JP2008175149A - Suction air spray device for compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a low cost spray device achieving atomization of water without replenishing the device with energy (heat, electricity or the like) for heating liquid to a temperature leading to decompression boiling from an outside of a system, in a system atomizing water using decompression boiling and blowing the same to compressor main flow fluid flowing in a compressor. <P>SOLUTION: A spray device 11 spraying water to a liquid before flowing into the compressor 10 is constructed to spray water heated by heat of liquid compressed by the compressor 10 to the liquid before flowing into the compressor 10. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a spray device that sprays water onto a fluid flowing into a compressor.

  With regard to the intake air spray device of the compressor, for example, as disclosed in Patent Document 1, a technique for spraying water atomized using vacuum boiling to the intake air of the compressor is disclosed.

JP-T-2002-519558

  In the technique described in Patent Document 1, a heating method for heating the liquid water to a temperature at which reduced-pressure boiling occurs (200 ° C. at a pressure of 100 bar) is not clearly described. Generally speaking, it is necessary to replenish energy for heating (such as heat or electricity) from outside the system. In this case, the conversion loss between the energy brought in from outside the system and the energy effectively used for heating the water leads to a reduction in the efficiency of the entire system including the heating system. Further, if a separate heating device is prepared, the cost increases accordingly. Furthermore, it is necessary to introduce a system that does not cause a steam explosion in equipment that generates a large amount of high-temperature water having a temperature far exceeding 100 ° C., which corresponds to the boiling point of atmospheric pressure, in order to ensure high reliability. These measures are essential. For this reason, an expensive heater as a heat source for generating the boiling under reduced pressure must be used, and it is difficult to avoid an increase in cost in this respect as well.

  An object of the present invention is to enable atomization of water to be sprayed onto a fluid flowing into a compressor with a low-cost spraying device.

  In order to achieve the above object, the spray device of the present invention is configured to spray water heated by the heat of the fluid compressed by the compressor onto the fluid flowing into the compressor.

  ADVANTAGE OF THE INVENTION According to this invention, atomization of the water sprayed on the fluid which flows in into a compressor can be achieved with a low cost spraying apparatus.

(Example 1)
An embodiment of the present invention will be described with reference to FIG. FIG. 1 is a configuration diagram of a regenerative cycle gas turbine system including a spraying device that sprays water onto a fluid flowing into a compressor according to an embodiment of the present invention.

The main components of the regeneration cycle gas turbine system shown in FIG. 1 are a compressor 10 that compresses air, a regenerator 60 that heats the air compressed by the compressor 10 using exhaust gas from the gas turbine, and a regenerator 60. A combustor 52 that generates a combustion gas by mixing and combusting heated air and fuel, a turbine 14 that is driven by the combustion gas generated by the combustor 52, and an exhaust gas that is a combustion gas that drives the turbine 14, The stack 82 is discharged after heat exchange with compressed air in the regenerator 60. In this embodiment, the pressure ratio of the compressor 10 is 16, and the intake flow rate of the gas turbine is 10 kg / s. Further, the temperature efficiency of the regenerator 60 is assumed to be 90%, and the polytropic efficiency of the compressor and the turbine is assumed to be about 90% and about 88%, respectively. The power obtained from the output shaft of the gas turbine is converted into electric power by the generator 16 and connected to a power transmission system (not shown).

Characteristic components of the present embodiment are a water addition tower 36 that is a cooling device installed in a discharge pipe 86 of the compressor 10 and a spray nozzle 11 that is a spray device that sprays water on the intake air of the compressor 10. . Water is supplied to the hydration tower 36 from the outside by a water supply pump 7 and a regulating valve 38. The water tower 36 is provided with a pipe 13 for taking out liquid water accumulated on the bottom surface of the tower, and the pipe 13 is connected to a spray nozzle 11 which is a compressor intake spray device via a valve 12. Next, the inside of the water tower 36 will be described with reference to FIG.

