WO2011105064A1

WO2011105064A1 - Method for generating power from exhaust heat and system for generating power from exhaust heat

Info

Publication number: WO2011105064A1
Application number: PCT/JP2011/001009
Authority: WO
Inventors: 三島　俊一; 伸季河合; 康之池上
Original assignee: メタウォーター株式会社
Priority date: 2010-02-24
Filing date: 2011-02-23
Publication date: 2011-09-01
Also published as: HK1176988A1; CN102770709A; JP2011174652A; JP5457880B2; KR101674705B1; KR20130010470A; CN102770709B

Abstract

Disclosed is a method for generating power from exhaust heat by effectively using the heat emitted from an incinerator. The method for generating power from exhaust heat includes: a first heat exchange step, in which hot air (2) heated by the exhaust gas from the incinerator (101) of a sewage treatment system (S) is supplied to a superheater (19), which is provided to the power generation system (G) at a position upstream from a turbine (10) and downstream from a separator (18), and undergoes heat exchange with a working liquid (L); a second heat exchange step, in which the hot air (2) is supplied to a heater (17) located upstream from the separator (18) and undergoes heat exchange with the working liquid (L); a waste water heat exchange step, in which the hot air (2) from the heater (17) undergoes heat exchange with the waste scrubbing water (W) emitted from the sewage treatment system (S) after scrubbing the exhaust gas; a third heat exchange step, in which the waste scrubbing water (W) is supplied to a vaporizer (16) upstream from the heater (17) and undergoes heat exchange with the working liquid (L); and a contact step when the hot air (2) comes into contact with the exhaust gas.

Description

Waste heat power generation method and waste heat power generation system

The present invention relates to a waste heat power generation method and a waste heat power generation system, and more particularly, a waste heat power generation method and waste heat using retained heat of high-temperature exhaust gas discharged from an incinerator such as a sewage sludge incinerator or a waste incinerator. The power generation system.

In recent years, efforts to global warming and environmental issues have been emphasized, and expectations for energy-saving technologies are increasing year by year. As efforts to address such environmental problems, attention has been focused on the effective use of new energy and unused energy. For example, attempts to produce new energy using energy that has been discarded without being used effectively are also included. It has been done.

For example, Patent Document 1 discloses a configuration in which steam is generated using the retained heat of exhaust gas generated from a sewage sludge incinerator and power is generated using the steam. Patent Document 2 discloses a configuration in which power is generated by superheating steam using combustion gas generated by waste incineration and guiding the steam to a steam turbine. Further, in Patent Document 3, the working liquefied medium of the power generation system is evaporated by the retained heat of the smoke washing wastewater obtained from the smoke treatment apparatus of the sewage purification processing system, and the turbine is driven by the working medium vapor to generate power. A configuration is disclosed.

In this way, when incinerating sludge and waste, high-temperature gas and wastewater are generated. Proposal to recover a part of them in the form of electric energy by using these heat energy that was previously discarded for power generation. There are many.

In the case of a sewage sludge incinerator, for example, the temperature of the exhaust gas from the incinerator is approximately 800 ° C to 850 ° C. In a general incineration plant, high-temperature exhaust gas from an incinerator is passed through a white smoke prevention air preheater or other heat exchanger to collect a part of the exhaust heat, and then dust is collected in a dust collector. Separated and removed, and further passed through a flue gas cleaning tower for water cleaning to remove components such as NOX and SOX in the exhaust gas.

If the incinerator is a fluidized incinerator, a fluidized air preheater may be installed in front of the white smoke prevention air preheater. When the dust collector is a ceramic filter, high-temperature dust collection is possible, but when it is a bag filter, dust collection is performed after the temperature is lowered to 300 ° C. or lower in a cooling tower.

In such an exhaust gas treatment system in an ordinary incineration plant, exhaust gas at about 200 ° C. to 400 ° C. is cooled to about 40 ° C. in the flue gas cleaning tower, while smoke wash wastewater is discharged at about 60 ° C. to 70 ° C. Is done. Although the smoke washing wastewater is relatively low in temperature, the specific heat of water is large, so the amount of heat is large and often exceeds 50% of the heat amount of the exhaust gas.

JP 2005-323131 A JP-A-9-310606 JP 9-32513 A

However, those described in the above-mentioned patent documents 1 to 3 simply apply to the power generation system a heat source that is discharged during incineration of waste or the like, and it cannot be said that the efficiency of energy use is sufficiently high. The recovery efficiency of thermal energy varies greatly depending on the position where the heat source is applied to the power generation system and the application method. However, the above patent documents do not provide sufficient proposals for improving the efficiency of such energy recovery. .

Also, the heat source discharged from the incinerator is not always constant, and the amount of heat may change. In such a case, if the exhaust heat source is applied to the power generation system as it is, the power generation efficiency is affected by the change in the amount of heat of the exhaust heat source, and there is a problem that stable and efficient power generation cannot be performed.

The present invention has been made in view of the above circumstances, and is an exhaust that can effectively and efficiently use a heat source discharged from an incinerator to improve its energy recovery efficiency and generate power stably and efficiently. It is an exemplary problem to provide a thermal power generation method and an exhaust heat power generation system.

In order to solve the above-described problems, an exhaust heat power generation method as an exemplary aspect of the present invention is configured to rotate high-temperature air heated by exhaust gas discharged from an incinerator included in an incineration processing system by rotating a turbine with a working fluid. Heat exchange between the hot air and the working fluid at the first position by applying the first position upstream of the turbine and downstream of the separator on the working fluid path in the exhaust heat power generation system that generates power Applying the hot air after the heat exchange at the first position to the second position upstream from the separator on the working fluid path, thereby A second heat exchange step for exchanging heat with the working fluid, and a heat exchange between the smoke-washed wastewater discharged from the incineration processing system after washing the exhaust gas and the high-temperature air after the heat exchange at the second position. By applying the heat exchange step for waste water and the smoke washing waste water after heat exchange with the high-temperature air to the third position upstream of the second position on the working fluid path, A third heat exchanging step for exchanging heat with the working fluid; and a contact step for bringing the hot air after heat exchanging with the smoke washing wastewater into contact with the exhaust gas as white smoke preventing air.

Since high-temperature air from the incineration treatment system is applied to the exhaust heat power generation system and heat exchange is performed between the high-temperature air and the working fluid, efficient power generation can be performed using waste heat. Further, the high-temperature air is applied to the exhaust heat power generation system over a plurality of locations at a first position upstream from the turbine and downstream from the separator and a second position upstream from the separator. Therefore, the amount of heat exchange with the working fluid can be increased, and sufficient heat can be given to the working fluid.

