KR20190005920A - Heat exchangers and vessels - Google Patents

Abstract

A heat exchanger and a ship with improved thermal efficiency are provided. The heat exchanger 40 includes a tubular casing 41 in which the working fluid flows from the upstream side to the downstream side, and a heat exchanger 40 which is provided inside the casing 41 and has a diameter A plurality of heat transfer tube layers 46 having a plurality of heat transfer tubes 47 arranged at equal pitches P in the direction of flow and a plurality of heat transfer tube blocks 43 arranged at intervals in the flow direction, And a downstream side guide portion 50 provided on the downstream side of the heat transfer pipe block 43 and protruding from the inner surface S of the casing 41 and having a first guide surface 51 directed to the upstream side .

Description

Heat exchangers and vessels

The present invention relates to a heat exchanger and a ship.

There is an arrangement recovery device that has a heat exchanger that performs heat exchange with exhaust gas and the like and that recovers the heat of the exhaust gas and the like. The array recovery device is mounted on a power generation facility or a ship. The exhaust heat recovery apparatus has a heat exchanger that performs heat exchange between exhaust gas and heat medium (for example, water). The heat exchanger includes a plurality of heat transfer tubes through which the heat flows, and a casing that covers the heat transfer tubes from the outside. The heat exchanger is disposed in a flue through which the exhaust gas flows, thereby performing heat exchange between the exhaust gas and the heat through the heat transfer tube. In such a heat exchanger, foreign matter such as soot and lubricant contained in the exhaust gas may adhere to the surface of the heat transfer pipe. Here, Patent Document 1 discloses a heat exchanger including an arrangement recovery device having a heat transfer pipe panel that collects the heat of fluid flowing between the casing and the heat transfer pipe and transfers the heat to the heat transfer pipe.

Patent Document 1: Japanese Patent Publication No. 5514690

Here, in the heat exchanger including a plurality of heat transfer tubes, a gap is formed between the heat transfer tube and the casing. The flow resistance against the exhaust gas in this gap is smaller than the flow resistance in the region between the plurality of heat transfer tubes. As a result, the exhaust gas flows into the gap between the heat transfer pipe and the casing, thereby forming a flow-out flow.

The heat exchanger described in Patent Document 1 is an apparatus for recovering the arrangement and can recover the heat of the steam flowing through the gap between the inner surface of the casing and the heat transfer tube. However, in the apparatus described in Patent Document 1, since the heat transfer pipe panel is mounted on the heat transfer pipe itself, a large space is still formed between the inner surface of the casing and the heat transfer pipe. As a result, there is a possibility that sufficient heat recovery can not be performed. In addition, since the heat transfer pipe panel is provided, the structure becomes complicated and large. This makes it difficult to adopt the structure to vessels with particularly strong demand for downsizing of onboard equipment. That is, the apparatus described in Patent Document 1 still has room for improvement.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a heat exchanger and a ship having improved heat exchange performance.

The heat exchanger of the present invention comprises: a tubular casing in which a working fluid flows from an upstream side to a downstream side; a plurality of heat exchangers arranged inside the casing and arranged at equal pitches in the flow direction of the working fluid A plurality of heat transfer pipe blocks formed by stacking a plurality of heat transfer pipe layers having heat transfer tubes in a direction orthogonal to the flow direction and spaced apart in the flow direction; a plurality of heat transfer pipe blocks provided on the downstream side of the heat transfer pipe block, And a downstream-side guide portion having a first guide surface facing the upstream side.

According to this construction, since the first guide surface of the downstream-side guide portion becomes the flow resistance against the working fluid, the working fluid is guided by the first guide surface, and the region where the heat transfer pipe block, which is the region on the upstream side of the first guide surface, In a direction away from the inner surface of the casing. Thereby, the working fluid can be reduced in the gap formed between the heat conductive pipe block and the inner surface of the casing.

In the heat exchanger of the present invention, the first guide surface may overlap with the heat transfer pipe closest to the inner surface in the flow direction.

According to this configuration, the possibility that the working fluid flows into the gap between the heat conductive pipe block and the inner surface of the casing can be further reduced. In addition, the distance between the heat transfer pipe block and the inner surface of the casing can be made closer.

In the heat exchanger of the present invention, the first guide surface may be inclined with respect to the flow direction as viewed from the direction in which the heat transfer pipe extends.

