JP6918662B2 - High temperature piping cooling structure and high temperature piping cooling system - Google Patents

Description

The present invention relates to a cooling structure for high temperature pipes and a cooling system for high temperature pipes used in plants such as thermal power plants, nuclear power plants, and chemical plants.

For example, in a thermal power plant, a large number of pipes for transporting steam heated by a boiler to a steam turbine are arranged. This pipe is a metal pipe, and since high-temperature and high-pressure steam flows inside, it is in a high-temperature environment heated by the steam. When such a metal pipe is used for a long time in the above-mentioned environment, creep damage progresses and creep voids are generated, and the connection of these creep voids may cause cracks and eventually breakage. There is.

In order to prevent such pipe breakage, the degree of creep void growth is analyzed by regular non-destructive inspection to derive the degree of creep damage, and the remaining life of the metal pipe is evaluated. In this case, in general, the metal pipe has a higher risk of creep damage at the welded portion than the base metal portion, so this welded portion is mainly the inspection target portion. As a result of non-destructive inspection, if the risk of creep damage during the period until the next periodic inspection cannot be ignored, measures will be taken to reduce the risk of creep damage by lowering the metal temperature of the metal piping by lowering the operating temperature of the entire plant. However, if the operating temperature of the entire plant is lowered, there is a drawback that the operating efficiency of the plant is lowered.

If the risk of creep damage during the period until the next periodic inspection cannot be ignored in this way, a method of reducing the risk of creep damage by cooling the metal pipe and lowering the metal temperature can be considered. As such a technique, for example, there is one described in Patent Document 1 below. In Patent Document 1, the heat insulating material covering the outer peripheral portion of the high-temperature pipe is removed, the high-temperature pipe is exposed, fins are provided for the exposed high-temperature pipe, and cooling air is supplied to the fins. Cool the hot piping.

Japanese Unexamined Patent Publication No. 2016-160959

However, in Patent Document 1, since the cooling air is supplied to the fins, the cooling air is disturbed by the fins. Therefore, the flow path of the cooling air could not be formed favorably, and the cooling air may stagnate. If the flow of cooling air is stagnant, the heated air stays there, so there is a possibility that the part to be cooled cannot be cooled appropriately at that location. On the other hand, in places where stagnation does not occur, the cooling effect is preferably exhibited. As described above, there is a possibility that non-uniformity of the cooling effect in the cooled portion may occur between the portion where the stagnation occurs and the portion where the stagnation does not occur. As described above, if the cooled portion cannot be cooled uniformly, the metal temperature of the cooled portion after cooling may become non-uniform. If the metal temperature of the part to be cooled after cooling becomes non-uniform, the life of the pipe cannot be extended uniformly, and it becomes difficult to predict the life of the high-temperature pipe.

In view of the above circumstances, the present disclosure describes a cooling structure for high-temperature piping, which can uniformly extend the life of the piping and improve the accuracy of predicting the life of the high-temperature piping by suppressing the non-uniformity of the cooling effect in the cooled portion. It is an object of the present invention to provide a cooling system for high temperature piping.

In order to solve the above problems, the following means are adopted for the cooling structure of the high temperature pipe and the cooling system of the high temperature pipe.
The cooling structure for the high-temperature pipe according to one aspect of the present invention is a cooling structure for the high-temperature pipe that cools the cooled portion of the high-temperature pipe whose outer peripheral surface is covered with the first heat insulating material, and is one of the first heat insulating materials. A second heat insulating material that is separated from the outer peripheral surface of the high-temperature pipe from which the portion has been removed and covers the cooled portion of the high-temperature pipe, a supply portion that supplies a cooling medium that cools the cooled portion, and the supply. The cooling medium supplied from the unit is provided with a discharge unit that discharges the cooling medium to the outer peripheral surface side of the first heat insulating material.

