production process such as a factory is generated by a boiler (see, for example, Patent Document 1).
JP-A-6-249450

  The energy of the steam obtained from the boiler is indicated by the loss obtained by subtracting the loss from the energy obtained by burning the fuel, and therefore does not exceed the energy of the fuel. In addition, when steam is produced using a boiler, water containing a large amount of impurities cannot be used, so that a large amount of industrial water is used, resulting in an increase in water costs. Thus, it is desired to provide a new steam production apparatus that replaces the boiler.

  This invention is made | formed in view of such a situation, Comprising: It aims at providing the steam manufacturing apparatus which can reduce the water supply expense at the time of steam manufacture.

  In order to solve the above-described problem, the steam production apparatus of the present invention has an environmental water storage section that is provided at a position higher than the surface of the environmental water and stores the environmental water, and the environment filled with the environmental water storage section An evaporator for reducing the inside of the environmental water storage unit by lowering the liquid level of the water by the water head pressure and evaporating the environmental water; and a compression means for compressing the vapor led from the evaporator. Features.

  According to the steam production apparatus of the present invention, it is possible to obtain steam having a desired temperature and pressure with high energy efficiency by compressing steam generated by water head pressure. Moreover, since steam can be generated from environmental water, the amount of industrial water used can be reduced compared to boilers.

Moreover, in the said steam production apparatus, it is preferable that the said multistage compression structure is comprised from the compressor arrange | positioned in multistage, and the said steam compressed by the front | former stage compressor is guide | induced to a back | latter stage compressor. Further, at least one of the compressors includes a multi-stage impeller provided with multi-stage impellers for compressing the steam by rotation so that the steam compressed by the front-stage impeller is guided to the rear-stage impeller. Also good.
If it does in this way, a vapor | steam can be reliably pressurized to a desired pressure by compressing the vapor | steam from an evaporator in multistage. Moreover, since multistage compression is enabled by the multistage impeller, the pressure ratio of the compressor alone can be improved.

In the steam production apparatus, at least one of the pre-stage compressor and the rear-stage compressor, and at least one of the front-stage impeller and the rear-stage impeller, the superheat generated by the front-stage compression process is generated. An intercooler for cooling the steam is preferably provided.
According to this configuration, the efficiency of the entire compression means is improved by cooling the superheated steam that is overheated when compressed by the front stage compressor or front stage impeller and guiding it to the rear stage compressor or rear stage impeller. Can be improved.

Furthermore, the intermediate cooler has a container to which cooling water for cooling the superheated steam is supplied from the outside, and the cooling water evaporates by contacting the superheated steam to generate steam. It is desirable to generate and cool the superheated steam by latent heat of vaporization.
According to this configuration, the cooling water can cool the superheated steam and function as a steam generation source. For example, when cooling superheated steam to near saturation temperature, a large amount of steam can be generated from the cooling water. Furthermore, since the cooling water supplied into the container evaporates into steam in the process of cooling the superheated steam, it is possible to prevent water from being wasted.

Moreover, in the said steam manufacturing apparatus, it is preferable that the said evaporator is equipped with the freezing prevention means which prevents the freezing in the said environmental water in the said environmental water storage part.
According to this configuration, since the environmental water is prevented from freezing, steam can be produced by arranging the environmental water storage section in an environment where the external temperature is low.

Moreover, in the said steam manufacturing apparatus, it is preferable that the said freeze prevention means contains the environmental water supply mechanism which supplies the said environmental water in the said environmental water storage part from the outside.
The environmental water in the environmental water reservoir is cooled by the latent heat of vaporization when the steam is generated, causing a temperature drop. On the other hand, the temperature of the environmental water supplied from the outside is higher than that of the environmental water in the environmental water reservoir. Therefore, it can be made to function as a freeze prevention means which prevents freezing in an environmental water storage part by supplying environmental water from the outside. Therefore, the freeze prevention means can be provided with a simple configuration.