  FIG. 2 shows an enlarged view of the hydration tower 36 of the present embodiment. A gas distributor 70 is installed in the hydration tower 36 in order to guide the compressed air from the compressor 10 from the discharge pipe 86 and distribute the air uniformly in the tower. This gas disperser has an opening in the downward direction in order to suppress the inflow of droplets falling from above. The packing 71 is installed above the gas disperser 70 in order to increase the effective area for gas-liquid contact in the tower. As the filler 71, a structure having a large surface area per volume, which is generally used in a chemical plant or the like, is used. In this example, a commercially available irregular packing was assumed as the packing 71. Further, the water pump 36 is provided with a circulation pump 6 that recirculates the circulating water dropped to the lower part of the tower above the packing 71 in the tower. The circulation pump 6 sucks liquid phase water from a liquid pool 74 generated in the lower part of the water addition tower 36 through a pipe 76, and a liquid disperser installed above the packing by a pipe 77 and a regulating valve 84. 80 is configured to be able to supply the required amount of liquid phase water. The liquid disperser 80 is generally used in a chemical plant or the like, and has a function of spraying liquid phase water over the entire surface of the packing as evenly as possible. The liquid reservoir 74 is configured to be able to supply makeup water from a water source (not shown) by the water supply pump 7 and the regulating valve 38. A water level gauge 78 is installed to control the water level of the liquid reservoir 74 so as to be close to a predetermined position. When the water level of the liquid pool 74 is lowered, the adjustment valve 38 provided in the pipe 75 is operated to supply makeup water from the water source. When the water level of the liquid pool 74 rises, the adjustment valve 39 provided in the pipe 79 is operated to discharge the liquid phase water out of the system. In a system configuration in which the internal pressure of the hydration tower 36 is lower than the pressure outside the system, a pressure pump or the like (not shown) is installed in the pipe 79 to discharge the liquid phase water at a pressure higher than the pressure outside the system.

The tower diameter of the hydration tower 36 was selected to be 1.8 m 2 from the flooding characteristics generally disclosed as the performance specifications of the packing 71. In addition, flooding is a packed tower or a perforated plate tower that flows down a liquid film opposite to an upward gas flow, and when the gas flow rate increases, This is a phenomenon that makes it impossible to flow downward. In this example, assuming that the outlet temperature of air is about 150 ° C. when 35 ° C. cold water is sprayed, the packing material 71 having a height of 0.8 m is selected. The mist remover 72 removes droplets such as entrainment generated by the shearing force between the upward air flow and the downward liquid film flow on the surface of the packing 71, and a regenerator installed downstream of the droplets. There is an action to suppress the inflow to 60. Therefore, it is desirable to install the mist remover above the filler 71 and the liquid disperser 80.

  The operation of the regenerative cycle gas turbine power generation system including the hydration tower 36 in this embodiment will be described with reference to FIG.

  The air sucked into an unillustrated intake chamber is compressed to about 1600 kPa by the compressor 10 after dust and the like are removed by an unillustrated intake filter. The compressed air flows into the hydration tower 36. In the water addition tower 36, 35 ° C. water having the same mass flow rate as that of air is sprayed on the surface of the filling 71. In the case of atmospheric conditions with an air temperature of 15 ° C. and a relative humidity of 60%, the dew point temperature of the compressed air at the inlet of the hydration tower 36 is about 29 ° C., and the hydration tower 36 is in gas-liquid contact with water higher than the dew point temperature. Air is cooled while being humidified.

The 360 ° C. air flowing in from the lower side of the water tower 36 is cooled and becomes low temperature as it flows upward while exchanging heat with the 35 ° C. liquid film flowing down the surface of the packing from above. The gas-liquid interface between the liquid film and air is covered with moist air having a saturated water vapor pressure corresponding to the temperature of the liquid film. In the lower region of the packing, since the absolute humidity of the humid air on the liquid film surface is higher than the absolute humidity of the mainstream humid air, the water vapor moves from the liquid film surface into the main air using the water vapor pressure difference as a driving force. As a result, the absolute humidity in the mainstream air increases as it flows upward. However, since the liquid film water temperature is low in the upper region of the packing, this relationship is reversed and the absolute humidity in the mainstream air is increased, and moisture in the mainstream air is condensed and moved to the liquid film. When 35 ° C. water is brought into contact with 360 ° C. compressed air as in this example, the amount of humidification from low-temperature water to air is relatively small, which is 0.6% by mass of the air mass. On the other hand, the air temperature at the outlet of the hydration tower 36 is cooled to 150 ° C., and the temperature difference is 200 ° C. or more. The liquid film water dropped from the packing flows down into the liquid pool 74 of the hydration tower 36. Moisture lost due to evaporation is replenished via the water supply pump 7 and the regulating valve 38. A part of the hot water of about 140 ° C. in the liquid pool 74 is supplied to the spray nozzle 11 through the pipe 13 and the valve 12.

