JP2005098552A5 - - Google Patents

Description

High moisture waste incineration facility equipped with gas turbine

  The present invention relates to a high moisture waste incineration facility equipped with a gas turbine. More specifically, an incinerator is equipped with an incineration unit for high-moisture waste, a waste heat boiler that uses the incineration exhaust gas generated by the incineration unit as a heat source, and desulfurization in which smoke washing water is brought into contact with the incineration exhaust gas that has passed through the waste heat boiler. The present invention relates to a case where a means, a heating means for incineration air supplied to the incineration means, and a gas turbine are provided.

  Currently, high moisture waste in sewage sludge discharged from houses, offices, factories, etc., sludge from wastewater treatment (such as wastewater treatment sludge from paper mills), industrial waste, and general waste is rendered harmless.・ Incinerated for the purpose of volume reduction, etc. and then disposed of (If the high-moisture waste is biomass, various ingenuity has been devised and incinerated for the purpose of recovering thermal energy, etc. ing.).

  Specifically, for example, in a sewage treatment facility, sewage is separated into sewage sludge and sewage treated water through appropriate facilities such as a first sedimentation basin, an aeration tank, and a final sedimentation basin. Incineration is performed by the incineration means. Incineration exhaust gas generated by this incineration is recovered by heat with a waste heat boiler, and after appropriate dust removal by a dust removal means such as a cyclone or a bag filter, a wet scrubber (washing tower) that directly contacts the incineration exhaust gas with smoke cleaning water, etc. After being desulfurized and cooled by this desulfurization means, it is exhausted to the atmosphere. On the other hand, the sewage treated water is discharged into a river after being subjected to appropriate treatment such as sterilization. In recent years, gas turbines are often installed in sewage treatment facilities as a power source for an aeration blower that requires a large amount of power.

  By the way, in the above sewage treatment facilities, for example, (1) the steam turbine is driven by the steam obtained from the waste heat boiler to recover the power, or (2) the exhaust gas of the gas turbine is passed through the boiler. Effective utilization of energy is achieved by methods such as (3) preheating the combustion air of the incineration means with gas turbine exhaust gas, and using the obtained steam effectively with an appropriate device (for example, Patent Documents). 1).

However, even with these methods, there is still room for improvement in terms of effective use of energy. For example, “a desulfurization means such as a scrubber is for bringing smoke-washed water into contact with the incineration exhaust gas after incineration, so that a large amount of heat energy is transferred to the smoke-washed water after the contact treatment. Regardless, such smoke-washed water is not so hot (generally, 80 ° C. or less), and thus is disposed of without being subjected to heat recovery.
JP 2000-213725 A

  The problem to be solved by the present invention is to provide a high moisture waste incineration facility equipped with a gas turbine that is remarkably excellent in the effective utilization of energy.

The present invention that has solved the above problems is as follows.
[Invention of Claim 1]
High-moisture waste incineration means, a waste heat boiler that uses incineration exhaust gas generated by this incineration means as a heat source, a steam turbine that uses steam obtained from this waste heat boiler as a drive source, and incineration via the waste heat boiler A high-moisture waste incineration facility comprising desulfurization means for bringing smoke-washed water into contact with exhaust gas, heating means for incineration air supplied to the incineration means, and a gas turbine,
A high-moisture waste disposal equipped with a gas turbine, comprising: a heat pump that uses smoke-washed water after the contact treatment as a heat source; and an intake air cooling means that cools the intake air of the gas turbine by the cold heat obtained by the heat pump. Incineration equipment.

[Invention of Claim 2]
The high-moisture waste incineration facility equipped with a gas turbine according to claim 1, wherein when the high-moisture waste is sewage sludge, the heat pump uses sewage as a cooling source.

[Invention of Claim 3]
High-moisture waste incineration means, a waste heat boiler that uses incineration exhaust gas generated by this incineration means as a heat source, a steam turbine that uses steam obtained from this waste heat boiler as a drive source, and incineration via the waste heat boiler A high-moisture waste incineration facility comprising desulfurization means for bringing smoke-washed water into contact with exhaust gas, heating means for incineration air supplied to the incineration means, and a gas turbine,
High moisture disposal equipped with a gas turbine, characterized in that, as heating means for incineration air supplied to the incineration means, in addition to heating means using gas turbine exhaust gas as a heat source, heating means using incineration exhaust gas as a heat source are provided Incineration equipment.