Moreover, in the said steam manufacturing apparatus, the said freeze prevention means has piping inserted in the said environmental water storage part, This piping is with respect to the said environmental water stored in the said environmental water storage part inside. It is preferable that high-temperature water is allowed to flow and the water after heat exchange with the environmental water can be taken out.
Water flowing in the pipe is prevented from freezing by warming the environmental water in the environmental water storage section, and is cooled by heat exchange with the environmental water. In the present invention, since water in the pipe after heat exchange can be taken out, while producing steam, cold water can also be produced.

Moreover, in the said steam manufacturing apparatus, it is preferable that the said evaporator is equipped with the water spraying means which sprays water in the said environmental water storage part.
According to this configuration, it is possible to obtain steam also from the sprayed water into the environmental water storage part, and it is possible to promote the evaporation of environmental water in the environmental water storage part.

Moreover, in the said steam manufacturing apparatus, it is preferable to use any of groundwater, seawater, and industrial waste water as said environmental water.
According to this configuration, environmental water such as groundwater, seawater, and industrial water is used as water for steam generation, which greatly reduces water costs compared to boilers that use a large amount of industrial water during steam generation. Can do.

  According to the present invention, desired steam can be obtained with high energy efficiency by compressing steam obtained from environmental water by water head pressure, and the amount of industrial water used at the time of steam production is significantly larger than that of boilers. Can be reduced.

  Hereinafter, an embodiment of a steam production apparatus according to the present invention will be described with reference to the drawings. In the following drawings, the scale of each member is appropriately changed to make each member a recognizable size.

(First embodiment)
FIG. 1 is a diagram schematically showing a configuration of a steam production apparatus according to the first embodiment of the present invention. As shown in FIG. 1, the steam production apparatus 1 includes an evaporator 2 that generates steam from environmental water, and a compression unit 3 that compresses the steam generated by the evaporator 2. Examples of the environmental water include groundwater, seawater, and industrial wastewater (this embodiment uses seawater). In addition, the steam manufacturing apparatus 1 which concerns on this embodiment is an apparatus for manufacturing the steam used in production processes, such as a factory, instead of a boiler.

  FIG. 2 is a schematic diagram showing the configuration of the evaporator 2. As illustrated in FIG. 2, the evaporator 2 includes a tank (environmental water storage unit) 10 that stores environmental water. The tank 10 is provided at a position higher than the sea level. The evaporator 2 reduces the pressure inside the tank 10 by lowering the liquid level of the seawater filled in the tank 10 by water head pressure, and evaporates the seawater to generate steam. In this embodiment, the temperature of the seawater is 10.0 ° C.

  A first pipe 11 is provided on the upper side surface of the tank 10, and the first pipe 11 is connected to the compression means 3. Moreover, the 2nd piping 12 is provided in the lower surface side of the tank 10, This 2nd piping 12 is inserted in seawater. The first pipe 11 and the second pipe 12 are provided with valves (not shown), so that the flow paths in the first and second pipes 11 and 12 can be opened and closed.

  Here, the principle that seawater evaporates in the tank 10 will be described. First, the flow paths of the first and second pipes 11 and 12 are closed, and the tank 10 and the second pipe 12 are filled with seawater. Subsequently, in the tank 10 filled with seawater, the flow path of the second pipe 12 is opened. Then, the liquid level of the seawater in the tank 10 begins to decrease due to its own weight, and eventually the decrease in the seawater level stops.

  Specifically, the inside of the tank 10 is depressurized as the sea level is lowered to a low vacuum state, whereby the sea water begins to evaporate. Then, when the pressure in the tank 10 reaches the saturated vapor pressure (corresponding to a temperature of 10 ° C.), the sea level decline stops. In order to evaporate the seawater in the tank 10 by utilizing the water head difference in this way, the upper portion of the tank 10 may be disposed at a place with an altitude of at least 10 m or more.

  After the pressure in the tank 10 reaches the saturated vapor pressure (1.23 kPa) corresponding to the seawater temperature (10.0 ° C.) as the seawater evaporates, the compression means is opened by opening the flow path of the first pipe 11. Saturated steam (pressure 1.23 kPa) is introduced into the cylinder 3.