In the above configuration, the cooling medium for cooling the cooled unit is supplied from the supply unit, and the supplied cooling medium is discharged from the discharge unit. Further, since the cooled portion is covered with the second heat insulating material separated from the outer peripheral surface of the high temperature pipe, a space is formed between the cooled portion and the second heat insulating material, and this space flows from the supply portion to the discharge portion. It serves as a flow path for the cooling medium. By providing the second heat insulating material and the discharge portion in this way, the flow path of the cooling medium is suitably formed, so that the cooling medium supplied from the supply portion does not stagnate. Since the cooling medium does not stagnate, the non-uniformity of the cooling effect in the cooled portion can be suppressed as compared with the case where the flow path is not formed. Since the cooled portion is uniformly cooled in this way, the metal temperature of the cooled portion after cooling is made uniform, and the life of the pipe can be uniformly extended. Therefore, the accuracy of life prediction of high-temperature piping can be improved, and the reliability of the plant can be improved.

Further, the second heat insulating material covers the cooled portion while being separated from the high temperature pipe. As a result, even in the portion where the first heat insulating material is removed, the high-temperature piping that becomes hot can be configured so as not to be exposed, so that the safety against burns and the like can be enhanced. Further, since the cooled portion is covered, it is possible to reduce the influence of the environment in which the high temperature pipe is installed when cooling the cooled portion. Therefore, the influence of the installation environment of the high-temperature piping can be suppressed, and the cooling performance can be stably exhibited. Further, even when it rains or the like, the second heat insulating material can block the rainwater or the like, and the rainwater or the like can be prevented from reaching the cooled portion. Therefore, it is not necessary to provide a rain shield structure or the like, and a compact structure can be obtained.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, an inflow prevention part for preventing inflow from the discharge part may be provided in the discharge part.

In the above configuration, an inflow prevention unit is provided in the discharge unit. As a result, it is possible to prevent rainwater or the like from flowing in from the discharge portion and the rainwater or the like from reaching the cooled portion.

Further, the cooling structure of the high temperature pipe according to one aspect of the present invention may be uniformly opened in the discharge portion with respect to the space for discharging the cooling medium.

In the above configuration, the space is uniformly opened to discharge the cooling medium. As a result, the cooling medium in which the cooled portion is cooled can be uniformly discharged to the outer peripheral surface side of the first heat insulating material. With such a configuration, it is possible to more effectively prevent the flow of the cooling medium flowing from the supply section to the discharge section from being biased to a part, and it is possible to make the flow of the cooling medium uniform. Therefore, since the cooled portion can be uniformly cooled, the metal temperature of the cooled portion after cooling can be made uniform, and the life of the pipe can be extended uniformly. Therefore, the accuracy of life prediction of the high temperature pipe can be improved, and the reliability of the plant to which the high temperature pipe is applied can be improved.
The state in which the cooling medium is uniformly opened with respect to the space for discharging the cooling medium means, for example, a state in which openings of the same shape are arranged at equal intervals, or a state in which slits having the same width are opened over substantially the entire area. Indicates the status, etc.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the total opening area of the discharge portion may be larger than the total opening area of the supply portion.

In the above configuration, the total opening area of the discharge portion is formed to be larger than the total opening area of the supply portion. As a result, the cooling medium supplied from the supply unit can be effectively discharged from the discharge unit in order to reduce the pressure loss on the discharge side. Therefore, it is possible to prevent the cooling medium supplied from the supply unit from staying and heat trapping, and to preferably discharge the cooling medium from the discharge unit.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the discharge part may be located above the supply part.

The cooling medium, which is supplied from the supply unit and cools the cooled unit, raises the temperature. The heated cooling medium flows upward because buoyancy is generated by the density difference due to the temperature difference. In the above configuration, since the discharge unit is located above the supply unit, the cooling medium after cooling the cooled unit can accelerate the flow toward the discharge unit by using buoyancy. Therefore, the flow of the cooling medium from the supply unit to the discharge unit can be more preferably formed.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the cooled portion extends in the central axis direction of the high temperature pipe, and the supply portion and the cooled portion form a circumferential direction. The angle may be 45 degrees or less.

