JP2005214089A - Combined cycle generating set - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combined cycle generating set, for eliminating the need for enlarging turbine blades of a steam turbine, and effectively utilizing calorie of steam discharged from the steam turbine for direct power generation. <P>SOLUTION: The combined cycle generating set comprises: a first generating set 2 using a gas turbine 1 as a drive source; a second generating set 4 using a steam turbine 3 as a drive source; and an exhaust heat recovery boiler 5 generating steam for driving the steam turbine 3 by using exhaust heat of the gas turbine 1. The combined cycle generating set further comprises: a regenerator 6 entering the calorie of the steam discharged from the steam turbine 3 into absorbent solution to regenerate the steam; and an absorber 7 making the absorbent solution absorb the steam to generate heat of absorption. The heat recovery boiler 5 incorporates two steam circuits through which high temperature steams of different temperature flow, that is, a circuit L1 having a fuel economizer, a steam drum and a superheater 1, and a circuit L2 having a superheater 2, so that the high temperature steams flowing through the steam circuits L1, L2 are heated. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a power generator. More specifically, a first power generation device that uses a gas turbine as a drive source, a second power generation device that uses a steam turbine as a drive source, and generates steam that drives the steam turbine using the exhaust heat of the gas turbine. The present invention relates to a combined cycle power generation device having an exhaust heat recovery boiler.

In recent thermal power plants, a combined cycle power plant having a shorter start-up operation time and higher plant thermal efficiency is becoming mainstream as compared with a conventional power plant.
This combined cycle power plant combines a gas turbine plant with a steam turbine plant and an exhaust heat recovery boiler, uses the exhaust heat (exhaust gas) from the gas turbine plant to generate steam in the exhaust heat recovery boiler, and the steam Is supplied to a steam turbine plant to generate electric power, an example of which is shown in FIG.

In this combined cycle power generation apparatus, the first power generation apparatus 2 is rotationally driven by the gas turbine 1.
The second power generation device 4 is rotationally driven by the steam turbine 3, and the steam for driving the steam turbine 3 is generated by the exhaust heat recovery boiler 5 using the exhaust heat of the gas turbine 1.

Combustion air compressed by the air compressor 10 and fuel provided via the fuel line LF are combusted by the combustor 11. The combustion gas “G” of the combustor 11 is expanded by the gas turbine 1 and rotationally drives the gas turbine 1. The rotational force rotates the rotor (not shown) of the first generator 2 via the shaft 16 to generate power.
The driving source of the air compressor 10 that compresses the combustion air also obtains the power generated in the gas turbine 1 from the rotational force transmitted through the shaft 16.

Exhaust gas from the gas turbine 1 is supplied to the exhaust heat recovery boiler 5 via an exhaust supply line LE. In the exhaust heat recovery boiler 5, the amount of heat held by the gas turbine exhaust is used to generate steam for driving the steam turbine 3. The high-pressure steam “V _H ” for driving the steam turbine generated by the exhaust recovery boiler 5 flows through the line L2 and flows into the steam turbine 3.

Here, the name of the device to be interposed in each area of the line LH2 in exhaust heat recovery boiler 5, the phase whether liquid (H 2 _O) flowing therethrough (liquid phase, gas phase), the name is different.

When condensed in the condenser 8 to become a liquid phase, a head is added by the water pump Pw and supplied into the exhaust heat recovery boiler 5, it flows in the economizer 51. At that stage, the temperature is raised to, for example, 500 ° C. (temperature at which water evaporates in the exhaust heat recovery boiler 5) while maintaining the liquid phase.
In other words, the economizer 51 is a mechanism for increasing the sensible heat from the seawater temperature to the evaporation temperature (500 ° C.).

Next, in the steam drum 52, the liquid phase water heated to 500 ° C. by the economizer 51 is evaporated (latently changed in heat) to become 500 ° C. steam.
Here, the steam at 500 ° C. generated by the phase change is saturated steam. If saturated steam is supplied to the steam turbine 3, the saturated steam that has been cooled down by rotating the steam turbine 3 immediately becomes water, and cavitation occurs. Due to the cavitation, the turbine blades of the steam turbine 3 are damaged.
In order to prevent damage to the turbine blades of the steam turbine 3 due to cavitation, it is only necessary to supply water vapor that does not immediately become water even after the turbine blades are rotated.
Therefore, the saturated water vapor (for example, 500 ° C.) generated in the steam drum 52 is further heated by the superheater H to be heated (for example, 700 ° C. to 800 ° C.).

For example, the high-pressure steam “V _H heated to 700 ° C. to 800 ° C. by the superheater _{H is used.}
”Flows through the line L2 and is supplied to the steam turbine 3 to be rotationally driven. Power generation is performed by the second generator 4 by rotating the steam turbine 3.
Since power is generated by the two generators 2 and 4, the power generation efficiency of the combined cycle power plant is high.

The low-pressure steam “V _L ” exiting the steam turbine 3 flows through the line L 1, and the amount of heat (latent heat) held therein is dumped into seawater (usually about 20 ° C.) in the condenser 8 to condense. To do.

Here, in order to increase the efficiency of the steam turbine 3, it is necessary to increase the pressure difference between the steam flowing into the steam turbine 3 and the steam flowing out from the steam.
In the case of a conventional combined cycle power plant, the pressure of the steam flowing out from the steam turbine 3 is about 1/20 of the steam pressure supplied via the line L2, and the specific volume increases.
However, as a result of the increase in specific volume, there is a problem that the volumetric flow rate of the steam passing through the steam turbine 3 is increased, and the blades of the turbine must be increased accordingly.

That is, the steam emitted from the steam turbine 3 has a low pressure and a temperature of about 20 ° C., and has latent heat, but the latent heat held by the low-temperature steam of about 20 ° C. is difficult to use. Therefore, as described above, the condenser 8 is dumped into seawater.
As described above, there is a demand for effective use of the amount of heat (latent heat) that has been discarded.

