JP2022030200A - Exhaust heat recovery boiler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an exhaust heat recovery boiler capable of optimal design according to exhaust gas conditions introduced into each of a superheater, an evaporator and a preheater. SOLUTION: The exhaust heat recovery boiler 10A of the embodiment is provided with a superheater 20, an evaporator 30, and a preheater 40 in order from the upstream side in the flow direction of the exhaust gas into which the exhaust gas from the gas turbine GT is introduced. The superheater 20, the evaporator 30, and the preheater 40 each include heat exchange units 21, 31, and 41, and main body bodies 22, 32, and 42 for accommodating heat exchange units 21, 31, and 41, respectively. Each body body 22, 32, 42 is composed of a separate body. [Selection diagram] Fig. 1

Description

Embodiments of the present invention relate to an exhaust heat recovery boiler.

In recent years, in thermal power plants, combined cycle power generation has been adopted in order to improve the thermal efficiency of the plant. The combined cycle power plant includes a gas turbine, a steam turbine, and an exhaust heat recovery steam generator (HRSG).

High-temperature and high-pressure combustion gas discharged from the combustor is introduced into the gas turbine. The gas turbine is rotated by the expansion work of the introduced combustion gas. Then, when the gas turbine rotates, the generator is rotated to generate electricity.

The exhaust gas from the gas turbine is introduced into the exhaust heat recovery boiler, and the exhaust heat recovery boiler uses the heat of the exhaust gas to generate steam. The steam is introduced into the steam turbine and rotates the generator together with the gas turbine.

As described above, the exhaust heat recovery boiler is used to effectively utilize the amount of heat of the exhaust gas discharged from the gas turbine. The conventional exhaust heat recovery boiler is provided with a heat exchanger of a superheater, an evaporator, and an economizer in one duct in the flow direction of the exhaust gas discharged from the gas turbine.

In recent years, decarbonization has been promoted, and the expansion of the use of renewable energy such as solar power and wind power and the utilization of hydrogen energy are attracting attention.

As one of the methods of utilizing the hydrogen, the development of a gas turbine power generation facility using hydrogen as a fuel is being promoted. In this gas turbine power generation facility, the turbine is rotated by the combustion gas obtained by burning hydrogen to drive the generator. Even in such a hydrogen combustion gas turbine, combined cycle power generation using an exhaust heat recovery boiler is being studied.

International Publication No. 2012/165601

In a combined cycle power generation equipped with a hydrogen combustion gas turbine, the temperature and pressure of the exhaust gas discharged from the hydrogen combustion gas turbine are, for example, the exhaust gas discharged from a conventional gas turbine that is rotated by a combustion gas obtained by burning natural gas. Higher than the temperature and pressure of. In a conventional gas turbine, the pressure of the exhaust gas at the turbine outlet is about atmospheric pressure. On the other hand, in the hydrogen combustion gas turbine, the pressure of the exhaust gas at the turbine outlet is higher than the atmospheric pressure.

Further, in order to improve the thermal efficiency, it is conceivable that the pressure and temperature of the gas turbine rotated by the combustion gas obtained by burning natural gas will be increased and the temperature and pressure of the exhaust gas will be increased.

Therefore, as an exhaust heat recovery boiler in which exhaust gas with a pressure higher than the pressure of the exhaust gas exhausted from the conventional turbine is introduced, a conventional exhaust heat recovery boiler designed on the premise that exhaust gas of about atmospheric pressure is introduced. Is not appropriate from the viewpoint of safety such as pressure resistance and heat resistance.

Also, when a superheater, an evaporator and a preheater are provided in one duct as in a conventional exhaust heat recovery boiler, the duct is made of materials according to the exhaust gas conditions at the inlet of the exhaust heat recovery boiler, which has the highest temperature and pressure. Selection and design are done. Therefore, the specifications are more than necessary for the exhaust gas conditions on the downstream side in the flow direction of the exhaust gas, and the manufacturing cost also increases.

An object to be solved by the present invention is to provide an exhaust heat recovery boiler capable of optimal design according to the exhaust gas conditions introduced in each of the superheater, the evaporator and the preheater.

The exhaust heat recovery heat exchanger of the embodiment is provided with a superheater, an evaporator, and a preheater in order from the upstream side in the flow direction of the exhaust gas into which the exhaust gas from the gas turbine is introduced. The superheater, the evaporator, and the preheater each include a heat exchange unit and a main body body for accommodating the heat exchange unit, and each main body body is configured as a separate body.

It is the schematic of the structure of the exhaust heat recovery boiler of 1st Embodiment. It is the schematic of the structure of the exhaust heat recovery boiler of the 2nd Embodiment. It is a schematic diagram when the evaporator when three evaporators are provided in parallel in the exhaust heat recovery boiler of the 2nd Embodiment is seen from the superheater side. It is the schematic of the structure of the exhaust heat recovery boiler of the 3rd Embodiment. It is the schematic of the structure of the exhaust heat recovery boiler of 4th Embodiment. It is a schematic diagram of the structure of the exhaust heat recovery boiler of the 5th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First Embodiment)
FIG. 1 is a schematic diagram of the configuration of the exhaust heat recovery boiler 10A according to the first embodiment. FIG. 1 is a side view of the exhaust heat recovery boiler 10A, and shows an outline of the internal configurations of the superheater 20, the evaporator 30, and the preheater 40.

Further, FIG. 1 schematically shows the gas turbine GT and the exhaust pipe G1 in order to show that the exhaust gas from the gas turbine GT is introduced into the exhaust heat recovery steam generator 10A, but the gas turbine GT and the exhaust gas are shown. The tube G1 is not included in the configuration of the exhaust heat recovery steam generator 10A (the same applies to the following embodiments).

The exhaust heat recovery boiler 10A generates steam by utilizing the amount of heat of the exhaust gas of the gas turbine GT. As shown in FIG. 1, the exhaust heat recovery boiler 10A is connected to an exhaust pipe G1 through which the exhaust gas discharged from the gas turbine GT flows. Then, the exhaust gas discharged from the gas turbine GT is introduced into the exhaust heat recovery boiler 10A.

As shown in FIG. 1, the exhaust heat recovery boiler 10A includes a superheater 20, an evaporator 30, and a preheater 40 in order from the upstream side in the flow direction of the exhaust gas introduced into the exhaust heat recovery boiler 10A.

The superheater 20 is arranged on the most upstream side in the flow direction of the exhaust gas. The superheater 20 includes a heat exchange unit 21, a main body body 22, an introduction unit 23, and a discharge unit 24.

The heat exchange unit 21 is composed of, for example, a multi-tube heat exchanger including a plurality of heat transfer tubes. The heat exchange unit 21 uses saturated steam flowing through the heat exchange unit 21 as superheated steam due to the amount of heat of the exhaust gas introduced into the main body 22. The heat exchange unit 21 functions as a first heat exchange unit.