In the above configuration, since the cooled portion extends in the central axis direction of the high temperature pipe, the cooling medium supplied from the supply portion flows along the circumferential direction of the high temperature pipe. The cooling medium flowing along the circumferential direction of the pipe is separated from the high-temperature pipe when the temperature reaches about 45 degrees or more from the supplied portion, and the local heat transfer coefficient decreases. In the above configuration, the angle between the supply unit and the cooled unit in the circumferential direction is 45 degrees or less. As a result, the cooling medium supplied from the supply unit is separated from the high-temperature pipe and reaches the cooled portion before the local heat transfer coefficient decreases, so that the decrease in the cooling capacity of the cooled portion can be suppressed.
Further, for example, when the removal location of the first heat insulating material is only a part in the circumferential direction from the supply portion, a high cooling effect can be obtained and the removal location of the first heat insulating material can be reduced. Therefore, the exposed surface of the high-temperature pipe can be reduced, and the safety against burns and the like can be improved.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the supply part and the discharge part may be formed on the second heat insulating material.

In the above configuration, the supply part and the discharge part are formed in the second heat insulating material. As a result, the supply unit and the discharge unit can be provided without providing a special device or structure. Therefore, failure or damage can be less likely to occur, and maintainability can be improved. In addition, since the special device has no structure and saves space, it can be applied to high-temperature piping in a situation where there is no empty space around it.

Further, the cooling structure of the high temperature pipe according to one aspect of the present invention includes a supply header into which the cooling medium is introduced from the cooling medium supply device, a discharge header into which the cooling medium that has cooled the cooled portion is introduced, and the like. The supply unit may be formed on the supply header, and the discharge unit may be formed on the discharge header.

In the above configuration, the supply unit is formed in the supply header and the discharge unit is formed in the discharge header. As a result, the cooling medium can be guided to the portion to be cooled, and the cooling medium can be discharged to the outer peripheral surface side of the first heat insulating material. Therefore, the cooling effect of the cooled portion can be improved.
Further, through the header, the cooling medium can be uniformly guided to the portion to be cooled, and the cooling medium can be uniformly discharged. Therefore, it is possible to prevent the flow of the cooling medium flowing from the supply section to the discharge section from being locally biased, and to make the flow of the cooling medium uniform. From the above, since the part to be cooled can be cooled uniformly, the metal temperature of the part to be cooled after cooling can be made uniform, and the life of the pipe can be extended uniformly. Reliability can be improved.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the discharge portion is formed between the first heat insulating material and the second heat insulating material, and the second heat insulating material is the high temperature pipe. It may protrude in the direction of the discharge portion so as to block the radiation from the outer peripheral surface toward the outer peripheral surface side of the second heat insulating material.

In the above configuration, the second heat insulating material projects toward the discharge portion so as to block radiation from the outer peripheral surface of the high temperature pipe toward the outer peripheral surface side of the second heat insulating material. As a result, the protruding portion shields the radiation from the outer peripheral surface of the high-temperature pipe toward the outer peripheral surface side of the second heat insulating material. Therefore, it is possible to prevent the discharge portion and the members in the vicinity of the discharge portion from being heated by the radiation from the outer peripheral surface of the high temperature pipe, and to improve the safety against burns and the like.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the first heat insulating material has an end face intersecting with the high temperature pipe, and the supply portion is a first plate material provided along the end face. And a flat plate-shaped second plate material facing the first plate material, and the end portion of the first plate material on the high temperature pipe side is larger than the end portion of the second plate material on the high temperature pipe side. At the end of the first plate material on the high temperature pipe side, which is located on the high temperature pipe side, a curved portion curved so as to be separated from the end face as the temperature approaches the high temperature pipe is formed, and the second plate material is said to have a curved portion. The cooling medium may be supplied from between the end on the high temperature pipe side and the outer peripheral surface of the high temperature pipe.