[Invention of Claim 4]
The heating means using the gas turbine exhaust gas as a heat source includes at least one heating means for waste heat boiler feed water and incineration exhaust gas after contact treatment, in addition to the heating means for incineration air supplied to the incineration means. High-moisture waste incineration facility equipped with a gas turbine.

[Invention of Claim 5]
High moisture waste incineration means, waste heat boiler using incineration exhaust gas generated by the incineration means as a heat source, desulfurization means for contacting the smoke exhaust water with the incineration exhaust gas passed through the waste heat boiler, and supply to the incineration means A high-moisture waste incineration facility comprising: a heating means for incineration air; and a gas turbine having a turbine driven by compression means for combustion, combustion means, and combustion gas,
A high-moisture waste incineration facility equipped with a gas turbine, comprising a mixing means for mixing at least a part of the steam obtained in the waste heat boiler with the compressed air from the compression means.

[Invention of Claim 6]
An incineration facility for high moisture waste equipped with a gas turbine according to any one of claims 1 to 5, further comprising heating means for supplying waste heat boiler water using smoke-washed water after contact treatment with incineration exhaust gas.

[Invention of Claim 7]
High-moisture waste incineration means, a waste heat boiler that uses incineration exhaust gas generated by this incineration means as a heat source, a steam turbine that uses steam obtained from this waste heat boiler as a drive source, and incineration via the waste heat boiler High moisture content provided with desulfurization means for bringing smoke-washed water into contact with exhaust gas, heating means for incineration air supplied to the incineration means, and a gas turbine having a compressor driven by intake air, combustion means and a turbine driven by combustion gas A waste incineration facility,
A heat pump that uses smoke-washed water after the contact treatment as a heat source, an intake air cooling means that cools the intake air of the gas turbine by the cold heat obtained by the heat pump, and an incineration that supplies the incineration means that uses the gas turbine exhaust gas as a heat source Heating means for supplying air and waste heat boiler feed water, heating means for incineration air using incineration exhaust gas generated by the incineration means as a heat source, and compression means for at least a part of the steam obtained in the waste heat boiler A high-moisture waste incineration facility equipped with a gas turbine.

[Main effects]
(A) The smoke-washed water is heated by contact with the incineration exhaust gas generated by the incineration means. Therefore, the smoke-washed water after the contact treatment can be used as a heat source of the heat pump, and cold heat can be obtained with the heat pump. If this cold heat is used for intake air cooling of the gas turbine, the efficiency of the gas turbine is improved.
This effect is very significant if the smoke-washed water after the contact treatment with the incineration exhaust gas has been disposed of conventionally. In addition, this effect has a great advantage because the object of incineration is high-moisture waste.
That is, when the moisture content of the waste is high, the incineration exhaust gas generated by the incineration means has a large amount of heat containing a large amount of water vapor. Therefore, the amount of heat transferred from the incineration exhaust gas to the smoke-washed water is large, and the cold heat obtained by the heat pump is large, and the gas turbine efficiency can be continuously and stably improved.

(B) Cold energy can be obtained by using the sewage after separating and removing sludge as a cooling source of the heat pump. Conventionally, sewage has been disposed of, and this effect is significant. Moreover, since the temperature of sewage is stable at 20 to 25 ° C. throughout the year, such an effect can be obtained stably. In addition, if the high-moisture waste is sewage sludge, that is, if the incineration facility is a sewage treatment facility (or part of it), "(cooling / heat removal) sewage", "(heating) smoke wash water Both have the advantage of being easy to implement because they can be obtained with a single facility.

(C) Heating (preheating) incineration air (air supplied to the incineration means) using gas turbine exhaust gas as a heat source has been conventionally performed. However, the temperature of the gas turbine exhaust gas is 450 to 480 ° C., and the amount of the incineration air is limited, so that the heat transfer (heating) cannot be sufficiently performed. However, this insufficiency can be compensated by heating the incineration exhaust gas as a heat source. If this supplement is performed, the auxiliary fuel used in the incineration means is significantly reduced.