  On the other hand, in the prior art (see Patent Documents 1 and 2), a technique is disclosed in which an absorption refrigerator is driven by exhaust heat to generate cold and warm heat.

However, large-scale power generation facilities such as a combined cycle power plant are provided in remote areas far from urban areas and residential areas due to location restrictions. Even if cold and hot are generated by the above-mentioned technology, in remote areas far away from urban areas and residential areas, houses and other facilities that use the cold and hot are located around the plant. Since it does not exist, the generated cold and heat are not used.
And if it is the cold and warm which are not utilized, there is no point in producing | generating. That is, the amount of heat held by the steam emitted from the steam turbine in the combined cycle power plant is not effectively used unless it is used for power generation.

In this regard, the conventional techniques described in Patent Documents 1 and 2 described above have introduced an example in which cold energy is generated using an absorption chiller / heater, or more heat is generated as an absorption heat pump. The present invention does not meet the above-described requirement for effectively using the amount of heat held by steam generated from a steam turbine in a power plant for power generation.
JP-A-3-134207 JP-A-5-263610

  The present invention has been proposed in view of the problems of the prior art described above, and it is not necessary to increase the size of the turbine blades of the steam turbine, and the amount of heat held by the steam discharged from the steam turbine can be directly generated. The purpose is to provide a combined cycle generator that can be used effectively.

The combined cycle power generation device of the present invention includes a first power generation device (2) using a gas turbine (1) as a drive source, a second power generation device (4) using a steam turbine (3) as a drive source, and a gas. In a combined cycle power generation device having an exhaust heat recovery boiler (5) that generates steam for driving the steam turbine (3) using exhaust heat of the turbine (1), the steam emitted from the steam turbine (3) It has a regenerator (6) that regenerates steam by putting the amount of heat it holds into the absorbing solution, and an absorber (7) that absorbs the steam into the absorbing solution and generates absorption heat, and an exhaust heat recovery boiler (5 ) Has two steam circuits (circuits L8, L13A, L24B, L34B having a economizer 51, a steam drum 52, a superheater H1, and circuits L7, L17B, L23 having a superheater H2 through which high-temperature steam having different temperatures flow. , L33B) and is configured to heat high-temperature steam flowing through each of the steam circuits (L8, L13A, L24B, L34B; L7, L17C, L23B, L33B) (claim 1). : Includes all embodiments of FIGS.

In carrying out the present invention, the steam turbine (3) is preferably configured to be driven to rotate by being supplied with two types of high-temperature steam generated in the exhaust heat recovery boiler (5) (FIG. 1). To FIG. 4).
The steam turbine (3) preferably has a steam temperature of about 100 ° C. and a pressure of about 0.1 MPa.

According to the present invention having such a configuration, the regenerator (6) that regenerates steam by putting the amount of heat held by the steam from the steam turbine (3) into the absorbing solution, and absorbs the steam into the absorbing solution. An absorber (7) that generates absorption heat, and the regenerator (6) and the absorber (7) constitute an absorption cycle, and in the absorption cycle, the absorption generated in the absorber (7). Using heat, high-temperature and high-pressure steam can be generated. Then, the generated high-temperature, high-pressure steam is allowed to flow through one of the two steam circuits (steam circuits L7, L17C, L23B, L33B having a superheater H2) built in the exhaust heat recovery boiler (5), It is heated and supplied to the steam turbine (3).
Here, since the high-temperature and high-pressure steam generated in the absorption cycle is directly used to generate power in the steam turbine (3), according to the present invention, the steam emitted from the steam turbine (3) is retained. The amount of heat can be directly used for power generation.

In addition, since the amount of heat held by the steam from the steam turbine (3) can be directly used for power generation, the power generation device (power generation) can be performed without increasing the efficiency of the steam turbine (3) as in the conventional combined cycle power generation device. The plant) overall power generation efficiency does not decrease. In other words, even if the temperature and pressure of the steam leaving the steam turbine (3) are not lowered as much as possible, the overall power generation efficiency is not lowered.
Therefore, it becomes possible to discharge steam at a much higher temperature and pressure from the steam turbine (3) as compared with the case of the conventional combined cycle power generation device (for example, the temperature of the steam discharged from the steam turbine (3) is reduced to about At 100 ° C., the pressure can be about 0.1 MPa), and the specific volume of the steam is much smaller than in the conventional case, and the volume of the steam passing through the turbine blades of the steam turbine (3) The flow rate also decreases. Therefore, the turbine blade can be reduced in size.

In the combined cycle power generation device of the present invention, a line through which steam from the steam turbine (3) flows is a line (L1) communicating with the absorber (7) and a line (L2) communicating with the regenerator (6). The line (L2) that is branched to (B1) and communicates with the regenerator (6) (line L3 and) communicates with the exhaust heat recovery boiler (5) via the absorber (7) (line L6), the steam flowing in the line is condensed in the regenerator (6) and then evaporated by the absorbed heat generated in the absorber (7) (high-pressure steam “V _H2 ”). A line (line L5) through which the steam that has been heated (superheated) in the second superheater H2) and supplied to the steam turbine (3) (via the line L7) and regenerated in the regenerator (6) flows is provided. Exhaust heat recovery via condenser (8 and first water pump P1) The regenerated steam that is in communication with the boiler (5) and flows inside the condenser is condensed by the condenser (8), heated by the exhaust heat recovery boiler (5) (superheated by the economizer 51 of the exhaust heat recovery boiler, and steam drum It can be configured such that it evaporates at 52 and is heated by the first superheater H1 (via line L8) and supplied to the steam turbine (3) (Claim 2: FIG. 1).

  In this case, the absorption cycle composed of the absorber (7) and the regenerator (6) is a so-called “single effect”, but it can also be a “double effect”.