At the first position after the separator where the working fluid is in a gaseous state, heat exchange is first performed to overheat the working fluid in the gaseous state. Then, heat exchange is performed at the second position before the separator where the working fluid is in a gas-liquid two-phase state, and vaporization of the working fluid is promoted. The high-temperature air gives heat to the working fluid in a gas state with a small heat capacity, and then gives surplus heat to the working fluid in a gas-liquid two-phase state with a large heat capacity. Therefore, efficient heat exchange can be performed, and as a result, it can contribute to suppression of the fall of power generation efficiency, and the suppression of the fall of power generation amount.

Further, after the heat exchange at the second position, heat exchange between the high temperature air and the smoke washing waste water is performed, and the heat exchange between the smoke washing waste water and the working fluid after the heat exchange with the high temperature air is performed upstream of the second position. In the third position on the side. Therefore, the waste heat discharged from the incineration processing system in the form of high-temperature air or smoke-washed wastewater can be fully reused and used for exhaust heat power generation.

As a general example, the temperature of the high-temperature air heated by the exhaust gas in the incineration processing system is about 300 ° C., and the temperature of the high-temperature air after the heat exchange at the first position is about 170 ° C. to 200 ° C. is there. Further, the temperature of the high-temperature air after the heat exchange at the second position is about 100 ° C. to 150 ° C. The temperature of the smoke effluent from the incineration system is about 60 ° C. to 70 ° C., and the temperature of the smoke effluent after heat exchange with high-temperature air is about 70 ° C. to 73 ° C.

The temperature of the high-temperature air after heat exchange with the smoke-washing wastewater is still in a high temperature state of about 90 ° C to 100 ° C. When this high-temperature air is brought into contact with the exhaust gas from the incinerator, it is sufficiently used as white smoke prevention air. be able to. Therefore, in this exhaust heat power generation method, efficient energy recovery is realized by exchanging a lot of heat before using high-temperature air as white smoke prevention air without impairing the function as white smoke prevention air is doing.

In addition, since the temperature of the smoke-washed wastewater after heat exchange with high-temperature air rises to about 70 ° C to 73 ° C, by applying this smoke-washed wastewater to the third position and exchanging heat with the working fluid, Further efficiency improvement of energy recovery can be achieved.

Consolidating each hot air from the plurality of incineration systems over the plurality of incineration systems prior to heat exchange at the first location; And aggregating over a plurality of incineration systems prior to the heat exchange.

廃棄 The situation of waste disposal such as sewage sludge and garbage in one incineration treatment system is not always constant. Therefore, it cannot be said that the discharge amount / temperature (amount of heat) of high-temperature air or smoke-washed wastewater from one incineration processing system is stable.

However, by collecting each high-temperature air and smoke-washed wastewater from multiple incineration treatment systems and applying them to the exhaust heat power generation system, energy recovery can be stabilized, and the exhaust heat power generation system The merit of scale can be utilized.

For example, an incineration processing system with a large incineration capacity (for example, 5 units of normal capacity) has a limit of enlargement, and there is a risk of periodic maintenance or a stoppage of the incineration processing system at the time of failure. For this reason, when the capacity of five units is required, five large incineration processing systems are connected and used instead of a large incineration processing system.

At this time, if five waste heat power generation systems with normal capacity are connected to five incineration treatment systems with normal capacity, the equipment costs of the five waste heat power generation systems are required, resulting in high costs. In addition, when the incineration system is in operation, each exhaust heat power generation system operates near full capacity, so the metal temperature of the heat exchanger at the first position rises to near the limit (the temperature difference becomes smaller and heat exchange takes place). Is not preferable from the viewpoint of the life of the apparatus.

However, if a large-scale (for example, five units of normal capacity) waste heat power generation system is connected to five normal capacity incineration treatment systems, the equipment cost of the exhaust heat power generation system is one unit first. Since it only takes a minute, there is a cost advantage. In addition, the five incineration processing systems are not always in operation, and if an average of about three incineration processing systems are in operation, the heat exchanger in the first position of the large exhaust heat power generation system The capacity can be set to a capacity of three cars (without making it large for five cars). Therefore, there is also a cost merit of the heat exchanger in this respect.

Also, if the exhaust heat power generation system itself is large and has a sufficient capacity, and the metal temperature of the heat exchanger at the first position does not rise so much, it can contribute to the improvement of the life of the heat exchanger. Here, “aggregation across multiple incineration systems” means that there are multiple incineration systems as a whole, and is not limited to the aggregation of them. “There are multiple incinerators in the incineration system. , Including the case of “aggregating over the plurality of incinerators”. In the following text, “inclusive of multiple incineration systems” includes “when multiple incinerators exist in the incineration system and are aggregated in multiple incinerators”. It is the same.

In addition, in the concentration of each high-temperature air, adjusting means (such as an adjusting valve) for adjusting the discharge amount from each incineration processing system is provided in the discharge path, and these adjusting means are adjusted by computer control. Of course, the same applies to the smoke-washed waste water from each incineration system.

A first heat exchange avoidance step for joining the hot air with the hot air after the heat exchange at the first position without applying the hot air to the first position, and the second without applying the hot air after joining to the second position. You may further have the 2nd heat exchange avoidance step combined with the hot air after the heat exchange in a position.

Heat exchange at the first position or the second position between the hot air and the working fluid can be avoided as necessary. Therefore, depending on the discharge amount / temperature (heat amount) of high-temperature air and smoke-washed wastewater from the incineration treatment system, or depending on the power generation amount required in the exhaust heat power generation system, the high-temperature air and the working fluid Heat exchange can be performed or stopped.

In addition, heat exchange is performed only at the first position to avoid heat exchange at the second position, heat exchange is avoided only at the first position and heat exchange is performed at the second position, Since heat exchange can be performed at both the position and the second position, the heat exchange execution position can be selected according to the situation.

For example, the heat transfer area of the heat exchanger at the first position is relatively large, and the heat transfer area of the heat exchanger at the second position is relatively small, so that the heat exchange efficiency at the first position is the heat exchange at the second position. If all hot air is applied to the first position when the efficiency is higher than the efficiency, heat exchange may be performed more than necessary.

However, if heat exchange between the high-temperature air and the working fluid at the first position can be avoided by the first heat exchange avoidance step, appropriate heat recovery according to the required amount of power generation can be performed. Therefore, for example, so-called reverse tone caused by generation of excessively generated power more than necessary power on the load side (power consumption side) can be prevented.