In the above configuration, the supply portion is formed by the end portion of the flat plate-shaped second plate material and the outer peripheral surface of the high temperature pipe. As a result, the velocity distribution and temperature distribution of the cooling medium flowing out from the supply section become large near the surface of the high-temperature piping. Therefore, the shearing force near the surface of the high-temperature pipe is increased and the heat transfer coefficient is improved, so that the cooled portion can be effectively cooled.
Further, since a curved portion is formed on the first plate material, the cooling medium flows along the curved portion, so that the velocity gradient and the temperature gradient of the cooling medium supplied from the supply port are increased near the surface of the high temperature pipe. Since it can be made larger, the cooled portion can be cooled more effectively.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the curved portion may be formed in an arc shape having a cross section smaller than 90 degrees.

Since the first plate material is arranged in the vicinity of the high temperature pipe, heat from the high temperature pipe may cause thermal deformation.
In the above configuration, the curved portion is formed in an arc shape having a cross section smaller than 90 degrees. As a result, even when the first plate material is inclined toward the first heat insulating material due to thermal deformation or the like, the direction in which the cooling medium flows can be made difficult to separate from the outer surface of the high temperature pipe. Therefore, even when the first plate material is thermally deformed, the supply direction of the cooling medium can be maintained along the outer peripheral surface of the high temperature pipe.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, the first heat insulating material has an end face intersecting with the high temperature pipe, and the supply portion has a flat plate shape provided along the end face. It has a first plate material and a flat plate-shaped second plate material facing the first plate material, and the end portion of the first plate material on the high temperature pipe side is the end portion of the second plate material on the high temperature pipe side. Rather, the cooling medium may be supplied from between the end of the second plate material on the high temperature pipe side and the outer peripheral surface of the high temperature pipe, which is located on the high temperature pipe side.

In the above configuration, the first plate material is formed in a flat plate shape, and the first plate material is not provided with a curved portion. As a result, even when the first plate material is inclined toward the end face side of the first heat insulating material due to thermal deformation or the like, the supply portion of the end portion of the first plate material on the high temperature pipe side is separated from the outer surface of the high temperature pipe. Don't look in the direction. Therefore, even when the first plate material is thermally deformed or the like, the cooling medium can be supplied along the outer peripheral surface of the high temperature pipe.

Further, in the cooling structure of the high temperature pipe according to one aspect of the present invention, a spacer may be provided between the end portion of the second plate material on the high temperature pipe side and the outer peripheral surface of the high temperature pipe.

In the above configuration, a spacer is provided between the end of the second plate material on the high temperature pipe side and the outer peripheral surface of the high temperature pipe. As a result, deformation of the supply portion between the end portion of the second plate material on the high temperature pipe side and the outer peripheral surface of the high temperature pipe can be suppressed, and the reliability of the cooling device can be improved.

Further, the cooling structure of the high temperature pipe according to one aspect of the present invention includes a duct for supplying the cooling medium from the cooling medium supply device to the supply header, and the duct may be arranged along the high temperature pipe. good.

In the above configuration, a duct for supplying the cooling medium from the cooling medium supply device to the supply header is provided. As a result, even when the cooling medium supply device and the supply header are separated from each other, the cooling medium can be supplied to the supply header, so that the reliability of the cooling device can be improved. Therefore, since it is not necessary to arrange the cooling medium supply device in the vicinity of the supply header, the high temperature pipe can be cooled even when there is no space for installing the cooling medium supply device in the vicinity of the high temperature pipe. Further, since the duct is provided along the high temperature pipe, it is not necessary to provide a special support tool or the like for supporting the duct, so that the duct can be installed in a compact device configuration.

In the cooling system for high-temperature piping according to one aspect of the present invention, in any of the above-mentioned cooling structures for high-temperature piping, a plurality of the cooled portions are formed, and a plurality of the above-mentioned coverings are formed from one cooling medium supply device. The cooling medium is supplied to the cooling unit.

