JPH09243002A - Exhaust heat recovery heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a temperature distribution and a velocity distribution of exhaust gases uniform and enhance a heat exchanging performance by arranging at least a heat exchanger tube except heat exchanger tubes of an evaporator in a different direction from that of the heat exchanger tubes of the evaporator in a horizontal type exhaust heat recovery heat exchanger. SOLUTION: A superheater 2 is provided in an exhaust heat recovery heat exchanger 1 in a flowing direction of exhaust gases G and is provided with superheater heat exchanger tubes 4. The heat exchanger tubes 4 are disposed in a horizontal direction and in a direction perpendicular to the flowing direction of exhaust gases G, and are arranged in multi-stage manner in a vertical direction. Provided downstream is an evaporator 7 provided with evaporator heat exchanger tubes 8, which are disposed in a vertical direction and in a direction perpendicular to the flow of the exhaust gases G and arranged in multi-stage manner in the flowing direction of the exhaust gases G. Further, a fuel economizer 11 is disposed downstream and is provided with fuel economizer heat exchanger tubes 13. In this manner, the superheater heat exchanger tubes 4 and the fuel economizer heat exchanger tubes 13 are disposed horizontally, and the evaporator heat exchanger tubes 8 disposed intermediate therebetween are arranged in a vertical direction.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an exhaust heat recovery heat exchanger, and more particularly to an exhaust heat recovery heat exchanger capable of improving heat transfer performance.

[0002]

2. Description of the Related Art Generally, a combined cycle power plant sends exhaust gas discharged from a gas turbine to an exhaust heat recovery heat exchanger (exhaust heat recovery boiler) to generate steam by using this exhaust gas as a heat source and generate the generated steam. The power is sent to a steam turbine to extract electric power. Therefore, the combined cycle power plant is characterized in that the exhaust heat of the gas turbine can be effectively used and the start / stop time can be greatly shortened.

FIG. 33 is a side view showing an example of a horizontal natural circulation type exhaust heat recovery heat exchanger which constitutes a part of a conventional combined cycle power generation plant. In FIG. 33, reference numeral 100 denotes an exhaust heat recovery heat exchanger body, and exhaust gas G from a gas turbine (not shown) is supplied to the inside of the exhaust heat recovery heat exchanger body 100 from the left side in the drawing. Inside the exhaust heat recovery heat exchanger 100, a superheater 101 is arranged at the most upstream part in the flow direction of the exhaust gas G. This superheater 1
Reference numeral 01 includes a superheater heat transfer tube 103 having U-shaped bend tubes 102, 102 installed vertically, and the superheater heat transfer tubes 103 are arranged in multiple stages in the horizontal direction.
The superheater inlet header 104 and the superheater outlet header 105 are provided at the inlet and the outlet of the superheater heat transfer tube 103, and the U-shaped bend pipes 102 and 102 are provided with superheater intermediate headers 106 and 106. ing.

A reheater 107 is arranged downstream of the superheater 101 in the flow direction of the exhaust gas G. The reheater 107 has U-shaped bend pipes 108, 108 and is installed in the vertical direction. The reheater heat transfer tubes 109 are provided, and the reheater heat transfer tubes 109 are arranged in multiple stages in the horizontal direction. A reheater inlet header 110 and a reheater outlet header 111 are provided at the inlet and outlet of the reheater heat transfer tube 109,
Further, the U-shaped bend pipes 108, 108 are provided with reheater intermediate headers 112, 112.

When viewed from the reheater 107, the evaporator heat transfer tube 113 is installed vertically in the downstream side of the flow direction of the exhaust gas G.
The evaporator heat transfer pipe 113 is arranged in multiple stages in the flow direction of the exhaust gas G.
An evaporator inlet header 115 and an evaporator outlet header 116 are provided at the inlet and outlet of the evaporator 114.

A economizer 117 is disposed downstream of the evaporator 114 in the flow direction of the exhaust gas G. The economizer 117 has U-shaped bend pipes 118, 118 and is installed vertically. The economizer heat transfer tube 119 is provided, and the economizer heat transfer tubes 119 are arranged in multiple stages in the horizontal direction. A economizer inlet header 120 and an economizer outlet header 121 are provided at the inlet and outlet of the economizer heat transfer tube 119,
The U-shaped bend pipes 118, 118 have an intermediate header 12 for the economizer.
2, 122 are provided.

A water supply pipe 12 is installed in the economizer inlet header 120.
3 are connected, and a water supply pump 124 is provided in the middle of the water supply pipe 123. Economizer outlet header 1
21 is connected to a steam drum 126 via a pipe 125, and this steam drum 126 is connected to an evaporator inlet header 115 via a pipe 127. The evaporator outlet header 116 is connected to the steam drum 126 via a pipe 128, and the steam drum 126 is connected to the superheater inlet header 104 via a pipe 129. The superheater outlet header 105 is connected to a steam turbine (not shown) via a pipe 130, and the outlet side of this steam turbine is connected to a reheater inlet header 110 via a pipe 131. The reheater outlet header 111 is connected to the inlet side of the steam turbine via a pipe 132.

In the conventional exhaust heat recovery heat exchanger having the above structure, the exhaust gas G exhausted from the gas turbine from the left side to the right side in the drawing is placed inside the exhaust heat recovery heat exchanger body 100. Supplied. On the other hand, the water supply W for generating steam is boosted by the water supply pump 124 and supplied to the water supply pipe 1.
It is sent to the economizer inlet header 120 via 23, and is heated by the heat of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger main body 100 while passing through the plural economizer heat transfer tubes 119. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 126. Further, the water supply W is sent from the economizer outlet header 121 to the steam drum 126 via the pipe 125. The feed water W sent to the steam drum 126 is sent to the evaporator inlet header 115 via the pipe 127, and the plurality of evaporator heat transfer tubes 1
When passing through 13, it is further heated by the heat of the exhaust gas G. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 116 to the steam drum 126 again via the pipe 128. Then, the steam-water mixed fluid is separated into steam and water in the steam drum 126, and the separated steam is passed through the pipe 129 to the superheater inlet header 1
04. The steam sent to the superheater inlet header 104 is heated by the heat of the exhaust gas G when passing through the plurality of superheater heat transfer tubes 103, becomes superheated steam under a predetermined steam condition, and then is connected to the superheater outlet header 105. Piping 1
Sent to the steam turbine via 30. And the steam that worked in the steam turbine and became superheated,
Sent to the reheater inlet header 110 via pipe 131,
When passing through the plurality of reheater heat transfer tubes 109, it is reheated by the exhaust gas G and sent to the steam turbine again.

[0009]

However, in the above-mentioned conventional exhaust heat recovery heat exchanger, as described above, the superheater heat transfer tube 103, the reheater heat transfer tube 109, and the evaporator heat transfer tube 1 are used.
13 and all the heat transfer tubes of the economizer heat transfer tube 119 are arranged in the vertical direction, the exhaust heat recovery heat exchanger body 10
Within 0, the stirring action of the exhaust gas G is unlikely to occur. Therefore, the temperature distribution and the velocity distribution of the exhaust gas G introduced into the exhaust heat recovery heat exchanger body 100 tended to be non-uniform within the exhaust heat recovery heat exchanger body 100. When the temperature distribution and the velocity distribution of the exhaust gas G become non-uniform inside the exhaust heat recovery heat exchanger body 100 in this way, the superheater 10
1, there was a problem that the heat transfer performance in the reheater 107, the evaporator 114 and the economizer 117 was deteriorated, which hindered the generation of superheated steam in the heat recovery heat exchanger.

Further, in the conventional exhaust heat recovery heat exchanger, as described above, the economizer heat transfer tube 5, the evaporator heat transfer tube 11, the reheater heat transfer tube 15 and the superheater heat transfer tube 19 are all arranged vertically. Since it is arranged, it is necessary to support the upper header to hang the heat transfer tube to support each heat transfer tube, or to support the lower header, and in any case, it is necessary to attach the header to each heat transfer tube. It was These headers not only complicate the structure of the exhaust heat recovery heat exchanger, but also increase the weight of the whole, and further, there is a problem that the reliability of the equipment is deteriorated due to the increase of the welded portion.

Therefore, an object of the present invention is to make the temperature distribution and velocity distribution of the exhaust gas flowing inside the exhaust heat recovery heat exchanger uniform and to improve the heat transfer performance. It is to provide a recovery heat exchanger.

[0012]

According to the first aspect of the present invention,
A plurality of heat exchanging means, which are sequentially arranged along the flow direction of the exhaust gas supplied in the horizontal direction and include at least an evaporator,
A heat transfer tube provided in each of the heat exchange means and arranged in a direction orthogonal to the flow direction of the exhaust gas; and the heat transfer tube of the evaporator is a horizontal exhaust heat recovery heat exchanger arranged in a vertical direction. In at least one of the heat transfer tubes other than the heat transfer tube of the evaporator is arranged in a direction different from that of the heat transfer tube of the evaporator.

According to a second aspect of the present invention, a plurality of heat exchanging means including at least an evaporator, which are sequentially arranged along the flow direction of the exhaust gas supplied upward, are provided in each of the heat exchanging means, and are horizontal. In a vertical exhaust heat recovery heat exchanger having heat transfer tubes arranged in a direction, at least one of the heat transfer tubes other than the heat transfer tube of the evaporator is arranged in a direction different from that of the heat transfer tube of the evaporator. It is characterized by that.

According to a third aspect of the present invention, the at least one
One of the heat transfer tubes is arranged in a direction orthogonal to the heat transfer tube of the evaporator.

The invention according to claim 4 is characterized in that each of the heat transfer tubes is arranged in a direction different from that of another adjacent heat transfer tube.

The invention according to claim 5 is characterized in that each of the heat transfer tubes is arranged in a direction orthogonal to another heat transfer tube adjacent thereto.