Of course, if not only whether to avoid heat exchange between the high-temperature air and the working fluid in the first position or the second position, but also if the avoidance amount can be adjusted, the appropriate amount as needed Can generate electricity. For example, in addition to the first and second heat exchange avoidance steps, by having first and second adjustment steps (for example, a flow rate adjustment step using a flow rate adjustment valve, etc.) as will be described later, If the application amount and the avoidance amount of high-temperature air can be adjusted, the heat exchange amount (that is, the application amount of high-temperature gas) can be finely adjusted according to the required power generation amount.

In addition, the adjustment effect of the power generation amount (generated power) by adjusting the application amount / avoidance amount of high-temperature air is high when the heat transfer area of the heat exchanger at the first position is large, and when the heat transfer area is small, the effect is high. The effect is low. In other words, when the heat transfer area of the heat exchanger at the first position is small, there is little decrease in the amount of power generated when the amount of high-temperature air applied is reduced (the amount of avoidance is increased), and there are a plurality of incinerators. Considering the fluctuations on the heat output side, the investment effect is also high.

If this property is used, the heat transfer area of either the first position or the second position of the heat exchanger is set large, and if the other is set small, the high temperature air to the heat exchanger having the larger heat transfer area is set. By adjusting the application amount and the avoidance amount, it is possible to precisely and effectively adjust the power generation amount as necessary. This is because in the heat exchanger with the smaller heat transfer area, even if the inflow heat amount due to the high-temperature air slightly varies, the influence on the power generation amount is small.

Further, when the heat transfer area of the heat exchanger at the first position is small, the degree of change in the amount of power generation due to the change in the amount of applied high-temperature air is small. The amount of power generation can be secured. For example, when high-temperature air from multiple incineration processing systems is aggregated and used in an exhaust heat power generation system, not all incineration processing systems are always operating and some incineration processing systems are not operating It may become.

Even in such a case, if the heat transfer area of the heat exchanger at the first position is set to be relatively small, even if the amount of high-temperature air decreases due to partial non-operation, the power generation amount is reduced as much as possible. Can be suppressed. By setting the heat transfer area of the heat exchanger small, the cost of the heat exchanger can also be reduced.

Measuring the first working fluid temperature of the working fluid after heat exchange at the first position; measuring the first high temperature air temperature of the hot air before heat exchange at the first position; and the first high temperature air temperature; A first adjustment step for adjusting a distribution between a high-temperature air amount applied to the first position and a high-temperature air amount avoiding application to the first position based on a difference from the first working fluid temperature; and heat at the second position A step of measuring the second working fluid temperature of the working fluid after the exchange, a step of measuring a second hot air temperature of the hot air before the heat exchange at the second position, a second hot air temperature and a second working fluid temperature. And a second adjustment step of adjusting the distribution of the high-temperature air amount applied to the second position and the high-temperature air amount avoided to be applied to the second position based on the difference between the second position and the second position.

Based on the temperature difference between the first working fluid temperature and the first high-temperature air temperature, the distribution of the high-temperature air amount that is applied / not applied to the first position is adjusted, so that appropriate heat exchange based on the temperature difference is performed at the first position. Can be realized. For example, when this temperature difference is small, heat exchange is not performed much even if high temperature air is applied to the first position. In such a case, it is preferable to reduce the amount of high-temperature air applied to the first position and increase the amount of high-temperature air that avoids (does not apply) the first position.

Further, since the distribution of the high-temperature air amount that is not applied / applied to the second position is adjusted based on the temperature difference between the second working fluid temperature and the second high-temperature air temperature, appropriate adjustment based on the temperature difference is also made at the second position. Heat exchange can be realized. For example, when this temperature difference is small, heat exchange is not performed much even if high temperature air is applied to the second position. In such a case, it is preferable to reduce the amount of high-temperature air applied to the second position and increase the amount of high-temperature air that avoids (does not apply) the second position.

Note that the step of measuring the first working fluid temperature of the working fluid immediately before the heat exchange at the first position, the step of measuring the first high temperature air temperature of the high temperature air before the heat exchange at the first position, and the first high temperature air A first adjustment step for adjusting a distribution between a high-temperature air amount applied to the first position and a high-temperature air amount avoiding application to the first position based on a difference between the temperature and the first working fluid temperature; and a second position Measuring the second working fluid temperature of the working fluid immediately before the heat exchange in step, measuring the second high temperature air temperature of the hot air before the heat exchange at the second position, and the second high temperature air temperature and the second operation. It may of course have a second adjustment step for adjusting the distribution of the high-temperature air amount applied to the second position and the high-temperature air amount avoiding application to the second position based on the difference from the fluid temperature.

The exhaust heat power generation method as another exemplary aspect of the present invention consolidates each high-temperature air heated by exhaust gas discharged from a plurality of incinerators included in a plurality of incineration systems over a plurality of incineration systems. And applying the aggregated high temperature air to the first position upstream of the turbine on the working fluid path in the exhaust heat power generation system that generates power by rotating the turbine with the working fluid. A first heat exchange step for exchanging heat between the high-temperature air and the working fluid, and a contact step for bringing the high-temperature air after heat exchange at the first position into contact with exhaust gas as white smoke prevention air.

Since high-temperature air from the incineration treatment system is applied to the exhaust heat power generation system and heat exchange is performed between the high-temperature air and the working fluid, efficient power generation can be performed using waste heat. However, the situation of waste disposal such as sewage sludge and garbage in one incineration treatment system is not always constant. Therefore, it cannot be said that the discharge amount / temperature (amount of heat) of high-temperature air or smoke-washed wastewater from one incineration processing system is stable.

However, by collecting each high-temperature air from a plurality of incineration processing systems and applying it to the exhaust heat power generation system, the energy recovery can be stabilized as described above, and the exhaust heat power generation system You can take advantage of the economies of scale. For example, by collecting high-temperature air and smoke-washed wastewater from multiple incineration treatment systems and applying them to a single large-scale exhaust heat power generation system, compared to installing multiple exhaust heat power generation systems. The apparatus cost can be reduced. It can also contribute to the improvement of the life of the exhaust heat power generation system.

In the concentration of each high-temperature air, adjustment means (adjustment valves, etc.) for adjusting the discharge amount from each incineration processing system are provided in the discharge path, and these adjustment means are adjusted by computer control. Of course it is good.