  As described above, the hydration tower 36 serving as the cooling device of the present embodiment has an inlet through which the compressed gas of the compressor 10 flows, and the compressed gas flowing from the gas distributor 70 serving as the inlet is more than the inlet. The gas to be compressed is cooled by direct contact heat exchange with a liquid more than a desired amount sprayed from the liquid disperser 80 which is a liquid spraying device installed at the upper part, and the cooled compressed gas is placed above the liquid disperser 80. After passing through a mist remover 72 that is a liquid passage restraint device, the liquid flows out from an outlet provided above the mist remover 72. With such a configuration, the compressed gas can be cooled to the saturation temperature while structurally suppressing a decrease in the reliability of the compressor 10 rather than controlling the amount of sprayed water. Here, the desired amount means an amount of water that can cool the temperature of the compressed gas at the outlet of the hydration tower 36 to the saturation temperature.

  Further, the hydration tower 36 which is the cooling device of the present embodiment is configured such that a part of the sprayed liquid is recovered and the recovered liquid can be sprayed again. With such a configuration, effective use of water can be achieved, and the amount of water necessary for the system can be reduced.

The compressed air cooled to 150 ° C. by the hydration tower 36 is supplied to the regenerator 60 through the discharge pipe 25 and recovers exhaust heat from the exhaust gas that is the combustion gas after driving the gas turbine 14. The high-humidity air heated to a high temperature by the regenerator 60 is mixed with the fuel 50 by the combustor 52 to become combustion gas, which drives the turbine 14 and the power is used as power for turning the generator 16 and the compressor 10. The

  The system of the present embodiment is a cooling device that cools compressed air before being supplied to the regenerator 60 by direct contact heat exchange with water, and part of the water that has been heat-exchanged with compressed air in the water adding tower 36. And a spray nozzle 11 which is a spray device for spraying the air before flowing into the compressor 10. With such a configuration, the exhaust heat recovery of the gas turbine system is performed with the compressed air cooled by the water tower 36, so that the amount of heat that can be recovered by the regenerator 60 is increased as compared with the system that is not cooled. In addition, the amount of heat that can be recovered from the exhaust heat is increased by the amount of water added by the hydration tower 36. In other words, since the amount of heat recovered from the turbine exhaust heat and effectively used as power for the turbine 14 increases, both the output and power generation efficiency are improved by about 1.5 times compared to a simple cycle gas turbine with the same intake flow rate. Expected.

  The lower the temperature of the working medium in the compression process, the higher the pressure ratio of the turbomachine can be achieved with less compression power. In a compressor that sprays water on the compressor intake air, a higher pressure ratio can be achieved with less compression power as the amount of droplets evaporated inside increases. In order to promote the evaporation of droplets inside the compressor, it is effective to increase the contact area between the droplets and the vapor, and the smaller the droplets to be sprayed, the more liquid per unit mass. The contact area with the droplet is increased to promote the evaporation of the droplet.

  In order to make the droplets finer, there are various methods from fluid to electrical. In this embodiment, the principle of the boiling of liquid water under reduced pressure is used. That is, water exists as liquid water in the hydration tower 36 due to the high atmospheric pressure, but when sprayed in a low-pressure atmosphere through the spray nozzle 11, the droplets boil under reduced pressure, The boiling nuclei grown inside expand to break up and refine the droplets. By this action of boiling under reduced pressure, it is possible to make the droplets sprayed from the spray nozzle 11 finer to about several μm. With this configuration, evaporation inside the compressor is promoted and sufficiently fined, so that the possibility of erosion even when colliding with the compressor blades can be kept low.