According to a sixth aspect of the present invention, at least one of the heat exchanging means other than the evaporator is arranged so as to face the first inlet and outlet headers and the first inlet and outlet headers. Second inlet and outlet headers, a plurality of first heat transfer tubes connected to the first inlet and outlet headers, and a plurality of second heat transfer tubes connected to the second inlet and outlet headers And the first heat transfer tubes and the second heat transfer tubes are arranged alternately along the axial direction of the header.

According to a seventh aspect of the present invention, at least one of the heat exchange means includes a plurality of heat transfer tubes, and the plurality of heat transfer tubes have an interval between upstream heat transfer tubes in a flow direction of the exhaust gas. It is smaller than the interval between the heat transfer tubes on the downstream side in the direction.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment Hereinafter, a first embodiment of an exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 1 and 2. 1 is a side view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 2 is a plan view of the same.

In FIGS. 1 and 2, reference numeral 1 denotes a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the left side in the figure. Inside the exhaust heat recovery heat exchanger body 1, a superheater 2 is arranged at the most upstream part in the flow direction of the exhaust gas G, and the superheater 2 has U-shaped bend pipes 3, 3, 3. The heat transfer tube 4 is provided. The superheater heat transfer tubes 4 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. A superheater inlet header 5 and a superheater outlet header 6 are arranged at the inlet and outlet of the superheater heat transfer tube 4 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.

An evaporator 7 is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G, and the evaporator 7 is
The evaporator heat transfer tubes 8 are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G, and the evaporator heat transfer tubes 8 are arranged in multiple stages in the flow direction of the exhaust gas G. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. The economizer inlet header 14 and the economizer outlet header 15 are arranged at the inlet and the outlet of the economizer heat transfer tube 13 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. .

As described above, the superheater heat transfer tube 4 and the economizer heat transfer tube 13 are arranged in the horizontal direction, and the evaporator heat transfer tube 8 located between them is arranged in the vertical direction.
That is, the heat transfer tubes 4, 8 and 13 are arranged such that the arrangement direction thereof alternately changes between the horizontal direction and the vertical direction in the flow direction of the exhaust gas G.

A water supply pipe 16 is connected to the economizer inlet header 14, and a water supply pump 17 is provided in the middle of the water supply pipe 16. The economizer outlet header 15 is connected to a steam drum 19 via a pipe 18, and the steam drum 19 is connected to an evaporator inlet header 9 via a pipe 20. The evaporator outlet header 10 is connected to the steam drum 19 via a pipe 21, and the steam drum 19 is connected to the superheater inlet header 5 via a pipe 22. The superheater outlet header 6 is connected to the inlet side of a steam turbine (not shown) via a pipe 23.

Next, the operation of the present embodiment will be described. Exhaust gas G discharged from the gas turbine is supplied to the inside of the exhaust heat recovery heat exchanger body 1 from the left side to the right side in the drawing. On the other hand, the feed water W for generating steam is pressurized by the water feed pump 17 and sent to the economizer inlet header 14 via the water supply pipe 16, and while passing through the plurality of economizer heat transfer tubes 13, exhaust heat recovery Exhaust gas G flowing inside the heat exchanger body 1
It is heated by the heat of. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 19. Further, the water supply W is sent from the economizer outlet header 15 to the steam drum 19 via the pipe 18. The feed water W sent to the steam drum 19 is sent to the evaporator inlet header 9 via the pipe 20, and is further heated by the heat of the exhaust gas G when passing through the plurality of evaporator heat transfer tubes 8. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 10 to the steam drum 19 again via the pipe 21. Steam-water mixed fluid is steam drum 1
In 9 the steam and water are separated, and the separated steam is sent to the superheater inlet header 5 via the pipe 22. The steam sent to the superheater inlet header 5 has a plurality of superheater heat transfer tubes 4
Is heated by the heat of the exhaust gas G and passes through the pipe 23 connected to the superheater outlet header 6 and then sent to the steam turbine.

Further, in this embodiment, the superheater heat transfer tube 4 is arranged horizontally, the evaporator heat transfer tube 8 located downstream thereof is arranged vertically, and the economizer heat transfer tube located downstream thereof. Since 13 is arranged horizontally, the exhaust gas G introduced into the inside of the exhaust heat recovery heat exchanger 1 passes through the heat transfer tubes 4, 8, 13 which are arranged so as to alternate in direction. The temperature distribution and velocity distribution of the exhaust gas G that is agitated and flows inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to the present embodiment, the temperature distribution and the velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the superheater 2, the evaporator 7 and the node are provided. The heat transfer performance in the carbonizer 11 is improved, and superheated steam can be appropriately generated.

Further, according to this embodiment, since the superheater heat transfer tube 4 and the economizer heat transfer tube 13 are arranged in the horizontal direction, it is not necessary to support the heat transfer tube by the header, and therefore, the structure is provided. Not only can it be simplified, but the overall weight can be reduced, and further, the number of welded parts can be reduced and the equipment reliability can be improved.

3 and 4 show a modification of the present embodiment, which is a modification of the superheater 2 and the economizer 11 in the first embodiment. , 6, 14, 15 are changed. That is, in this modification, two superheater heat transfer tubes 4, 4 on the outer and inner circumferences are connected in parallel between the superheater inlet header 5 and the superheater outlet header 6 at the same vertical height. Similarly, between the economizer inlet header 14 and the economizer outlet header 15, the two economizer heat transfer tubes 13, 13 on the outer and inner circumferences are connected in parallel. Also in the present embodiment having such a configuration, the same effect as that of the first embodiment can be obtained.

Second Embodiment Next, a second embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 5 and 6. 5 is a side view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 6 is a plan view of the same.

In FIGS. 5 and 6, reference numeral 1 denotes a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the left side in the figure. Inside the exhaust heat recovery heat exchanger main body 1, a superheater 2 is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the superheater 2 has U-shaped bend pipes 3 and 3. It is equipped with 4. The superheater heat transfer tubes 4 are arranged in the vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the horizontal direction. A superheater inlet header 5 and a superheater outlet header 6 are provided at the inlet and outlet of the superheater heat transfer tube 4.
Are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G. Further, the U-shaped bend pipes 3 and 3 are provided with intermediate headers 24 and 24.

A reheater 25 is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G.
Includes a reheater heat transfer tube 27 having U-shaped bend tubes 26, 26, 26. The reheater heat transfer tubes 27 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. At the inlet and outlet of the reheater 25, the reheater inlet header 2
8 and the reheater outlet header 29 are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.
In addition, the reheater inlet header 28 and the reheater outlet header 29
A pipe 30 and a pipe 31 are connected to each.

An evaporator 7 is arranged downstream of the reheater 25 in the flow direction of the exhaust gas G.
Includes an evaporator heat transfer tube 8 arranged in the vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G, and the evaporator heat transfer tubes 8 are arranged in multiple stages in the flow direction of the exhaust gas G. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G.

A economizer 11 is arranged downstream of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. The economizer inlet header 14 and the economizer outlet header 15 are arranged at the inlet and the outlet of the economizer heat transfer tube 13 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. .

In this way, the reheater heat transfer tube 27 and the economizer heat transfer tube 13 are arranged horizontally, and the superheater heat transfer tube 4 and the evaporator heat transfer tube 8 are arranged vertically. That is, the heat transfer tubes 4, 27, 8 and 13 are arranged such that the arrangement direction thereof alternately changes between the horizontal direction and the vertical direction in the flow direction of the exhaust gas G.

A water supply pipe 16 is connected to the economizer inlet header 14, and a water supply pump 17 is provided in the middle of the water supply pipe 16. The economizer outlet header 15 is connected to a steam drum 19 via a pipe 18, and the steam drum 19 is connected to an evaporator inlet header 9 via a pipe 20. The evaporator outlet header 10 is connected to the steam drum 19 via a pipe 21, and the steam drum 19 is connected to the superheater inlet header 5 via a pipe 22. The superheater outlet header 6 is connected to the inlet side of a steam turbine (not shown) via a pipe 23.

Next, the operation of the present embodiment will be described. Exhaust gas G discharged from the gas turbine is supplied to the inside of the exhaust heat recovery heat exchanger body 1 from the left side to the right side in the drawing. On the other hand, the feed water W for generating steam is pressurized by the water feed pump 17 and sent to the economizer inlet header 14 via the water supply pipe 16, and while passing through the plurality of economizer heat transfer tubes 13, exhaust heat recovery Exhaust gas G flowing inside the heat exchanger body 1
It is heated by the heat of. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 19. Further, the water supply W is sent from the economizer outlet header 15 to the steam drum 19 via the pipe 18. The feed water W sent to the steam drum 19 is sent to the evaporator inlet header 9 via the pipe 20, and is further heated by the heat of the exhaust gas G when passing through the plurality of evaporator heat transfer tubes 8. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 10 to the steam drum 19 again via the pipe 21. Steam-water mixed fluid is steam drum 1
In 9 the steam and water are separated, and the separated steam is sent to the superheater inlet header 5 via the pipe 22. The steam sent to the superheater inlet header 5 has a plurality of superheater heat transfer tubes 4
Is heated by the heat of the exhaust gas G and passes through the pipe 23 connected to the superheater outlet header 6 and then sent to the steam turbine.

In the present embodiment, the superheater heat transfer tube 4 is arranged vertically, the reheater heat transfer tube 27 located downstream thereof is arranged horizontally, and the evaporator heat transfer tube located downstream thereof. 8 is arranged in the vertical direction, and the economizer heat transfer tube 13 located downstream thereof is arranged in the horizontal direction, so that the exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 is alternately oriented. The temperature distribution and the velocity distribution of the exhaust gas G that is agitated by passing through the heat transfer tubes 4, 27, 8 and 13 that are arranged differently and that flows inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to this embodiment, the temperature distribution and velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the superheater 2 and the reheater 2 are provided.
5, the heat transfer performance in the evaporator 7 and the economizer 11 is improved, and superheated steam can be appropriately generated.