Note that the temperature of the high-temperature air after heat exchange with the working fluid is generally still sufficiently high, and when this high-temperature air is brought into contact with the exhaust gas from the incinerator, it can be sufficiently utilized as white smoke prevention air. Therefore, in this exhaust heat power generation method, efficient energy recovery is performed by exchanging heat with the working fluid until high-temperature air is used as white smoke prevention air without impairing the function as white smoke prevention air. Is realized.

When the first position is downstream of the separator in the exhaust heat power generation system, hot air after the first heat exchange step and before the contact step is upstream of the separator on the working fluid path. You may further have the 2nd heat exchange step which performs heat exchange with the hot air in the 2nd position, and a working fluid by applying to the 2nd position.

In order to cool the working fluid after rotating the turbine, a step of applying cooling water to a position on the downstream side of the turbine on the working fluid path, and the cooling water after cooling the working fluid as flue gas And a step of contacting with.

Since the cooling fluid of the working fluid is brought into contact with the exhaust gas as smoke wash water, it can contribute to the saving of the amount of water used as an entire incineration processing system and exhaust heat power generation system. In addition, since the temperature of the cooling water is raised after cooling the working fluid (ie, exchanging heat with the working fluid), if it is used for supplying water to the flue gas cleaning tower of the incineration processing system, it contributes to an increase in the temperature inside the tower. And has the effect of increasing the temperature of the smoke drainage.

The working fluid may be any of ammonia, chlorofluorocarbon or ammonia / water mixed fluid.

These fluids are easy to vaporize at a relatively low boiling point. Therefore, by using these fluids as working fluids, it is possible to effectively use the heat from waste heat (low-temperature heat source) that is present in a large quantity but at a low temperature, thereby realizing exhaust heat power generation using a temperature difference. it can.

A waste heat power generation system as still another exemplary aspect of the present invention is a waste heat power generation system that generates power by rotating a turbine with a working fluid, and is heated by exhaust gas discharged from an incinerator included in the incineration processing system. Applied to the first position upstream of the turbine and downstream of the separator in the working fluid path, thereby performing heat exchange between the hot air and the working fluid in the first position. By applying the heat exchange function and the hot air after heat exchange at the first position to the second position upstream of the separator on the working fluid path, the hot air and the working fluid at the second position A second heat exchange function for exchanging heat, and a waste heat exchange function for exchanging heat between the smoke-washed wastewater discharged from the incineration processing system after washing the exhaust gas and the high-temperature air after heat exchange at the second position, , By applying the smoke washing drain after heat exchange with warm air to the third position upstream of the second position on the working fluid path, heat exchange between the smoke washing drain and the working fluid at the third position is performed. A third heat exchange function to be performed and a contact function for bringing the high-temperature air after heat exchange with the smoke-washing wastewater into contact with the exhaust gas as white smoke prevention air.

According to still another exemplary aspect of the present invention, an exhaust heat power generation system is an exhaust heat power generation system that generates power by rotating a turbine with a working fluid, and each exhaust gas is discharged from a plurality of incinerators included in the plurality of incineration processing systems. A function of consolidating the high temperature air heated by the exhaust gas to be distributed over a plurality of incineration processing systems, and applying the aggregated high temperature air to the first position upstream of the turbine on the working fluid path A first heat exchange function for exchanging heat between the high-temperature air and the working fluid at the first position, and a contact function for bringing the high-temperature air after the heat exchange at the first position into contact with the exhaust gas as white smoke prevention air. Have.

Further problems or other features of the present invention will become apparent from the preferred embodiments described below with reference to the accompanying drawings.

According to the present invention, the heat source discharged from the incinerator can be used effectively, the energy recovery efficiency can be improved, and power generation can be performed stably and efficiently. For example, by applying high-temperature air from an incineration treatment system equipped with the incinerator to the exhaust heat power generation system at multiple locations and then using it as white smoke prevention air, efficient energy recovery of previously discarded thermal energy can be achieved. In addition, the white smoke prevention function can be sufficiently achieved.

By consolidating high-temperature air and smoke-washed wastewater from multiple incineration treatment systems and applying them to the exhaust heat power generation system, the impact of changes in the operating status of each incineration treatment system is reduced and stable energy recovery is realized. ing. In addition, by adjusting the amount of high-temperature air that is applied to the exhaust heat power generation system and the amount of high-temperature air that is not applicable, the exhaust heat power generation system can be adapted to changes in the amount of waste heat from the incineration system and the required power generation amount. The amount of high-temperature air to be applied can be changed, and the required amount of power generation can be appropriately performed stably.

1 is a block diagram showing a schematic configuration of a sewage treatment plant including a power generation system that realizes an exhaust heat power generation method according to an embodiment of the present invention. It is a block diagram which shows the outline of an internal structure of the processing system shown in FIG. It is a block diagram which shows the outline of the internal structure of the electric power generation system shown in FIG. It is a block diagram of the electric power generation system which concerns on Example 1 of this invention. It is a block diagram of the electric power generation system which concerns on the comparative example 1 of this invention. It is a block diagram of the electric power generation system which concerns on the comparative example 2 of this invention. It is a block diagram of the electric power generation system which concerns on the comparative example 3 of this invention. It is a block diagram of the electric power generation system which concerns on the comparative example 4 of this invention.

Hereinafter, an exhaust heat power generation system that realizes an exhaust heat power generation method according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a block diagram showing a schematic configuration of a sewage treatment plant (hereinafter abbreviated as a plant) P according to an embodiment of the present invention. The plant P includes a sewage treatment system (hereinafter abbreviated as a treatment system) S and a power generation system (exhaust heat power generation system) G as a plurality of incineration treatment systems. In the plant P, high-temperature air (white smoke prevention air) 2 and smoke-washed waste water W from the processing system S are applied to the power generation system G. Each high-temperature air 2 and each smoke-washing waste water W from the plurality of processing systems S are aggregated and applied to the power generation system G.

Further, the high-temperature air 2 after heat exchange in the power generation system G is sent from the power generation system G to the flue gas cleaning tower 105 (see FIG. 2) of each processing system S as white smoke prevention air 2. It has become. Further, the cooling water C used for cooling the working fluid in the power generation system G is sent to the flue gas cleaning tower 105 of each processing system S as a part of the smoke cleaning water.

FIG. 2 is a block diagram showing an outline of the internal configuration of the processing system S. Since the plurality of processing systems S have almost the same configuration, the configuration of one processing system S will be described, and the description of the configuration of other processing systems S will be omitted. This processing system S is roughly configured to include an incinerator 101, a fluidized air preheater 102, a white smoke prevention air preheater 103, a dust collector 104, and a flue gas cleaning tower 105.