  Further, the evaporator 2 according to the present embodiment includes water spraying means 13 for spraying water into the tank 10. The water spraying means 13 sprays water at normal temperature and normal pressure as water droplets D in the tank 10. Thereby, it is possible to obtain steam from the sprayed water droplets D, and the generation of steam in the tank 10 can be promoted. Therefore, a sufficient amount of steam can be generated even when the amount of evaporation from the liquid level is insufficient.

  By the way, the seawater in the tank 10 may be deprived of heat by latent heat of vaporization and the water temperature may be lowered. In particular, when the tank 10 is disposed in a place where the external temperature is low, the possibility that seawater in the tank 10 will freeze increases. Therefore, in the present embodiment, the evaporator 2 is provided with the freeze prevention means 14 for preventing the seawater in the tank 10 from freezing.

  The freeze prevention means 14 includes a third pipe (pipe) 15 inserted through the bottom side of the tank 10 and a flow rate adjusting valve B1 that adjusts the flow rate in the third pipe 15. In the third pipe 15, water (hot water) having a temperature higher than that of seawater stored in the tank 10 flows. As such warm water, various kinds of water can be used as long as the temperature is higher than that of seawater in the tank 10 (for example, in this embodiment, wastewater obtained in a factory or the like can be exemplified). At this time, heat exchange occurs between the water flowing in the third pipe 15 and the seawater in the tank 10, and the seawater in the tank 10 is warmed to prevent freezing, while flowing in the third pipe 15. Water is cooled and the temperature drops. Further, on the downstream side of the third pipe 15, a take-out unit 50 that can take out water after heat exchange is provided. As this extraction part 50, a valve etc. are used, for example. With this configuration, the steam production apparatus 1 according to the present embodiment can produce steam while also producing cold water. Moreover, the steam production apparatus 1 includes the antifreezing means 14 so that the seawater in the tank 10 can be generated satisfactorily even in an environment where the external temperature is low, without being frozen. In addition, what is necessary is just to stop supply of the warm water into the tank 10 by closing the flow volume adjustment valve B1, when the temperature of the grade which the seawater in the tank 10 does not freeze can be maintained.

  In the present invention, a seawater supply mechanism 17 for supplying seawater from the outside into the tank 10 as shown in FIG. The seawater supply mechanism 17 includes a suction pump P that sucks seawater from the seawater surface, and a pipe 18 that supplies the seawater sucked by the suction pump P to the tank 10. The suction pump P is configured to reduce the load on the compression means 3 by keeping the sea level in the tank 10 substantially constant and thereby stabilizing the amount of steam generated. Note that a backflow prevention valve (not shown) for preventing the backflow of seawater is provided between the suction pump P and the evaporator 2 in the pipe 18.

  Here, since the seawater on the reference surface is not affected by the latent heat of vaporization, the temperature is higher than the seawater in the tank 10. Therefore, freezing of seawater can be prevented by transferring heat to the seawater in the tank 10 through the pipe 18 inserted into the tank 10. Therefore, according to this configuration, the seawater supply mechanism 17 can function as the freeze prevention means 14 with a simple configuration in which seawater is supplied into the pipe 18 as a heat medium.

(Compression means)
Then, the structure of the said compression means 3 is demonstrated. FIG. 4 is a schematic diagram showing the configuration of the compression means 3. The compression means 3 according to the present embodiment generates steam at a desired temperature and pressure by compressing low-pressure (1.23 kPa) steam generated by the evaporator 2.

  The compression means 3 which concerns on this embodiment is comprised so that 10.0 degreeC vapor | steam guide | induced to the inlets as mentioned above may be discharged | emitted as 120 degreeC vapor | steam from an exit. Since steam at 100 ° C. or higher has a pressure of atmospheric pressure (101 kPa) or higher, it can be easily taken out without using a suction pump or the like. In addition, the vapor | steam obtained by this invention is not restricted to 100 degreeC or more, Of course, the vapor | steam below 100 degreeC can also be taken out outside by using the suction pump etc. which were mentioned above.