Further, according to this embodiment, since the reheater heat transfer tube 27 and the economizer heat transfer tube 13 are arranged in the horizontal direction, it is not necessary to support the heat transfer tube by the header, and therefore, Not only can the configuration be simplified, but the overall weight can be reduced, and further, the effect of reducing the number of welded portions and improving equipment reliability can be obtained.

Third Embodiment Next, a third embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 7 and 8. 7. FIG. 7 is a side view showing a schematic configuration of the exhaust heat recovery heat exchanger according to this embodiment, and FIG. 8 is a plan view of the same.

In FIGS. 7 and 8, reference numeral 1 denotes a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the left side in the figure. Inside the exhaust heat recovery heat exchanger body 1, a first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the first superheater 2a is a U-shaped bend pipe 3a, 3a, 3a. The first superheater heat transfer tube 4a having The first superheater heat transfer tubes 4a are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. A first superheater inlet header 5a and a first superheater outlet header 6a are provided at the inlet and outlet of the first superheater heat transfer tube 4a.
Are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.

A reheater 25 is disposed downstream of the first superheater 2a in the flow direction of the exhaust gas G, and the reheater 25 has U-shaped bend pipes 26, 26. It is equipped with 27. The reheater heat transfer tubes 27 are arranged in the vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the horizontal direction. At the inlet and outlet of the reheater 25, the reheater inlet header 2
8 and the reheater outlet header 29 are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.
The U-shaped bend pipes 26, 26 have intermediate headers 32, 3
2 are provided. Further, a pipe 30 and a pipe 31 are connected to the reheater inlet header 28 and the reheater outlet header 29, respectively.

A second superheater 2b is arranged downstream of the reheater 25 in the flow direction of the exhaust gas G.
The superheater 2b includes a second superheater heat transfer tube 4b having U-shaped bend tubes 3b, 3b, 3b. The second superheater heat transfer tubes 4b are arranged in a horizontal direction and in a direction orthogonal to the flow direction of the exhaust gas G, and are also arranged in multiple stages in the vertical direction. A second superheater inlet header 5b and a second superheater outlet header 6b are arranged at the inlet and outlet of the second superheater heat transfer pipe 4b in a vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G. Has been done.

An evaporator 7 is arranged downstream of the second superheater 2b in the flow direction of the exhaust gas G, and the evaporator 7 is arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. The evaporator heat transfer tubes 8 are arranged in the same manner, and the evaporator heat transfer tubes 8 are arranged in multiple stages in the flow direction of the exhaust gas G. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. The economizer inlet header 14 and the economizer outlet header 15 are arranged at the inlet and the outlet of the economizer heat transfer tube 13 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. .

As described above, the first superheater heat transfer tube 4a and the second superheater heat transfer tube 4a
The superheater heat transfer tube 4b and the economizer heat transfer tube 13 are arranged horizontally, and the reheater heat transfer tube 27 and the evaporator heat transfer tube 8 are arranged vertically. That is, each heat transfer tube 4a, 2
5, 4b, 8 and 13 are arranged such that their arrangement directions alternate between the horizontal direction and the vertical direction in the flow direction of the exhaust gas G.

A water supply pipe 16 is connected to the economizer inlet header 14, and a water supply pump 17 is provided in the middle of the water supply pipe 16. The economizer outlet header 15 is connected to a steam drum 19 via a pipe 18, and the steam drum 19 is connected to an evaporator inlet header 9 via a pipe 20. The evaporator outlet header 10 is connected to a steam drum 19 via a pipe 21, and the steam drum 19 is connected to a first superheater inlet header 5a and a second superheater inlet via a pipe 22 having branch pipes 22a and 22b. It is connected to the header 5b. The first superheater outlet header 6a and the second superheater outlet header 6b are connected to the inlet side of a steam turbine (not shown) via a pipe 23 having pipes 23a and 23b.

Next, the operation of the present embodiment will be described. Exhaust gas G discharged from the gas turbine is supplied to the inside of the exhaust heat recovery heat exchanger body 1 from the left side to the right side in the drawing. On the other hand, the feed water W for generating steam is pressurized by the water feed pump 17 and sent to the economizer inlet header 14 via the water supply pipe 16, and while passing through the plurality of economizer heat transfer tubes 13, exhaust heat recovery Exhaust gas G flowing inside the heat exchanger body 1
It is heated by the heat of. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 19. Further, the water supply W is sent from the economizer outlet header 15 to the steam drum 19 via the pipe 18. The feed water W sent to the steam drum 19 is sent to the evaporator inlet header 9 via the pipe 20, and is further heated by the heat of the exhaust gas G when passing through the plurality of evaporator heat transfer tubes 8. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 10 to the steam drum 19 again via the pipe 21. Steam-water mixed fluid is steam drum 1
The steam is separated into steam and water at 9, and the separated steam is passed through the pipe 22 to the first and second superheater inlet headers 5 a, 5
b. First and second superheater inlet headers 5a, 5
The steam sent to b is heated by the heat of the exhaust gas G when passing through the plurality of first and second superheater heat transfer tubes 4a, 4b, and becomes the superheated steam of a predetermined steam condition, and then the first and second steams. 2 It is sent to the steam turbine through a pipe 23 connected to the two superheater outlet headers 6a and 6b.

In the present embodiment, the first superheater heat transfer pipe 4a is arranged horizontally, the reheater heat transfer pipe 27 located downstream thereof is arranged vertically, and the second heat exchanger pipe 4a located downstream thereof is arranged. Since the superheater heat transfer tube 4b is arranged horizontally, the evaporator heat transfer tube 8 located downstream thereof is arranged vertically, and the economizer heat transfer tube 13 located downstream thereof is arranged horizontally. The exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 has heat transfer tubes 4a arranged in alternating directions.
The temperature distribution and velocity distribution of the exhaust gas G that is agitated by passing through the heat exchangers 27, 4b, 8 and 13 and flows inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to this embodiment, the temperature distribution and the velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the first superheater 2a and the reheater are provided. 25, the 2nd superheater 2b, the evaporator 7, and the economizer 11 are improved in heat transfer performance, and superheated steam can be appropriately generated.

Further, according to this embodiment, the first superheater heat transfer tube 4a, the second superheater heat transfer tube 2b and the economizer heat transfer tube 13 are provided.
Since it is arranged in the horizontal direction, it is not necessary to support the heat transfer tube by the header, so not only the structure can be simplified, but also the overall weight can be reduced. The effect is obtained that the number of parts is reduced and the device reliability is improved.

Fourth Embodiment Next, a fourth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 9 and 10. Note that FIG.
[Fig. 10] is a side view showing a schematic configuration of an exhaust heat recovery heat exchanger according to the present embodiment, and Fig. 10 is a plan view of the same.

In FIGS. 9 and 10, reference numeral 1 denotes a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the left side in the figure. Inside the exhaust heat recovery heat exchanger body 1, a first reheater 25a is arranged at the most upstream portion in the flow direction of the exhaust gas G.
5a comprises a first reheater heat transfer tube 27a having U-shaped bend tubes 26a, 26a, 26a. The first reheater heat transfer tubes 27a are arranged in the horizontal direction and in the direction orthogonal to the flow direction of the exhaust gas G, and are also arranged in multiple stages in the vertical direction. A first reheater inlet header 28a and a first reheater outlet header 29a are provided in an inlet portion and an outlet portion of the first reheater 25a in a vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G. It is arranged.

A superheater 2 is arranged downstream of the first reheater 25a in the flow direction of the exhaust gas G, and the superheater 2 includes a superheater heat transfer tube 4 having U-shaped bend tubes 3 and 3. I have it. The superheater heat transfer tubes 4 are arranged in the vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the horizontal direction. At the inlet and outlet of the superheater heat transfer tube 4, a superheater inlet header 5 and a superheater outlet header 6 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G. Further, the U-shaped bend pipes 3 and 3 are provided with intermediate headers 24 and 24.

A second reheater 25b is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G.
The reheater 25b includes a second reheater heat transfer tube 27b having U-shaped bend tubes 26b, 26b, 26b. This second
The reheater heat transfer tubes 27b are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. A second reheater inlet header 28b and a second reheater outlet header 29b are provided at the inlet and outlet of the second reheater 25b in the vertical direction and the exhaust gas G.
Are arranged in a direction orthogonal to the flow direction of.

An evaporator 7 is arranged downstream of the second reheater 25b in the flow direction of the exhaust gas G, and the evaporator 7 is vertical and orthogonal to the flow direction of the exhaust gas G. The evaporator heat transfer tubes 8 are arranged in the direction, and the evaporator heat transfer tubes 8 are arranged in multiple stages in the flow direction of the exhaust gas G. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. The economizer inlet header 14 and the economizer outlet header 15 are arranged at the inlet and the outlet of the economizer heat transfer tube 13 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. .

As described above, the first reheater heat transfer tube 27a, the second reheater heat transfer tube 27b, and the economizer heat transfer tube 13 are horizontally arranged, and the superheater heat transfer tube 4 and the evaporator heat transfer tube 4 are arranged. 8
Are arranged vertically. That is, each heat transfer tube 27
The a, 4, 27b, 8, and 13 are arranged such that their arrangement directions alternate between the horizontal direction and the vertical direction in the flow direction of the exhaust gas G.

A water supply pipe 16 is connected to the economizer inlet header 14, and a water supply pump 17 is provided in the middle of the water supply pipe 16. The economizer outlet header 15 is connected to a steam drum 19 via a pipe 18, and the steam drum 19 is connected to an evaporator inlet header 9 via a pipe 20. The evaporator outlet header 10 is connected to the steam drum 19 via a pipe 21, and the steam drum 19 is connected to the superheater inlet header 5 via a pipe 22. The superheater outlet header 6 is connected to the inlet side of a steam turbine (not shown) via a pipe 23. Also,
The first reheater inlet header 28a and the second reheater inlet header 28b include a pipe 30 having a pipe 30a and a pipe 30b.
Connected to the outlet side of the steam turbine. Further, the first reheater outlet header 29a and the second reheater outlet header 29b are connected to the inlet side of the steam turbine via a pipe 31 having a pipe 31a and a pipe 31b.