The main body 22 houses the heat exchange unit 21. The main body 22 is composed of, for example, a cylinder whose both ends are closed. The heat exchange unit 21 is housed in this cylinder. The main body 22 also has a function as a pressure vessel. The main body 22 functions as a first main body.

The introduction unit 23 introduces the exhaust gas exhausted from the gas turbine into the main body 22. As shown in FIG. 1, the introduction unit 23 is connected to the exhaust pipe G1 of the gas turbine GT. That is, the introduction portion 23 of the superheater 20 is the inlet of the exhaust heat recovery boiler 10A. The introduction portion 23 is provided, for example, on the side wall of the main body body 22. The introduction unit 23 functions as a first introduction unit.

Here, since the superheater 20 is arranged on the most upstream side in the flow direction of the exhaust gas, the temperature and pressure of the exhaust gas introduced into the superheater 20 is the temperature of the exhaust gas introduced into the evaporator 30 and the preheater 40. And higher than pressure. That is, the hottest and highest pressure exhaust gas in the exhaust heat recovery boiler 10A is introduced into the main body 22 of the superheater 20. For example, exhaust gas having a pressure higher than the atmospheric pressure can be introduced into the main body 22.

The discharge unit 24 discharges the exhaust gas introduced into the main body body 22 and heat-exchanged in the heat exchange unit 21 from the main body body 22. The discharge unit 24 is provided on the opposite side of the introduction unit 23 via the heat exchange unit 21, for example. As a result, the exhaust gas introduced into the main body 22 from the introduction unit 23 flows through the heat exchange unit 21, is sufficiently heat exchanged by the heat exchange unit 21, and then discharged from the discharge unit 24. The discharge unit 24 functions as a first discharge unit.

The evaporator 30 is arranged on the downstream side of the superheater 20 in the flow direction of the exhaust gas. The evaporator 30 includes a heat exchange unit 31, a main body body 32, an introduction unit 33, and a discharge unit 34.

The heat exchange unit 31 is composed of, for example, a multi-tube heat exchanger provided with a plurality of heat transfer tubes. The heat exchange unit 31 uses the heated water flowing through the heat exchange unit 31 as saturated steam according to the amount of heat of the exhaust gas introduced into the main body 32. The heat exchange unit 31 functions as a second heat exchange unit.

The main body 32 houses the heat exchange unit 31. The main body 32 is composed of, for example, a cylinder whose both ends are closed. The heat exchange unit 31 is housed in the cylinder. The main body 32 also has a function as a pressure vessel. The main body 32 functions as a second main body.

The introduction unit 33 introduces the exhaust gas discharged from the discharge unit 24 of the superheater 20 into the main body 32. The introduction portion 33 is provided on the side wall of the main body 32, for example. Further, the introduction portion 33 is connected to the discharge portion 24 of the superheater 20 via the pipe 50. The introduction unit 33 functions as a second introduction unit.

The discharge unit 34 discharges the exhaust gas introduced into the main body 32 and heat-exchanged in the heat exchange unit 31 from the main body 32. The discharge unit 34 is provided on the opposite side of the introduction unit 33 via the heat exchange unit 31, for example. As a result, the exhaust gas introduced from the introduction unit 33 into the main body 32 flows through the heat exchange unit 31, is sufficiently heat exchanged by the heat exchange unit 31, and then discharged from the discharge unit 34. The discharge unit 34 functions as a second discharge unit.

The preheater 40 is arranged on the downstream side of the evaporator 30 in the flow direction of the exhaust gas. That is, the preheater 40 is arranged on the most downstream side in the flow direction of the exhaust gas. Therefore, the temperature and pressure of the exhaust gas introduced into the preheater 40 is lower than the temperature and pressure of the exhaust gas introduced into the superheater 20 and the evaporator 30.

The preheater 40 includes a heat exchange unit 41, a main body body 42, an introduction unit 43, and a discharge unit 44.

The heat exchange unit 41 is composed of, for example, a multi-tube heat exchanger including a plurality of heat transfer tubes. The heat exchange unit 41 uses the water flowing through the heat exchange unit 41 as heated water according to the amount of heat of the exhaust gas introduced into the main body body 42. The temperature of the heated water is, for example, lower than the saturation temperature under the pressure of the heated water, but close to the saturation temperature. The heat exchange unit 41 functions as a third heat exchange unit.

The main body 42 houses the heat exchange unit 41. The main body 42 is composed of, for example, a cylinder whose both ends are closed. The heat exchange unit 41 is housed in the cylinder. The main body 42 also has a function as a pressure vessel. The main body 42 functions as a third main body.

The introduction unit 43 introduces the exhaust gas discharged from the discharge unit 34 of the evaporator 30 into the main body body 42. The introduction portion 43 is provided, for example, on the side wall of the main body body 42. Further, the introduction portion 43 is connected to the discharge portion 34 of the evaporator 30 via the pipe 51. The introduction unit 43 functions as a third introduction unit.

The discharge unit 44 discharges the exhaust gas introduced into the main body body 42 and heat-exchanged in the heat exchange unit 41 from the inside of the main body body 42. The discharge unit 44 is provided on the opposite side of the introduction unit 43 via the heat exchange unit 41, for example. As a result, the exhaust gas introduced from the introduction unit 43 into the main body body 42 flows through the heat exchange unit 41, is sufficiently heat exchanged by the heat exchange unit 41, and then discharged from the discharge unit 44. The discharge unit 44 functions as a third discharge unit.

As described above, the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body 42 of the preheater 40 are respectively configured as separate bodies. The superheater 20 and the evaporator 30 are connected by a pipe 50. The evaporator 30 and the preheater 40 are connected by a pipe 51.

At least one introduction unit 23, 33, 43 and an discharge unit 24, 34, 44 of the superheater 20, the evaporator 30, and the preheater 40 are provided. FIG. 1 shows an example in which two introduction units 23, 33, 43 and discharge units 24, 34, 44 are provided, but the introduction units 23, 33, 43 and the discharge units 24, 34, 44 are 3. One or more may be provided.

Further, an inlet pipe 60 for introducing water into the heat exchange section 41 is connected to the inlet 41a of the heat exchange section 41 of the preheater 40. The inlet pipe 60 penetrates the main body 42 and is connected to the inlet 41a of the heat exchange unit 41. The water introduced from the inlet pipe 60 flows into, for example, a plurality of heat transfer pipes constituting the heat exchange unit 41.

Here, when the exhaust heat recovery boiler 10A is used in a combined cycle power plant equipped with a gas turbine and a steam turbine, the inlet pipe 60 guides the condensate condensed water in the condenser to the exhaust heat recovery boiler 10A. It is connected to the water return pipe.