Such a “double effect” combined cycle power generation device of the present invention has a first absorber (71) and a second absorber (low temperature absorber 72) as an absorber, and a steam turbine (3). The line through which the vapor “V _M ” flowing out from the pipe branches (B11) into a line (L11) communicating with the second absorber (low temperature absorber 72) and a line (L12) communicating with the regenerator. The line (L12) communicating with the regenerator (6) communicates with the exhaust heat recovery boiler (5) (via the line L12A, the second water pump P12 and the line L12B interposed in the line L12A), The steam flowing in the inside is condensed in the regenerator (6) and heated in the exhaust heat recovery boiler (5) (with the head added by the second water pump P12) (in the economizer 51 of the exhaust heat recovery boiler 5). The first superheater is heated and evaporated on the steam drum 52 1 superheated) is by through (line L13A) is supplied to the steam turbine (3), the regenerator (6) low-pressure steam _{"V L"} flows lines reproduced by (L15) is, condenser (8 and Via the first water pump P11), it communicates with the first absorber (71) (L17) and communicates with the exhaust heat recovery boiler (5) (L17A) with the branch line (L17) and the second absorber (B12) branches to a branch line (L16) communicating with (low temperature absorber 72), and the branch line (L16) communicating with the second absorber (low temperature absorber 72) is connected to the first absorber (72). ) (L16A), in the second absorber (low-temperature absorber 72), the steam emitted from the steam turbine (3) is absorbed by the absorbing solution to generate absorption heat, and the regenerator (6 ) play reproduction vapor "V _L" in is condensed by the condenser (8), (branched Flows in L16) a second absorber (cold absorber 72) condensed water is heated by the absorbed thermal evaporation (medium-pressure steam "V _HM" flowing in) the first absorber (71) in And is absorbed by the absorbing solution (in the first absorber 71) to generate absorption heat, and the condensed liquid flowing through the branch line (L17) communicating with the first absorber (71) by the absorption heat. Is superheated and evaporated (high-pressure steam “V _H2 ”) (via the line L17A) and heated (overheated) in the exhaust heat recovery boiler (second superheater H2 in 5) (via the line L17B). It can be configured to be supplied to the steam turbine (3) (Claim 3: FIG. 2).

In the combined cycle power generator of the present invention, the line through which the steam “V _M ” emitted from the steam turbine (3) flows is connected to the line (L21) communicating with the regenerator (6) and the evaporator (9). The line (L21, L21A) is branched (B21) to the regenerating line (L22) and communicated with the regenerator (6) (via the confluence G21), and the exhaust heat is recovered via the absorber (7). In addition to communicating with the boiler (5) (lines L23, L23A), the branch (B22) branches to a branch line (L24) directly communicating with the exhaust heat recovery boiler (5). The line (L27, L27A, L27B, L27C) through which _VL ”flows communicates with the absorber (7) via the condenser (8) and the (first water pump P21) evaporator (9). The steam regenerated by the regenerator (6) is condensed water The steam is condensed in the vessel (8) (the head is added by the first water pump P21), and the evaporator (9) is charged with the amount of heat held by the steam exiting the steam turbine (3) to evaporate (high / medium pressure steam) “V _HM ”) and supplied to the absorber (7), and the steam (high-medium pressure steam “V _HM ”) supplied into the absorber (7) is absorbed by the absorbing solution to generate absorption heat, and the absorption The condensed water flowing through the lines (L21A, L23) communicating with the absorber from the regenerator (6) by heat is evaporated (high-pressure steam “V _H2 ”) (via the line L23A), and the exhaust heat recovery boiler (5th 2 is heated (superheated) by the superheater H2) (via the line L23B) and supplied to the steam turbine (3), and the steam emitted from the steam turbine (3) is condensed by the evaporator (9) and then regenerated. (6) joins the line (L21A) communicating with the absorber (7) (G21 The condensed water flowing in the branch line (L24) directly communicating with the exhaust heat recovery boiler (5) from the regenerator (6) is heated by the exhaust heat recovery boiler (5) (in the economizer 51 of the exhaust heat recovery boiler 5). Superheated, evaporated by the steam drum 52, heated by the first superheater H1, and supplied to the steam turbine (3) (via the line L24B). 3).

When such a configuration is adopted, the low-pressure steam regenerated by the regenerator (6) (flows through the line L27) is condensed by the condenser (8), and (by the first water pump P21 via the line L27A). After adding the head and passing through the line L27B) and evaporating in the evaporator (9) (after becoming high and medium pressure steam “V _HM ”), it is absorbed by the absorbing solution in the absorber (7) and regenerated. Return to vessel (6). That is, the regenerated steam that may entrain lithium bromide (LiBr), which is the solute of the absorbing solution, consists of a regenerator (6), a condenser (8), an evaporator (9), and an absorber (7). It only circulates in the absorption cycle, which is a closed system, and is not supplied to the steam turbine (3).
In other words, when the configuration described above is employed, the possibility that the highly corrosive lithium bromide will corrode the turbine blades of the steam turbine (3) is prevented.

  Here, in the configuration of the steam having the absorption cycle as a closed system, the absorption cycle is a so-called “single effect”, but it is also possible to make this a “double effect”.