In the above configuration, the cooling medium is supplied from one cooling medium supply device to the plurality of units to be cooled. As a result, when there are a plurality of cooling units, the installation cost can be reduced and the space can be saved as compared with the case where one cooling medium supply device is installed for each cooling unit. can.

According to the present disclosure, by making the cooling performance in the cooled portion uniform, it is possible to make the life extension of the high temperature pipe uniform and improve the reliability of the plant using the high temperature pipe.

It is sectional drawing (welded part is the pipe circumferential direction) in the pipe axial direction which shows the cooling structure of the high temperature pipe which concerns on 1st Embodiment. It is a perspective view which shows the cooling structure of the high temperature pipe of FIG. (A) shows a partially enlarged cross-sectional view of the cooling structure of the high temperature pipe of FIG. 1, (b) and (c) show the modification of (a), and (d) is the case where (a) is inclined. show. It is an end view which shows typically the supply part of FIG. It is a side view which shows typically the discharge part of FIG. It is a perspective view which shows the discharge part of FIG. It is sectional drawing which shows the cooling structure of the high temperature pipe which concerns on 2nd Embodiment (weld part is a pipe axial direction). (A) is a model diagram in which a uniform flow of cooling air collides with the side surface of the cylinder, and (b) is a graph showing the local heat transfer coefficient on the side surface of the cylinder. It is sectional drawing in the pipe axial direction which shows the cooling structure of the high temperature pipe which concerns on 3rd Embodiment (the weld part is upward in the pipe axial direction). 9 is an end view taken along the line XX of FIG. It is an end view which shows the modification of FIG. It is sectional drawing in the pipe axial direction which shows the cooling structure of the high temperature pipe which concerns on 4th Embodiment (the weld part is downward in the pipe axial direction). It is the end view of the XIII-XIII arrow view of FIG. It is sectional drawing in the pipe axial direction which shows the cooling structure of the high temperature pipe which concerns on 5th Embodiment (the weld part is a pipe circumferential direction). It is an end view of the XV-XV arrow view of FIG. It is an end view which shows the modification of FIG. It is a schematic block diagram of the cooling system of a high temperature pipe which concerns on 6th Embodiment.

Hereinafter, embodiments of a high-temperature pipe cooling structure and a high-temperature pipe cooling system will be described with reference to the drawings.
[First Embodiment]
Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 6.

The pipe (high temperature pipe) 2 in the cooling structure 1 of the high temperature pipe according to the present embodiment is, for example, a metal pipe 2 that conveys steam heated by a boiler to a steam turbine in a thermal power plant. It is in a state of being heated by high-temperature and high-pressure steam flowing in. Further, the pipe 2 extends linearly in a predetermined direction, and a welded portion 5 is provided along the circumferential direction. The outer peripheral surface 2a of the pipe 2 is covered with the first heat insulating material 3 in order to suppress a decrease in steam temperature at high temperature and high pressure.

If the pipe 2 is used for a long time in a high temperature environment, creep damage progresses and creep voids are generated, and the connection of these creep voids causes cracks, which may eventually lead to rupture. In order to prevent this breakage, the pipe 2 is periodically subjected to a non-destructive inspection, the degree of creep void growth of the pipe 2 is analyzed, the degree of creep damage is derived, and the remaining life of the pipe 2 is evaluated. When the creep damage risk in the period until the next periodic inspection cannot be ignored, the creep damage risk is reduced by applying the cooling structure 1 according to the present embodiment and lowering the temperature of the pipe 2.

Since the creep damage risk of the welded portion 5 connected to the pipe 2 and the like is higher than that of the base metal portion, in the present embodiment, the welded portion provided mainly along the circumferential direction of the pipe 2. The area around 5 is the part to be cooled.

The cooling structure 1 according to the present embodiment will be described in detail with reference to FIGS. 1 to 6. As shown in FIG. 1, the first heat insulating material 3 is arranged on the outer periphery of the pipe 2. A welded portion (cooled portion) 5 is formed in the pipe 2 in the circumferential direction, and a part of the first heat insulating material 3 is removed in a region including the welded portion 5 to form a space 4. That is, the outer peripheral surface 2a of the pipe 2 is exposed to the space 4. The welded portion may be formed so as to extend in the pipe axial direction, and in that case, the first heat insulating material 3 is partially removed so that the region along the welded portion formed in the pipe axial direction is exposed. Will be done.