  In the present embodiment, the heat of the superheated steam at the outlet of the compressor is used in order to heat the spray water to such a temperature that causes boiling under reduced pressure. The pressure at the compressor outlet is higher than that at the inlet, and the saturation temperature at the outlet pressure corresponds to the superheat temperature at the compressor inlet pressure. If water collected on the bottom of the high-pressure side of the water tower is sprayed on the low-pressure side of the compressor inlet, it causes boiling under reduced pressure. Therefore, it is not necessary to prepare a new heating source such as a heat exchanger or a heater, and since the spraying is performed at the inlet of the compressor 10 with the internal pressure of the hydration tower 36, a new pump for spraying is not necessary.

  As described above, in this embodiment, the water heated by the heat of the fluid compressed by the compressor is sprayed onto the fluid flowing into the compressor, so that the hydration tower 36 has only the original hydration function. In addition, it will be responsible for heating the spray water and pumping for spraying, and the system configuration can be simplified and the cost can be reduced. That is, atomization of water sprayed on the fluid flowing into the compressor can be achieved with a low-cost spraying device. Furthermore, since spray water having an appropriate temperature and pressure is passively generated according to the operating state of the compressor, the control is simplified as compared with the case where an external heat source is used for heating the spray water.

  In the present embodiment, high-temperature water of about 140 ° C. in the hydration tower 36 is sprayed to the intake air of the compressor by the spray nozzle 11. The intake air of the compressor 10 is usually atmospheric pressure, and the boiling point of water with respect to this is about 100 ° C. Since warm water exceeding the boiling point at that pressure is sprayed in an atmospheric pressure intake atmosphere, the sprayed droplets can be atomized to a few μm by boiling under reduced pressure. By configuring the sufficiently atomized droplets to be sucked into the compressor, it is possible to suppress the occurrence of erosion caused by the water droplets colliding with the moving blades. Further, since the atomized droplets have a high evaporation rate, a large amount of water can be evaporated inside the compressor, and the compressor power reduction effect is great.

  The heating source of the spray water in the system of the present embodiment is the heat secondarily obtained by humidifying the compressed fluid in the hydration tower 36, and is not the heat prepared for heating the spray water. If the spraying apparatus of the present embodiment is used, the heat obtained secondarily can be used as a heating source of the spray water, so that a system with high thermal efficiency can be constructed as a whole.

(Example 2)
An embodiment of the present invention will be described with reference to FIG. FIG. 1 is a configuration diagram of a heat pump system including a spraying device that sprays water on a compressor intake fluid according to an embodiment of the present invention.

The main components of the regenerative cycle gas turbine system shown in FIG. 1 are an evaporator 42 that evaporates liquid water 35 under the condition of atmospheric pressure or less by heat of hot water 40 introduced from the outside, and generates steam. The compressors 10a, 10b, 10c, and 10d that are driven by the driving device that pressurizes the steam generated by the evaporator 42, and the high-temperature steam that has been boosted by the compressor 10d are supplied to a steam demand destination such as a heat utilization facility. This is the discharge pipe 25 to be used. The compressors 10a, 10b, 10c, and 10d are connected in series, and are configured to gradually increase the water vapor pressure. Further, as characteristic constituent elements of the present embodiment, the hydration tower 36a connected to the discharge pipe 86a of the compressor 10a, the spray nozzle 11a for spraying the intake air of the compressor 10a, and the discharge pipe 86b of the compressor 10b are connected. Spray nozzle 11b for spraying to the intake air of the added water tower 36b and compressor 10b, spray nozzle 11c for spraying to the intake air of the water tower 36c and compressor 10c connected to the discharge pipe 86c of the compressor 10c, discharge of the compressor 10d A water spray tower 36d connected to a pipe 86d and a spray nozzle 11d spraying the intake air of the compressor 10d. The internal structure of the hydration towers 36a, 36b, 36c, and 36d is the same as that of the hydration tower 36 of Example 1, and therefore detailed description thereof is omitted.