  In the steam production apparatus 1 according to the present embodiment, the compression means 3 produces steam having an atmospheric pressure (101 kPa) or higher, so that the compression means as a whole requires a high compression ratio. Therefore, as shown in FIG. 4, the compression means 3 has a multistage compression structure for compressing steam in multiple stages.

  Specifically in this embodiment, a multistage compression structure is comprised by arrange | positioning a compressor by multistage (5 stages). In the present embodiment, the overall efficiency of the compression means 3 as a whole is 64.5%. The compression ratio of the compression means 3 as a whole is set to 2.76. The driving power of the first stage compressor 22 is 100 kW, the driving power of the second stage compressor 23 is 112 kW, the driving power of the third stage compressor 24 is 125 kW, and the fourth stage compressor 24. Is set to 140 kW, and the driving power of the fifth stage compressor 26 is set to 157 kW.

  The multi-stage compression structure according to the present embodiment includes a single-stage compressor 22, a two-stage compressor 23, a three-stage compressor 24, a four-stage compressor 25, and a five-stage compressor 26 from the evaporator 3 side in multiple stages (five stages). It is composed by arranging. Each compressor 22,23,24,25,26 functions as a centrifugal compressor, and compresses the vapor | steam led to the flow path formed between an impeller and a casing by rotating an impeller. It is supposed to be.

  The vapor from the evaporator 2 is compressed by the first stage compressor 22 to increase the pressure. At this time, 1556 Kg (per hour; referred to as Kg / h in the following description) of steam is sent from the evaporator 2 into the first stage compressor 22. Specifically, in the present embodiment, the vapor (temperature: 10.0 ° C., vapor pressure: 1.23 kPa) from the evaporator 2 is compressed by the first stage compressor 22 to have a temperature of 89.7 ° C., vapor pressure. Becomes 3.39 kPa of steam. The steam after compression by the first stage compressor 22 is in an overheated state.

  Therefore, the steam producing apparatus 1 according to the present embodiment performs the intermediate cooling of the steam (superheated steam) compressed by the first stage compressor 22 between the first stage compressor 22 and the second stage compressor 23. One intermediate cooler 27 is provided. FIG. 5 is a diagram showing a schematic configuration of the first intermediate cooler 27. The first intermediate cooler 27 includes a container 40 in which cooling water is stored as shown in FIG. The container 40 is provided with a pipe 47 through which cooling water can be supplied. As this cooling water, industrial water with a low impurity content is used. The first intermediate cooler 27 allows the temperature of the steam to be cooled to a predetermined saturation temperature by bringing the superheated steam introduced into the container 40 into direct contact with the cooling water. In the step of cooling the superheated steam, the cooling water supplied into the container 40 evaporates to generate steam, and the superheated steam can be cooled by latent heat of vaporization. That is, the first intermediate cooler 27 also functions as a steam generation source. Thus, since the cooling water supplied in the container 40 evaporates and becomes a vapor | steam, water is not consumed wastefully.

  Further, the piping 47 is provided with an electromagnetic valve B2 for adjusting the flow rate, whereby the amount of cooling water supplied into the container 40 can be controlled. The first intermediate cooler 27 includes a float switch F that is electrically connected to the electromagnetic valve B2. The float switch F makes it possible to detect the water surface height of the cooling water in the container 40. Therefore, the intermediate cooler 27 controls the opening and closing of the electromagnetic valve B2 based on the detection result of the float switch F so that the water level of the cooling water in the container 40 is constant. The configuration of the intermediate cooler is not limited to this, and for example, the superheated steam may be cooled by sprinkling water from the upper surface side of the container 40.