According to this configuration, since the first guide surface is inclined with respect to the flow direction, the working fluid can be smoothly guided along the first guide surface. In other words, it is possible to reduce stagnation and stagnation in the flow of the working fluid leading to the accumulation of foreign matter such as soot or droplet of lubricant accompanying the working fluid.

In the heat exchanger of the present invention, the first guide surface may be curved in a direction away from the inner surface along the direction from the upstream side toward the downstream side.

According to this configuration, since the first guide surface is curved, the working fluid can be more smoothly guided along the first guide surface. In other words, the stagnation or stagnation of the flow of the working fluid leading to the accumulation of foreign matter such as soot or droplet of lubricant accompanying the working fluid can be further reduced.

In the heat exchanger of the present invention, the downstream-side guide portion may have a plate-like shape in which the region extending in the direction away from the inner surface does not change its thickness.

According to this configuration, the possibility that the working fluid flows into the gap between the heat conductive pipe block and the inner surface of the casing can be reduced. In addition to this, the downstream-side guide portion can be provided simply and inexpensively as compared with the case of the other complicated configuration.

In the heat exchanger of the present invention, the dimension of the downstream-side guide portion protruding from the inner surface may be not less than 1 times and not more than 3 times the pitch of the heat transfer tubes.

According to this construction, since the gap between the heat conductive pipe block and the inner surface of the casing can be sufficiently covered by the downstream-side guide portion, the working fluid flowing into the gap can be further reduced.

In the heat exchanger of the present invention, the distance between the first guide surface and the heat transfer pipe closest to the first guide surface may be 10 mm or more and 50 mm or less.

According to this configuration, heat exchange in the heat transfer tube can be performed more efficiently.

The heat exchanger of the present invention may further comprise an upstream guide provided on the upstream side of the heat transfer pipe block and projecting from the inner surface of the casing and having a second guide surface facing the upstream side.

According to this structure, the inflow of the working fluid from the upstream side to the gap between the heat conductive pipe block and the inner surface of the casing can be reduced.

The ship of the present invention includes the above-mentioned heat exchanger, a flue in which the heat exchanger is disposed, and a main engine that supplies exhaust gas to the flue.

According to this configuration, it is possible to provide a ship having a heat exchanger with improved efficiency.

According to the present invention, the efficiency of heat exchange can be improved.

1 is a schematic diagram showing a configuration of a ship according to a first embodiment of the present invention.
2 is a cross-sectional view of the heat exchanger of the exhaust heat collecting apparatus according to the first embodiment of the present invention.
3 is an enlarged cross-sectional view of the heat exchanger according to the first embodiment of the present invention.
4 is an enlarged sectional view showing a modified example of the heat exchanger according to the first embodiment of the present invention.
5 is an enlarged sectional view showing another modification of the heat exchanger according to the first embodiment of the present invention.
6 is an enlarged sectional view of a heat exchanger according to a second embodiment of the present invention.

[First Embodiment]

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In addition, the present invention is not limited by these embodiments, and in the case where there are a plurality of embodiments, the embodiments may be combined.

A first embodiment of the present invention will be described with reference to Figs. 1 to 3. Fig. As shown in FIG. 1, a ship 100 includes a ship 1, a diesel engine 11, and an array recovery device 10.

The hull 1 is a housing in which cargo and passengers can be mounted. The diesel engine 11 is a main engine. Further, the main engine may be an internal combustion engine other than the diesel engine 11. The diesel engine 11 generates power for driving the propeller shaft, for example, and exhausts the exhaust gas. In the present embodiment, heat is exhausted from the exhaust gas discharged from the diesel engine 11 of the ship 100 to the exhaust heat recovery apparatus 10, and the exhaust heat recovery apparatus 10 recovers the heat of the high temperature gas Is not particularly limited. That is, the array recovery apparatus 10 can be installed on the downstream side of a device for discharging a high-temperature gas such as a gas turbine, a boiler, or a fuel cell, and can recover heat of a high-temperature gas. The ship 100 may be provided with an exhaust gas treatment device for removing and reducing harmful substances of the exhaust gas on the downstream side of the exhaust heat collecting device 10.

The heat exchanger 40 performs heat exchange between the exhaust gas discharged from the diesel engine 11 and water as a fuel. The water heated by the heat exchange becomes superheated steam, and is used for driving another apparatus (not shown) such as a steam turbine.