In FIG. 2, 101 is an incinerator, and in this embodiment, a fluidized incinerator for incinerating a sewage sludge dewatered cake. However, in the present invention, the incinerator 101 is not limited to this, and may be a waste incinerator. The exhaust gas is usually a high temperature exhaust gas of about 800 to 850 ° C. Reference numeral 102 denotes a fluidized air preheater into which this high-temperature exhaust gas is introduced. The fluidized air is preheated to, for example, 650 ° C. and supplied to the dispersion tube at the bottom of the furnace. When the incinerator 101 is not a fluidized incinerator, the fluidized air preheater 102 is omitted.

A white smoke prevention air preheater 103 is installed after the flowing air preheater 102. This white smoke prevention air preheater 103 is a heat exchanger for obtaining high-temperature air (white smoke prevention air) 2 for preventing the water vapor in the exhaust gas discharged from the chimney from being seen as white smoke, and is about 300 A heated gas (white smoke prevention air) at 0 ° C. is obtained. On the other hand, when the exhaust gas passes through the white smoke prevention air preheater 103, the temperature is lowered to 250 to 400 ° C., and is led to the next dust collector 104 to remove dust.

Here, as a typical example of the high-temperature air (white smoke prevention air) 2, air is generally conceivable, but of course, other various gases may be applied. Also, the air heated by the white smoke prevention air preheater 103 and before being sent to the chimney 108 described later is called high-temperature air, and the air sent to the chimney 108 and exhibiting the white smoke prevention function is called white smoke prevention air. However, since both are the same in practice, the same reference numeral 2 is used for explanation.

In this embodiment, the dust collector 104 is a ceramic dust collector excellent in heat resistance, and can collect the exhaust gas at 250 to 400 ° C. that has passed through the white smoke prevention air preheater 103 as it is. However, a bag filter can also be used as the dust collector 104. In that case, it is necessary to arrange a cooling tower in the preceding stage and to lower the temperature to the heat resistance temperature of the bag filter. The temperature drop of the exhaust gas in the dust collector 104 is small, and the exhaust gas enters the next flue gas cleaning tower 105 at 200 to 400 ° C.

The flue gas cleaning tower 105 is an apparatus that removes components such as NOX and SOX in the exhaust gas by introducing the exhaust gas from the lower part of the tower and bringing it into contact with water (smoke water) W sprayed from the upper nozzle 106. . As in the prior art, the water in the tower is sent to the nozzle 106 by the pump 107 and circulated for use. In the exhaust gas cleaning tower 105 of this embodiment, a chimney 108 is connected to the upper part of the tower, and the exhaust gas cleaned in the tower is discharged from the chimney 108. In addition, a multi-stage shelf portion 109 is formed at an intermediate portion between the flue gas cleaning tower 105 and the chimney 108, and washing with water is sufficiently performed by sufficiently bringing the clean water supplied from the upper portion into contact with the exhaust gas. It is devised to be done.

In the flue gas cleaning tower 105, since the exhaust gas comes into contact with water, most of the retained heat of the exhaust gas at 200 to 400 ° C. moves to the water side, and the smoke washing drain discharged from the flue gas cleaning tower 105 as described above. W is warm water of 60-70 ° C. In the present invention, the exhaust heat power generation is performed using the retained heat of the high-temperature air 2 at about 300 ° C., but the retained heat of the smoke washing waste water W is also utilized together with this.

For this reason, in the present embodiment, as will be described later, the smoke-washed waste water W coming out of the smoke-flushing tower 105 is heated by heat exchange with the high-temperature air 2 (drain heat exchange step, waste heat exchange function). Therefore, it is supplied to the exhaust heat power generation system G. The temperature rise varies depending on the equipment and operation method, but is usually in the range of 5 to 15 ° C. Since the high temperature air 2 after heat exchange with the smoke washing waste water W maintains a temperature of about 90 ° C. to 100 ° C., it can be sent to the chimney 108 to perform its original function as the white smoke prevention air 2 it can.

If the temperature rise of the smoke washing waste water W is increased, the temperature of the high-temperature air 2 after heat exchange with the smoke washing waste water W (the heat exchange step for waste water, the heat exchange function for waste water) decreases, Even if the temperature is reduced to the extent, white smoke is not generated under the climatic conditions where the atmospheric temperature is 20 ° C. and the humidity is 100%, but white smoke is generated when the atmospheric temperature is 0 ° C. and the humidity is 100%. However, there are no legal restrictions on the generation of white smoke, and this condition is only a few days even in winter. Further, the smoke-washed waste water W that has been heated by heat exchange with the high-temperature air 2 in this way becomes warm water of about 70 ° C. to 73 ° C. and is supplied to the exhaust heat power generation system G.

FIG. 3 is a block diagram showing an outline of the internal configuration of the power generation system G. As the power generation system G, it is preferable to use a temperature difference power generation system using a working fluid L as a low boiling point fluid such as ammonia, chlorofluorocarbon or an ammonia / water mixed fluid. Such a temperature difference power generation system itself is already known as described in, for example, Japanese Patent Application Laid-Open No. 7-91361, which is filed by Saga University. For example, surface seawater having relatively high temperature and cold seawater having a deep layer are known. It is a system that can perform temperature difference power generation using the temperature difference between.

As shown in FIG. 3, the power generation system G includes a turbine 10, a generator 11, an absorber 12, a condenser 13, a circulation pump 14, a regenerator 15, an evaporator 16, a heater 17, a separator 18, and a superheater. A (steam heater) 19 and a pressure reducing valve 20 are provided for the general configuration. The power generation system G also includes temperature sensors 21 to 24, first control means 25, second control means 26, first adjustment valve 27, and second adjustment valve 28. As shown in FIG. 3, since the working fluid L circulates in the working fluid path R while repeating heating and cooling, the working fluid L is sequentially directed from the circulation pump 14 toward the downstream (the direction in which the working fluid flows). Each of the above configurations will be described.

The liquid-phase working fluid L sent out by the circulation pump 14 is preheated by the regenerator 15 and then sent to the evaporator 16. The position where the evaporator 16 is installed is a third position in the working fluid path R. In the evaporator 16, heat exchange between the working fluid L and the smoke washing waste water W is performed (third heat exchange step, third heat exchange function), and heat transfer from the smoke washing waste water W to the working fluid L is performed. . As a result, the working fluid L becomes a gas-liquid two-phase state in which the internal heat energy state is increased, and is sent to the next heater 17.