(D) When you want to make the best use of the energy in the incineration facility as electric power, generally, install a waste heat boiler that uses incineration exhaust gas as a heat source, and use the steam obtained from this waste heat boiler to a steam turbine equipped with a generator, etc. send. Therefore, if the gas turbine exhaust gas is used as a heat source to heat the incineration air supplied to the incineration means and the heating (preheating) of the waste heat boiler feed water, the power can be recovered more efficiently.
In other words, gas turbines are most efficient at maximum load, so it is desirable to continue operation at maximum load. On the other hand, the incineration air supplied to the incineration means is a high-moisture waste whose required amount is incinerated. If the gas turbine is continuously operated at the maximum load, the gas turbine exhaust gas becomes redundant when the amount of high moisture waste is reduced. However, if the waste heat boiler feed water is heated together with the heating of the incineration air supplied to the incineration means using the gas turbine exhaust gas as a heat source, such surplus is prevented.

  Moreover, in this invention, it can replace with the heating of waste heat boiler feed water, or can heat the incineration exhaust gas after contact processing with smoke-washed water with the heating of waste heat boiler feed water. When the incineration exhaust gas after the contact treatment with the smoke-washing water is heated, surplus heat energy is effectively used, and generation of white smoke when the incineration exhaust gas is released into the atmosphere is prevented. Although this white smoke prevention effect depends on weather conditions, it is realized in the summer if the gas turbine exhaust gas is 95 to 100 ° C.

(E) In addition to the gas turbine, the provision of a steam turbine that uses steam obtained from a waste heat boiler as a driving source is accompanied by the disadvantages of increased equipment costs and an increased device installation area. However, if the steam obtained by the waste heat boiler is mixed with the compressed air obtained by the compression means of the gas turbine, and the mixed gas is combusted, then it is used as a turbine drive source (steam-injected gas turbine system). This difficulty is avoided. Normally, there is a limit to the amount of steam injected into the gas turbine, and the entire amount of steam obtained from the waste heat boiler cannot be used. Therefore, when the present invention is equipped with, for example, equipment that can use steam such as a blower or driving of an air compressor, when applied as a form for sending a part of the steam obtained with a waste heat boiler to such equipment, It becomes more preferable.

(F) The smoke-washed water after the contact treatment with the incineration exhaust gas can be used as a heating means for heating the waste heat boiler feed water depending on the amount thereof, thereby further increasing the effective utilization of energy. become.

  According to the present invention, an incineration facility for high moisture waste provided with a gas turbine that is remarkably excellent in the effective utilization of energy.

Embodiments of the present invention will be described below.
The incineration facility of the present invention is intended to treat sludge in sewage, sludge from wastewater treatment (such as wastewater treatment sludge from a paper mill), industrial waste, general waste, etc. High moisture waste is, for example, waste having a moisture content (percentage of loss on drying due to drying of sample (110 ± 5 ° C., 1 hour)) of 30% by mass or more, preferably 50% by mass or more. If it is sludge, it will generally be 70-85 mass%. Below, the case where a high moisture waste is a sewage sludge is demonstrated.

[First Embodiment]
FIG. 1 shows an equipment flow diagram of the incineration equipment 30 according to the first embodiment.
In the incineration facility 30, sewage sludge D obtained by precipitation or the like is first supplied into the incineration means 31 by a conveying means such as a conveyor. In the incineration means 31, auxiliary fuel is supplied as necessary, and the sewage sludge D is subjected to incineration processing such as combustion, thermal decomposition, and thermal decomposition by partial combustion at a high temperature of about 850 ° C., for example.

  The type of the incineration means 31 is not particularly limited, and for example, a multistage furnace, a kiln, or the like can be used. However, in the present invention where high moisture waste is subject to incineration, it is preferable to use a fluidized bed furnace such as a bubbling fluidized bed furnace or a fast fluidized bed furnace. This is because the amount of processing per volume is large and the thermal efficiency is extremely high. In the present embodiment, a bubbling fluidized bed furnace in which incineration air A is blown through an air diffuser 45a inserted from the furnace bottom side wall is used. The bubbling fluidized bed furnace 31 contains a fluid medium such as sand. Moreover, incineration residues such as ash are discharged out of the furnace from a discharge port (not shown) provided at the bottom of the furnace.

  In the incineration means 31, the incineration exhaust gas G <b> 1 generated along with the incineration is a flow path 32 connected to the top of the furnace (the flow path can circulate liquid, gas, etc., for example, ducts, pipes, etc. The same applies to other flow paths described below.) In the process of being sent to the desulfurization means 33, the waste heat boiler 51 is passed through. The waste heat boiler 51 is supplied with feed water W through a flow path 52, and the feed water W receives heat from the incineration exhaust gas G1 and becomes steam. The steam is sent to the steam turbine 56 through the flow path 54 and used for driving the steam turbine 56. As the steam turbine 56 is driven, power is collected by the generator 57. The steam after being used for driving the steam turbine 56 can be condensed by a condenser or the like (not shown) and reused as the feed water W to the waste heat boiler 51 as in the present embodiment.