Next, the operation of the present embodiment will be described. Exhaust gas G discharged from the gas turbine is supplied to the inside of the exhaust heat recovery heat exchanger body 1 from the left side to the right side in the drawing. On the other hand, the feed water W for generating steam is pressurized by the water feed pump 17 and sent to the economizer inlet header 14 via the water supply pipe 16, and while passing through the plurality of economizer heat transfer tubes 13, exhaust heat recovery Exhaust gas G flowing inside the heat exchanger body 1
It is heated by the heat of. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 19. Further, the water supply W is sent from the economizer outlet header 15 to the steam drum 19 via the pipe 18. The feed water W sent to the steam drum 19 is sent to the evaporator inlet header 9 via the pipe 20, and is further heated by the heat of the exhaust gas G when passing through the plurality of evaporator heat transfer tubes 8. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 10 to the steam drum 19 again via the pipe 21. Steam-water mixed fluid is steam drum 1
In 9 the steam and water are separated, and the separated steam is sent to the superheater inlet header 5 via the pipe 22. The steam sent to the superheater inlet header 5 has a plurality of superheater heat transfer tubes 4
Is heated by the heat of the exhaust gas G and passes through the pipe 23 connected to the superheater outlet header 6 and then sent to the steam turbine.
Then, the steam that has worked in the steam turbine and has a low degree of superheat is sent to the first and second reheater inlet headers 28a and 28b through the pipe 30, and the plurality of first and second reheater inlet headers
Reheated by the exhaust gas G when passing through the reheater heat transfer tubes 27a and 27b, and the first and second reheater outlet headers 29
It is sent again to the steam turbine via a pipe 31 connected to a and 29b.

In the present embodiment, the first reheater heat transfer pipe 27a is horizontally arranged, the superheater heat transfer pipe 4 located downstream thereof is arranged vertically, and the second heat exchanger pipe 27a located downstream thereof is arranged. Since the reheater heat transfer tube 27b is arranged horizontally, the evaporator heat transfer tube 8 located downstream thereof is arranged vertically, and the economizer heat transfer tube 13 located downstream thereof is arranged horizontally. The exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 has heat transfer tubes 27 arranged so as to alternate in direction.
The temperature distribution and velocity distribution of the exhaust gas G that is agitated by passing through a, 4, 27b, 8, 13 and flows inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to this embodiment, the temperature distribution and the velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the first reheater 25a and the superheater are provided. 2, the heat transfer performance in the 2nd reheater 25b, the evaporator 7, and the economizer 11 is improved, and superheated steam can be appropriately generated.

Further, according to this embodiment, since the first reheater heat transfer tube 27a, the second reheater heat transfer tube 27b and the economizer heat transfer tube 13 are arranged in the horizontal direction, the heat transfer by the header is performed. Since there is no need to support the heat tube, not only the structure can be simplified, but also the overall weight can be reduced, and further, there is an effect that the welded portion is reduced and the equipment reliability is improved. can get.

Fifth Embodiment Next, a fifth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 11 and 12. 11. FIG. 11 is a side view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 12 is a plan view of the same.

In FIGS. 11 and 12, reference numeral 1 denotes a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the left side in the figure. Inside the exhaust heat recovery heat exchanger main body 1, a first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G.
The a includes a first superheater heat transfer tube 4a having U-shaped bend tubes 3a and 3a. The first superheater heat transfer tubes 4a are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the horizontal direction. A first superheater inlet header 5a and a first superheater outlet header 6a are provided at the inlet and outlet of the first superheater heat transfer tube 4a.
Are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G. In addition, U-shaped bend pipes 3a, 3
Intermediate headers 24a and 24a are provided in a.

A first reheater 25a is arranged downstream of the first superheater 2a in the flow direction of the exhaust gas G, and the first reheater 25a includes U-shaped bend pipes 26a, 26a, 2b.
It is provided with a first reheater heat transfer tube 27a having 6a. The first reheater heat transfer tube 27a is arranged horizontally and in the exhaust gas G.
Are arranged in a direction orthogonal to the flow direction of, and are arranged in multiple stages in the vertical direction. First reheater 25
The first reheater inlet header 28 is provided at the inlet and outlet of a.
a and the first reheater outlet header 29a are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.

A second superheater 2b is disposed downstream of the first reheater 25a in the flow direction of the exhaust gas G, and the second superheater 2b has a second U-shaped bend pipe 3b, 3b. The superheater heat transfer tube 4b is provided. The second superheater heat transfer tubes 4b are arranged in the vertical direction and in a direction orthogonal to the flow direction of the exhaust gas G, and are also arranged in multiple stages in the horizontal direction. A second superheater inlet header 5b and a second superheater outlet header 6b are arranged in the inlet and outlet of the second superheater heat transfer tube 4b in a horizontal direction and in a direction orthogonal to the flow direction of the exhaust gas G. Has been done. Further, the U-shaped bend pipes 3b and 3b are provided with intermediate headers 24b and 24b.

A second reheater 25b is arranged downstream of the second superheater 2b in the flow direction of the exhaust gas G, and the second reheater 25b includes U-shaped bend pipes 26b, 26b, 2b.
The second reheater heat transfer tube 27b having 6b is provided. The second reheater heat transfer tube 27b is arranged horizontally and in the exhaust gas G.
Are arranged in a direction orthogonal to the flow direction of, and are arranged in multiple stages in the vertical direction. Second reheater 25
The second reheater inlet header 28 is provided at the inlet and outlet of b.
b and the second reheater outlet header 29b are arranged in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G.

An evaporator 7 is arranged downstream of the second reheater 25b in the flow direction of the exhaust gas G, and the evaporator 7 is vertical and orthogonal to the flow direction of the exhaust gas G. The evaporator heat transfer tubes 8 are arranged in the direction, and the evaporator heat transfer tubes 8 are arranged in multiple stages in the flow direction of the exhaust gas G. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the flow direction of the exhaust gas G, and are arranged in multiple stages in the vertical direction. The economizer inlet header 14 and the economizer outlet header 15 are arranged at the inlet and the outlet of the economizer heat transfer tube 13 in the vertical direction and in the direction orthogonal to the flow direction of the exhaust gas G. .

As described above, the first reheater heat transfer tube 27a, the second reheater heat transfer tube 27b and the economizer heat transfer tube 13 are arranged in the horizontal direction, and the first superheater heat transfer tube 4a and the second reheater heat transfer tube 4a are arranged. The superheater heat transfer tube 4b and the evaporator heat transfer tube 8 are arranged in the vertical direction. That is, each heat transfer tube 4a, 27a, 4b, 27b,
8 and 13 are arranged such that their arrangement direction alternates between the horizontal direction and the vertical direction in the flow direction of the exhaust gas G.

A water supply pipe 16 is connected to the economizer inlet header 14, and a water supply pump 17 is provided in the middle of the water supply pipe 16. The economizer outlet header 15 is connected to a steam drum 19 via a pipe 18, and the steam drum 19 is connected to an evaporator inlet header 9 via a pipe 20. The evaporator outlet header 10 is connected to a steam drum 19 via a pipe 21, and the steam drum 19 is connected to a first superheater inlet header 5a and a second superheater inlet header via a pipe 22 having pipes 22a and 22b. 5b
It is connected to the. First superheater outlet header 6a and second
The superheater outlet header 6b is connected to the inlet side of a steam turbine (not shown) via a pipe 23 having pipes 23a and 23b. Also, the first and second reheater inlet headers 2
8a and 28b are connected to the outlet side of the steam turbine via a pipe 30 having pipes 30a and 30b. Further, the first and second reheater outlet headers 29a and 29b are connected to the inlet side of the steam turbine via a pipe 31 having pipes 31a and 31b.

Next, the operation of this embodiment will be described. Exhaust gas G discharged from the gas turbine is supplied to the inside of the exhaust heat recovery heat exchanger body 1 from the left side to the right side in the drawing. On the other hand, the feed water W for generating steam is pressurized by the water feed pump 17 and sent to the economizer inlet header 14 via the water supply pipe 16, and while passing through the plurality of economizer heat transfer tubes 13, exhaust heat recovery Exhaust gas G flowing inside the heat exchanger body 1
It is heated by the heat of. The heating temperature at this time is slightly lower than the saturation temperature determined by the internal pressure of the steam drum 19. Further, the water supply W is sent from the economizer outlet header 15 to the steam drum 19 via the pipe 18. The feed water W sent to the steam drum 19 is sent to the evaporator inlet header 9 via the pipe 20, and is further heated by the heat of the exhaust gas G when passing through the plurality of evaporator heat transfer tubes 8. The heated feed water W boils and becomes a gas-water mixed fluid, and is sent from the evaporator outlet header 10 to the steam drum 19 again via the pipe 21. Steam-water mixed fluid is steam drum 1
The steam is separated into steam and water at 9, and the separated steam is passed through the pipe 22 to the first and second superheater inlet headers 5 a, 5
b. First and second superheater inlet headers 5a, 5
The steam sent to b is heated by the heat of the exhaust gas G when passing through the plurality of first and second superheater heat transfer tubes 4a, 4b, and becomes the superheated steam of a predetermined steam condition, and then the first and second steams. 2 It is sent to the steam turbine through a pipe 23 connected to the two superheater outlet headers 6a and 6b. The steam that has worked in the steam turbine and has a low degree of superheat is pipe 3
0 through the first and second reheater inlet headers 28a, 28
b, and a plurality of first and second reheater heat transfer tubes 27a,
When passing through 27b, it is reheated by the exhaust gas G and sent again to the steam turbine via the pipe 31 connected to the first and second reheater outlet headers 29a and 29b.