Hereinafter, the detailed configuration of the heat exchanger 40 will be described with reference to Fig. The heat exchanger 40 has a casing 41 and a heat exchanger main body 42 as shown in Fig. The casing (41) is in the shape of a cylinder, and the exhaust gas flows from the upstream side toward the downstream side. In the following description, the direction in which the exhaust gas flows is referred to as "flow direction ". The casing 41 is part of an exhaust path through which the exhaust gas discharged from the diesel engine 11 flows. In the interior space of the casing 41, a heat exchanger main body 42 is provided.

The heat exchanger main body 42 includes a plurality of (two) heat transfer pipe blocks 43 arranged at intervals in the flow direction and a downstream side guide portion 43 for guiding exhaust gas (working fluid) around each heat transfer pipe block 43 (50). In the present embodiment, two heat transfer pipe blocks 43 are provided. However, the number of the heat transfer pipe blocks 43 is not limited to two, but may be three or more. In the following description, the heat transfer pipe block 43 located on the upstream side is referred to as a first heat transfer pipe block 44, and the heat transfer pipe block 43 located on the downstream side is referred to as a first heat transfer pipe block 44. [ 43 are referred to as a second heat conductive pipe block 45 to discriminate between them.

In the heat-transfer-tube block 43, a plurality of heat-transfer-tube layers 46 are laminated in the flow direction. The heat conductive pipe layer 46 has a plurality of heat conductive pipes 47 arranged at an equal pitch P in a direction orthogonal to the flow direction. Here, the pitch P of the heat transfer tubes 47 indicates the distance between the center points of the adjacent heat transfer tubes 47. Each of the heat conductive pipes 47 is formed by inverting a single tube continuously extending in the flow direction plural times with intervals in the flow direction. That is, the heat transfer tubes 47 are arranged over a plurality of heat transfer tube layers 46.

Each heat transfer tube 47 has a circular cross-sectional shape and extends in a direction perpendicular to the flow direction. Water in the heat transfer pipe (47) flows inside from the downstream side in the flow direction toward the upstream side. In the heat transfer tubes 47 between the adjoining heat transfer tube layers 46, the direction in which the water flows therein is opposite to each other.

The heat conductive pipe blocks 43 of the present embodiment are arranged in a zigzag form when viewed from the direction orthogonal to the flow direction and from the direction in which the heat conductive pipes 47 extend in one heat conductive pipe layer. In other words, in the heat conductive pipe layer 46 adjacent to each other, a plurality of heat conductive pipes 47 are disposed at different positions in the direction orthogonal to the flow direction. Further, the heat transfer pipe block 43 may be arranged in a lattice shape instead of the zigzag shape.

The heat exchanger 40 has a gap G1 formed between the outer peripheral edge of the heat transfer pipe block 43 and the inner surface S of the casing 41. [ The outer peripheral edge of the heat conductive pipe block 43 is an edge portion formed by an outer peripheral surface of a plurality of heat conductive pipes 47 located at the outermost peripheral side of the heat conductive pipe block 43.

The downstream side guide portion 50 is provided in the region on the downstream side of the heat transfer tube block 43 on the inner surface S of the casing 41. [ Specifically, the downstream-side guide portion 50 is in the form of a plate projecting from the inner surface S of the casing 41 in the direction orthogonal to the inner surface S. The downstream side guide portion 50 is formed such that the region extending in the direction away from the inner surface S does not change in thickness. In other words, the thickness of the downstream-side guide portion 50 is constant. The downstream side guide portion 50 can be provided by fixing the plate member to the inner surface S of the casing 41 by welding or the like. The downstream-side guide portion 50 may have a configuration in which the cross-section is L-shaped, and one side of the L-shaped portion faces the casing 41 and one side thereof protrudes from the casing 41. The downstream-side guide portion 50 may have a structure in which the plate-like member is supported by a stay.