Such a “double effect” combined cycle power generation device of the present invention has a first absorber (71) and a second absorber (low temperature absorber 72) as an absorber, and a steam turbine (3). The line through which the steam that has flowed out branches (B31) into a line (L31) that communicates with the regenerator (6) and a line (L32) that communicates with the evaporator (9), and the regenerator (6) The line (L31) that communicates with the exhaust heat recovery boiler (5) via the first absorber (71) (via the confluence G31 and via the second water pump P32) (line) L33, L33A), and a branch line (B33) branched to a branch line (L34) directly communicating with the exhaust heat recovery boiler (5) (L38, L38A, L38B) through which steam regenerated by the regenerator (6) flows Is the condenser (8), (first water pump P31 A branch line (L39, L39A) interposing the evaporator (9) and communicating with the absorber via the second absorber (low temperature absorber 72) (at branch point B33); It branches to the branch line (L40, L40A) communicating with the second absorber (low temperature absorber 72) via the evaporator (9), and the second via the evaporator (9). The condensed water flowing through the branch lines (L40, L40A) communicating with the other absorber (low temperature absorber 72) is charged with the amount of heat held by the steam from the steam turbine (3) in the evaporator (9). When it evaporates (high and medium pressure steam “V _HM1 ”) and flows into the second absorber (low temperature absorber 72), it is absorbed by the absorbing solution to generate absorption heat, and the second absorber (low temperature absorber 72). ) Through the branch lines (L39, L39A) communicating with the absorber (71) via Water absorbs heat absorbed in the second absorber (low-temperature absorber 72) to evaporate (high and _{medium pressure} steam “V _HM2 ”) and flows into the first absorber (71) into the absorbing solution. Lines (L33, L33A) that are absorbed and generate absorption heat and communicate with the exhaust heat recovery boiler (5) via the first absorber (71) (via the junction G31) by the absorption heat The condensed water flowing through is heated and evaporated (high-pressure steam “V _H2 ”) (via the line L33A) and heated (superheated) in the exhaust heat recovery boiler (second superheater H2 of 5) (line L33B). To the steam turbine (3) and branch to the exhaust heat recovery boiler (5) branched from the line (L33) communicating with the exhaust heat recovery boiler (5) via the first absorber (71). The condensed water flowing through the communicating line (L34) is heated (exhausted by the exhaust heat recovery boiler (5)). Superheated by the economizer 51 of the heat recovery boiler, evaporated by the steam drum 52, heated by the first superheater H1, and supplied to the steam turbine (3) (via the line L34B). The steam exiting from the steam turbine (3) passes through the line L32 and condenses in the evaporator (9), and then joins the line (L31A) flowing from the steam turbine (3) via the regenerator (6) (G31). : Merge line G31W) (Claim 5: FIG. 4).

In the practice of the present invention, the solution circulating in the absorption cycle is preferably an aqueous lithium bromide solution.
However, the solution is not limited to the lithium bromide aqueous solution, and any solution that can easily absorb water vapor and has corrosivity within an allowable range can be used.

The effects of the present invention are listed below.
(1) It has a regenerator that regenerates steam by putting the amount of heat held by the steam from the steam turbine into the absorbing solution, and an absorber that absorbs the steam into the absorbing solution and generates absorption heat. An absorption cycle is constituted by the regenerator and the absorber, and in this absorption cycle, high-temperature and high-pressure steam can be generated by utilizing the absorption heat generated in the absorber. The generated high-temperature and high-pressure steam is passed through one of the two steam circuits built in the exhaust heat recovery boiler, heated, and supplied to the steam turbine.
Since the high-temperature and high-pressure steam generated in the absorption cycle is directly used to generate power with the steam turbine, the amount of heat held by the steam from the steam turbine can be directly used for power generation. .
(2) Since the amount of heat held by the steam from the steam turbine can be directly used for power generation, the power generation efficiency of the entire power generation system does not decrease even if the efficiency of the steam turbine is not increased as in the conventional combined cycle power generation system . In other words, even if the temperature and pressure of the steam exiting the steam turbine are not lowered as much as possible, the overall power generation efficiency is not lowered.
(3) Since the overall power generation efficiency is not reduced, it is possible to discharge steam at a much higher temperature and pressure from the steam turbine than in the case of a conventional combined cycle power generation device. The temperature of the generated steam can be about 100 ° C. and the pressure can be about 0.1 MPa. Accordingly, the specific volume of the steam is much smaller than in the conventional case, and the volume flow rate of the steam passing through the turbine blades of the steam turbine is also reduced. Therefore, the turbine blade can be reduced in size.
(4) Regenerated steam that may entrain lithium bromide (LiBr), which is the solute of the absorbing solution, only circulates in the absorption cycle, which is a closed system consisting of a regenerator, condenser, evaporator, and absorber. And is not supplied to the steam turbine.
Therefore, there is no risk that the highly corrosive lithium bromide will corrode the turbine blades of the steam turbine.

Embodiments of the present invention will be described below with reference to the attached documents.
A first embodiment will be described with reference to FIG.

The gas turbine rotation drive system is the same as that of the prior art shown in FIG. That is, the fuel gas supplied from the fuel supply line LF is burned by the combustor 11 by the air compressed by the air compressor 10 driven by the gas turbine 1, and the high-temperature and high-pressure combustion gas G is blown to the gas turbine 1. Then, the gas turbine 1 is rotated, and the first generator 2 generates electric power with the rotational force.
Exhaust gas of the combustion gas G input to the gas turbine 1 is supplied to the exhaust heat recovery boiler 5.

Two systems of high-pressure steam (first high-pressure steam “V _H1 ” and second high-pressure steam “V _H2 ”) are supplied from the exhaust recovery boiler 5 to the steam turbine 3 via a line L8 and a line L7 by a method described later. The
Temperature and pressure of the steam V _M in exiting the steam turbine 3, as those of the prior art not lower, of the order of 0.1 MPa (atmospheric pressure) at about e.g. 100 ° C..
As a result, the specific volume of the medium pressure steam “V _M ” emitted from the steam turbine 3 is smaller than that of the prior art. As a result, the steam turbine passage volume flow rate is reduced, and the turbine blades can be made smaller accordingly.

About 100 ° C. and 0.1 MPa steam (intermediate pressure steam “V _M ”) exiting the steam turbine 3 is connected to a line L1 communicating with the absorber 7 and a line L2 communicating with the regenerator 6 at a branch point B1. Branch.