The position where the heater 17 is installed is the second position in the working fluid path R. In the heater 17, heat exchange between the working fluid L and the high temperature air 2 is performed (second heat exchange step, second heat exchange function), and heat transfer from the high temperature air 2 to the working fluid L is performed. As a result, the working fluid L becomes a gas-liquid two-phase state in which the internal thermal energy state is further increased, and is sent to the separator 18.

The separator 18 separates the working fluid L in a gas-liquid two-phase state into a gas phase and a liquid phase. The working fluid L in the liquid phase portion is again sent to the regenerator 15 to take heat, and is further sent to the absorber 12 through the pressure reducing valve 20. On the other hand, the working fluid L in the gas phase is sent from the separator 18 to the superheater 19. The position where the superheater 19 is installed is the first position in the working fluid path R. In the superheater 19, heat exchange between the working fluid L and the high temperature air 2 is performed (first heat exchange step, first heat exchange function), and heat transfer from the high temperature air 2 to the working fluid L is performed. As a result, the working fluid L becomes superheated steam whose internal thermal energy state is further increased and is sent to the turbine 10.

The working fluid L in the superheated steam state rotates the turbine 10 and generates power by a generator connected to the turbine 10. Then, the working fluid L that has finished the power generation work is sent to the absorber 12 and merges with the working fluid L sent via the pressure reducing valve 20. The absorber 12 is, for example, a nozzle spray type, and the working fluid L (liquid phase) from the pressure reducing valve 20 is sprayed toward the working fluid L (gas phase) after the power generation, and the gas phase The working fluid L is deprived of heat and cooled.

Thereafter, the working fluid L sent to the condenser 13 is cooled by the cooling water C, returns to the liquid phase, and reaches the circulation pump 14 again. In this way, the working fluid L is heated by the smoke washing waste water W and the high-temperature air 2 while being sent by the circulation pump 14, cooled by the cooling water C after rotating the turbine 10, and circulated in the path R. Generate electricity. The superheater 19 is provided at a first position upstream from the turbine 10 and downstream from the separator 18, and the heater 17 is provided at a second position upstream from the separator 18, The evaporator 16 is provided at a third position upstream of the heater 17.

The high-temperature air 2 from the processing system S is aggregated from the plurality of processing systems S (high-temperature air aggregation step, high-temperature air aggregation function) and sent to the power generation system G in a combined state. Thereby, the influence of the fluctuation | variation of the processing condition for every processing system S is reduced, and the provision of the stable high temperature air 2 is enabled.

The concentrated hot air 2 is first applied to the superheater 19 in the first position. Then, it is applied to the heater 17 at the second position, and then applied to the drainage heater 29 to perform heat exchange with the smoke washing drainage W (drainage heat exchange step, drainage heat exchange). Function). Then, the high-temperature air 2 after completion of the waste heat exchange step is sent to the processing system S again, applied to the flue gas cleaning tower 105 of each processing system S, and used as white smoke prevention air 2. It has become. The white smoke prevention air 2 comes into contact with the exhaust gas (contact step, contact function) and prevents the generation of white smoke in the exhaust gas.

In the power generation system G, a superheater avoidance path 30 for avoiding application of the high-temperature air 2 to the superheater 19 (first heat exchange avoidance step, first heat exchange avoidance function) is arranged, and on the path 30 Is provided with a first regulating valve 27. The first adjusting valve 27 opens or closes the valve based on a control signal from the first control means 25 to apply the hot air 2 to the superheater 19 or to the superheater avoidance path 30. In other words, the application to the superheater 19 is avoided.

The first control means 25 is composed of, for example, a computer, a sequencer, a relay switch, etc., receives the sensor outputs of the

temperature sensors

21 and 22, and controls the opening and closing of the first adjustment valve 27 based on those sensor outputs. The temperature sensor 21 measures the temperature t1 of the working fluid L on the downstream side of the working fluid path R from the superheater 19 (first working fluid temperature measuring step, first working fluid temperature measuring function). It is. The temperature sensor 22 is a sensor for measuring the temperature T1 of the high-temperature air 2 upstream of the superheater 19 on the high-temperature air 2 path (first high-temperature air temperature measurement step, first high-temperature air temperature measurement function). It is.

More specifically, the first control means 25 determines the amount of gas of the high-temperature air 2 applied to the superheater 19 based on the temperature difference between the measured temperature T1 measured by the temperature sensor 22 and the measured temperature t1 measured by the temperature sensor 21, and the superheater. The distribution of the gas amount of the high-temperature air 2 that avoids the application to 19 is adjusted by the opening / closing control of the first adjustment valve 27. At this time, when the temperature difference (T1-t1) between the temperature T1 and the temperature t1 is small, the first regulating valve 27 is opened so that as much hot air 2 as possible passes through the superheater avoidance path 30, and the temperature T1 When the temperature difference (T1−t1) between the temperature t1 and the temperature t1 is large, the first adjustment valve 27 is closed, and control is performed so that as much hot air 2 as possible passes through the superheater 19.

In the power generation system G, a heater avoidance path 31 for avoiding application of the high-temperature air 2 to the heater 17 (second heat exchange avoidance step, second heat exchange avoidance function) is disposed. Is provided with a second regulating valve 28. The second adjustment valve 28 opens or closes the valve based on a control signal from the second control means 26 to apply the high temperature air 2 to the heater 17 or to the heater avoidance path 31. To avoid application to the heater 17.

The second control means 26 is composed of, for example, a computer, a sequencer, a relay switch, etc., receives the sensor outputs of the

temperature sensors

23 and 24, and controls the opening and closing of the second adjustment valve 28 based on those sensor outputs. The temperature sensor 23 measures the temperature t2 of the working fluid L on the downstream side of the working fluid path R from the heater 17 (second working fluid temperature measuring step, second working fluid temperature measuring function). It is. The temperature sensor 24 measures the temperature T2 of the high temperature air 2 on the upstream side (and downstream side of the superheater 19) on the high temperature air 2 path from the heater 17 (second high temperature air temperature measurement step, 2 high temperature air temperature measuring function).