The downstream side guide portion 50 is provided at the downstream side guide portion 50 so that the dimension of the projecting height, that is, the distance between the end portion of the downstream side guide portion 50 remote from the inner surface S and the inner surface S, Is not less than 1 and not more than 3 times the pitch (P). It is more preferable that the projection height of the downstream side guide portion 50 is not less than one time and not more than twice the pitch P of the heat transfer tubes 47. [ It is most preferable that the projection height of the downstream side guide portion 50 is one time the pitch P of the heat transfer tubes 47. [ The heat exchanger (40) can make the gap (G1) narrower than the pitch (P), thereby increasing the heat exchange efficiency. The downstream side guide portion 50 can have a shape overlapping the heat transfer tube 47 closest to the inner surface S of the casing 41 when viewed from the direction of flow by setting the projecting height in the above range. The first guide surface 51 which faces the upstream side among the both surfaces of the downstream side guide portion 50 faces the gap G1 and the heat transfer tube block 43 from the downstream side in the flow direction. In other words, the gap G1 is blocked by the downstream-side guide portion 50 in the flow direction. The first guide surface 51 is a surface spreading in a plane orthogonal to the inner surface S of the casing 41.

The distance between the first guide surface 51 and the heat transfer pipe 47 closest to the first guide surface 51 is preferably 10 mm or more and 50 mm or less, more preferably 10 mm or more and 30 mm or less, Most preferably 10 mm.

Hereinafter, the operation of the heat exchanger 40 according to the first embodiment will be described. The exhaust gas discharged from the diesel engine 11 flows into the heat exchanger 40. The exhaust gas flowing into the heat exchanger (40) comes into contact with the heat transfer pipe block (43). The exhaust gas is heat-exchanged with water as the heat that flows through the heat transfer pipe 47, becomes low temperature, and is then discharged to the atmosphere.

The downstream side guide portion 50 regulates and guides the flow of the exhaust gas, and reduces the amount of the exhaust gas flowing into the gap G1. The downstream side guide portion 50 will be described with reference to Fig. The downstream side guide portion 50 becomes the flow resistance against the exhaust gas so that the periphery of the first guide surface 51 which is the downstream side portion of the first heat transfer tube block 44 and which is in the vicinity of the inner surface S, It becomes a region where the gas does not easily flow. Thus, the exhaust gas flowing in the vicinity of the inner surface (S) or in the gap (G1) flows in a direction away from the inner surface (S) while flowing through the region in which the first heat transfer pipe block (44) is disposed.

Specifically, as shown in Fig. 3, the exhaust gas flowing through the gap G1 does not form a flow (broken line arrow F1) along the inner surface S, but flows from the downstream side of the first heat transfer pipe block 44 And is changed in direction by the first guide surface 51 of the downstream-side guide portion 50. As a result, the exhaust gas flows along the first guide surface 51 in a direction away from the inner surface S as indicated by an arrow F2. Thereafter, the exhaust gas flows along the flow (arrow F3) of the exhaust gas flowing through the portion other than the gap G1 through the first heat transfer pipe block 44. [ As a result, the amount of exhaust gas flowing is not more on the side of the gap G1 but on the side of the arrow F3 close to the center of the casing 41. [ Therefore, since more exhaust gas can be brought into contact with the first heat conductive pipe block 44, the heat exchange efficiency can be improved. In addition, the exhaust gas guided by the downstream-side guide portion 50 flows into the second heat transfer pipe block 45 located on the downstream side from the position apart from the inner surface S of the casing 41. [ In other words, since the downstream side guide portion 50 is provided on the downstream side of the first heat conductive pipe block 44, the exhaust gas flowing into the gap G2 between the second heat transfer pipe block 45 and the casing 41 The inflow amount is reduced. Therefore, the efficiency of the heat exchanger (40) can be improved as compared with a configuration in which the downstream side guide portion (50) is not provided.

In the heat exchanger 40 described above, the first guide surface 51 overlaps with the heat transfer pipe 47 closest to the inner surface S in the flow direction. According to this configuration, the gap G1 can be sufficiently covered from the downstream side by the downstream-side guide portion 50. [ Therefore, the flow resistance against the exhaust gas by the downstream-side guide portion 50 can be sufficiently secured and the exhaust gas can be supplied to the gap G1 between the heat transfer pipe block 43 and the inner surface S of the casing 41 The possibility of flow can be further reduced.

In addition, by providing the downstream side guide portion 50, the distance between the heat transfer pipe block 43 and the inner surface S of the casing 41 can be reduced. In other words, when the downstream side guide portion 50 is provided, the dimension of the heat transfer tube block 43 (that is, the number of the heat transfer tube layers 46) ) Can be increased. Thus, the efficiency of the heat exchanger 40 can be further improved.

In the heat exchanger 40 described above, the downstream-side guide portion 50 has a plate shape with a constant thickness. According to this configuration, the downstream-side guide portion 50 can be provided simply and inexpensively as compared with the case of the other complicated configuration.