In the present embodiment, the first superheater heat transfer pipe 4a is arranged vertically, the first reheater heat transfer pipe 27a located downstream thereof is arranged horizontally, and the first reheater heat transfer pipe 27a is located downstream thereof. The second superheater heat transfer tube 4b is arranged in the vertical direction,
The second reheater heat transfer tube 27b located downstream thereof is arranged horizontally, the evaporator heat transfer tube 8 located downstream thereof is arranged vertically, and the economizer heat transfer tube 13 located downstream thereof is horizontally arranged. The exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 passes through the heat transfer tubes 4a, 27a, 4b, 27b, 8 and 13 arranged so as to alternate in direction because they are arranged in the direction. By doing so, the temperature distribution and velocity distribution of the exhaust gas G that is agitated and flows inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to the present embodiment, the temperature distribution and velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the first superheater 2a, the first superheater 2a
The heat transfer performance in the reheater 25a, the second superheater 2b, the second reheater 25b, the evaporator 7, and the economizer 11 is improved, and superheated steam can be appropriately generated.

Further, according to this embodiment, since the first reheater heat transfer tube 27a, the second reheater heat transfer tube 27b and the economizer heat transfer tube 13 are arranged in the horizontal direction, the heat transfer by the header is performed. Since there is no need to support the heat tube, not only the structure can be simplified, but also the overall weight can be reduced, and further, there is an effect that the welded portion is reduced and the equipment reliability is improved. can get.

Sixth Embodiment Next, a sixth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG. Note that FIG. 13 is a perspective view showing a schematic configuration of a main part of the exhaust heat recovery heat exchanger according to the present embodiment.

In FIG. 13, reference numeral 1 indicates a horizontal type natural circulation type exhaust heat recovery heat exchanger main body, and an exhaust gas G from a gas turbine (not shown) is supplied into the exhaust heat recovery heat exchanger main body 1. To be done. Inside the exhaust heat recovery heat exchanger body 1,
The first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the first superheater 2a is the first superheater heat transfer tube 4
a. The reheater 2 is provided downstream of the first superheater 2a.
5 are arranged, and this reheater 25 is a reheater heat transfer tube 2
7 is provided. The second superheater 2 is provided downstream of the reheater 25.
b is arranged, and the second superheater 2b includes a second superheater heat transfer tube 4b. An evaporator (not shown) is arranged downstream of the second superheater 2b, and a economizer (not shown) is arranged further downstream thereof.

The first superheater heat transfer tube 4a is arranged in a plane perpendicular to the flow direction of the exhaust gas G, inclined with respect to the vertical direction. In addition, the reheater heat transfer tube 2
In the plane perpendicular to the flow direction of the exhaust gas G, 7 is arranged to be inclined in the direction opposite to the first superheater heat transfer tube 4a with respect to the vertical direction. Further, the second superheater heat transfer tube 4b is inclined in a direction opposite to the reheater heat transfer tube 27, that is, in the same direction as the first superheater heat transfer tube 4a in a plane perpendicular to the flow direction of the exhaust gas G. Are arranged.

As described above, according to the present embodiment, the first superheater heat transfer tubes 4a, the reheater heat transfer tubes 27, and the second superheater heat transfer tubes 4b are alternately arranged so as to be inclined in opposite directions. , Exhaust gas G flowing inside the exhaust heat recovery heat exchanger body 1
Are heat transfer tubes 4a, 27, 4b that are alternately inclined in opposite directions.
The heat distribution of the exhaust heat recovery heat exchanger is improved because the temperature distribution and the speed distribution are made uniform by the stirring.

Seventh Embodiment Next, a seventh embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG. In the following description, the superheater 2 will be described as an example, but the same configuration can be applied not only to the superheater 2 but also to a reheater and a economizer, and to all of them. It can be applied partially or partially.

FIG. 14 is a perspective view showing a part of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to the present embodiment. In the figure, reference numeral 2 indicates a superheater, and the inside of the superheater 2 is shown. Is provided with a superheater first inlet header 5c and a superheater first outlet header 6c standing on the right side when viewed from the upstream side in the flow direction of the exhaust gas G, and a superheater second inlet header 5d and a superheater on the left side. A second outlet header 6d is erected so as to face the first superheater inlet and outlet headers 5c and 6c.

Superheater first inlet and outlet headers 5c, 6c
, A plurality of superheater first heat transfer tubes 4c, 4c, ... It is installed in.

On the other hand, the superheater second inlet and outlet header 5
A plurality of superheater second heat transfer tubes 4d, 4d ... 4d having U-shaped bend tubes 3d, 3d, 3d are arranged in the vertical direction of the plurality of superheater first heat transfer tubes 4c, 4c. It is arranged so as to be located in the gap. That is, the superheater first heat transfer tubes 4c and the superheater second heat transfer tubes 4d are alternately arranged in the vertical direction.

As described above, in the present embodiment,
Since the superheater first heat transfer tubes 4c and the superheater second heat transfer tubes 4d are alternately arranged inside the superheater 2 in the vertical direction, the flow directions of the fluids flowing inside the heat transfer tubes 4c and 4d are opposed to each other. However, for this reason, the temperature distribution of the exhaust gas G is made uniform in the horizontal direction and in the direction orthogonal to the flow direction of the exhaust gas G. By making the temperature distribution of the exhaust gas G uniform in this way, the heat transfer performance in the exhaust heat recovery heat exchanger is significantly improved.

FIG. 15 shows a modified example of this embodiment. In this modified example, the superheater first inlet header 5c and the superheater first outlet header 6c are arranged at the same height in the vertical direction. Two superheater heat transfer tubes 4c and 4c on the outer and inner circumferences having a U-shaped bend tube 3c are connected in parallel, and similarly, a superheater second inlet header 5d and a superheater second outlet are provided. Two superheater heat transfer tubes 4d and 4d on the inner and outer circumferences, which have a U-shaped bend tube 3d, are connected in parallel with the header 6d. Also in this modification having such a configuration, the same effect as that of the above embodiment can be obtained.

Eighth Embodiment Next, an eighth embodiment of the horizontal type natural circulation type exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG.
In the following description, the superheater 2 will be described as an example, but the same configuration can be applied to not only the superheater 2 but also a reheater, an evaporator, and a economizer. Can be applied to all or some.

FIG. 16 is a side sectional view showing an outline of the superheater 2 arranged inside the exhaust heat recovery heat exchanger body (not shown). In FIG. 16, reference numeral 4e is an exhaust gas inlet of the superheater 2. A side heat transfer tube is shown. Further, in FIG. 16, symbols P1 and P2 indicate the pitches of the heat transfer tubes 4e on the exhaust gas inlet side in the direction orthogonal to the exhaust gas G. As can be seen from FIG. 16, the pitch of the heat transfer tubes 4e on the exhaust gas inlet side is larger on the downstream side P2 than on the upstream side P1 in the flow direction of the exhaust gas G.

As described above, according to this embodiment, the superheater 2
Since the pitch between the heat transfer tubes is small on the upstream side in the flow direction of the exhaust gas G and is large on the downstream side, the exhaust gas G causes a pressure loss when passing through the heat transfer tube on the upstream side with a small pitch, which causes stirring. Therefore, the temperature distribution and the velocity distribution of the exhaust gas G are made uniform, and the heat transfer performance of the exhaust heat recovery heat exchanger is improved.

Ninth Embodiment A ninth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described below with reference to FIGS. 17 and 18. Note that FIG. 17 is a front view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 18 is a side view of the same.

In FIG. 17 and FIG. 18, reference numeral 1 denotes a vertical type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from below. Inside the exhaust heat recovery heat exchanger body 1, a superheater 2 is arranged at the most upstream part in the flow direction of the exhaust gas G, and the superheater 2 has U-shaped bend pipes 3, 3, 3. The heat transfer tube 4 is provided. The superheater heat transfer tubes 4 are arranged in a horizontal direction and are arranged in multiple stages in a direction orthogonal to the axis of the heat transfer tubes. At the inlet and outlet of the superheater heat transfer tube 4, a superheater inlet header 5 and a superheater outlet header 6 are arranged horizontally and in a direction orthogonal to the axis of the superheater heat transfer tube 4.

An evaporator 7 is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G, and the evaporator 7 is
An evaporator heat transfer tube 8 arranged in a horizontal direction is provided, and the evaporator heat transfer tube 8 is arranged in a horizontal direction and in a direction orthogonal to the axis of the superheater heat transfer tube 4, and the axis of the evaporator heat transfer tube 8 is provided. Are arranged in multiple stages in a direction orthogonal to. Evaporator 7
An evaporator inlet header 9 and an evaporator outlet header 10 are arranged at the inlet and outlet of the device in the horizontal direction and in the direction orthogonal to the axis of the evaporator heat transfer tube 8.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the axis of the evaporator heat transfer tubes 8, and are arranged in multiple stages in a direction orthogonal to the axis of the economizer heat transfer tubes 13. At the inlet and outlet of the economizer heat transfer tube 13, a economizer economizer header 14 and an economizer economizer outlet header 15 are arranged horizontally and in a direction orthogonal to the axis of the economizer heat exchanger tube 13. There is.

As described above, the superheater heat transfer tube 4 and the economizer heat transfer tube 13 are arranged in the same direction, and the evaporator heat transfer tube 8 positioned between these heat transfer tubes is the superheater heat transfer tube 4 And the coal economizer heat transfer tubes 13 are arranged in a direction orthogonal to the heat transfer tubes 13. That is, the heat transfer tubes 4, 8 and 13 are arranged such that the arrangement direction thereof alternately changes in the flow direction of the exhaust gas G. Therefore, the exhaust gas G introduced into the inside of the exhaust heat recovery heat exchanger 1 is agitated by passing through the heat transfer tubes 4, 8, 13 which are arranged so as to alternately change their directions,
The temperature distribution and velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform.

As described above, according to this embodiment, the temperature distribution and the velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform, so that the superheater 2, the evaporator 7 and the node are provided. The heat transfer performance in the carbonizer 11 is improved, and superheated steam can be appropriately generated.