  Specifically, in the first intermediate cooler 27, the inside of the container 40 is held at a saturated steam pressure (temperature: 26.2 ° C., pressure: 3.39 kPa) of the steam temperature discharged from the outlet 42. Then, the superheated steam compressed by the first stage compressor 22 is led into the container 40 from the inlet 41, and comes into contact with the cooling water as the saturated steam (temperature: 26.2 ° C., pressure: 3.39 kPa). It is discharged from the outlet 42. Thus, the compression efficiency can be increased by cooling the superheated steam and introducing the saturated vapor pressure to the next-stage compressor. In the cooling process in the first intermediate cooler 27, industrial water (10.0 ° C., 75 Kg / h) supplied into the container 40 is evaporated and discharged from the outlet 42 as steam. As a result, the first intermediate cooler 27 can send 1631 Kg / h of steam into the second stage compressor 23.

  The saturated steam sent from the first intermediate cooler 27 is similarly compressed by the second stage compressor 23, so that the temperature becomes 110.6 ° C. and the steam pressure becomes 9.39 kPa. The steam compressed by the second stage compressor 23 is in an overheated state.

  A second intermediate cooler 28 is provided between the second stage compressor 23 and the third stage compressor 24. The second intermediate cooler 28 has the same configuration as the first intermediate cooler 27. Therefore, in the following description, the same members will be described with the same reference numerals. The internal pressure of the container 40 in the second intermediate cooler 28 is maintained at a saturated steam pressure (temperature: 44.6 ° C., pressure: 9.37 kPa) of the steam temperature discharged from the outlet 42. The superheated steam compressed by the second intermediate cooler 28 is cooled in the container 40 and discharged from the outlet 42 as the saturated steam (temperature: 44.6 ° C., pressure: 9.37 kPa). In the cooling process in the second intermediate cooler 28, industrial water (10.0 ° C., 81 kg / h) is evaporated and discharged from the outlet 42 as steam. As a result, the second intermediate cooler 28 can send 1712 Kg / h of steam into the third stage compressor 24.

  The saturated steam sent from the third intermediate cooler 29 is similarly compressed by the third stage compressor 24, so that the temperature becomes 134.0 ° C. and the steam pressure becomes 25.9 kPa. The steam compressed by the third stage compressor 24 is in an overheated state.

  A third intermediate cooler 29 is provided between the third stage compressor 24 and the fourth stage compressor 25. The third intermediate cooler 29 has the same configuration as the first and second intermediate coolers 27 and 28. Therefore, in the following description, the same members will be described with the same reference numerals. The internal pressure of the container 40 in the third intermediate cooler 29 is maintained at a saturated vapor pressure (temperature: 65.7 ° C., pressure: 25.9 kPa) of the vapor temperature discharged from the outlet 42. Then, the superheated steam compressed by the third intercooler 29 is cooled in the container 40 and discharged from the outlet 42 as the saturated steam (temperature: 65.7 ° C., pressure: 25.9 kPa). In the cooling step in the third intermediate cooler 29, industrial water (10.0 ° C., 88 kg / h) is evaporated and discharged from the outlet 42 as steam. As a result, the third intermediate cooler 29 can feed 1800 Kg / h of steam into the fourth stage compressor 25.

  The saturated steam sent from the third intermediate cooler 29 is similarly compressed by the fourth stage compressor 25, so that the temperature becomes 160.3 ° C. and the steam pressure becomes 71.5 kPa. The steam compressed by the fourth stage compressor 25 is in an overheated state.

  A fourth intermediate cooler 30 is provided between the fourth stage compressor 25 and the fifth stage compressor 26. The fourth intermediate cooler 30 has the same configuration as the first, second, and third intermediate coolers 27, 28, and 29. Therefore, in the following description, the same members will be described with the same reference numerals. The internal pressure of the container 40 in the fourth intermediate cooler 30 is maintained at the saturated steam pressure (temperature: 90.3 ° C., pressure: 71.5 kPa) of the steam temperature discharged from the outlet 42. The superheated steam compressed by the fourth intermediate cooler 30 is cooled in the container 40 and discharged from the outlet 42 as the saturated steam (temperature: 90.3 ° C., pressure: 71.5 kPa). In the cooling process in the fourth intermediate cooler 30, industrial water (10.0 ° C., 96 kg / h) is evaporated and discharged from the outlet 42 as steam. As a result, the fourth intercooler 30 can feed 1896 Kg / h of steam into the fifth stage compressor 26.