The outlet 41b of the heat exchange section 41 of the preheater 40 and the inlet 31a of the heat exchange section 31 of the evaporator 30 are connected by a heated water pipe 61. One end of the heated water pipe 61 penetrates the main body 42 and is connected to the outlet 41b of the heat exchange unit 41, and the other end of the heated water pipe 61 penetrates the main body 32 and is connected to the inlet 31a of the heat exchange unit 31. ing.

As shown in FIG. 1, the inlet 31a of the heat exchange section 31 of the evaporator 30 is provided, for example, at the bottom of the heat exchange section 31. As shown in FIG. 1, the outlet 31b of the heat exchange unit 31 of the evaporator 30 is provided, for example, on the upper part of the heat exchange unit 31. With this configuration, the saturated steam generated in the heat exchange unit 31 can be smoothly discharged from the heat exchange unit 31.

The outlet 31b of the heat exchange section 31 of the evaporator 30 and the inlet 21a of the heat exchange section 21 of the superheater 20 are connected by a saturated steam pipe 62. One end of the saturated steam pipe 62 penetrates the main body 32 and is connected to the outlet 31b of the heat exchange unit 31, and the other end of the saturated steam pipe 62 penetrates the main body 22 and reaches the inlet 21a of the heat exchange unit 21. It is connected.

An outlet pipe 63 for discharging superheated steam to the outside is connected to the outlet 21b of the heat exchange unit 21 of the superheater 20. The outlet pipe 63 penetrates the main body 22 and is connected to the outlet 21b of the heat exchange unit 21.

Here, when the exhaust heat recovery boiler 10A is used in a combined cycle power plant equipped with a gas turbine and a steam turbine, the outlet pipe 63 is connected to a main steam pipe that introduces superheated steam into the high-pressure turbine.

Next, the operation of the exhaust heat recovery boiler 10A will be described.

First, the operation of the water system will be described.

The low-temperature water introduced from the inlet pipe 60 is introduced into the heat exchange section 41 of the preheater 40. The water introduced into the heat exchange unit 41 is heated by the exhaust gas introduced into the main body 42 of the preheater 40 to become heated water.

The heated water is introduced from the heat exchange unit 41 through the heated water pipe 61 to the heat exchange unit 31 of the evaporator 30. The heated water introduced into the heat exchange unit 31 is heated by the exhaust gas introduced into the main body 32 of the evaporator 30 to become saturated steam.

The saturated steam passes from the heat exchange unit 31 through the saturated steam pipe 62 and is introduced into the heat exchange unit 21 of the superheater 20. The saturated steam introduced into the heat exchange unit 21 is heated by the exhaust gas introduced into the main body 22 of the superheater 20 and becomes superheated steam.

The superheated steam passes from the heat exchange unit 21 through the outlet pipe 63 and is guided to, for example, the main steam pipe of the steam turbine.

Next, the operation of the exhaust gas system will be described.

The exhaust gas discharged from the gas turbine and introduced into the main body 22 of the superheater 20 from the introduction unit 23 spreads in the main body 22 and is guided to the heat exchange unit 21. The amount of heat of the exhaust gas is taken away in order to generate superheated steam in the heat exchange unit 21. Then, the exhaust gas whose temperature has dropped is introduced into the main body 32 of the evaporator 30 from the discharge unit 24 through the pipe 50 and the introduction unit 33.

The exhaust gas introduced into the main body 32 spreads inside the main body 32 and is guided to the heat exchange unit 31. The amount of heat of the exhaust gas is further deprived in order to generate saturated steam in the heat exchange unit 31. Then, the exhaust gas whose temperature has dropped is introduced into the main body 42 of the preheater 40 from the discharge unit 34 through the pipe 51 and the introduction unit 43.

The exhaust gas introduced into the main body 42 spreads inside the main body 42 and is guided to the heat exchange unit 41. The amount of heat of the exhaust gas is further deprived in order to heat the water in the heat exchange unit 41. Then, the exhaust gas whose temperature has dropped is discharged to the outside from the discharge unit 44.

Here, the temperature of the fluid flowing through the water system rises as it advances in the flow direction. On the other hand, the temperature of the exhaust gas flowing through the exhaust gas system decreases as it advances in the flow direction. Further, the pressure of the exhaust gas flowing through the exhaust gas system also decreases as it advances in the flow direction, like the temperature.

As described above, according to the exhaust heat recovery boiler 10A of the first embodiment, the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body 42 of the preheater 40 are separately configured. can do. In other words, each of the heat exchange units 21, 31, and 41 can be divided and stored in three containers of the preheater 40, the evaporator 30, and the superheater 20 according to the change of state of the fluid flowing through the water system.

Here, as described above, the temperatures and pressures of the exhaust gas introduced into the superheater 20, the evaporator 30, and the preheater 40 are different from each other.

By configuring the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body 42 of the preheater 40 as separate bodies, materials can be selected and designed according to the temperature and pressure of the exhaust gas to be introduced. Etc. can be performed for each of the main body bodies 22, 32, and 42.

That is, in the exhaust heat recovery boiler 10A, it is possible to appropriately design each of the main body bodies 22, 32, and 42 as compared with the conventional exhaust heat recovery boiler having a superheater, an evaporator, and a preheater in one duct. ..

For example, when a superheater, an evaporator and a preheater are provided in one duct as in a conventional exhaust heat recovery boiler, the duct is selected and designed according to the exhaust gas conditions at the highest temperature and high pressure. .. Therefore, the specifications are more than necessary for the exhaust gas conditions on the downstream side in the flow direction of the exhaust gas, and the manufacturing cost also increases.

On the other hand, in the exhaust heat recovery boiler 10A, each of the main body bodies 22, 32, and 42 that function as pressure vessels can be individually designed according to the exhaust gas conditions. That is, it is possible to limit the range of the expensive high temperature heat resistant member. As a result, an appropriate design can be made and the manufacturing cost can be reduced.

Further, even when the pressure or temperature of the exhaust gas at the inlet of the exhaust heat recovery boiler 10A is higher than the pressure or temperature of the exhaust gas introduced into the conventional exhaust heat recovery boiler, the main body bodies 22, 32, and 42 are respectively. Since it can be designed individually, it is possible to make an optimum design according to the exhaust gas conditions.

Thereby, it is possible to provide the exhaust heat recovery boiler 10A having excellent safety from the viewpoint of pressure resistance and heat resistance.

As a case where the pressure and temperature of the exhaust gas are higher than the pressure and temperature of the exhaust gas introduced in the conventional exhaust heat recovery boiler, for example, the exhaust gas discharged from the hydrogen combustion gas turbine is introduced into the exhaust heat recovery boiler 10A. There are cases where it is done.

Further, in the exhaust heat recovery boiler 10A, the conditions of the exhaust gas to be introduced can be divided into three stages, so that it becomes easy to deal with thermal deformation and thermal stress of each component. By dividing the conditions of the exhaust gas to be introduced into three stages, even if the physical properties of the fluid flowing through the water system are different for each of the liquid, phase change, and gas, the heat exchange units 21, 31, and 41 are according to the respective states. Optimal design is possible.