Steam "V _M" in supplied to the absorber 7 flows through line L1 is absorbed by the absorption solution to be dropped in the absorber 7 (concentrated solution) aqueous lithium bromide solution Q _C.

When the absorption solution Q _C has absorbed vapor, so that the absorption heat is latent heat is generated in the absorber 7 by the absorption heat, communicated to the absorber 7 from the regenerator 6 in the extension of the line L2, Condensed water flowing through the line L3 interposing the second water pump P2 is heated, and the temperature of the water in the line L3 is raised and increased.

The solution that has absorbed the medium pressure vapor “V _M ” has a low concentration and becomes a dilute solution Q _n , and connects the liquid phase of the absorber 7 and the gas phase of the regenerator 6 from the absorber 7 through the pressure reducing valve V1. It flows through the loaded line L40 and is dropped into the regenerator 6.

Pressure steam in flowing in the line L2 side with the branch point B1 exits the steam turbine 3 'V _M "flows through region LG in the regenerator, the dilute solution Q _N which is dropped into the regenerator 6 in its On the other hand, latent heat is input (latent heat exchange is performed with a dilute solution dripped into the regenerator 6), and the water becomes 100 ° C. and is sent to the second water pump P2.

Results steam in flowing line LG in the regenerator 6 "V _M" turns on the latent heat of a rare solution Q _N, steam is reproduced from a dropwise dilute solution Q _n, reproduced low-pressure steam "V _L Flows through line L5. The concentration of the absorption solution after the steam has been reproduced is increased, the concentrated solution Q _C, and the by a solution pump P to be added head solution line L4 flows, sent to the absorber 7, is dropped.
Then, when passing through the solution line L4, the sensible heat was poured into a dilute solution Q _n of the solution heat exchanger 12 through a dilute solution line L3, increasing the steam regeneration amount of the dilute solution Q _n.

On the other hand, the water in which the medium-pressure steam “V _M ” is condensed by introducing sensible heat to the absorbing solution in the region LG in the regenerator 6 is added with a head by the second water pump P2, and flows through the line L3. As described above, the absorption heat is input by the absorber 7, becomes high-pressure steam V _H2 of about 150 ° C. and 0.5 MPa, flows through the line L <b> 6, and is sent to the exhaust heat recovery boiler 5.

The high-pressure steam “V _H2 ” flowing through the line L6 is further heated and boosted in the region indicated by the symbol L67 of the exhaust heat recovery boiler 5 (second heater H2 of claim 2), and the steam turbine 3 rotates. Sufficient temperature and pressure. And it flows through the line L7, is supplied to the steam turbine 3, and the steam turbine 3 is rotationally driven.

 That is, the steam after rotationally driving the steam turbine 3 is used to generate steam flowing through the line L7. In other words, it is used for generating rotational power of the steam turbine 3 and directly used for power generation.

The steam regenerated by the regenerator 6 (for example, low-pressure steam “V _L ” of about 0.005 MPa) flows through the line L5 and is condensed in the condenser 8 through heat exchange with the seawater by the seawater line Ls.
Here, in the condenser 8, the amount of heat (latent heat) held by the low-pressure steam “V _L ” flowing through the line L5 is abandoned in the seawater, but this steam is one of the steam branched at the branch point B1. Therefore, compared with the prior art, the exhaust heat discarded in the seawater by the condenser 8 is about ½.

The water condensed in the plurality of units 8 is supplied with a head by the first water pump P1, and then supplied to the steam drum 52 having the evaporator 52a through the economizer 51 of the exhaust heat recovery boiler 5.
The temperature is raised to the evaporation temperature by the economizer 51, evaporated to vapor by the evaporator 52a, and further heated by the first superheater H1.
When not heated by the first superheater H1, when the saturated steam drives and rotates the steam turbine 3 and consumes its thermal energy, it immediately becomes a liquid phase, which causes cavitation and destroys the turbine blades. In order to prevent this, the temperature of the saturated steam is raised by the superheater H1.

The high-pressure steam “V _H1 ” heated by the first superheater H1 flows through the line L8 and is supplied to the steam turbine 3 to rotationally drive turbine blades (not shown).

Here, there are two types of high-pressure steam supplied to the turbine blades, steam “V _H2 ” flowing through the line L7 and steam “V _H1 ” flowing through the line L8. These steams have different temperatures and pressures. Accordingly, the steam turbine 3 is of a type that is supplied with steam of a plurality of types of temperatures and is rotationally driven.

Next, a second embodiment will be described with reference to FIG.
The first embodiment of FIG. 1 has a single effect, but the second embodiment of FIG. 2 exhibits a so-called “double effect”.

Such a “double-effect” combined cycle power generation device has a first absorber 71 and a second absorber (low temperature absorber) 72 as absorbers, and is about 100 ° C. from the steam turbine 3, 0.1MPa steam (medium-pressure steam _{V M)} is a branch point B11, a line L11 communicating with the cold absorber 72, branches into line L12 communicating with the regenerator 6.

Steam "V _M 'in which flow through the line L12 side at the branch point B11 exits the steam turbine 3 flows through a region LG of the regenerator 6, dilute solution Q _n being dropped into the regenerator 6 in its sent by introducing the latent heat (regenerator 6 in a dilute solution Q _n and to latent heat exchange is dropped), becomes 100 ° C. water, the second water pump P12 flows through line L12A against .
After the head is added by the second water pump P <b> 12, the head is heated by the economizer 51 of the exhaust heat recovery boiler 5 through the line L <b> 12 </ b> B and is vaporized by the steam drum 52. The vaporized steam flows through the line L13, is heated by the first superheater H1, flows through the line L13A, and is supplied to the steam turbine 3.

The medium pressure steam “V _M ” flowing through the line L11 and supplied to the low temperature absorber 72 is absorbed by the absorbing solution dropped in the low temperature absorber 72. At that time, absorption heat is generated in the low-temperature absorber 72. The condensed water flowing in the line L16 is heated by the absorbed heat generated in the low-temperature absorber 72, and the water in the line L16 is heated and pressurized.