19 and 20 show a modified example of the present embodiment, which is a heat transfer tube 4 of the superheater 2, evaporator 7 and economizer 11 in the ninth embodiment. , 8, 13 and headers 5, 6, 9, 10, 14, 1
The configuration of 5 is changed. That is, in this modification, two superheater heat transfer tubes 4, 4 on the outer and inner circumferences are connected in parallel between the superheater inlet header 5 and the superheater outlet header 6 in the same vertical plane. Similarly, between the evaporator inlet header 9 and the evaporator outlet header 10, and between the economizer inlet header 14 and the economizer outlet header 15 as well.
Between and, two evaporator heat transfer pipes 8 and 8 and an economizer heat transfer pipe 13, 13 are connected in parallel, respectively. Also in the present embodiment having such a configuration, the same effect as that of the ninth embodiment can be obtained.

Tenth Embodiment Next, a tenth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 21 and 22. In addition,
FIG. 21 is a front view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 22 is a side view of the same.

21 and 22, reference numeral 1 denotes a vertical type natural circulation type exhaust heat recovery heat exchanger body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger body 1. G is supplied from below. Inside the exhaust heat recovery heat exchanger main body 1, a superheater 2 is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the superheater 2 has U-shaped bend pipes 3 and 3. It is equipped with 4. The superheater heat transfer tubes 4 are arranged in a horizontal direction and are arranged in multiple stages in a direction orthogonal to the axis of the heat transfer tubes. The superheater inlet header 5 is provided at the inlet and outlet of the superheater heat transfer tube 4.
Also, the superheater outlet header 6 is arranged horizontally and in a direction orthogonal to the axis of the superheater heat transfer tube 4.

A reheater 25 is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G.
Includes a reheater heat transfer tube 27 having U-shaped bend tubes 26, 26, 26. The reheater heat transfer tubes 27 are arranged horizontally and in a direction orthogonal to the axis of the superheater heat transfer tubes 4, and are arranged in multiple stages in a direction perpendicular to the axis of the reheater heat transfer tubes 27. . At the inlet and outlet of the reheater 25, a reheater inlet header 28 and a reheater outlet header 29 are provided.
Are arranged horizontally and in a direction orthogonal to the reheater heat transfer tube 27.

An evaporator 7 is arranged downstream of the reheater 25 in the flow direction of the exhaust gas G, and the evaporator 7 is provided with an evaporator heat transfer tube 8. This evaporator heat transfer tube 8
They are arranged horizontally and in a direction orthogonal to the axis of the reheater heat transfer tube 27, and are arranged in multiple stages in a direction orthogonal to the axis of the evaporator heat transfer tube 8. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the axis of the evaporator heat transfer tube 8.

A economizer 11 is arranged downstream of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the axis of the evaporator heat transfer tubes 8, and are arranged in multiple stages in a direction orthogonal to the axis of the economizer heat transfer tubes 13. At the inlet and outlet of the economizer heat transfer tube 13, a economizer economizer header 14 and an economizer economizer outlet header 15 are arranged horizontally and in a direction orthogonal to the axis of the economizer heat exchanger tube 13. There is.

As described above, the superheater heat transfer tube 4, the reheater heat transfer tube 27, the evaporator heat transfer tube 8 and the economizer heat transfer tube 13 have their arrangement directions alternately changed in the flow direction of the exhaust gas G. Therefore, the temperature distribution and the velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform. Therefore, the heat transfer performance in the superheater 2, the reheater 25, the evaporator 7, and the economizer 11 is improved, and superheated steam can be appropriately generated.

Eleventh Embodiment Next, an eleventh embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 23 and 24. In addition,
FIG. 23 is a front view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 24 is a side view of the same.

In FIGS. 23 and 24, reference numeral 1 denotes a vertical type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from below. Inside the exhaust heat recovery heat exchanger body 1, a first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the first superheater 2a is a U-shaped bend pipe 3a, 3a, 3a. The first superheater heat transfer tube 4a having The first superheater heat transfer tubes 4a are arranged in the horizontal direction and are arranged in multiple stages in a direction orthogonal to the axis of the heat transfer tube. The first superheater inlet header 5a and the first superheater outlet header 6a are arranged at the inlet and the outlet of the first superheater heat transfer tube 4a in a horizontal direction and in a direction orthogonal to the first superheater heat transfer tube 4a. Has been done.

A reheater 25 is arranged downstream of the first superheater 2a in the flow direction of the exhaust gas G, and the reheater 25 has U-shaped bend pipes 26, 26. It is equipped with 27. The reheater heat transfer tubes 27 are arranged horizontally and in a direction orthogonal to the axis of the first superheater heat transfer tubes 4 a, and are arranged in multiple stages in a direction orthogonal to the axis of the reheater heat transfer tubes 27. ing. At the inlet and outlet of the reheater 25, a reheater inlet header 28 and a reheater outlet header 29 are arranged horizontally and in a direction orthogonal to the axis of the reheater heat transfer tube 27.

A second superheater 2b is arranged downstream of the reheater 25 in the flow direction of the exhaust gas G.
The superheater 2b includes a second superheater heat transfer tube 4b having U-shaped bend tubes 3b, 3b, 3b. The second superheater heat transfer tube 4b is arranged horizontally and in a direction orthogonal to the axis of the reheater heat transfer tube 27, and the second superheater heat transfer tube 4b is provided.
They are arranged in multiple stages in the direction orthogonal to the axis of b. Second
A second superheater inlet header 5b and a second superheater outlet header 6b are arranged at the inlet and the outlet of the superheater heat transfer tube 4b in a horizontal direction and in a direction orthogonal to the axis of the second superheater heat transfer tube 4b. Has been done.

An evaporator 7 is arranged downstream of the second superheater 2b in the flow direction of the exhaust gas G, and the evaporator 7 is provided with an evaporator heat transfer tube 8. This evaporator heat transfer tube 8
Are arranged horizontally and in a direction orthogonal to the second superheater heat transfer tube 4b, and are arranged in multiple stages in a direction orthogonal to the axis of the evaporator heat transfer tube 8. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the axis of the evaporator heat transfer tube 8.

A economizer 11 is arranged on the downstream side of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the axis of the evaporator heat transfer tubes 8, and are arranged in multiple stages in a direction orthogonal to the axis of the economizer heat transfer tubes 13. At the inlet and outlet of the economizer heat transfer tube 13, a economizer economizer header 14 and an economizer economizer outlet header 15 are arranged horizontally and in a direction orthogonal to the axis of the economizer heat exchanger tube 13. There is.

As described above, the first superheater heat transfer tube 4
a, the reheater heat transfer tube 27, the second superheater heat transfer tube 4b, the evaporator heat transfer tube 8, and the economizer heat transfer tube 13 are arranged such that their arrangement directions are alternately changed toward the flow direction of the exhaust gas G. Since they are arranged, the exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 is agitated by passing through the heat transfer tubes 4a, 27, 4b, 8 and 13 which are arranged so as to alternately change their directions. The temperature distribution and velocity distribution of the exhaust gas G flowing inside the exhaust heat recovery heat exchanger 1 are made uniform. Therefore, the first
The heat transfer performance in the superheater 2a, the reheater 25, the second superheater 2b, the evaporator 7 and the economizer 11 is improved, and superheated steam can be appropriately generated.

Twelfth Embodiment Next, a twelfth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 25 and 26. In addition,
FIG. 25 is a front view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 26 is a side view of the same.

In FIGS. 25 and 26, reference numeral 1 denotes a vertical type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from below. Inside the exhaust heat recovery heat exchanger body 1, a first reheater 25a is arranged at the most upstream portion in the flow direction of the exhaust gas G.
a is a first having U-shaped bend pipes 26a, 26a, 26a
The reheater heat transfer tube 27a is provided. The first reheater heat transfer tubes 27a are arranged in the horizontal direction and are arranged in multiple stages in a direction orthogonal to the axis of the heat transfer tube. A first reheater inlet header 28a and a first reheater outlet header 29a are provided at the inlet and outlet of the first reheater 25a in a horizontal direction and orthogonal to the axis of the first reheater heat transfer tube 27a. It is arranged in the direction to.

A superheater 2 is arranged downstream of the first reheater 25a in the flow direction of the exhaust gas G, and the superheater 2 includes a superheater heat transfer tube 4 having U-shaped bend tubes 3 and 3. I have it. This superheater heat transfer tube 4 is horizontally and
It is arranged in a direction orthogonal to the reheater heat transfer tube 27a, and is arranged in multiple stages in a direction orthogonal to the axis of the superheater heat transfer tube 4. At the inlet and outlet of the superheater heat transfer tube 4,
The superheater inlet header 5 and the superheater outlet header 6 are arranged horizontally and in a direction orthogonal to the superheater heat transfer tube 4.

A second reheater 25b is arranged downstream of the superheater 2 in the flow direction of the exhaust gas G.
The reheater 25b includes a second reheater heat transfer tube 27b having U-shaped bend tubes 26b, 26b, 26b. This second
The reheater heat transfer tube 27b is arranged horizontally and in the superheater heat transfer tube 4
The second superheater heat transfer pipes 27b are arranged in a multi-stage manner in a direction orthogonal to the axis of the second superheater heat transfer tube 27b. A second reheater inlet header 28b and a second reheater outlet header 29b are provided at the inlet and outlet of the second reheater 25b.
Are arranged in a horizontal direction and in a direction orthogonal to the second reheater heat transfer tube 27b.

An evaporator 7 is arranged downstream of the second reheater 25b in the flow direction of the exhaust gas G, and the evaporator 7 is equipped with an evaporator heat transfer tube 8. The evaporator heat transfer tubes 8 are provided horizontally and in a direction orthogonal to the second reheater heat transfer tubes 27b, and are arranged in multiple stages in a direction orthogonal to the axis of the evaporator heat transfer tubes 8. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the evaporator heat transfer tube 8.