Here, in the above-described embodiment, an example is shown in which one superheater 20, an evaporator 30, and a preheater 40 are provided, but the present invention is not limited to this configuration.

A plurality of at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in series. For example, when two preheaters 40 are provided in series, the low-temperature water introduced from the inlet pipe 60 is heated by the first-stage preheater 40, and the water heated by the first-stage preheater 40 is generated. It is introduced into the heat exchange unit 41 of the second stage preheater 40. Then, the heated water discharged from the heat exchange unit 41 of the second-stage preheater 40 has a temperature close to the saturation temperature as described above. Even when a plurality of superheaters 20 and evaporators 30 are provided in series, the same configuration is used.

For example, when a plurality of preheaters 40 are provided in series, the amount of heat of the exhaust gas introduced into the preheater 40 can be sufficiently transferred to the water flowing through the heat exchange unit 41. The same effect can be obtained even when a plurality of superheaters 20 and evaporators 30 are provided in series.

Further, at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in parallel. For example, when a plurality of preheaters 40 are provided in parallel, the amount of water introduced into the preheater 40 increases, and the flow rate of superheated steam discharged from the superheater 20 increases.

When a plurality of evaporators 30 are provided in parallel, it is possible to operate another evaporator 30 while maintaining one evaporator 30. As a result, maintenance of the exhaust heat recovery boiler 10A can be performed without stopping the operation of the power plant provided with the exhaust heat recovery boiler 10A.

Further, by providing a plurality of evaporators 30 in parallel, the range of the flow rate of saturated steam that can be generated in the evaporator 30 can be increased. This makes it possible to generate saturated steam with an optimum flow rate according to the output of the power plant.

Even when a plurality of superheaters 20 are provided in parallel, the same effect as when a plurality of evaporators 30 are provided in parallel can be obtained.

Further, the evaporator 30 is not limited to the configuration in which the exhaust gas is introduced into the main body 32 and the heated water is introduced into the heat exchange unit 31.

The evaporator 30 may be provided with, for example, a kettle-type heat exchange unit. Specifically, the evaporator 30 is housed in a main body body for storing the heated water introduced from the preheater 40 via the heated water pipe 61 and in the main body body so as to be located in the heated water, and exhaust gas is introduced. It is equipped with a heat exchange unit.

In this case, the heated water is heated by the exhaust gas flowing in the heat exchange section and becomes saturated steam. Then, the saturated steam generated in the main body body is discharged from the outlet provided in the upper part of the main body body, and is introduced into the heat exchange unit 21 of the superheater 20 via the saturated steam pipe 62.

Even when such a kettle-type heat exchange unit is provided, the main body of the evaporator 30 is composed of a separate body from the main body 22 and 42 of the superheater 20 and the preheater 40. Therefore, the same effect as that of the exhaust heat recovery boiler 10A shown in FIG. 1 can be obtained.

(Second embodiment)
FIG. 2 is a schematic diagram of the configuration of the exhaust heat recovery boiler 10B of the second embodiment. FIG. 2 is a side view of the exhaust heat recovery boiler 10B, and shows an outline of the internal configurations of the superheater 20, the evaporator 30, the preheater 40, and the steam drum 70.

In the following embodiments, the same components as those of the exhaust heat recovery boiler 10A of the first embodiment are designated by the same reference numerals, and duplicated description will be omitted or simplified.

In the exhaust heat recovery boiler 10B of the second embodiment, the configuration including the steam drum 70 is different from the configuration of the exhaust heat recovery boiler 10A of the first embodiment. Therefore, here, this different configuration will be mainly described.

As shown in FIG. 2, the exhaust heat recovery boiler 10B includes a steam drum 70 interposed in the heated water pipe 61 and the saturated steam pipe 62.

The steam drum 70 is installed in the evaporator 30. In the steam drum 70, heated water is stored up to a predetermined water level.

The heating water pipe 61 includes a first heating water pipe 61A and a second heating water pipe 61B. The first heated water pipe 61A is arranged between the outlet 41b of the heat exchange portion 41 of the preheater 40 and the steam drum 70. The second heated water pipe 61B is arranged between the bottom of the steam drum 70 and the inlet 31a of the heat exchange portion 31 of the evaporator 30. The second heated water pipe 61B has a function as a precipitation pipe that lowers the heated water from the bottom of the steam drum 70 and guides it to the inlet 31a provided at the bottom of the heat exchange unit 31.

Here, the second heated water pipe 61B may be provided with a pump for pumping the heated water stored in the steam drum 70 to the inlet 31a of the heat exchange unit 31.

The saturated steam pipe 62 includes a first saturated steam pipe 62A and a second saturated steam pipe 62B. The first saturated steam pipe 62A is arranged between the outlet 31b of the heat exchange portion 31 of the evaporator 30 and the bottom of the steam drum 70 in which the heated water is stored. The first saturated steam pipe 62A has a function as a steam return pipe for returning the saturated steam generated in the heat exchange unit 31 into the steam drum 70. The second saturated steam pipe 62B is arranged between the upper outlet of the steam drum 70 and the inlet 21a of the heat exchange portion 21 of the superheater 20.

Next, the operation of the exhaust heat recovery boiler 10B will be described.

The heated water heated by the heat exchange unit 41 of the preheater 40 is introduced from the heat exchange unit 41 into the steam drum 70 through the first heated water pipe 61A.

The heated water introduced into the steam drum 70 passes through the second heated water pipe 61B and is introduced into the heat exchange section 31 of the evaporator 30. The heated water introduced into the heat exchange unit 31 is heated by the exhaust gas introduced into the main body 32 of the evaporator 30 to become saturated steam.

The saturated steam is introduced into the steam drum 70 from the heat exchange unit 31 through the first saturated steam pipe 62A. The saturated steam introduced into the steam drum 70 is introduced into the heated water stored in the steam drum 70 to be gas-liquid separated.

The saturated steam separated from the liquid by the gas-liquid separation is introduced into the heat exchange section 21 of the superheater 20 from the outlet of the steam drum 70 through the second saturated steam pipe 62B.

On the other hand, the water separated by gas and liquid by the steam drum 70 passes through the second heated water pipe 61B again and is introduced into the heat exchange section 31 of the evaporator 30.

The action of the other exhaust heat recovery boiler 10B is as described in the action of the exhaust heat recovery boiler 10A of the first embodiment.

According to the exhaust heat recovery boiler 10B of the second embodiment, by providing the steam drum 70, the saturated steam generated in the evaporator 30 can be gas-liquid separated and introduced into the superheater 20. In the exhaust heat recovery boiler 10B as well, the effect of forming the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body 42 of the preheater 40 as separate bodies is the first implementation. It is the same as the action and effect in the exhaust heat recovery boiler 10A in the form of.