  Next, the operation of this embodiment will be described. The evaporator 42 is supplied with hot water 40 heated to about 70 ° C. by an external heat source. Examples of external heat sources to be used include exhaust heat from factories, waste incineration plants, thermal power generation facilities, internal combustion engines, and the like. The liquid water 35 of the evaporator 42 is maintained at about 63 ° C. by indirect heat exchange with the hot water 40. As a method for maintaining the temperature at about 63 ° C., for example, there is a method of controlling the flow rate or temperature at which the hot water 40 is supplied. The liquid surface of the liquid water 35 is in a vapor-liquid equilibrium state of about 23 kPa of water vapor having a saturated water vapor pressure of 63 ° C. and liquid phase water of about 63 ° C. The upper space of the evaporator 42 is a space filled with water vapor having an absolute pressure of about 23 kPa by discharging air with a vacuum pump or the like in advance.

When the compressor 10a is driven by a driving device (not shown), a volume of water vapor corresponding to the capacity of the compressor 10a is sucked from the suction pipe 85a. By this suction, water vapor is continuously generated from the liquid surface of the liquid water 35, and a large amount of latent heat of evaporation is taken from the liquid water 35, but the heat is provided by heat exchange with the hot water 40. The water vapor sucked into the compressor 10a at a temperature of about 63 ° C. and a pressure of about 23 kPa is mixed with droplets sprayed by the spray nozzle 11a via the system 13a connected to the hydration tower 36a, and is then fed to the compressor 10a. Supplied. The water vapor is pressurized to about 48 kPa inside the compressor 10a, and at the same time the temperature is raised by obtaining compression power. The droplets entrained by the steam flow and flowed into the compressor take the heat from the steam in the compression process and evaporate, and the main steam is cooled by the latent heat of vaporization.

In the case where there is no cooling of the mainstream water vapor due to evaporation of the droplets, the pressure ranges from 23 kPa to 48
The steam compressed to kPa becomes superheated steam at about 145 ° C. However, when the mixture of steam and droplets is compressed as in this embodiment, the temperature of the mainstream water vapor is suppressed by evaporation of the droplets. In addition, the discharge temperature of the compressor 10a can be brought closer to the saturation temperature of about 80 ° C. at a pressure of 48 kPa as the evaporation amount of droplets increases.

  Note that the higher the temperature of the sprayed liquid water is higher than the saturation temperature relative to the pressure of the air stream to be sprayed, the more intense the reduced-pressure boiling after spraying, but if the temperature of the liquid water is too high, the effect of cooling the working medium is diminished. . Therefore, in the system of the present embodiment, it is desirable to set the temperature of the spray water to be low within the range where the reduced-pressure boiling occurs.

  As described above, some of the droplets added by the spray nozzle 11a evaporate inside the compressor 10a, and reduce the compression power by lowering the temperature of the compressor mainstream water vapor, and the remaining droplets Together with the steam compressed by the compressor 10a, it is supplied to the hydration tower 36a. In general, since the residence time of the droplets staying inside the compressor is short, it is difficult to evaporate the droplets so that they become saturated at the outlet of the compressor 10a. To be supplied.

  This superheated steam flows from the gas disperser 70 of the hydration tower 36a into the hydration tower 36a, and is sprayed from the liquid disperser 80 on the surface of the packing 71, and is hot water having a temperature lower than 80 ° C. which is the saturation temperature. Gas-liquid contact with the liquid film. Due to this contact, a part of the liquid film existing on the surface of the filler 71 is heated and evaporated by the superheated steam supplied from the gas disperser 70 and functions to lower the temperature of the superheated steam by the latent heat of evaporation. Therefore, the temperature of the superheated steam decreases as it rubs through the packing 71, and the flow rate increases due to evaporation of the liquid film. Therefore, after passing through the packing 71, the steam temperature reaches a saturation temperature of about 80 ° C. at a vapor pressure of 48 kPa, and the amount of steam increases by 5%.

  On the other hand, the spray water flowing down from the packing reaches about 80 ° C., which is the saturation temperature in the hydration tower 36 a, and flows down to the liquid pool 74. Since the amount of water flowing down due to evaporation is smaller than that at the time of supply, the water level is measured by the water level meter 78 in order to maintain the amount of water in the liquid pool 74, and the adjustment valve 38 is automatically controlled to supply makeup water from the pipe 75. As a result, by mixing with cooler water, the water temperature of the liquid pool 74 becomes a few degrees lower than the saturation temperature of 80 ° C.