  The saturated steam fed from the fourth intermediate cooler 30 is similarly compressed by the fifth stage compressor 26, and becomes a steam having a temperature of 190.7 ° C. and a vapor pressure of 197.4 kPa. The steam compressed by the fifth stage compressor 26 is in an overheated state.

  The compression means 3 includes a steam generation unit 31 that cools the superheated steam from the fifth stage compressor 26 and generates steam at a predetermined temperature and pressure. The steam generation unit 31 is configured to cool the superheated steam, for example, similarly to the first to fourth intermediate coolers 27, 28, 29, and 30.

  The steam generating unit 31 cools the superheated steam guided from the fifth stage compressor 26 and generates saturated steam having a temperature of 120 ° C. and a pressure of 197.4 kPa. In the cooling process in the steam generating unit 31, industrial water (10.0 ° C., 104 Kg / h) is evaporated and discharged as steam. Thereby, the compression means 3 can produce 2000 kg / h of steam by compressing the steam generated by the evaporator 2.

  As described above, the steam producing apparatus 1 according to the present embodiment can produce 2000 kg / h steam (120 ° C., 197.4 kPa) from 10.0 ° C. seawater (used amount: 1556 kg / h). it can. In addition, the compressor power in the steam production apparatus 1 is 634 kW in total. In this embodiment, since the overall efficiency of the compressor is 64.5% as described above, the COP (coefficient of performance; obtained energy / input energy) is 2.33, which is compared with the conventional boiler. However, high energy efficiency can be obtained.

  Moreover, the usage-amount of the industrial water in the steam production apparatus 1 will be 444 kg / h in total (total usage in the intercoolers 27-30 and the steam generation part 31). Therefore, in the manufacturing apparatus 1, the ratio of seawater occupied by all the water used when generating steam (seawater use ratio) is 77.8%. Therefore, the amount of industrial water required at the time of steam generation can be greatly reduced as compared with a boiler that requires a large amount of industrial water at the time of steam generation.

  FIG. 6 shows a simulation result when the number of compressor stages constituting the compression means, the seawater temperature (inlet temperature) in the tank 10, and the steam output temperature are changed in a steam production apparatus having the same configuration as that of the present embodiment. Is shown. In Fig.6 (a), when the number of compressor stages is five, it corresponds to the steam production apparatus 1 which concerns on the above-mentioned embodiment.

  Generally, when the pressure ratio in the compressor is set low (increasing the number of stages of the compressor), the efficiency (COP) of the compressor is improved, but the cost of the apparatus increases due to the increase in the number of stages of the compressor. . In this simulation, a condition (pressure ratio) is calculated so that a high COP is obtained when the number of compression stages is set to five.

  As shown in FIG. 6 (a), when the steam generated in the evaporator 2 is compressed in four stages, steam having the same conditions as in the above embodiment is obtained when the compression ratio is 3.56 (COP; 2.31). In addition, when the steam generated in the evaporator 2 is compressed in six stages, steam having the same conditions as in the above embodiment is obtained when the compression ratio is 2.33 (COP; 2.28).

  On the other hand, when the steam generated in the evaporator 2 is compressed in five stages as in the above-described embodiment, each compression ratio is 2.76 and the COP is 2.33. That is, it can be confirmed that the configuration according to the above-described embodiment (5-stage compression) obtains a desired vapor with high energy efficiency.

  FIGS. 6B to 6H show simulation results for selecting the optimum number of stages according to the optimum pressure ratio according to the compressor type and the temperature of the steam at the inlet and outlet of the steam production apparatus. Similarly, in FIGS. 6B to 6H, it can be seen that the highest energy efficiency can be obtained when five-stage compression is performed. Therefore, if the compression means 3 is designed based on the simulation results shown in FIG. 6, a low-cost and energy-efficient steam production apparatus can be provided.