More specifically, the second control means 26 determines the amount of gas of the high-temperature air 2 applied to the heater 17 based on the temperature difference between the measured temperature T2 measured by the temperature sensor 24 and the measured temperature t2 measured by the temperature sensor 23, and the heater. The distribution of the gas amount of the high-temperature air 2 that avoids application to 17 is adjusted by opening / closing control of the second adjustment valve 28. At this time, when the temperature difference (T2−t2) between the temperature T2 and the temperature t2 is small, the second adjustment valve 28 is opened so that as much hot air 2 as possible passes through the heater avoidance path 31, and the temperature T2 When the temperature difference (T2−t2) between the temperature t2 and the temperature t2 is large, the second regulating valve 28 is closed and control is performed so that as much hot air 2 as possible passes through the heater 17.

Smoke washing wastewater W from the treatment system S is aggregated from a plurality of treatment systems S (smoke wash drainage concentration step, smoke wash drainage concentration function) into the power generation system G in a combined state. Sent. Thereby, the influence of the fluctuation | variation of the processing condition for every processing system S is reduced, and the provision of the stable smoke washing waste water W is enabled.

The collected smoke washing waste water W is subjected to heat exchange with the high-temperature air 2 after the second heat exchange step or the second heat exchange avoidance step in the waste water heater 29 (drain heat exchange step, drain heat exchange function). It is like that. Then, the smoke washing waste water W is applied to the evaporator 16 at the third position, and heat exchange with the working fluid L is performed (third heat exchange step, third heat exchange function).

Normal temperature water can be used as the cooling water C which is a low-temperature heat source. The cooling water C applied to the condenser 13 is clean water. By supplying water to the upper part of the flue gas cleaning tower 105 of the processing system S after the condenser 13, the amount of water used can be suppressed. Since the cooling water C is reused as the smoke washing waste water W, it contributes to water saving as a whole system and contributes to improvement of environmental suitability. Since the cooling water C is also heated by the condenser 13, if it is used for water supply to the flue gas cleaning tower 105, it contributes to an increase in the temperature in the tower and has an effect of increasing the temperature of the smoke washing waste water W. .

[Example 1]
The power generation amount (turbine output) in the power generation system G having the configuration shown in FIG. 4 was estimated by simulation calculation. The calculation conditions are as follows. In the first embodiment, the temperature T, the pressure p, the density index value ρ, the ammonia / water ratio Y, the entropy s of the working fluid L at each position r1 to r10 on the working fluid path R shown in FIG. And the enthalpy H was estimated. The calculation results are shown in Table 1. Here, the density index value means the reciprocal of the density (kg / m ³ ).

<Calculation conditions>
-Hot air 2:
-Flow rate: 9300 m ³ / h
-Temperature at position g1: 300 ° C
The temperature at position g2: 170 ° C.
-Temperature at position g3: 150 ° C
-Temperature at position g4: 100 ° C
-Smoke drainage W:
-Flow rate: 53m ³ / h
-Temperature at position w1: 70 ° C
-Temperature at position w2: 60 ° C
The temperature at position w3: 73 ° C.
・ Cooling water C:
-Temperature at position c1: 20 ° C
The temperature at position c2: 25 ° C.
・ Working fluid L:
-Component: ammonia / water ratio = 0.95

[Comparative Example 1]
The power generation amount (turbine output) in the power generation system G configured as shown in FIG. 5 was estimated by simulation calculation. In this comparative example 1, high-temperature air 2 is not applied to the power generation system G. The conditions are the same as in Example 1. In Comparative Example 1, the temperature, pressure, and density of the working fluid L were estimated at the respective positions r1 to r10 on the working fluid path R shown in FIG. Table 2 shows the calculation results. Here, the density index value means the reciprocal of the density (kg / m ³ ).

[Comparative Example 2]
The power generation amount (turbine output) in the power generation system G configured as shown in FIG. 6 was estimated by simulation calculation. The calculation conditions for the hot air 2 are as follows. The calculation conditions regarding the smoke-washing waste water W (temperature at the positions w1 and w2), the cooling water C (temperature at the positions c1 and c2) and the working fluid L are the same as those in the first embodiment. In Comparative Example 2, the temperature, pressure, and density of the working fluid L were estimated at each position r1 to r10 on the working fluid path R shown in FIG. Table 3 shows the calculation results. Here, the density index value means the reciprocal of the density (kg / m ³ ).

<Calculation conditions>
-Hot air 2:
-Flow rate: 9300 m ³ / h
-Temperature at position g1: 300 ° C
The temperature at position g2: 100 ° C.

[Comparative Example 3]
The power generation amount (turbine output) in the power generation system G having the configuration shown in FIG. 7 was estimated by simulation calculation. The calculation conditions for the hot air 2 are as follows. The calculation conditions regarding the smoke-washing waste water W (temperature at the positions w1 and w2), the cooling water C (temperature at the positions c1 and c2) and the working fluid L are the same as those in the first embodiment. In Comparative Example 3, the temperature, pressure, and density of the working fluid L were estimated at the respective positions r1 to r10 on the working fluid path R shown in FIG. Table 4 shows the calculation results. Here, the density index value means the reciprocal of the density (kg / m ³ ).

[Comparative Example 4]
The power generation amount (turbine output) in the power generation system G configured as shown in FIG. 8 was estimated by simulation calculation. The calculation conditions for the hot air 2 are as follows. The calculation conditions regarding the smoke-washing waste water W (temperature at the positions w1 and w2), the cooling water C (temperature at the positions c1 and c2) and the working fluid L are the same as those in the first embodiment. In Comparative Example 4, the temperature, pressure and density of the working fluid L were estimated at the respective positions r1 to r10 on the working fluid path R shown in FIG. Table 5 shows the calculation results. Here, the density index value means the reciprocal of the density (kg / m ³ ).

<Calculation conditions>
-Hot air 2:
-Flow rate: 9300 m ³ / h
-Temperature at position g1: 300 ° C
The temperature at position g2: 170 ° C.
-Temperature at position g3: 100 ° C

As described above, the power generation system G according to the first embodiment of the present invention (hot air 2 is applied to the first position downstream of the separator 18 and the second position upstream of the separator 18 to exchange heat with the working fluid L. Then, the high-temperature air 2 is applied to the smoke washing waste water W to exchange heat with the smoke washing waste water W, and the subsequent smoke washing waste water W is applied to the third position upstream from the second position to apply the working fluid L and heat. According to the replacement configuration, the power generation efficiency can be significantly improved. The turbine output (power generation amount) is 181% higher than Comparative Example 1, 29% higher than Comparative Example 2, 26% higher than Comparative Example 3, and 0.6% higher than Comparative Example 4. is doing.