  Due to the shearing force between the liquid film flowing down the surface of the filling 71 and the water vapor flowing upward, a fine mist called entrainment is generated from the surface of the liquid film. In addition, droplets that could not evaporate inside the compressor 10a are also included in this mist. The flowing water vapor and fine mist flow upward in the flow path of the filler 71 and then flow into the mist remover 72 located above. In the mist remover 72, most of the mist is removed, and the water vapor exiting the hydration tower 36a in the state of dry water vapor at the saturation temperature passes through the pipe 85b to the compressor 10b together with droplets supplied by the spray nozzle 11b. Inflow.

  The steam compressed by the compressor 10b becomes superheated steam having a pressure of about 95 kPa, and is supplied to the hydration tower 36b while containing unvaporized droplets supplied by the spray nozzle 11b. The hydration tower 36b operates in the same manner as the hydration tower 36a, and after passing through the hydration tower 36b, the droplets are sprayed by the spray nozzle 11c installed upstream of the compressor 10c in the state of dry steam at a saturation temperature at a pressure of about 95 kPa. Is supplied to the compressor 10c. Similarly, saturated steam at a temperature of about 117 ° C. and a pressure of about 179 kPa flows out from the water tower 36c, and saturated steam at a temperature of about 187 ° C. and a pressure of about 312 kPa flows out from the water tower 36d. The steam flowing out from the water tower 36d is supplied to the heat utilization facility.

  Next, the operation and effect of this embodiment will be described. In the case of a turbo compressor, the lower the temperature of the working medium in the compression process (in this case, water vapor), the greater the pressure ratio for the same compression work. As another viewpoint, when the pressure ratio is constant, the lower the working medium temperature, the smaller the compression power required for compression. In the present embodiment, the temperature of the main steam is just before the spray nozzles 11a, 11b, 11c, 11d on the upstream side of the respective inlets of the compressors 10a, 10b, 10c, 10d by the action of the water adding towers 36a, 36b, 36c, 36d. The saturation temperature for each inlet pressure, ie the minimum temperature that exists as dry steam. This means that steam having a necessary vapor pressure can be generated with a minimum necessary compression power when spraying from the spray nozzles 11a, 11b, 11c, and 11d is not considered. In addition, since the amount of steam increases each time it passes through the water tower, the amount of working medium in the upstream compressor is less than the amount of steam required in the heat utilization facility, and this action of reducing the compression flow rate. Can also reduce the compression power. Furthermore, the droplet sprayed from the spray nozzles 11a, 11b, 11c, and 11d evaporates inside the compressor, so that the temperature of the steam in the compression process can be reduced, and the required pressure can be reduced with less compression power. Steam can be generated. Since the unevaporated portion of the sprayed droplets is removed by the mist remover of the water tower installed downstream, it is possible to suppress the occurrence of erosion caused by the unevaporated vapor colliding with the downstream compressor blades. , The reliability of the compressor can be improved.

  In addition, the hydration tower 36d installed at the final outlet of the compressor has an effect of evaporating liquid water by the amount of heat of steam that is in a superheated state at the outlet of the compressor 10d to increase the amount of steam, and is also supplied to heat utilization equipment. By reducing the heat quantity of the steam, it is possible to improve the reliability of the discharge pipe 25 and to suppress the upgrading of the material. Further, by reducing the temperature difference from the atmosphere, there is an effect of suppressing heat dissipation loss of the pipe 25.

  In this embodiment, in the steam compressors 10a, 10b, 10c, and 10d, the compressed fluid supplied to each compressor is cooled by direct contact heat exchange with water, and a part of the water exchanged with the compressed fluid is sprayed by the spray device. By being configured to supply to certain spray nozzles 11a, 11b, 11c, and 11d, the compression power can be reduced by the effects of intake spray and intermediate cooling, and fine droplets can be generated with a simple configuration and control. Therefore, a highly reliable system that suppresses the occurrence of erosion can be realized at low cost. Further, since the heat energy possessed by the superheated steam at the time of intake air cooling and intermediate cooling can be converted into the mass energy of water vapor, the efficiency of the entire system can be increased.