In addition, in the above-described heat exchanger 40, the dimension (i.e., the projecting height) that the downstream-side guide portion 50 projects from the inner surface S is equal to or larger than the pitch P of the heat transfer tubes 47 3 times or less. The distance between the first guide surface 51 and the heat transfer pipe 47 closest to the first guide surface 51 is 10 mm or more and 50 mm or less. This configuration further reduces the possibility that the exhaust gas flows into the gap G1 between the heat transfer pipe block 43 and the inner surface S of the casing 41 and sufficiently improves the efficiency of the heat exchanger 40 .

The first embodiment of the present invention has been described above. In addition, various modifications can be made to the above-described constitution without departing from the gist of the present invention.

For example, in the first embodiment, the configuration in which the first guide surface 51 of the downstream-side guide portion 50 is a surface orthogonal to the inner surface S of the casing 41 has been described. However, the configuration of the first guide surface 51 is not limited to this, and a configuration as shown in Fig. 4 may be employed. Specifically, in the example of Fig. 4, the first guide surface 52 is inclined with respect to the flow direction of the exhaust gas. In other words, the first guide surface 52 extends gradually from the inner surface S toward the downstream side from the upstream side.

According to this configuration, since the first guide surface 52 is inclined with respect to the flow direction, the exhaust gas can be smoothly guided along the first guide surface 52. Therefore, the possibility of stagnation or stagnation of the flow of exhaust gas can be reduced.

The first guide surface 51 may have a structure as shown in Fig. Specifically, in the example of Fig. 5, the first guide surface 53 gradually curves toward the direction away from the inner surface S as it goes from the upstream side toward the downstream side.

With this configuration, since the first guide surface 51 is curved, the exhaust gas can be more smoothly guided along the first guide surface 53.

[Second Embodiment]

Next, a second embodiment of the present invention will be described with reference to Fig. In the present embodiment, the upstream side guide portion 60 is further provided on the upstream side of the second heat transfer tube block 45. The upstream side guide portion 60 is provided in the region on the upstream side of the heat transfer tube block 43 on the inner surface S of the casing 41. [ More specifically, the upstream-side guide portion 60 is in the shape of a plate projecting from the inner surface S of the casing 41 in the direction orthogonal to the inner surface S. The upstream side guide portion 60 is formed such that the region extending in the direction away from the inner surface S does not change in thickness. In other words, the thickness of the upstream-side guide portion 60 is constant. The upstream side guide portion 60 can be provided by fixing the plate material to the inner surface S of the casing 41 by welding or the like, like the downstream side guide portion 50. The upstream-side guide portion 60 may have a configuration in which the cross-section is L-shaped, and one side of the L-shaped portion may protrude from the casing 41. The upstream-side guide portion 60 may have a structure in which the plate-like member is supported by a stay.

The upstream side guide portion 60 is formed so that the dimension of the projecting height, that is, the distance between the end portion of the upstream side guide portion 60 which is separated from the inner surface S and the inner surface S, Is not less than 1 and not more than 3 times the pitch (P). It is more preferable that the projection height of the upstream side guide portion 60 is not less than one time and not more than twice the pitch P of the heat transfer tubes 47. [ It is most preferable that the projection height of the upstream side guide portion 60 is one times the pitch P of the heat transfer tubes 47. [ The heat exchanger 40 can increase the efficiency of heat exchange by making the gap G2 narrower than the pitch P. [ The upstream side guide portion 60 can have a shape overlapping the heat transfer tube 47 closest to the inner surface S of the casing 41 when viewed from the direction of flow by setting the projection height to the above range. As a result, the second guide surface 61, which is the surface facing the upstream side of both surfaces of the upstream side guide portion 60, faces the gap G1 and the second heat transfer tube block 45 from the upstream side in the flow direction. In other words, the gap G1 is blocked by the upstream-side guide portion 60 in the flow direction. The second guide surface 61 is a surface spreading in a plane orthogonal to the inner surface S of the casing 41.

The distance between the second guide surface 61 and the heat transfer pipe 47 closest to the second guide surface 61 is preferably 10 mm or more and 50 mm or less. The distance between the second guide surface 61 and the heat transfer pipe 47 closest to the second guide surface 61 is more preferably 10 mm or more and 30 mm or less. It is most preferable that the distance between the second guide surface 61 and the heat transfer pipe 47 closest to the second guide surface 61 is 10 mm.