  Even after passing through the waste heat boiler 51, the incineration exhaust gas G1 having a temperature of about 250 ° C. is removed by the dust removing means 47 such as a cyclone or a bag filter and then sent to the desulfurization means 33. The desulfurization means 33 removes sulfur and the like contained in the incineration exhaust gas G1 by directly contacting the incineration exhaust gas G1 with the smoke washing water S. For example, a known wet scrubber (washing tower) or the like is used. it can.

  The incineration exhaust gas G1 is supplied into the desulfurization means 33 from the bottom side wall of the desulfurization means 33, desulfurized by contact with the smoke washing water S, sent to the chimney 33a, and released from the chimney 33a into the atmosphere. . On the other hand, the smoke-washed water S having thermal energy by contact with the incineration exhaust gas G1 is sent to the heat pump 10 through the heat exchanger 72 through the flow path 26 and used as a heat source. The heat exchanger 72 heats the waste heat boiler feed water W using the smoke-washed water S as a heat source. In addition to using the smoke-washed water S as a heat source for the heat pump 10, the heat energy of the smoke-washed water S can be used more effectively by using it as a heat source for the waste heat boiler feed water W.

The type of the heat pump 10 that can be used in the present invention is not particularly limited as long as it can obtain cold heat. However, the use of the heat pump 10 shown below is recommended.
That is, as shown in FIG. 2, the heat pump 10 of the present embodiment has a low pressure (for example, when the refrigerant is water and the absorbent is LiBr, 0.87 to 1.23 [ kPa], when the refrigerant is ammonia and the absorption liquid is water, the evaporator 11 is 0.35 to 0.52 [MPa]) and the low pressure (for example, the refrigerant is water, absorption is provided). When the liquid is LiBr, 0.87 to 1.23 [kPa], when the refrigerant is ammonia, and when the absorbing liquid is water, the absorber 12 and the heating means are used. High pressure provided in the heating tube 13a (for example, 2.33 to 5.63 [kPa] when the refrigerant is water and the absorbing liquid is LiBr, and 0.86 to 1.3 when the refrigerant is ammonia and the absorbing liquid is water). 17 [MPa]) regenerator 13 and cooling as cooling means 14a (for example, when the refrigerant is water and the absorbing liquid is LiBr, 2.33 to 5.63 [kPa], and when the refrigerant is ammonia and the absorbing liquid is water, 0.86 to 1.17 [ MPa]) of condenser 14.

  In the present heat pump 10, the refrigerant R evaporates at a low temperature by heating such as brine heating by the heating tube 11 a in the evaporator 11 to generate cold heat. The evaporated refrigerant R flows to the absorber 12 through the flow pipe 21. The refrigerant R is absorbed by the absorbent C in the absorber 12. The absorbed heat generated along with this absorption is removed by the heat removal pipe 12a. The absorbing liquid C + R that has absorbed the refrigerant R is boosted by the booster pump P1 through the circulation pipe 22 and flows to the regenerator 13. In the regenerator 13, the refrigerant R evaporates from the absorbing liquid C + R by heating with the heating tube 13a. The absorbing liquid C from which the refrigerant R has evaporated returns to the absorber 12 through the flow pipe 23 and is used again to absorb the refrigerant R. On the other hand, the refrigerant R evaporated in the regenerator 13 flows to the condenser 14 through the flow pipe 24. In the condenser 14, the refrigerant R is condensed by cooling with the cooling pipe 14a. The condensed refrigerant R is returned to the evaporator 11 through a flow pipe 25 having a pressure reducing valve (not shown), and the same circulation is repeated. Reference numeral 15 denotes a supercooler, which performs heat exchange between the condensed refrigerant R and the refrigerant vapor R by heat exchange means provided therein. Reference numeral 16 denotes a heat exchanger that performs heat exchange between the absorbing liquid C + R that has absorbed the refrigerant R and the absorbing liquid C from which the refrigerant R has evaporated.