  In this embodiment, a water source having a temperature as close as possible is used as a water source for the replenishment water to the liquid pool 74 of the hydration towers 36a, 36b, 36c. The basic operation is the same. In that case, the water temperature of the water spray from each liquid disperser 80 becomes low, and the amount of heat (sensible heat) taken from the superheated steam increases, while the amount of water vapor generated in the hydration tower 36 decreases.

  Further, in this embodiment, the circulation pump 6 and the water supply pump 7 are assumed to be mechanical, but in this embodiment, a steam jet pump is used by using higher-pressure steam in the discharge pipe 25 and the discharge pipe 86. It is also possible to configure. In this case, the heat energy of the higher-pressure steam is converted into kinetic energy that drives circulating water or water supply, and the efficiency of the entire system is reduced. However, there is an effect of simplification of the device, and it is advantageous in that there is less possibility of fluid leakage from the shaft seal portion and mixing of impurities from the outside as compared with a mechanical pump.

BRIEF DESCRIPTION OF THE DRAWINGS The block diagram of the gas turbine system which is Example 1 of this invention is shown. The enlarged view of the water tower of the gas turbine system which is Example 1 of this invention is shown. The block diagram of the heat pump system which is Example 2 of this invention is shown.

Explanation of symbols

6 Circulation pump 10, 10a, 10b, 10c, 10d Compressor 11, 11a, 11b, 11c, 11d Spraying device 12 Valve 14 Turbine 36, 36a, 36b, 36c, 36d Water tower 42 Evaporator 52 Combustor 60 Regenerator 70 Gas distributor 72 Mist remover 74 Liquid reservoir 78 Water level gauge 76, 77 Piping 80 Liquid distributor 84 Regulating valve

Claims (8)

  A spraying device configured to spray water heated by heat of a fluid compressed by a compressor onto a fluid flowing into the compressor. A spraying device for spraying water on a fluid flowing into a compressor,
The spray apparatus according to claim 1, wherein the water is heat-exchanged with the fluid compressed by the compressor. A compressor that compresses air; a combustor that mixes and burns air and fuel compressed by the compressor; a turbine that is driven by combustion gas from the combustor; the combustion gas that drives the turbine; A gas turbine system comprising a regenerator for exchanging heat between compressed air compressed by a compressor before the compressed air is supplied to a combustor,
A cooling device that cools the compressed air before being supplied to the regenerator by direct contact heat exchange with water, and an air that flows a part of the water heat-exchanged with the compressed air by the cooling device into the compressor A gas turbine system comprising: a spraying device that sprays the gas. An intermediate cooling device for a compressor that cools compressed fluid compressed by a first compressor that compresses air cooled by water spray from a spraying device before supplying the second compressor,
The compressed fluid before being supplied to the second compressor is cooled by direct contact heat exchange with water, and a part of the water exchanged with the compressed fluid is supplied to the spraying device. Compressor intermediate cooling system. An evaporator that evaporates water by heat exchange with a heat source to generate steam, a plurality of compressors that compress the steam generated by the evaporator, and water that is sprayed on the steam that flows into the plurality of compressors A heat pump system comprising a spraying device and an intermediate cooling device for cooling steam between the plurality of compressors,
The intermediate cooling device is configured to cool the steam by direct contact between the steam and water, and is configured to supply a part of the water exchanged with the steam by the intermediate cooling device to the spraying device. And heat pump system. The cooling device according to claim 3, wherein
The compressor is provided with an inlet through which compressed gas flows and an upper portion of the inlet. A desired amount or more of liquid is sprayed on the compressed gas flowing from the inlet, and direct contact heat exchange with the liquid is performed. A liquid spraying device that cools the compressed gas, and a liquid passage suppression device that is installed above the liquid spraying device and suppresses the passage of the cooled compressed gas, and a device that is provided above the liquid passage suppression device. Cooling device with an outlet. The cooling device according to claim 6,
A cooling device characterized in that a part of the sprayed liquid is recovered and the recovered liquid can be sprayed again. A spraying method for spraying water onto a fluid flowing into a compressor,
The spray method according to claim 1, wherein the water is heat-exchanged with the fluid compressed by the compressor.

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