Further, also in the exhaust heat recovery boiler 10B of the second embodiment, at least one of the superheater 20, the evaporator 30, and the preheater 40 is used in the same manner as in the exhaust heat recovery boiler 10A of the first embodiment. A plurality of them may be arranged in series. Further, at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in parallel.

Here, FIG. 3 is a schematic view of the exhaust heat recovery boiler 10B of the second embodiment when the evaporator 30 when three evaporators 30 are provided in parallel is viewed from the superheater 20 side. ..

As shown in FIG. 3, a second heated water pipe 61B is connected to an inlet 31a provided at the bottom of the heat exchange portion 31 of each evaporator 30. Further, a first saturated steam pipe 62A is connected between the outlet 31b of the heat exchange unit 31 of each evaporator 30 and the steam drum 70.

The saturated steam generated in the heat exchange unit 31 passes through each of the first saturated steam pipes 62A and is introduced into the steam drum 70. Here, each heat exchange unit 31 is connected to one steam drum 70 via a first saturated steam pipe 62A.

When a plurality of evaporators 30 are provided in parallel in this way, it is possible to operate another evaporator 30 while maintaining one evaporator 30. This sets, for example, in the case of providing three evaporators 30, the flow rate of saturated steam that can be produced by one evaporator 30 is set to 50, where the flow rate of saturated steam generated by the entire evaporator 30 is 100. It can be realized by. As a result, maintenance of the exhaust heat recovery boiler 10B can be performed without stopping the operation of the power plant provided with the exhaust heat recovery boiler 10B.

Further, by providing a plurality of evaporators 30 in parallel, the range of the flow rate of saturated steam that can be generated in the evaporator 30 can be increased. This makes it possible to generate saturated steam with an optimum flow rate according to the output of the power plant.

(Third embodiment)
FIG. 4 is a schematic diagram of the configuration of the exhaust heat recovery boiler 10C according to the third embodiment. FIG. 4 is a side view of the exhaust heat recovery boiler 10C, and shows an outline of the internal configurations of the superheater 20, the evaporator 30, the preheater 40, and the outer body 91.

In the exhaust heat recovery boiler 10C of the third embodiment, the configuration including the cooling mechanism 90 for cooling the main body 22 of the superheater 20 is different from the configuration of the exhaust heat recovery boiler 10A of the first embodiment. Therefore, here, this different configuration will be mainly described.

As shown in FIG. 4, the exhaust heat recovery boiler 10C includes a cooling mechanism 90 for cooling the main body 22 of the superheater 20.

As shown in FIG. 4, the cooling mechanism 90 includes an outer body 91, a cooling introduction pipe 92, and an exhaust gas introduction pipe 93.

The outer body 91 houses the main body 22 of the superheater 20. The outer body 91 is composed of, for example, a cylinder whose both ends are closed. The main body 22 is housed in this cylinder. Here, the outer body 91 arranged at the boundary with the outside air also has a function as a pressure vessel. In this case, the main body 22 does not need to function as a pressure vessel.

The cooling introduction pipe 92 introduces a part of the exhaust gas introduced into the main body 32 of the evaporator 30 and exchanged heat in the heat exchange unit 31 into the space between the outer body 91 and the main body 22. As shown in FIG. 4, one end of the cooling introduction pipe 92 is connected to the discharge portion 34 of the evaporator 30, and the other end of the cooling introduction pipe 92 is connected to the outer body 91.

The exhaust gas introduction pipe 93 introduces the exhaust gas introduced into the space between the outer cylinder 91 and the main body 22 and cooling the main body 22 into the main body 42 of the preheater 40. One end of the exhaust gas introduction pipe 93 is connected to the outer body 91, and the other end of the exhaust gas introduction pipe 93 is connected to, for example, the introduction portion 43 of the preheater 40.

Here, the connection portion of the exhaust gas introduction pipe 93 with the outer cylinder 91 is located at the position farthest from the connection portion of the cooling introduction pipe 92 with the outer cylinder 91 via the main body cylinder 22, for example, as shown in FIG. It is preferable that it is provided in. That is, the exhaust gas introduced from the cooling introduction pipe 92 into the space between the outer cylinder 91 and the main body 22 flows along the periphery of the main body 22, and after sufficiently cooling the main body 22, the exhaust gas introduction pipe 93 It is preferable to have a configuration that flows into.

Next, the operation of the cooling mechanism 90 will be described.

A part of the exhaust gas introduced into the main body 32 of the evaporator 30 and exchanged heat in the heat exchange unit 31 passes through the cooling introduction pipe 92 and is introduced into the space between the outer body 91 and the main body 22. .. The exhaust gas introduced into the space between the outer body 91 and the main body 22 flows around the main body 22 to cool the main body 22. The temperature of the exhaust gas introduced into the space between the outer body 91 and the main body 22 is lower than the temperature of the main body 22.

The exhaust gas that has cooled the main body 22 passes through the exhaust gas introduction pipe 93 and is introduced into the main body 42 of the preheater 40. The temperature of the exhaust gas that has cooled the main body 22 rises by obtaining heat from the main body 22.

The exhaust gas introduced into the main body 42 of the preheater 40 spreads in the main body 42 together with the exhaust gas introduced into the main body 42 of the preheater 40 from the pipe 51, and is guided to the heat exchange unit 41. Then, the exhaust gas obtained by heating the water in the heat exchange unit 41 is discharged to the outside from the discharge unit 44.

As described above, according to the exhaust heat recovery boiler 10C of the third embodiment, the main body 22 of the superheater 20 that becomes hot can be cooled by providing the cooling mechanism 90. Further, the design temperature of the outer cylinder 91 that functions as a pressure vessel by introducing the exhaust gas as a cooling medium between the outer cylinder 91 and the main body 22 functions as a pressure vessel in the above-mentioned conventional exhaust heat recovery boiler. It can be lower than the design temperature of the duct.

Further, although the main body 22 of the superheater 20 becomes hot, it is not necessary to secure the strength as a pressure vessel by providing the outer body 91. Therefore, the wall thickness of the main body 22 can be made thin. Further, even in a high temperature environment, the main body 22 is configured without using an expensive material having a high allowable stress.

Further, the exhaust gas obtained by cooling the main body 22 is introduced into the preheater 40, and the heat amount of the exhaust gas is effectively used. That is, the amount of heat obtained by cooling the main body 22 is effectively used in the heat exchange unit 41 of the preheater 40.

In the exhaust heat recovery boiler 10C of the third embodiment, at least one of the superheater 20, the evaporator 30, and the preheater 40 is used in the same manner as in the exhaust heat recovery boiler 10A of the first embodiment. A plurality of them may be arranged in series. Further, at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in parallel.