By the way, in this heat pump 10, the smoke-washed water S and the sewage U after a contact process with the incineration waste gas G1 are utilized as follows.
That is, first, a part of the sewage U is circulated in the cooling pipe 14a of the condenser 14, and the remaining part is circulated in the heat removal pipe 12a of the absorber 12. It is used for heat removal of the absorbing liquid C (one form of use as a cooling source of the heat pump 10). Since the temperature of sewage is stable at 20 to 23 ° C. throughout the year, such an effect can be obtained stably.

  Further, the smoke-washed water S after being contacted with the incineration exhaust gas G1 by the desulfurization means 33 is passed through the heating pipe 13a of the regenerator 13 through the circulation pipe 26 to heat the absorbing liquid C + R (evaporation of the refrigerant R). (One form of use as a heat source of the heat pump 10). The smoke-washed water S after being used for this heating is returned to the desulfurization means 33 through the flow pipe 28, sprayed from a spray means such as a nozzle (not shown) provided at the tip of the flow pipe 28, and again incinerated exhaust gas G1. It is used for desulfurization. The circulation of the above smoke-washed water S is performed by the circulation pump P4.

  The cooling heat obtained by the heat pump 10 is used for intake air cooling of the gas turbine 38. Specifically, in the evaporator 11, a heat transfer fluid such as brine flowing through the heating pipe 11 a whose temperature has decreased is sent to the intake air cooling means 36 including a heat exchanger or the like through the flow path 34. Heat is exchanged with air B from the flow path 37 passing through the means 36. The heat transfer fluid heated by this heat exchange is returned to the heating pipe 11a through the flow path 35 and used again for the evaporation of the refrigerant R.

  On the other hand, the air B cooled by heat exchange with the heat transfer fluid is compressed by the compressor 39 and then sent to the combustion means 40 such as a combustor through the flow path 42. In the combustion means 40, the compressed air B is combusted together with the fuel supplied into the combustion means 40, and then sent to the turbine (expander) 41 through the flow path 43 and used for driving the turbine 41. As the turbine 41 is driven, power is collected by the generator 48.

  Although it is well known that the turbine efficiency is improved by the intake air cooling (basic of the Brighton cycle), in the present invention, by using cold waste water and sewage that has been disposed of in the past, the cold energy is obtained. Since such an effect (improvement of turbine efficiency) is obtained, energy efficiency is significantly improved. Specifically, when the sewage U is 20 to 25 ° C. and the smoke-washed water S is 70 to 80 ° C., according to the heat pump 10 described above, a cold temperature of about −5 ° C. can be obtained. By setting the air B to 0 ° C., the turbine efficiency can be improved by 3 to 4%.

  Since the gas turbine exhaust gas G2 used for driving the turbine 41 has thermal energy, it is sent to the heat exchanger 46A through the flow path 44 and used for preheating (heating) the incineration air A. preferable. However, the temperature of the gas turbine exhaust gas G2 is 480 to 550 ° C., and the amount of the incineration air A is limited, so that the amount of heat transfer (heating) cannot be sufficiently performed. Therefore, it is preferable to further heat the incineration exhaust gas G1 as a heat source. In the present embodiment, the heating is performed by exchanging heat between the incineration air A and the incineration exhaust gas G1 in the heat exchanger 46B. Thus, in the present embodiment, as the heating means 46 for the incineration air A, the heating means 46A using the gas turbine exhaust gas G2 as a heat source and the heating means 46B using the incineration exhaust gas G1 as a heat source are provided. . However, the heating means 46 for the incineration air A may be any means that can raise the temperature of the combustion air A, and may be other than the above two-stage heating (46A, 46B).

  In the present embodiment, the intake air of the gas turbine 38 is air B and the fuel is city gas. However, the present invention is not limited to this. For example, if the facility generates digestion gas from sewage sludge D, the generated methane gas can be used as fuel for the gas turbine 38.

  Further, in the present embodiment, the pressure of the incineration air A is increased by a pushing fan or the like and then supplied into the incineration means 31.

  Further, in the present embodiment, utilization of the gas turbine exhaust gas G2 as a heat source is more effective. Specifically, in addition to heating (preheating) the incineration air A with the heat exchanger 46A using the gas turbine exhaust gas G2 as a heat source, the heat exchanger 53 heats the waste heat boiler feed water W. Further, the gas turbine exhaust gas G2 used for the above heating is sent to the chimney 33a and mixed in the incineration exhaust gas G1 after the contact treatment with the smoke-washed water S. Thereby, the incineration exhaust gas G1 is heated (heated), and the white smoke prevention effect is obtained. This white smoke prevention effect is sufficient if the incineration exhaust gas G1 is set to a dew point or higher, so that even the gas turbine exhaust gas G2 after being used for the previous heating can sufficiently achieve its purpose.