A economizer 11 is arranged downstream of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the evaporator heat transfer tubes 8, and are arranged in multiple stages in a direction orthogonal to the axis of the economizer heat transfer tubes 13. At the inlet and outlet of the economizer heat transfer tube 13, a economizer inlet header 14 and an economizer outlet header 15 are provided.
Are arranged horizontally and in a direction orthogonal to the economizer heat transfer tube 13.

As described above, the first reheater heat transfer tube 27
a, the superheater heat transfer tube 4, the second reheater heat transfer tube 27b, the evaporator heat transfer tube 8, and the economizer heat transfer tube 13 are arranged such that their arrangement directions alternately change toward the flow direction of the exhaust gas G. Since they are arranged, the exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 is agitated by passing through the heat transfer tubes 27a, 4, 27b, 8 and 13 which are arranged so that their directions are alternately changed. Of the exhaust gas G that is generated and flows inside the exhaust heat recovery heat exchanger 1
The temperature distribution and the velocity distribution of are uniformed. Therefore, the heat transfer performance in the first reheater 25a, the superheater 2, the second reheater 25b, the evaporator 7, and the economizer 11 is improved, and superheated steam can be appropriately generated.

Thirteenth Embodiment Next, a thirteenth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIGS. 27 and 28. In addition,
FIG. 27 is a front view showing a schematic configuration of the exhaust heat recovery heat exchanger according to the present embodiment, and FIG. 28 is a side view of the same.

In FIGS. 27 and 28, reference numeral 1 indicates a vertical type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas from a gas turbine (not shown) is provided inside the exhaust heat recovery heat exchanger main body 1. G is supplied from the lower side in the figure. Inside the exhaust heat recovery heat exchanger main body 1, a first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G.
The a includes a first superheater heat transfer tube 4a having U-shaped bend tubes 3a and 3a. The first superheater heat transfer tubes 4a are arranged in the horizontal direction and are arranged in multiple stages in a direction orthogonal to the axis of the heat transfer tube. The first superheater inlet header 5a and the first superheater outlet header 6a are arranged at the inlet and the outlet of the first superheater heat transfer tube 4a in a horizontal direction and in a direction orthogonal to the first superheater heat transfer tube 4a. Has been done.

A first reheater 25a is disposed downstream of the first superheater 2a in the flow direction of the exhaust gas G, and the first reheater 25a includes U-shaped bend pipes 26a, 26a, 2b.
It is provided with a first reheater heat transfer tube 27a having 6a. The first reheater heat transfer tubes 27a are arranged horizontally and in a direction orthogonal to the first superheater heat transfer tubes 4a, and are arranged in multiple stages in a direction orthogonal to the axis of the first reheater heat transfer tubes 27a. It is set up. A first reheater inlet header 28a and a first reheater outlet header 29a are provided horizontally and at the inlet and outlet of the first reheater 25a.
Are arranged in a direction orthogonal to.

A second superheater 2b is arranged downstream of the first reheater 25a in the flow direction of the exhaust gas G, and the second superheater 2b has a U-shaped bend pipe 3b, 3b. The superheater heat transfer tube 4b is provided. The second superheater heat transfer tube 4b is arranged horizontally and in a direction orthogonal to the first reheater heat transfer tube 27a, and at the same time, the second superheater heat transfer tube 4b is provided.
It is arranged in multiple stages in a direction orthogonal to b. A second superheater inlet header 5b and a second superheater outlet header 6b are arranged at the inlet and the outlet of the second superheater heat transfer tube 4b in a horizontal direction and in a direction orthogonal to the second superheater heat transfer tube 4b. Has been done.

A second reheater 25b is arranged downstream of the second superheater 2b in the flow direction of the exhaust gas G, and the second reheater 25b is a U-shaped bend pipe 26b, 26b, 2b.
The second reheater heat transfer tube 27b having 6b is provided. The second reheater heat transfer tubes 27b are arranged horizontally and in a direction orthogonal to the second heat sensitive heat transfer tubes 4b, and are arranged in multiple stages in a direction orthogonal to the axis of the second reheater heat transfer tubes 27b. It is set up. A second reheater inlet header 28b and a second reheater outlet header 29b are horizontally and at the inlet and outlet of the second reheater 25b, respectively.
Are arranged in a direction orthogonal to.

An evaporator 7 is arranged downstream of the second reheater 25b in the flow direction of the exhaust gas G, and the evaporator 7 is provided with an evaporator heat transfer tube 8. The evaporator heat transfer tubes 8 are arranged horizontally and in a direction orthogonal to the second reheater heat transfer tubes 27b, and are arranged in multiple stages in a direction orthogonal to the axis of the evaporator heat transfer tubes 8. At the inlet and outlet of the evaporator 7, an evaporator inlet header 9 and an evaporator outlet header 10 are arranged horizontally and in a direction orthogonal to the evaporator heat transfer tube 8.

[0124] A economizer 11 is arranged downstream of the evaporator 7 in the flow direction of the exhaust gas G.
Is equipped with a economizer heat transfer tube 13 having U-shaped bend tubes 12, 12, 12. The economizer heat transfer tubes 13 are arranged horizontally and in a direction orthogonal to the evaporator heat transfer tubes 8 and are arranged in multiple stages in a direction orthogonal to the economizer heat transfer tubes 13. At the inlet and outlet of the economizer heat transfer tube 13,
The economizer inlet header 14 and the economizer outlet header 15 are arranged horizontally and in a direction orthogonal to the axis of the economizer heat transfer tube 13.

Thus, the first superheater heat transfer tube 4a and the first superheater heat transfer tube 4a
Reheater heat transfer tube 27a, second superheater heat transfer tube 4b, second reheater heat transfer tube 27b, evaporator heat transfer tube 8, charcoal saver heat transfer tube 13
Are arranged so that their arrangement direction alternates toward the flow direction of the exhaust gas G, so that the exhaust gas G introduced into the exhaust heat recovery heat exchanger 1 changes its direction alternately. Each heat transfer tube 4a, 27a, 4b, 27 arranged
The temperature distribution and velocity distribution of the exhaust gas G that is agitated by passing through b, 8 and 13 and flows inside the exhaust heat recovery heat exchanger 1 are made uniform. Therefore, the first superheater 2a, the first reheater 25a, the second superheater 2b, the second reheater 25b,
The heat transfer performance in the evaporator 7 and the economizer 11 is improved, and superheated steam can be appropriately generated.

Fourteenth Embodiment Next, a fourteenth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG. Note that FIG. 29 is a perspective view showing a schematic configuration of a main part of the exhaust heat recovery heat exchanger according to the present embodiment.

In FIG. 29, reference numeral 1 denotes a vertical type natural circulation type exhaust heat recovery heat exchanger main body, and exhaust gas G from a gas turbine (not shown) is supplied into the exhaust heat recovery heat exchanger main body 1. To be done. Inside the exhaust heat recovery heat exchanger body 1,
The first superheater 2a is arranged at the most upstream portion in the flow direction of the exhaust gas G, and the first superheater 2a is the first superheater heat transfer tube 4
a. The reheater 2 is provided downstream of the first superheater 2a.
5 are arranged, and this reheater 25 is a reheater heat transfer tube 2
7 is provided. The second superheater 2 is provided downstream of the reheater 25.
b is arranged, and the second superheater 2b includes a second superheater heat transfer tube 4b. An evaporator (not shown) is arranged downstream of the second superheater 2b, and a economizer (not shown) is arranged further downstream thereof.

Then, the first superheater heat transfer tube 4a is arranged to be inclined with respect to the body barrel 40 in the horizontal plane. Further, the reheater heat transfer tube 27 is arranged in a horizontal plane with an inclination in a direction opposite to the first superheater heat transfer tube 4a with respect to the main body 40. Further, the second superheater heat transfer tube 4b
Is the direction opposite to the reheater heat transfer tube 27 in the horizontal plane,
That is, the first superheater heat transfer tubes 4a are arranged so as to be inclined in the same direction.

As described above, according to the present embodiment, the first superheater heat transfer tubes 4a, the reheater heat transfer tubes 27, and the second superheater heat transfer tubes 4b are alternately arranged so as to be inclined in opposite directions.
The exhaust gas G flowing inside the exhaust heat recovery heat exchanger main body 1 is agitated by the heat transfer tubes 4a, 27, 4b that are alternately inclined in opposite directions, and the temperature distribution and the velocity distribution thereof are made uniform, and the exhaust heat recovery heat The heat transfer performance of the exchanger is improved.

Fifteenth Embodiment Next, a fifteenth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG. In the following description, the superheater 2 will be described as an example, but the same configuration can be applied to not only the superheater 2 but also a reheater, an evaporator, and a economizer, and all of them. Or, it can be applied to a part.

FIG. 30 shows the superheater 2 provided inside the vertical type natural circulation type exhaust heat recovery heat exchanger according to this embodiment. Inside the superheater 2, the superheater arranged horizontally is provided. Heater first inlet header 5c and superheater first outlet header 6c
Are juxtaposed. Further, inside the superheater 2, a superheater second inlet header 5d and a superheater second outlet header 6d which are horizontally arranged are provided, and the superheater first inlet and outlet header 5 are provided.
They are arranged in parallel vertically so as to face c and 6c.

Superheater first inlet and outlet headers 5c, 6c
Is provided with a superheater first heat transfer pipe 4c having U-shaped bend pipes 3c, 3c, 3c in a horizontal direction, and the superheater first heat transfer pipes 4c are arranged in multiple stages in a direction orthogonal to the axis thereof. There is.

On the other hand, the superheater second inlet and outlet header 5
A plurality of superheater second heat transfer tubes 4d, 4d ... 4d having U-shaped bend tubes 3d, 3d, 3d are located in the gaps between the plurality of superheater first heat transfer tubes 4c, 4c ... 4c. Are arranged in such a manner. That is, the superheater first heat transfer tubes 4c and the superheater second heat transfer tubes 4d are alternately arranged in the horizontal direction.