Further, as shown in FIGS. 1 and 2, the cooling structure 1 includes a supply header 11 into which cooling air is introduced from a cooling medium supply device (not shown, but showing a cooling medium supply device such as a fan or a blower). The welded portion 5 is provided with a discharge header 12 from which cooling air after cooling is led out. In FIG. 2, for the sake of illustration, the first heat insulating material 3 is omitted.

The supply header 11 has a header portion 13 that surrounds the outer peripheral surface 3a of the first heat insulating material 3 over substantially the entire circumferential direction, and a supply portion 14 that extends inward in the radial direction from the inner peripheral surface of the header portion 13.

The header portion 13 is an annular member having a rectangular cross section, and the outer shape is formed into a polygonal shape. The central shaft of the header portion 13 and the pipe shaft C1 of the pipe 2 are concentric. Further, a duct 15 through which the cooling medium supplied from the cooling medium supply device flows is connected to the outer peripheral surface of the header portion 13. The duct 15 communicates with the internal space of the header portion 13 and supplies a cooling medium to the internal space of the header portion 13. The header portion 13 is arranged so as to protrude toward the space 4 by a predetermined distance from one end surface 3b of the first heat insulating material 3 that intersects the pipe 2 (hereinafter, referred to as “one end surface 3b of the first heat insulating material 3”). The supply portion 14 extends inward in the radial direction (that is, on the piping side) from the lower surface of the portion protruding toward the space 4. Further, a plurality of first flange portions 16 are formed on the outer peripheral surface of the supply header 11 in the circumferential direction (see FIGS. 1 and 2). The first flange portion 16 is fixed to the second flange portion 17 provided on the discharge header 12 (the second flange portion 17 will be described later) to connect the supply header 11 and the discharge header 12.

As shown in FIG. 3A, the supply unit 14 has a first plate material 18 provided along one end surface 3b of the first heat insulating material 3 intersecting with the pipe 2, and a flat plate shape facing the first plate material 18. It has the second plate material 19 of the above. The first plate material 18 and the second plate material 19 are separated by a predetermined distance, and a flow path through which the cooling medium flows is formed between the first plate material 18 and the second plate material 19. The flow path communicates with the internal space of the header portion 13.
The end of the first plate 18 on the pipe 2 side is located closer to the pipe 2 than the end of the second plate 19 on the pipe 2 side. Further, at the end of the first plate member 18 on the pipe 2 side, a curved portion 20 is formed so as to be separated from one end surface 3b of the first heat insulating material 3 as it approaches the pipe 2. The curved portion 20 is formed in an arc shape having a cross section of approximately 90 degrees. Further, the supply port of the supply unit 14 is formed by the end portion of the second plate member 19 facing the pipe 2 and the outer peripheral surface 2a of the pipe 2. As shown in FIG. 2, the supply port is provided over the entire area along the circumferential direction of the pipe 2. As a result, the cooling air supplied from the supply port is uniformly supplied along substantially the entire circumferential direction of the outer peripheral surface 2a of the pipe 2 as shown by the arrow in FIG.

Further, as shown in FIG. 4, a plurality of spacers 21 are provided between the end portion of the second plate member 19 facing the pipe 2 and the outer peripheral surface 2a of the pipe 2. The spacer 21 is fixed to the end of the second plate member 19 and is not fixed to the pipe 2 side. Further, the two spacers 21 are arranged so as to be symmetrical on one side and the other side with respect to the center line C2 when the supply header 11 is viewed from the extending direction of the pipe shaft C1.