[Second Embodiment]
Next, an incineration facility 50 according to the second embodiment will be described with reference to FIG. However, description is made only on points different from the incineration facility 30 according to the first embodiment, and description of the same points is omitted (the same devices are denoted by the same reference numerals).

  In the incineration facility 50, the steam turbine 56 is not installed, and a part of the steam generated in the waste heat boiler 51 passes through the flow path 54 and serves as a mixing unit, in this embodiment, a combustion unit that also functions as a mixing unit. To the combustion means 40 such as a vessel. The mixing means mixes the compressed air B from the compressor 39 and the (saturated, superheated) steam from the waste heat boiler 51 to convert the saturated steam to superheated steam (the steam from the waste heat boiler 51 is saturated steam). , When the compressed air B is compressed by the compressor 39 until the temperature becomes higher than the temperature of the saturated steam.) Alternatively, the steam partial pressure is decreased to increase the degree of superheat. (For example, an ejector). Due to the mixing in the mixing means, the work amount of the turbine 41 is increased and the thermal energy is effectively used. Further, it is not necessary to send all of the steam from the waste heat boiler 51 to the mixing means, and a part of the steam can be sent to other equipment that can use steam such as a blower or a compressor. .

[Others]
(1) In heat pump 10, the combination of the refrigerant | coolant and absorption liquid which can be used is not specifically limited. For example, water (refrigerant) and LiBr (inorganic absorption liquid), NH ₃ (refrigerant), water (absorption liquid), and the like are conceivable.

(2) The smoke-washed water in the present invention is a liquid for desulfurizing and cooling the sulfur content in the incineration exhaust gas. For example, water can be used.

(3) In the present invention, the cooling source of the heat pump is expressed as “sewage” because the sludge is not separated and removed in addition to the sewage treated water obtained by separating and removing the sludge. The purpose is to include sewage that is not completely separated and removed from the sludge (because the sewage temperature is not a problem, only the sewage temperature is a problem). However, naturally, sewage is generally used as sewage treated water obtained by completely separating and removing sludge.

A fluid incinerator equipped with a fluid incinerator (diameter 5.9 m × 6.5 m), gas turbine, waste heat boiler, and steam turbine has a moisture content of 79.4 mass% [kg (water) / kg (wet material )], Sewage sludge with a calorific value of 16890 [kJ / kg (dry matter)] was supplied at 12.6 [t / h]. Combustion air consists of gas turbine exhaust gas 27100 [kg (dry gas) / h] burning city gas 13A at 554 [m ³ N / h], fluidized incinerator exhaust gas, and two heat exchangers The temperature was raised to 414 ° C. and blown into the fluidized incinerator at 23720 [kg (dry gas) / h]. Simultaneously with this blowing, city gas 13A gas was supplied at 256 [m ³ N / h] as auxiliary fuel.

The obtained incineration exhaust gas 24220 [kg (dry gas) / h] is supplied to a waste heat boiler (heat transfer area: superheated part 50 m ² , evaporation part 460 m ² , preheating part 80 m ² ). Superheated steam 9116 [kg / h] of 7 MPa and 350 ° C. was obtained. This superheated steam was put in a steam turbine and condensed at a total amount of 0.013 MPa to generate 1271 kW.

  The gas turbine operates at a combustion temperature of 1050 ° C. and an exhaust temperature of 520 ° C. under the fuel supply conditions described above, and supplies 28 ° C. intake air to 8 ° C. with cold water obtained by a heat pump as described below. did. The power generation amount of the gas turbine was 1550 kW.

The intake of the gas turbine was cold water of 2 to 3 ° C. using an ammonia-water absorption heat pump by an intake air cooler (heat transfer area 150 m ² ), and intake air of 28 ° C. was used as 8 ° C. Cold heat is obtained by putting incineration exhaust gas 23300 [m ³ N / h] through a waste heat boiler into a smoke washing tower as a desulfurization means having a diameter of 3400 mm × height 15 m, condensing moisture in the incineration exhaust gas with smoke washing water, A part (84 [m ³ / h]) of the smoke-washed water (warm water) thus obtained was taken out and obtained by driving a heat pump using this as a drive heat source.