The solution that has absorbed intermediate pressure steam "V _M" in the cold absorber 72, the concentration is low, dilute solution Q _n becomes, flowed through the in line L19A, regenerator via the second pressure reducing valve V2 6 It is dripped in.

Within regenerator 6, line L12 flow, steam in passing line LG in the regenerator 6 "V _M" turns on the latent heat of a rare solution Q _n. As a result, the low-pressure steam “V _L ” is regenerated from the dropped diluted solution Q _n , and the regenerated low-pressure steam “V _L ” flows through the line L15. The concentration of the absorption solution after the low-pressure steam "V _L" is reproduced is increased, the concentrated solution Q _C, and the flow solution line L18, is added to the head by a solution pump P, the first absorber 71 Sent and dripped.
Then, when flowing through the solution line L18, sensible heat is introduced into the absorbing solution flowing through the absorbing solution line L19A via the low-temperature solution heat exchanger 12, and further flows through the absorbing solution line L19 via the high-temperature solution heat exchanger 13. Apply sensible heat to the absorbing solution.

In the regenerator 6 again, the low-pressure steam “V _L ” regenerated by charging the latent heat of the medium pressure steam “V _M ” flowing through the line L12 flows through the line L15 and is sent to the condenser 8, where the condenser 8 When the seawater is supplied by the seawater line LS, the water is condensed and the head is added by the first water pump P11.
And it branches to lines L16 and L17 at branch point B12.

The water flowing through the line L <b> 16 passes through the low temperature absorber 72 and is heated by the above-described absorption heat, and becomes, for example, high intermediate pressure steam “V _HM ” at 150 ° C. and 0.5 MPa, and is supplied into the absorber 71. Absorber high-in supplied into the 71 steam "V _HM" is absorbed by the absorption solution (concentrated solution) Q _C dropwise addition of the absorber 71. At that time, absorption heat is generated in the absorber 71.
The absorption heat generated in the absorber 71 heats the water flowing through the line L17, for example, becomes high-pressure steam “V _H2 ” at 200 ° C. and 1.5 MPa, and flows through the line L17A. And it heats with the 2nd superheater H2 of the waste heat recovery boiler 5, is supplied to the steam turbine 3 via the line L17B, and the steam turbine 3 is rotationally driven.

 Also in FIG. 2, the steam after rotationally driving the steam turbine 3 is used to generate high-pressure steam flowing through the line L <b> 17 </ b> B, is used for generating rotational power of the steam turbine 3, and is directly used for power generation. is there.

 About another structure and an effect, it is the same as that of embodiment shown in FIG. 1, and subsequent description is abbreviate | omitted.

Next, a third embodiment will be described with reference to FIG.
In the first embodiment of FIG. 1, the steam flowing through the absorbing solution circulation system of the absorber 7 and the regenerator 6 may reach the turbine 3 and corrode the turbine blades.
Therefore, in the third embodiment shown in FIG. 3, the steam flowing in the absorption solution circuit and the steam circuit that rotates the turbine 3 are made independent of each other to prevent corrosion of the turbine 3.

The absorbing solution concentrated in the regenerator 6 is added with a head by the solution pump P, and the absorbing solution flowing through the line L25 is dropped in the absorber 7 to absorb the vapor and flow through the line L26 to the regenerator 6. Return.
The intermediate pressure steam “V _M ” exiting the steam turbine 3 and branching at the branch point B21 and flowing through the line L21 administers latent heat to the absorbing solution (dilute solution) Q _n when passing through the line LG in the regenerator 6. Then, it condenses into water and flows through the line L21A.

As a result of the administration of latent heat, steam is regenerated from the absorbing solution, and the regenerated low-pressure steam “V _L ” flows through the line L27. The steam “V _L ” flowing through the line L27 is condensed by the condenser 8 and flows through the line L27A. A head is added by the first water pump P21, and then flows through the line L27B and sent to the evaporator 9.
On the other hand, the intermediate pressure steam “V _M ” that leaves the steam turbine 3 and branches to the other line L 22 side at the branch point B 21 is supplied to the evaporator 9. The latent heat possessed by the medium pressure steam “V _M ” is input to the water flowing through the line L27B in the evaporator 9, and the water flowing through the line L27B is vaporized to form the high medium pressure steam “V _HM ”. The high intermediate pressure steam “V _HM ” flows through the line L27C.

The high intermediate pressure steam “V _HM ” flowing through the line L27C is supplied to the absorber 7 and is absorbed by the absorbing solution dripping inside the absorber 7 to generate absorption heat, thereby heating the inside of the absorber 7. And the water which flows through the line L23 is heated.

The medium pressure steam “V _M ” flowing through the line L22 and supplying latent heat by the evaporator 9 becomes condensed water and flows through the line L22A. Then, at the confluence G21, the condensed water flowing through the line L21A is merged, and then flows to the second water pump P22 via the line L21W, and the head is added. The condensed water to which the head is added by the second water pump P22 flows through the line L21B and branches into the line L23 and the line L24 at the branch point B22.
The water flowing through the line L23 is heated in the absorber 7 as described above, becomes high-pressure steam “V _H2 ”, and flows through the line L23A. And it heats with the 2nd superheater H2 in the waste heat recovery boiler 5, becomes high pressure steam, is supplied to the steam turbine 3 via the line L23B, and rotationally drives the steam turbine 3.

On the other hand, the water flowing through the line L <b> 24 is heated by the economizer 51 in the exhaust heat recovery boiler 5 and is vaporized by the steam drum 52. The vaporized steam flows through the line L24A, is heated by the first superheater H1, becomes high-pressure steam “V _H1 ”, flows through the line L24B, and is supplied to the steam turbine 3.