As described above, in the present embodiment,
Since the superheater first heat transfer tubes 4c and the superheater second heat transfer tubes 4d are alternately arranged in the horizontal direction inside the superheater 2, the flow directions of the fluids flowing inside the heat transfer tubes 4c and 4d are opposed to each other. However, for this reason, the temperature distribution of the exhaust gas G is made uniform in the axial direction of the superheater first and second heat transfer tubes 4c and 4d.
By thus making the temperature distribution of the exhaust gas G uniform, the heat transfer performance in the exhaust heat recovery heat exchanger is significantly improved.

FIG. 31 shows a modified example of this embodiment. In this modified example, the U-shaped bend pipe 3c is provided between the superheater first inlet header 5c and the superheater first outlet header 6c. Outer heat exchanger heat transfer tubes 4 having an outer circumference and an inner circumference
c and 4c are connected in parallel in the same vertical plane, and similarly, a U-shaped bend pipe 3d is provided between the superheater second inlet header 5d and the superheater second outlet header 6d. Two superheater heat transfer tubes 4d and 4d on the periphery are connected in parallel in the same vertical plane. Also in this modification having such a configuration, the same effect as that of the above embodiment can be obtained.

Sixteenth Embodiment Next, a sixteenth embodiment of the exhaust heat recovery heat exchanger according to the present invention will be described with reference to FIG. In the following description, the superheater 2 will be described as an example, but the same configuration can be applied to not only the superheater 2 but also a reheater, an evaporator, and a economizer. Can be applied to all of
It can also be applied to some.

FIG. 32 is a side sectional view showing an outline of the superheater 2 arranged inside a vertical type natural circulation type exhaust heat recovery heat exchanger body (not shown). In FIG. The exhaust gas inlet side heat transfer tube of the superheater 2 is shown. Further, in FIG. 32, symbols P1 and P2 indicate horizontal pitches between the exhaust gas inlet side heat transfer tubes 4e. As can be seen from FIG. 32, the horizontal pitch between the exhaust gas inlet side heat transfer tubes 4e is larger at the downstream pitch P2 than at the upstream pitch P1 in the flow direction of the exhaust gas G.

As described above, according to this embodiment, the superheater 2
Since the horizontal pitch of the heat transfer tube is small on the upstream side in the flow direction of the exhaust gas G and large on the downstream side, the exhaust gas G causes a pressure loss when passing through the heat transfer tube on the upstream side with a small pitch. Since the gas is agitated, the temperature distribution and velocity distribution of the exhaust gas G are made uniform, and the heat transfer performance of the exhaust heat recovery heat exchanger is improved.

[0139]

As described above, according to the present invention, since at least one heat transfer tube other than the heat transfer tube of the evaporator is arranged in a direction different from that of the heat transfer tube of the evaporator, the inside of the exhaust heat recovery heat exchanger is The exhaust gas flowing in the exhaust gas is agitated and its temperature distribution and velocity distribution are made uniform, and the heat transfer performance in the exhaust heat recovery heat exchanger is greatly improved.

[Brief description of drawings]

FIG. 1 is a side view showing a schematic configuration of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a first embodiment of the present invention.

FIG. 2 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG.

FIG. 3 is a side view showing a schematic configuration of a modified example of the horizontal type natural circulation type exhaust heat recovery heat exchanger of the first embodiment of the present invention.

FIG. 4 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG.

FIG. 5 is a side view showing a schematic configuration of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a second embodiment of the present invention.

6 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG.

FIG. 7 is a side view showing a schematic configuration of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a third embodiment of the present invention.

8 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 7. FIG.

FIG. 9 is a side view showing a schematic configuration of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a fourth embodiment of the present invention.

10 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 9. FIG.

FIG. 11 is a side view showing a schematic configuration of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a fifth embodiment of the present invention.

12 is a plan view of the horizontal type natural circulation type exhaust heat recovery heat exchanger shown in FIG.

FIG. 13 is a perspective view showing a schematic configuration of a main part of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a sixth embodiment of the present invention.

FIG. 14 is a perspective view showing a schematic configuration of a superheater of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to a seventh embodiment of the present invention.

FIG. 15 is a perspective view showing a schematic configuration of a modified example of the superheater of the horizontal type natural circulation type exhaust heat recovery heat exchanger of the seventh embodiment of the present invention.

FIG. 16 is a view showing a schematic configuration of a superheater of a horizontal type natural circulation type exhaust heat recovery heat exchanger according to an eighth embodiment of the present invention.

FIG. 17 is a front view showing a schematic configuration of a vertical type natural circulation type exhaust heat recovery heat exchanger according to a ninth embodiment of the present invention.

FIG. 18 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 17.

FIG. 19 is a front view showing a schematic configuration of a modification of the vertical type natural circulation type exhaust heat recovery heat exchanger of the ninth embodiment of the present invention.

20 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG.

FIG. 21 is a front view showing a schematic configuration of a vertical type natural circulation type exhaust heat recovery heat exchanger according to a tenth embodiment of the present invention.

22 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 21. FIG.

FIG. 23 is a front view showing a schematic configuration of a vertical type natural circulation type exhaust heat recovery heat exchanger according to an eleventh embodiment of the present invention.

FIG. 24 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 23.

FIG. 25 is a front view showing a schematic configuration of a vertical type natural circulation type exhaust heat recovery heat exchanger according to a twelfth embodiment of the present invention.

FIG. 26 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 25.

FIG. 27 is a front view showing a schematic configuration of a vertical type natural circulation type exhaust heat recovery heat exchanger according to a thirteenth embodiment of the present invention.

28 is a side view of the vertical type natural circulation type exhaust heat recovery heat exchanger shown in FIG. 27. FIG.

FIG. 29 is a perspective view showing a schematic configuration of a main part of a vertical type natural circulation type exhaust heat recovery heat exchanger of a fourteenth embodiment of the present invention.

FIG. 30 is a perspective view showing a schematic configuration of a superheater of a vertical type natural circulation type exhaust heat recovery heat exchanger of a fifteenth embodiment of the present invention.

FIG. 31 is a perspective view showing a modified example of the same embodiment.

FIG. 32 is a side sectional view showing a schematic configuration of a superheater of a vertical type natural circulation type exhaust heat recovery heat exchanger of a sixteenth embodiment of the present invention.

FIG. 33 is a side view showing a schematic configuration of a conventional horizontal type natural circulation type exhaust heat recovery heat exchanger.

[Explanation of symbols]

 1 Exhaust heat recovery heat exchanger 2, 2a, 2b Superheater 4, 4a, 4b, 4c, 4d, 4e Superheater heat transfer tube 5, 5a, 5b, 5c, 5d Superheater inlet header 6, 6a, 6b, 6c, 6d Superheater outlet header 7 Evaporator 8 Evaporator heat transfer tube 9 Evaporator inlet header 10 Evaporator outlet header 11 Coal saver 13 Coal saver heat transfer tube 14 Coal saver inlet header 15 Coal saver outlet header 16 Water supply pipe 17 Water supply Pump 19 Steam drum 24 Intermediate header 25, 25a, 25b Reheater 27, 27a, 27b Reheater heat transfer tube 28, 28a, 28b Reheater inlet header 29, 29a, 29b Reheater outlet header G G exhaust gas P1, P2 Pitch between heat transfer tubes

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Masashi Tsutsui 2-4 Suehiro-cho, Tsurumi-ku, Yokohama-shi, Kanagawa Toshiba I-Tech Co., Ltd.

Claims (7)

[Claims] 1. A plurality of heat exchange means, which are sequentially arranged along a flow direction of exhaust gas supplied in a horizontal direction and include at least an evaporator, and which are provided in each of the heat exchange means and are orthogonal to a flow direction of the exhaust gas. With each heat transfer tube arranged in the direction
In a horizontal exhaust heat recovery heat exchanger in which the heat transfer tubes of the evaporator are vertically arranged, at least one heat transfer tube other than the heat transfer tubes of the evaporator is arranged in a direction different from that of the heat transfer tube of the evaporator. Exhaust heat recovery heat exchanger characterized by having been performed. 2. A plurality of heat exchange means, which are sequentially arranged along the flow direction of the exhaust gas supplied upward and include at least an evaporator, and each of which is provided in each of the heat exchange means and arranged in the horizontal direction. In a vertical exhaust heat recovery heat exchanger having a heat transfer tube, at least one of the heat transfer tubes other than the heat transfer tube of the evaporator is arranged in a direction different from that of the heat transfer tube of the evaporator. Exhaust heat recovery heat exchanger. 3. The exhaust heat recovery heat exchanger according to claim 1, wherein the at least one heat transfer tube is arranged in a direction orthogonal to the heat transfer tube of the evaporator. 4. The exhaust heat recovery heat exchanger according to claim 1, wherein each of the heat transfer tubes is arranged in a direction different from that of the other adjacent heat transfer tubes. . 5. The exhaust heat recovery heat exchanger according to claim 4, wherein each of the heat transfer tubes is arranged in a direction orthogonal to the other adjacent heat transfer tubes. 6. At least one said heat exchange means other than said evaporator comprises a first inlet and outlet header, and a second inlet arranged so as to face said first inlet and outlet header. An outlet header, a plurality of first heat transfer pipes connected to the first inlet and outlet headers, and a plurality of second heat transfer pipes connected to the second inlet and outlet headers, the header 6. The exhaust heat recovery heat according to claim 1, wherein the first heat transfer tubes and the second heat transfer tubes are alternately arranged along the axial direction of Exchanger. 7. The at least one heat exchanging means comprises a plurality of heat transfer tubes, wherein the plurality of heat transfer tubes have a space between upstream heat transfer tubes in a flow direction of exhaust gas, and a space between the heat transfer tubes on a downstream side in a flow direction of exhaust gas. The exhaust heat recovery heat exchanger according to any one of claims 1 to 6, which is smaller than a space between the heat pipes.