This heat pump has a regenerator (heat transfer area 40 m ² ), a rectifying tower (diameter 600 mm × height 4000 mm), a condenser (heat transfer area 70 m ² ), an evaporator (heat transfer area 50 m ² ), a supercooler ( Heat transfer area 8m ² ), absorber (heat transfer area 50m ² ), smoke heat exchanger and booster pump (7 [m ³ / h] × 190m head), operating pressure is regenerator and The condenser was 1.35 to 1.38 MPa, and the evaporator and absorber were 0.43 MPa. The operating temperature and refrigerant concentration are as follows: the top of the regenerator (45 ° C./99.5% by mass), the high temperature part (70 ° C./50% by mass), the condenser (25 ° C./99.8% by mass), the evaporator ( 0-1 ° C./99.9% by mass) and an absorber (25-28 ° C./28-42% by mass). 100 [m ³ / h] 2 ° C. brine obtained by the evaporator was sent to the intake air cooler of the gas turbine, and the gas turbine intake air was lowered to 8 ° C. This increased power generation by 125 kW and secured 1550 kW (however, the power consumption of the heat pump was about 24 kW). The total power generation amount is 2821 kW, and the power generation efficiency for all the gases used is 3.48 [kW / m ³ N].

  In summer temperature (air temperature) of 30 to 34 ° C., it was foreseen to contribute to peak saving of daytime power.

Using the same apparatus as in Example 1, the heat exchange with the gas turbine exhaust gas (heat transfer area 800 m ² ) was 430 ° C., and the heat exchange with the incineration exhaust gas (850 ° C.) (heat transfer area 600 m ² ) was 650 ° C. Combustion air was blown into the fluid medium. The obtained incineration exhaust gas was supplied to a waste heat boiler to obtain superheated steam 7340 [kg / h] having a pressure of 1.7 MPa and 350 ° C. The superheated steam was sent to a steam turbine to generate 1165 kW, and was fully condensed at 48 ° C. The auxiliary fuel is 137 [m ³ N / h], the total power generation amount is 2665 kW, the power generation efficiency for all gases used is 3.84 [kW / m ³ N], and the auxiliary fuel is half that of Example 1. And improved efficiency.

Under the same operating conditions as the apparatus of Example 1, the exhaust gas passed through the waste heat boiler is put into a washing tower and wet-cooled, and the circulating water outlet temperature is 72 ° C and the returning hot water temperature is 68 ° C, and the circulating amount [38 m ³ / h] is set. This was heated to 68 ° C. using a heating of 45 ° C. of the waste heat boiler feed water 7200 [kg / h] from the condenser of a steam turbine by the feed water heater of 30 m ^2, then washed smoke drainage preheating of 160 m ² In order to maintain a smoke outlet condition of 75 ° C. under a weather condition of 30 ° C. and 70% humidity, an exhaust gas with an inlet temperature of 150 ° C. is set to an outlet temperature of 110 ° C., which is necessary for white smoke prevention. The outlet temperature of the boiler was raised to 120 ° C., and the boiler feed water from the smoke effluent preheater was heated to 112 ° C. and supplied to the waste heat boiler. At this time, the increase amount of the saturated steam is 710 [kg / h], which is an increase of about 10% of the evaporation amount.

It comprised with the apparatus except the steam turbine related installation among the main installations of Example 1. FIG. Of saturated steam 7344 [kg / h] generated from the waste heat boiler under operating conditions, 3200 [kg / h] is sent to the process in the treatment plant, and the remaining 4144 [kg / h] is superheated steam at 350 ° C. and 1.6 MPa. Was supplied to the combustion chamber of the gas turbine, and was supplied to the gas turbine (expansion turbine) together with the combustion gas whose temperature was increased, to generate power and obtain 2250 kW. This system enables cogeneration that can generate power and supply steam at the same time, eliminating the need for steam turbine-related equipment and making it economical. The consumption of 13A gas at this time was 687 [m ³ / h].

It is an equipment flow figure of the incineration equipment concerning a 1st embodiment. It is an equipment flow diagram of a heat pump. It is an equipment flow figure of the incineration equipment concerning a 2nd embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Heat pump 30, 50 ... Incineration equipment, 31 ... Incineration means, 33 ... Desulfurization means, 36 ... Intake air cooling means, 38 ... Gas turbine, D ... Sewage sludge, G1, G2 ... Exhaust gas, U ... Sewage.