  In the above description, the case where the steam generated in the evaporator 2 is compressed by a five-stage compressor has been described. However, the present invention is not limited to this, and the optimum pressure ratio according to the type of the compressor. Of course, the optimum number of stages can be appropriately set according to the temperature of the steam at the inlet and outlet of the steam production apparatus.

(Second embodiment)
Next, a second embodiment of the steam production apparatus of the present invention will be described. In this embodiment, the structure of the compression means 3 differs from the said embodiment. In addition, since it has the same structure about the structure other than that, the same code | symbol is attached | subjected about the same member and the detailed description is abbreviate | omitted or simplified.

  FIG. 7 shows the configuration of the compression means 3 according to this embodiment. In the present embodiment, the multistage compression structure includes a front stage compressor 120 and a rear stage compressor 121. The upper stage compressor 120 arranged on the evaporator 2 side is larger than that of the rear stage compressor 121.

  The pre-stage compressor 120 includes a multi-stage impeller provided with multi-stage impellers that compress steam by rotation. That is, the front stage compressor 120 functions as a multistage (two stage in this embodiment) centrifugal compressor, and a first stage impeller 122 (front stage impeller) and a second stage impeller (rear stage impeller) 123. Are provided with a multi-stage impeller 130. The first stage impeller 122 and the second stage impeller 123 are connected to each other via a rotating shaft (not shown) and are rotated at the same rotational speed.

  When the first stage impeller 122 rotates in the front stage compressor 120, the vapor from the evaporator 2 is compressed. Further, a first intermediate cooler 127 that intermediately cools the steam compressed by the first stage impeller 22 is provided between the first stage impeller 122 and the second stage impeller 123. The first intermediate cooler 127 has the same configuration as the intermediate coolers 27, 28, 29, and 30 according to the above-described embodiment. The steam that has passed through the first intermediate cooler 127 is compressed in two stages by being guided to the second stage impeller 123. Thereafter, the pressurized steam is guided to the rear stage compressor 121.

  Moreover, the steam production apparatus according to the present embodiment includes the second intermediate cooler 128 between the front-stage compressor 120 and the rear-stage compressor 121, and after cooling the superheated steam compressed by the front-stage compressor 120. Then, it is led into the rear-stage compressor 21. The first intermediate cooler 128 has the same configuration as the intermediate coolers 27, 28, 29, and 30 according to the above-described embodiments.

  The rear-stage compressor 121 functions as a multi-stage (three-stage in this embodiment) centrifugal compressor, similarly to the front-stage compressor 120, and includes a third-stage impeller 124, a fourth-stage impeller 125, and a fifth-stage impeller. A multi-stage impeller 134 provided with an impeller 126 is provided. The basic configuration of the rear stage compressor 121 other than the multistage impeller 134 is the same as that of the front stage compressor 120.

When the third stage impeller 124 rotates in the rear stage compressor 121, the saturated steam from the front stage compressor 120 is compressed and the pressure is increased.
In the present embodiment, the third intercooler 129 for intercooling the steam compressed by the third stage impeller 124 is provided between the third stage impeller 124 and the fourth stage impeller 125. After the superheated steam compressed by the third stage impeller 124 is cooled, it is guided to the fourth rear impeller 125.

  Further, the fourth intercooler 130 for intercooling the steam compressed by the fourth stage impeller 125 is provided between the fourth impeller 125 and the fifth stage impeller 126, and the fourth stage impeller. After the superheated steam compressed by 125 is cooled, it is guided to the fifth rear impeller 126.

  Thus, in the present embodiment, the steam guided from the front stage compressor 120 is compressed in three stages by the rear stage compressor 121. That is, in the present embodiment, the steam generated in the evaporator 2 is compressed in a total of five stages by the front-stage compressor 120 and the rear-stage compressor 121.

  The compression unit 3 includes the steam generation unit 31 that cools the superheated steam from the rear-stage compressor 121 to generate steam at a predetermined temperature and pressure. Also in the steam production apparatus according to the present embodiment, environmental water can be used during steam generation as in the above embodiment, so that the amount of industrial water used can be reduced compared to boilers.