With this configuration, the working fluid flowing from the upstream side can be reduced with respect to the gap G2 between the second heat transfer pipe block 45 and the inner surface S of the casing 41. [ More specifically, the exhaust gas is guided in the direction away from the inner surface S by the downstream side guide portion 50 provided on the downstream side of the first heat transfer pipe block 44, and then the exhaust gas is guided to the first heat transfer pipe block 44 Flows into the flow of the exhaust gas flowing through the portion of the exhaust gas flowing through the portion other than the gap G1, and flows toward the downstream side. The exhaust gas guided by the downstream side guide portion 50 can be exhausted from the position separated from the inner surface S of the casing 41 by the provision of the upstream side guide portion 60, And then flows into the heat transfer pipe block 45. In other words, since the downstream side guide portion 50 is provided on the downstream side of the first heat conductive pipe block 44 and the upstream side guide portion 60 is provided on the upstream side of the second heat conductive pipe block 45, It is possible to further reduce the inflow amount of the exhaust gas to the gap G2 between the two heat transfer pipe blocks 45 and the casing 41. [ Thus, the efficiency of the heat exchanger 40 can be further improved.

The second embodiment of the present invention has been described above. In addition, various modifications can be made to the above-described constitution without departing from the gist of the present invention.

For example, in the second embodiment, the configuration in which the second guide surface 61 of the upstream-side guide portion 60 is a surface orthogonal to the inner surface S of the casing 41 has been described. However, the configuration of the second guide surface 61 is not limited to this, and the configuration as shown in Fig. 4 or 5 can be adopted similarly to the downstream guide portion 50. [ Concretely, it is possible to employ a configuration in which the second guide surface 61 is inclined with respect to the flow direction, or a configuration in which the second guide surface 61 is curved.

The object to be applied to the heat exchanger 40 is not limited to the exhaust heat collecting apparatus 10. For example, the heat exchanger 40 may be a superheater of an exhaust heat recovery boiler, an evaporator,

100 vessels
1 Hull
10 Array recovery device
11 Diesel engine
40 Heat Exchanger
41 casing
42 Heat exchanger body
43 Heat Transfer Pipe Block
44 First heat transfer pipe block
45 Second heat transfer pipe block
50 downstream side guide portion
46 Heat pipe layer
47 Heat pipe
51 first guide surface
52 first guide surface
53 first guide surface
60 upstream side guide portion
61 second guide surface
G1 clearance
G2 clearance
P pitch
S inner surface

Claims (9)

Shaped casing in which the working fluid flows from the upstream side to the downstream side,
A plurality of heat transfer tube layers provided in the casing and having a plurality of heat transfer tubes arranged at equal peaks in a plane orthogonal to the flow direction of the working fluid are formed by laminating a plurality of heat transfer tube layers in the flow direction, A plurality of heat transfer pipe blocks,
And a downstream side guide portion provided on the downstream side of the heat transfer pipe block and projecting from the inner surface of the casing and having a first guide surface facing the upstream side. The method according to claim 1,
And the first guide surface overlaps with the heat transfer pipe closest to the inner surface as viewed in the flow direction. The method according to claim 1 or 2,
Wherein the first guide surface is inclined with respect to the flow direction as viewed in a direction in which the heat transfer tube extends. The method according to any one of claims 1 to 3,
Wherein the first guide surface is curved in a direction away from the inner surface from an upstream side toward a downstream side. The method according to any one of claims 1 to 4,
Wherein the downstream-side guide portion is a plate-like shape in which a region extending in a direction away from the inner surface is not changed in thickness. The method according to any one of claims 1 to 5,
Wherein a dimension of the downstream-side guide portion protruding from the inner surface is not less than 1 times and not more than 3 times the pitch of the heat transfer tubes. The method according to any one of claims 1 to 6,
Wherein the distance between the first guide surface and the heat transfer pipe closest to the first guide surface is 10 mm or more and 50 mm or less. The method according to any one of claims 1 to 7,
Further comprising an upstream guide provided on an upstream side of the heat transfer pipe block and projecting from an inner surface of the casing and having a second guide surface facing the upstream side. A heat exchanger comprising: the heat exchanger according to any one of claims 1 to 8;
A year in which the heat exchanger is disposed,
And a main engine for supplying exhaust gas to the flue.

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