That is, also in the embodiment of FIG. 3, the amount of heat held by the intermediate-pressure steam “V _M ” exiting the steam turbine 3 is input to the generation of high-pressure steam flowing through the line L23A in the absorber 7, and the rotational power of the steam turbine 3 Used for creation and used directly for power generation.

 The steam regenerated in the regenerator 6 flows through the line L27, the condenser 8, the line L27A, the first water pump P21, the line L27B, the evaporator 9, and the line L27C, and is absorbed by the absorber 7 again. It is absorbed by the solution and does not reach the steam turbine 3. Therefore, the possibility that the turbine blades of the steam turbine 3 are corroded is also avoided.

 Other configurations and operational effects are the same as those of the embodiment of FIGS. 1 and 2, and the subsequent description is omitted.

Next, a fourth embodiment will be described with reference to FIG.
The fourth embodiment shown in FIG. 4 provides a “double effect” as in the second embodiment shown in FIG.

Steam V _M in flowing in the line L31 side at the branch point B31 exits the steam turbine 3, it flows through the L31A condensed by administering a latent heat regenerator 6.
In the regenerator 6, the intermediate pressure steam “V _M ” regenerates steam from the absorbing solution, and the regenerated low-pressure steam “V _L ” flows into the plurality of units 8 through the line _L 38.

In the condenser 8, the low-pressure steam “V _L ” is condensed by supplying seawater through the seawater supply line LS, flows through L38A, is pressurized by the first water pump P31, and branches through L38B. Branch to L39 and L40 at point B33. The water flowing on the line L40 side from the branch point B33 is supplied to the evaporator 9.

Here, the intermediate pressure steam “V _M ” exiting the steam turbine and branching to L32 at B31 is supplied to the evaporator 9, and latent heat is introduced into the water flowing through the line L40. The water flowing through the line L40 becomes the high intermediate pressure steam “V _HM1 ”, flows through the L40A, and flows into the low temperature absorber 72.

The high and medium pressure steam “V _HM1 ” is absorbed in the absorbing solution by the low temperature absorber 72, generates absorption heat, and heats the inside of the low temperature absorber 72. As a result, the water flowing through the line L39 is heated.
Then, the water flowing through the line L39 becomes a high intermediate pressure steam “V _HM ” and flows into the absorber 71 through the line L39A. In the absorber 71, it is absorbed by the absorbing solution, generates absorption heat, and heats the absorber 71.

The intermediate pressure steam “V _M ” flowing out of the steam turbine 3 and passing through the branch point B31 and flowing through the L32 gives latent heat to the water flowing through the line L40 in the evaporator 9 as described above, and condenses into water. . The water flows through the line L32A and merges with the water flowing through the L31A at the merge point G31.
The combined water is pressurized by the second water pump P32, flows through the line L31B, and branches to the line L33 and the line L34 at the branch point B32.

The water flowing through L33 is heated by the absorption heat in the absorber 71, becomes high-pressure steam “V _H2 ”, flows through the line L33A, and is further superheated by the second superheater H2 of the exhaust heat recovery boiler 5. The superheated high-pressure steam “V _H2 ” flows into the steam turbine 3 via the line L33B and rotates the turbine 3. When the turbine 3 rotates, the generator 4 that rotates integrally with the turbine 3 generates power.

On the other hand, the water flowing through the line L34 is heated by the economizer 51 of the exhaust heat absorption boiler 5, and the vapor which is vaporized by the steam drum 52 and further vaporized flows into the first heater H1 via the line L34A. .
The high-pressure steam “V _H1 ” superheated by the first heater H1 flows into the steam turbine 3 via the line L34B and rotates the turbine 3. When the turbine 3 rotates, the generator 4 that rotates integrally with the turbine 3 generates power.

 The absorbent solution concentrated in the regenerator 6 is added with a head by the solution pump P and flows into the absorber 71 through the line L35, the low temperature solution heat exchanger 12, and the high temperature solution heat exchanger 13.

In the low-temperature solution heat exchanger 12, the concentrated solution Q _C flowing through the line L35 is to raise the temperature receives heat from the dilute solution Q _n flowing past the line L37. Further, the high-temperature solution heat exchanger 13, the concentrated solution Q _C flowing through the line L35 receives heat from the dilute solution Q _n flowing past the line L36, further raising the temperature.

In the absorber 71, the intermediate solution absorbs the medium-high pressure steam “V _HM2 ” flowing through the line L39A and flows into the low-temperature absorber 72 through the line L36, the first pressure reducing valve V1, and the line L36A. Temperature absorber 72 in a dilute solution _{Q n} absorbs steam _{"V HM1"} intermediate-flowing line L40A, line L37, the second pressure reducing valve V2, through line L37A enters into the regenerator 6.

Also in the embodiment of FIG. 4, the amount of heat held by the intermediate-pressure steam “V _M ” exiting the steam turbine 3 is used for generating high-pressure steam flowing in the line L33A in the absorber 71, and the rotational power of the steam turbine 3 is generated. It is used live and used directly for power generation.

The low-pressure steam “V _L ” regenerated in the regenerator 6 flows through the line L38, the condenser 8, the line L38A, the first water pump P31, the lines L38B and L40, the evaporator 9, and the line L40A. It is absorbed into the absorbing solution by the low-temperature absorber 72. Further, the water flowing into the low-temperature absorber 72 from the line L39 is heated in the low-temperature absorber 72 and _becomes high intermediate pressure steam “V _HM2 ”, flows through L39A, and is absorbed by the absorber 71 in the absorber 71. The steam turbine 3 is not reached. Therefore, the possibility of corrosion of the turbine blades of the steam turbine 3 is also prevented.

 Other configurations and operational effects are the same as those of the embodiment of FIGS.

  It should be noted that the illustrated embodiment is merely an example and is not intended to limit the technical scope of the present invention.