(Fourth Embodiment)
FIG. 5 is a schematic diagram of the configuration of the exhaust heat recovery boiler 10D according to the fourth embodiment. FIG. 5 is a side view of the exhaust heat recovery boiler 10D, and shows an outline of the internal configurations of the superheater 20, the evaporator 30, the preheater 40, and the outer cylinders 91 and 101.

In the exhaust heat recovery boiler 10D of the fourth embodiment, the configuration including the cooling mechanism 100 for cooling the main body 22 of the superheater 20 and the main body 32 of the evaporator 30 is the exhaust heat recovery of the first embodiment. It is different from the configuration of the boiler 10A. Further, the cooling mechanism 100 in the fourth embodiment is provided with a configuration for further cooling the main body 32 of the evaporator 30 in addition to the cooling mechanism 90 in the third embodiment. In FIG. 5, the same components as those of the cooling mechanism 90 in the third embodiment are designated by the same reference numerals, and duplicate description will be omitted or simplified.

Here, the configuration of the cooling mechanism 100 will be mainly described.

As shown in FIG. 5, the exhaust heat recovery boiler 10D includes a cooling mechanism 100 for cooling the main body 22 of the superheater 20 and the main body 32 of the evaporator 30.

As shown in FIG. 5, the cooling mechanism 100 includes an outer cylinder 101, a cooling discharge unit 102, an outer cylinder 91, a cooling introduction pipe 92A, and an exhaust gas introduction pipe 93.

The outer cylinder 101 houses the main body 32 of the evaporator 30. The outer body 101 is composed of, for example, a cylinder whose both ends are closed. The main body 32 is housed in this cylinder. Here, the outer cylinder 101 arranged at the boundary with the outside air also has a function as a pressure vessel. In this case, the main body 32 does not need to function as a pressure vessel.

The cooling discharge unit 102 discharges a part of the exhaust gas introduced into the main body 32 and exchanged heat in the heat exchange unit 31 into the space between the outer body 101 and the main body 32. The cooling discharge unit 102 includes a discharge hole 102A that communicates the inside of the main body 32 with the space between the outer body 101 and the main body 32.

The outer body 91 houses the main body 22 of the superheater 20. The configuration of the outer body 91 is as described in the third embodiment.

The cooling introduction pipe 92A is introduced into the space between the outer cylinder 101 and the main body 32, and the exhaust gas that has cooled the main body 32 is introduced into the space between the outer cylinder 91 and the main body 22. As shown in FIG. 5, one end of the cooling introduction pipe 92A is connected to the outer body 101, and the other end of the cooling introduction pipe 92A is connected to the outer body 91.

Here, it is preferable that the connecting portion of the cooling introduction pipe 92A with the outer cylinder 101 is provided at the position farthest from the cooling discharge portion 102 via the main body cylinder 32, for example, as shown in FIG. That is, the exhaust gas introduced from the cooling discharge unit 102 into the space between the outer cylinder 101 and the main body 32 flows along the periphery of the main body 32, and after sufficiently cooling the main body 32, the cooling introduction pipe is used. It is preferable to have a configuration that flows into 92A.

The exhaust gas introduction pipe 93 introduces the exhaust gas introduced into the space between the outer cylinder 91 and the main body 22 and cooling the main body 22 into the main body 42 of the preheater 40. The configuration of the exhaust gas introduction pipe 93 is as described in the third embodiment.

Next, the operation of the cooling mechanism 100 will be described.

A part of the exhaust gas introduced into the main body 32 of the evaporator 30 and exchanged heat in the heat exchange unit 31 is discharged from the discharge hole 102A of the cooling discharge unit 102 into the space between the outer body 101 and the main body 32. Will be done.

The remaining portion of the exhaust gas heat-exchanged in the heat exchange unit 31 passes through the pipe 51 and is introduced into the main body 42 of the preheater 40.

The exhaust gas discharged into the space between the outer body 101 and the main body 32 flows around the main body 32 to cool the main body 32. The temperature of the exhaust gas introduced into the space between the outer cylinder 101 and the main body 32 is lower than the temperature of the main body 32.

The exhaust gas that has cooled the main body 32 passes through the cooling introduction pipe 92A and is introduced into the space between the outer body 91 and the main body 22. The exhaust gas introduced into the space between the outer body 91 and the main body 22 flows around the main body 22 to cool the main body 22. The temperature of the exhaust gas introduced into the space between the outer body 91 and the main body 22 is lower than the temperature of the main body 22.

The exhaust gas that has cooled the main body 22 passes through the exhaust gas introduction pipe 93 and is introduced into the main body 42 of the preheater 40. Subsequent actions are as described in the third embodiment.

As described above, according to the exhaust heat recovery boiler 10D of the fourth embodiment, the main body 22 of the superheater 20 and the main body 32 of the evaporator 30, which become hot by providing the cooling mechanism 100, are cooled. can do.

Further, in the superheater 20 having the highest temperature in the exhaust heat recovery boiler 10D, the effect obtained by introducing the exhaust gas as a cooling medium between the outer cylinder 91 and the main body 22 is obtained in the third embodiment. As explained.

Further, although the main body 32 of the evaporator 30 becomes hot, it is not necessary to secure the strength as a pressure vessel by providing the outer body 101. Therefore, the wall thickness of the main body 32 can be made thin. Further, even in a high temperature environment, the main body 32 is configured without using an expensive material having a high allowable stress.

Further, the exhaust gas obtained by cooling the main body 22 and the main body 32 is introduced into the preheater 40, and the heat contained in the exhaust gas is effectively used. That is, the amount of heat obtained by cooling the main body 22 and the main body 32 is effectively used in the heat exchange unit 41 of the preheater 40.

In the exhaust heat recovery boiler 10D of the fourth embodiment, at least one of the superheater 20, the evaporator 30, and the preheater 40 is used in the same manner as in the exhaust heat recovery boiler 10A of the first embodiment. A plurality of them may be arranged in series. Further, at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in parallel.

(Fifth Embodiment)
FIG. 6 is a schematic diagram of the configuration of the exhaust heat recovery boiler 10E according to the fifth embodiment. FIG. 6 is a side view of the exhaust heat recovery boiler 10E, and outlines the internal configurations of the superheater 20, the evaporator 30, the preheater 40, and the outer cylinders 91, 101, and 111.

In the exhaust heat recovery boiler 10E of the fifth embodiment, the configuration including the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the cooling mechanism 110 for cooling the main body 42 of the preheater 40 is the first. It is different from the configuration of the exhaust heat recovery boiler 10A of the embodiment.

Further, the cooling mechanism 110 in the fifth embodiment cools the main body 42 of the preheater 40 in a configuration in which the cooling discharge portion 102 and the exhaust gas introduction pipe 93 of the cooling mechanism 100 in the fourth embodiment are removed. It is equipped with a configuration to be used. In FIG. 6, the same components as those of the cooling mechanism 100 in the fourth embodiment are designated by the same reference numerals, and duplicate description will be omitted or simplified.