  In addition, this invention is not limited to the said embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably. For example, in the above-described embodiment, only the steam that has passed through the steam generation unit 29 can be taken out, but the present invention is not limited to this. For example, it is possible to employ a configuration in which a steam outlet is provided in a pipe that guides steam between the front-stage compressor 20 and the rear-stage compressor 21 and between the respective impellers. In this case, it is possible to take out steam after cooling by the intermediate coolers 27, 28, 29, and 30 or before cooling. In this way, it is possible to provide a steam production apparatus that can simultaneously obtain a plurality of types of pressures.

It is a figure which shows the structure of a steam manufacturing apparatus typically. 3 is a schematic diagram showing a configuration of an evaporator 2. FIG. It is a figure which shows the structure which concerns on another form of a freezing prevention means. It is a figure which shows the structure of a compression means. It is a schematic diagram which shows the structure of an intercooler. It is a simulation result which shows the relationship between the pressure ratio and efficiency of a compression means. It is a figure which shows the structure of the compression means which concerns on 2nd embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Steam production apparatus, 2 ... Evaporator, 3 ... Compression means, 10 ... Tank (environmental water storage part), 13 ... Water spraying means, 14 ... Freezing prevention means, 17 ... Seawater supply mechanism (environmental water supply mechanism), 22 ... First stage compressor, 23 ... Second stage compressor, 24 ... Third stage compressor, 25 ... Fourth stage compressor, 26 ... Fifth stage compressor, 27 ... First intermediate cooler, 28 ... Second intermediate cooler, 29 ... third intermediate cooler, 30 ... fourth intermediate cooler, 120 ... front stage compressor, 121 ... rear stage compressor, 122 ... first stage impeller, 123 ... second stage impeller, 124 ... Third stage impeller, 125 ... Fourth stage impeller, 126 ... Fifth stage impeller, 127, 128, 129 ... Intermediate cooler, 130 ... Multistage impeller, 134 ... Multistage impeller

Claims (10)

The environmental water storage unit is provided at a position higher than the surface of the environmental water, and stores the environmental water. An evaporator that depressurizes the inside and evaporates the environmental water;
And a compressing means for compressing the steam guided from the evaporator.   The steam production apparatus according to claim 1, wherein the multistage compression structure includes compressors arranged in multiple stages, and the steam compressed by the front stage compressor is guided to the rear stage compressor.   At least one of the compressors includes a multi-stage impeller provided with multi-stage impellers that compress the steam by rotation, and the steam compressed by the front-stage impeller is guided to a rear-stage impeller. The steam production apparatus according to claim 2.   An intermediate cooler that cools the superheated steam generated by the preceding compression step is provided between at least one of the front compressor and the rear compressor and between the front impeller and the rear impeller. The steam producing apparatus according to claim 2, wherein the steam producing apparatus is provided.   The intermediate cooler has a container to which cooling water for cooling the superheated steam is supplied from the outside, and the cooling water evaporates by contacting with the superheated steam to generate steam, and the superheated steam is generated by latent heat of vaporization. The steam producing apparatus according to claim 4, wherein the steam is cooled.   The said evaporator is provided with the freezing prevention means which prevents the freezing in the said environmental water in the said environmental water storage part, The steam manufacturing apparatus as described in any one of Claims 1-5 characterized by the above-mentioned.   The steam manufacturing apparatus according to claim 6, wherein the freeze prevention unit includes an environmental water supply mechanism that supplies the environmental water from the outside into the environmental water storage unit.   The anti-freezing means has a pipe inserted into the environmental water storage part, and the pipe is supplied with high-temperature water to the environmental water stored in the environmental water storage part and the environment. The steam production apparatus according to claim 6 or 7, wherein the water after heat exchange with water is configured to be taken out.   The said evaporator is provided with the water spraying means which sprays water in the said environmental water storage part, The steam manufacturing apparatus as described in any one of Claims 1-8 characterized by the above-mentioned.   The steam production apparatus according to any one of claims 1 to 9, wherein any one of groundwater, seawater, and industrial wastewater is used as the environmental water.

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