The block diagram which shows the structure of 1st Embodiment of this invention. The block diagram which shows the structure of 2nd Embodiment of this invention. The block diagram which shows the structure of 3rd Embodiment of this invention. The block diagram which shows the structure of 4th Embodiment of this invention. The block diagram which shows the structure of the combined cycle electric power generating apparatus of a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Gas turbine 2 ... 1st generator 3 ... Steam turbine 4 ... 2nd generator 5 ... Waste heat recovery boiler 6 ... Regenerator 7, 71 ... Absorber 8 ... Condenser 9 ... Evaporator 12 ... Low temperature solution heat exchanger 13 ... High temperature solution heat exchanger 72 ... Low temperature absorbers B1, B11, B21, B31 ... 1st branch point P ... Solution pump P1, P11, P21, P31 ... 1st water pump L1-L40 ... line

Claims (5)

A first power generation device using a gas turbine as a drive source, a second power generation device using a steam turbine as a drive source, and an exhaust heat recovery boiler that generates steam for driving the steam turbine using exhaust heat of the gas turbine , And a regenerator that regenerates steam by charging the absorption solution with the amount of heat held by the steam from the steam turbine, and an absorber that generates absorption heat by absorbing the steam into the absorption solution. And the exhaust heat recovery boiler has two steam circuits through which high-temperature steam at different temperatures flow, and is configured to heat the high-temperature steam flowing through each steam circuit. Power generation device. The line through which the steam from the steam turbine flows branches into a line communicating with the absorber and a line communicating with the regenerator, and the line communicating with the regenerator communicates with the exhaust heat recovery boiler via the absorber. The steam flowing in the line is condensed by the absorption heat generated in the absorber after being condensed in the regenerator, heated by the exhaust heat recovery boiler, supplied to the steam turbine, and regenerated by the regenerator The line through which the steam flows is connected to the exhaust heat recovery boiler via the condenser, and the regenerated steam flowing inside the condenser is condensed by the condenser, heated by the exhaust heat recovery boiler, and supplied to the steam turbine. Item 1. A combined cycle power generation device according to item 1. The absorber has a first absorber and a second absorber, and a line through which steam from the steam turbine flows branches into a line communicating with the second absorber and a line communicating with the regenerator. The line communicating with the regenerator communicates with the exhaust heat recovery boiler, and the steam flowing through the regenerator is condensed by the regenerator, heated by the exhaust heat recovery boiler, supplied to the steam turbine, and regenerated by the regenerator The line through which the refrigerant flows is branched into a branch line that communicates with the first absorber through the condenser and communicates with the exhaust heat recovery boiler and a branch line that communicates with the second absorber. The branch line communicating with the vessel communicates with the first absorber. In the second absorber, the steam emitted from the steam turbine is absorbed by the absorbing solution to generate absorption heat, and is regenerated by the regenerator. The regenerated steam is condensed in the condenser and flows through the second absorber. Condensed water is heated by absorption heat, evaporated and supplied into the first absorber, absorbed by the absorption solution to generate absorption heat, and flows through a branch line communicating with the first absorber by the absorption heat. The combined cycle power generation device according to claim 1, wherein the condensate is heated and evaporated, heated by an exhaust heat recovery boiler, and supplied to the steam turbine. The line through which the steam from the steam turbine flows branches into a line communicating with the regenerator and a line communicating with the evaporator, and the line communicating with the regenerator communicates with the exhaust heat recovery boiler via the absorber. At the same time, it is branched to a branch line that directly communicates with the exhaust heat recovery boiler, and the line through which steam regenerated by the regenerator communicates with the absorber via the condenser and evaporator, and is regenerated by the regenerator The condensed steam is condensed in the condenser, the amount of heat held by the steam exiting the steam turbine in the evaporator is charged and evaporated to be supplied to the absorber, and the steam supplied into the absorber is absorbed by the absorbing solution. The absorbed water is evaporated and condensed water flowing through a line communicating from the regenerator to the absorber is evaporated by the absorbed heat and heated by the exhaust heat recovery boiler and supplied to the steam turbine. From the regenerator after condensing in The condensed water flowing in a branch line joining the line communicating with the collector and directly communicating with the exhaust heat recovery boiler from the regenerator is heated by the exhaust heat recovery boiler and supplied to the steam turbine. Combined cycle power generator. The line having the first absorber and the second absorber as the absorber, and the steam flowing out from the steam turbine flows into a line communicating with the regenerator and a line communicating with the evaporator, Line communicating with the regenerator It communicates with the exhaust heat recovery boiler via the first absorber and branches to a branch line directly communicating with the exhaust heat recovery boiler. A water line and an evaporator are installed, and a branch line that communicates with the absorber via the second absorber and a branch line that communicates with the second absorber via the evaporator The condensed water flowing through the branch line that is branched and communicated with the second absorber via the evaporator is evaporated by the amount of heat held by the steam emitted from the steam turbine in the evaporator, and is evaporated. 2 is absorbed by the absorbing solution when it flows into the absorber 2 and generates heat of absorption. The condensed water flowing through the branch line communicating with the absorber via the second absorber is evaporated when the absorption heat in the second absorber is input and flows into the first absorber. Absorbed in the absorbing solution to generate absorption heat, the condensed heat causes the condensed water flowing through the line communicating with the exhaust heat recovery boiler via the first absorber to be heated and evaporated to be heated in the exhaust heat recovery boiler. The condensed water that is supplied to the steam turbine and branches from the line that communicates with the exhaust heat recovery boiler via the first absorber and flows through the line that communicates with the exhaust heat recovery boiler is heated by the exhaust heat recovery boiler. The combined cycle power generation device according to claim 1, wherein the steam supplied from the steam turbine and condensed from the steam turbine is condensed by the evaporator and then merged with a line flowing from the steam turbine via the regenerator.

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