Here, the configuration of the cooling mechanism 110 will be mainly described.

As shown in FIG. 6, the exhaust heat recovery boiler 10E includes a cooling mechanism 110 for cooling the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body 42 of the preheater 40.

As shown in FIG. 6, the cooling mechanism 110 includes an outer cylinder 111, a cooling discharge unit 112, an outer cylinder 101, a cooling introduction pipe 92B, an outer cylinder 91, a cooling introduction pipe 92A, and cooling. A discharge unit 113 is provided.

The outer body 111 houses the main body 42 of the preheater 40. The outer body 111 is composed of, for example, a cylinder whose both ends are closed. The main body body 42 is housed in this cylinder. Here, the outer cylinder 111 arranged at the boundary with the outside air also has a function as a pressure vessel. In this case, the main body 42 does not need to function as a pressure vessel.

The cooling discharge unit 112 discharges the exhaust gas introduced into the main body body 42 and heat-exchanged in the heat exchange unit 41 into the space between the outer body body 111 and the main body body 42. The cooling discharge unit 112 includes a discharge hole 112A that communicates the inside of the main body 42 with the space between the outer body 111 and the main body 42. The cooling discharge unit 112 functions as a first cooling discharge unit.

Here, an example is shown in which the entire amount of the exhaust gas heat-exchanged in the heat exchange unit 41 is discharged to the space between the outer cylinder 111 and the main body 42, but the configuration is not limited to this. For example, a part of the exhaust gas exchanged by the heat exchange unit 41 may be discharged to the space between the outer body 111 and the main body body 42, and the remaining part of the exhaust gas may be discharged to the outside of the outer body 111.

The outer cylinder 101 houses the main body 32 of the evaporator 30. The configuration of the outer body 101 is as described in the fourth embodiment.

The cooling introduction pipe 92B is introduced into the space between the outer cylinder 111 and the main body 42, and the exhaust gas that has cooled the main body 42 is introduced into the space between the outer cylinder 101 and the main body 32. As shown in FIG. 6, one end of the cooling introduction pipe 92B is connected to the outer cylinder 111, and the other end of the cooling introduction pipe 92B is connected to the outer cylinder 101. The cooling introduction pipe 92B functions as a first cooling introduction pipe.

Here, it is preferable that the connecting portion of the cooling introduction pipe 92B with the outer cylinder 111 is provided at the position farthest from the cooling discharge portion 112 via the main body cylinder 42, for example, as shown in FIG. That is, the exhaust gas introduced from the cooling discharge unit 112 into the space between the outer cylinder 111 and the main body 42 flows along the periphery of the main body 42, and after sufficiently cooling the main body 42, the cooling introduction pipe is used. It is preferable to have a configuration that flows into 92B.

The outer body 91 houses the main body 22 of the superheater 20. The configuration of the outer body 91 is as described in the third embodiment.

The cooling introduction pipe 92A is introduced into the space between the outer cylinder 101 and the main body 32, and the exhaust gas that has cooled the main body 32 is introduced into the space between the outer cylinder 91 and the main body 22. The cooling introduction pipe 92A is as described in the fourth embodiment. The cooling introduction pipe 92A functions as a second cooling introduction pipe.

The cooling discharge unit 113 is introduced into the space between the outer body 91 and the main body 22 and discharges the exhaust gas that has cooled the main body 22 to the outside. One end of the cooling discharge unit 113 is transferred to the outer body 91. The cooling discharge unit 113 functions as a second cooling discharge unit.

Here, the connecting portion of the cooling discharge portion 113 with the outer cylinder 91 is farthest from the connecting portion of the cooling introduction pipe 92A with the outer cylinder 91 via the main body cylinder 22, for example, as shown in FIG. It is preferably provided at a position. That is, the exhaust gas introduced from the cooling introduction pipe 92A into the space between the outer cylinder 91 and the main body 22 flows along the periphery of the main body 22, and after sufficiently cooling the main body 22, the cooling discharge unit It is preferable that the configuration is such that the exhaust is discharged from the 113 to the outside.

Next, the operation of the cooling mechanism 110 will be described.

The exhaust gas introduced into the main body 42 of the preheater 40 and heat-exchanged in the heat exchange unit 41 is discharged from the discharge hole 112A of the cooling discharge unit 112 into the space between the outer body 111 and the main body 42. At this time, for example, the entire amount of the exhaust gas heat-exchanged in the heat exchange unit 41 is discharged into the space between the outer body 111 and the main body 42.

The exhaust gas discharged into the space between the outer body 111 and the main body 42 flows around the main body 42 to cool the main body 42. The temperature of the exhaust gas introduced into the space between the outer cylinder 111 and the main body 42 is lower than the temperature of the main body 42.

The exhaust gas that has cooled the main body 42 passes through the cooling introduction pipe 92B and is introduced into the space between the outer body 101 and the main body 32. The exhaust gas introduced into the space between the outer body 101 and the main body 32 flows around the main body 32 to cool the main body 32. The temperature of the exhaust gas introduced into the space between the outer cylinder 101 and the main body 32 is lower than the temperature of the main body 32.

The exhaust gas that has cooled the main body 32 passes through the cooling introduction pipe 92A and is introduced into the space between the outer body 91 and the main body 22. The exhaust gas introduced into the space between the outer body 91 and the main body 22 flows around the main body 22 to cool the main body 22. The temperature of the exhaust gas introduced into the space between the outer body 91 and the main body 22 is lower than the temperature of the main body 22.

The exhaust gas that has cooled the main body 22 passes through the cooling discharge unit 113 and is discharged to the outside.

As described above, according to the exhaust heat recovery boiler 10E of the fifth embodiment, by providing the cooling mechanism 110, the main body 22 of the superheater 20, the main body 32 of the evaporator 30, and the main body of the preheater 40 are provided. The body 42 can be cooled.

Here, the effect of cooling the main body 22 of the superheater 20 and the main body 32 of the evaporator 30 is as described in the fourth embodiment.

Further, in the exhaust heat recovery boiler 10E, in the preheater 40, the main body 42 of the preheater 40 becomes hot, but by providing the outer body 111, it is not necessary to secure the strength as a pressure vessel. Therefore, the wall thickness of the main body body 42 can be made thin. Further, even in a high temperature environment, the main body body 42 is configured without using an expensive material having a high allowable stress.

Here, an example is shown in which the exhaust gas introduced into the space between the outer cylinder 91 and the main body 22 is discharged into the atmosphere from the cooling discharge unit 113 after cooling the main body 22. Not limited to.

For example, as in the fourth embodiment, the exhaust gas introduction pipe 93 may be provided and the exhaust gas obtained by cooling the main body 22 may be introduced into the main body 42 of the preheater 40. In this case, the exhaust gas introduction pipe 93 may be provided with a pump to pressurize the exhaust gas to a pressure that can be introduced into the main body 42.