The preferred embodiments of the present invention have been described above, but the present invention is not limited to these embodiments, and various modifications and changes can be made within the scope of the gist. For example, as the retained heat used for power generation, factory exhaust heat or hot spring heat can be used instead of the exhaust gas retained heat discharged from the incinerator.

C: Cooling water G: Power generation system (exhaust heat power generation system)
L: Working fluid P: Plant (sewage treatment plant)
R: Working fluid path S: Treatment system (sewage treatment system, incineration treatment system)
W: Water (smoke wash water, smoke wash drain)
2: High temperature air (white smoke prevention air)
10: turbine 11: generator 12: absorber 13: condenser 14: circulation pump 15: regenerator 16: evaporator 17: heater 18: separator 19: superheater (steam heater)
20: Pressure reducing valve 21 to 24: Temperature sensor 25: First control means 26: Second control means 27: First adjustment valve 28: Second adjustment valve 29: Drain heater 30: Superheater avoidance path 31: Heater avoidance Path 101 Incinerator 102 Fluid air preheater 103 White smoke prevention air preheater 104 Dust collector 105 Smoke exhaust cleaning tower 106 Nozzle 107 Pump 108 Chimney 109 Shelf

Claims

The high-temperature air heated by the exhaust gas discharged from the incinerator included in the incineration processing system is upstream of the turbine on the working fluid path in the exhaust heat power generation system that generates power by rotating the turbine with the working fluid. A first heat exchanging step for exchanging heat between the hot air at the first position and the working fluid by applying to a first position downstream of the separator;
The hot air after the heat exchange at the first position is applied to the second position upstream of the separator on the working fluid path, so that the hot air and the working fluid at the second position are A second heat exchange step for exchanging heat with
A waste water heat exchange step for performing heat exchange between the smoke washed waste water discharged from the incineration processing system after washing the exhaust gas and the high temperature air after heat exchange in the second position;
By applying the smoke-washed waste water after heat exchange with the high-temperature air to a third position upstream of the second position on the working fluid path, the smoke-washed waste water at the third position and the A third heat exchange step for exchanging heat with the working fluid;
And a contact step of bringing the high-temperature air after heat exchange with the smoke-washing wastewater into contact with the exhaust gas as white smoke prevention air.
Concentrating the high temperature air from a plurality of the incineration treatment systems across the plurality of incineration treatment systems prior to heat exchange at the first location;
The exhaust heat according to claim 1, further comprising the step of consolidating the smoke effluent from the plurality of incineration processing systems over the plurality of incineration processing systems before heat exchange with the high temperature air. Power generation method.
A first heat exchange avoidance step of joining the high temperature air with the high temperature air after heat exchange at the first position without applying the high temperature air to the first position;
The second heat exchange avoiding step of joining the high-temperature air after the merging with the high-temperature air after the heat exchange at the second position without applying to the second position. The exhaust heat power generation method described in 1.
Measuring a first working fluid temperature of the working fluid after heat exchange at the first position;
Measuring a first hot air temperature of the hot air before heat exchange at the first position;
Based on the difference between the first high-temperature air temperature and the first working fluid temperature, the distribution of the high-temperature air amount applied to the first position and the high-temperature air amount avoiding application to the first position is adjusted. A first adjusting step,
Measuring a second working fluid temperature of the working fluid after heat exchange at the second position;
Measuring a second hot air temperature of the hot air before heat exchange at the second position;
Based on the difference between the second high temperature air temperature and the second working fluid temperature, the distribution of the high temperature air amount applied to the second position and the high temperature air amount avoiding application to the second position is adjusted. The exhaust heat power generation method according to any one of claims 1 to 3, further comprising: a second adjustment step.
Aggregating each high temperature air heated by the exhaust gas discharged from each of the plurality of incinerators included in the plurality of incineration systems over the plurality of incineration systems;
By applying the aggregated high temperature air to the first position upstream of the turbine on the working fluid path in the exhaust heat power generation system that generates power by rotating the turbine with the working fluid, the first position A first heat exchanging step for exchanging heat between the hot air and the working fluid;
And a contact step of bringing the high-temperature air after heat exchange at the first position into contact with the exhaust gas as white smoke prevention air.
When the first position is downstream of the separator in the exhaust heat power generation system,
Applying the hot air after the first heat exchanging step and before the contacting step to a second position upstream of the separator on the working fluid path; The exhaust heat power generation method according to claim 5, further comprising a second heat exchange step for performing heat exchange between the high-temperature air and the working fluid.
Applying cooling water to a position downstream of the turbine on the working fluid path to cool the working fluid after rotating the turbine;
The exhaust heat power generation method according to any one of claims 1 to 6, further comprising a step of bringing the cooling water after cooling the working fluid into contact with the exhaust gas as smoke wash water.
The exhaust heat power generation method according to any one of claims 1 to 7, wherein the working fluid is any one of ammonia, chlorofluorocarbon, and an ammonia / water mixed fluid.
An exhaust heat power generation system that generates power by rotating a turbine with a working fluid,
By applying the high temperature air heated by the exhaust gas discharged from the incinerator included in the incineration processing system to the first position on the working fluid path upstream from the turbine and downstream from the separator, A first heat exchange function for exchanging heat between the hot air and the working fluid in the first position;
The hot air after the heat exchange at the first position is applied to the second position upstream of the separator on the working fluid path, so that the hot air and the working fluid at the second position are A second heat exchange function for exchanging heat with
A heat exchange function for drainage that performs heat exchange between the smoke-washed wastewater discharged from the incineration processing system after washing the exhaust gas and the high-temperature air after heat exchange in the second position;
By applying the smoke-washed waste water after heat exchange with the high-temperature air to a third position upstream of the second position on the working fluid path, the smoke-washed waste water at the third position and the A third heat exchange function for exchanging heat with the working fluid;
A waste heat power generation system having a contact function for bringing the high-temperature air after heat exchange with the smoke washing waste water into contact with the exhaust gas as white smoke prevention air.
An exhaust heat power generation system that generates power by rotating a turbine with a working fluid,
A function of consolidating each high-temperature air heated by the exhaust gas discharged from each of the plurality of incinerators included in the plurality of incineration systems over the plurality of incineration systems;
By applying the aggregated high temperature air to the first position upstream of the turbine on the working fluid path, the first heat for exchanging heat between the high temperature air and the working fluid at the first position. Exchange function,
A waste heat power generation system comprising: a contact function for bringing the high-temperature air after heat exchange at the first position into contact with the exhaust gas as white smoke prevention air.