When the exhaust gas obtained by cooling the main body 22 is introduced into the main body 42 of the preheater 40 in this way, the exhaust gas obtained by cooling the main body 42, the main body 32 and the main body 22 is the preheater. It is introduced into 40, and the amount of heat contained in the exhaust gas is effectively used. That is, the amount of heat obtained by cooling the main body 42, the main body 32, and the main body 22 is effectively used in the heat exchange unit 41 of the preheater 40.

In the exhaust heat recovery boiler 10E of the fifth embodiment, at least one of the superheater 20, the evaporator 30, and the preheater 40 is used in the same manner as in the exhaust heat recovery boiler 10A of the first embodiment. A plurality of them may be arranged in series. Further, at least one of the superheater 20, the evaporator 30, and the preheater 40 may be arranged in parallel.

The configurations of the cooling mechanisms 90, 100, and 110 in the third to fifth embodiments can also be applied to the exhaust heat recovery boiler 10B provided with the steam drum 70 of the second embodiment. When the exhaust heat recovery boiler 10B is provided with a cooling mechanism, it is possible to obtain the same effect as the action and effect of the exhaust heat recovery boilers 10C, 10D, and 10E according to the third to fifth embodiments.

According to the embodiment described above, the optimum design according to the exhaust gas conditions introduced into each of the superheater, the evaporator and the preheater becomes possible.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and variations thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

10A, 10B, 10C, 10D, 10E ... Exhaust heat recovery boiler, 20 ... Superheater, 21, 31, 41 ... Heat exchange unit, 21a, 31a, 41a ... Inlet, 21b, 31b, 41b ... Outlet, 22, 32, 42 ... Main body, 23, 33, 43 ... Introduction, 24, 34, 44 ... Discharge, 30 ... Evaporator, 40 ... Preheater, 50, 51 ... Piping, 60 ... Inlet piping, 61 ... Heating water pipe, 61A ... first heated water pipe, 61B ... second heated water pipe, 62 ... saturated steam pipe, 62A ... first saturated steam pipe, 62B ... second saturated steam pipe, 63 ... outlet pipe, 70 ... steam drum, 90 , 100, 110 ... Cooling mechanism, 91, 101, 111 ... Outer body, 92, 92A, 92B ... Cooling introduction pipe, 93 ... Exhaust exhaust gas introduction pipe, 102, 112, 113 ... Cooling discharge unit, 102A, 112A ... Discharge Hole, G1 ... Exhaust pipe, GT ... Gas turbine.

Claims (9)

An exhaust heat recovery boiler equipped with a superheater, an evaporator, and a preheater in order from the upstream side in the flow direction of the exhaust gas into which the exhaust gas from the gas turbine is introduced.
The superheater, the evaporator and the preheater are each
Heat exchange part and
It is equipped with a main body that houses the heat exchange unit.
Each of the main body bodies is a waste heat recovery boiler characterized in that it is composed of a separate body. The superheater is
The first heat exchange unit and
The first main body body for accommodating the first heat exchange unit,
A first introduction portion for introducing the exhaust gas into the first main body body,
The exhaust gas introduced into the first main body and heat-exchanged in the first heat exchange unit is provided with a first discharge unit that discharges the exhaust gas from the first main body.
The evaporator is
The second heat exchange unit and
A second main body that houses the second heat exchange unit,
A second introduction section for introducing the exhaust gas discharged from the first discharge section into the body of the second main body, and a second introduction section.
It is provided with a second exhaust unit which is introduced into the second main body and discharges the exhaust gas which has been heat-exchanged in the second heat exchange unit from the second main body.
The preheater
With the third heat exchange section,
A third main body that houses the third heat exchange unit,
A third introduction section for introducing the exhaust gas discharged from the second discharge section into the body of the third main body, and a third introduction section.
It is provided with a third exhaust unit which is introduced into the third main body and discharges the exhaust gas which has been heat-exchanged in the third heat exchange unit from the third main body.
The exhaust heat recovery boiler is
A heated water pipe connecting the outlet of the third heat exchange section and the inlet of the second heat exchange section,
The exhaust heat recovery boiler according to claim 1, further comprising a saturated steam pipe connecting the outlet of the second heat exchange section and the inlet of the first heat exchange section. The exhaust heat recovery boiler according to claim 2, wherein a steam drum is interposed in the heated water pipe and the saturated steam pipe. An outer body for accommodating the first main body of the superheater, and
A cooling introduction pipe that is introduced into the second main body and introduces a part of the exhaust gas that has been heat-exchanged in the second heat exchange section between the outer body and the first main body.
It is provided with an exhaust gas introduction pipe that is introduced between the outer cylinder and the first main body and that cools the first main body and introduces the exhaust gas into the third main body of the preheater. The exhaust heat recovery boiler according to claim 2 or 3, which is characterized by this. A first outer body for accommodating the first main body of the superheater, and
A second outer body for accommodating the second main body of the evaporator, and a second outer body,
Cooling discharge that is introduced into the second main body and discharges a part of the exhaust gas that has been heat-exchanged in the second heat exchange section between the second outer body and the second main body. Department and
The exhaust gas introduced between the second outer body and the second main body and cooling the second main body is introduced between the first outer body and the first main body. Introductory piping for cooling and
An exhaust gas introduction pipe that is introduced between the first outer cylinder and the first main body and that cools the first main body and introduces the exhaust gas into the third main body of the preheater. The exhaust heat recovery boiler according to claim 2 or 3, characterized in that it is provided. A first outer body for accommodating the first main body of the superheater, and
A second outer body for accommodating the second main body of the evaporator, and a second outer body,
A third outer body for accommodating the third main body of the preheater, and
A first unit that is introduced into the third main body and discharges a part of the exhaust gas that has been heat-exchanged in the third heat exchange section between the third outer body and the third main body. The exhaust gas introduced between the cooling discharge unit, the third outer body, and the third main body and cooling the third main body is used in the second outer body and the second main body. The first cooling introduction pipe to be introduced between
The exhaust gas introduced between the second outer body and the second main body and cooling the second main body is introduced between the first outer body and the first main body. The second cooling introduction pipe and
It is characterized by comprising a second cooling discharge unit which is introduced between the first outer cylinder and the first main body and discharges the exhaust gas which has cooled the first main body to the outside. The exhaust heat recovery boiler according to claim 2 or 3. The exhaust heat recovery boiler according to any one of claims 1 to 6, wherein the pressure of the exhaust gas introduced into the superheater is higher than the atmospheric pressure. The exhaust heat recovery boiler according to any one of claims 1 to 7, wherein at least one of the superheater, the evaporator, and the preheater is provided in series. The exhaust heat recovery boiler according to any one of claims 1 to 7, wherein at least one of the superheater, the evaporator, and the preheater is provided in parallel.

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