The discharge header 12 is formed in a substantially cylindrical shape, and covers substantially the entire area of the space 4 from the outside in the radial direction of the pipe 2. The central shaft of the discharge header 12 and the pipe shaft C1 of the pipe 2 are concentric. Further, the discharge header 12 has a configuration that can be divided into three in the circumferential direction. FIG. 2 illustrates only one of the plurality of discharge headers 12.

The discharge header 12 includes an exterior plate 23 that constitutes the outer peripheral surface of the cylinder, an interior plate 24 that constitutes the inner peripheral surface of the cylinder, one end of the exterior plate 23 in the piping shaft C1 direction, and the interior plate 24 in the piping shaft C1 direction. A first side plate 25 for connecting one end, a second side plate 26 extending from the other end of the exterior plate 23 in the piping shaft C1 direction toward the piping direction, and a second provided between the exterior plate 23 and the interior plate 24. It has a heat insulating material 27. In FIG. 2, the second heat insulating material 27 is omitted for the sake of illustration.

The exterior plate 23, the first side plate 25, and the interior plate 24 form a space corresponding to the shape of the second heat insulating material 27, and the second heat insulating material 27 is housed inside this space.
The exterior plate 23 is a cylindrical member made of metal and covers the outer peripheral surface of the second heat insulating material 27. Further, a second flange portion 17 is formed on the outer peripheral surface of the exterior plate 23 at a position corresponding to the first flange portion 16. As described above, the supply header 11 and the discharge header 12 are connected by fixing the first flange portion 16 and the second flange portion 17. The interior plate 24 is a member having a substantially cylindrical shape and covers the inner peripheral surface of the second heat insulating material 27.

The second heat insulating material 27 is a cylindrical member, and is provided at a predetermined distance outward in the radial direction from the outer peripheral surface 2a of the pipe 2 portion from which the first heat insulating material 3 has been removed, and the welded portion 5 has a radius. Cover from the outside in the direction. Further, the second heat insulating material 27 has a base portion 28 located on the outer side in the radial direction, and a protruding portion 29 protruding from the end portion of the base portion 28 in the direction of the second side plate 26 in the direction of the second side plate 26.
The thickness (length in the radial direction) of the base 28 is set to a thickness capable of suitably insulating radiation from the pipe 2. For example, the thickness of the base 28 is set so that the temperature of the outer peripheral surface of the exterior plate 23 in contact with the outer peripheral surface of the second heat insulating material 27 is a temperature (about 50 ° C.) that does not cause burns.
The distance from the radial inner end of the base 28 to the outer peripheral surface 2a of the pipe 2 is desirable as the distance from the outer peripheral surface 2a of the pipe 2 decreases because the temperature of the outer peripheral surface of the exterior plate 23 decreases. The heat insulating material 3 is arranged so as to be substantially the same as the distance from the outer peripheral surface 3a of the heat insulating material 3 to the outer peripheral surface 2a of the pipe 2.
The thickness of the protrusion 29 is set to be thinner than the thickness of the base 28 in order to derive the cooling air after cooling. In order to make the discharge header 12 compact, the outer peripheral surface of the protruding portion 29 and the outer peripheral surface of the base portion 28 may be arranged so as to be flush with each other. In order to suppress the heating of the exterior plate 23, the projecting portion 29 is projected so as to block radiation from the outer peripheral surface 2a of the pipe 2 toward the exterior plate 23 or the second side plate 26. Specifically, the contact point between the one end surface 3b of the first heat insulating material 3 and the outer peripheral surface 2a of the pipe 2 and the other end surface 3c of the first heat insulating material 3 (the end surface facing the one end surface 3b of the first heat insulating material 3). ) Protrudes to the extension of the straight line B connecting the outer end in the radial direction.
In order to form a flow path for drawing out the cooled air after cooling between the second heat insulating material 27 and the first heat insulating material 3, the connecting portion between the base portion 28 and the protruding portion 29 is connected to the other end surface of the first heat insulating material 3. One end surface 3b may be provided on the one end surface 3b side of the 3c, and the radial inner end portion of the protruding portion 29 may be provided on the radial outer side of the outer peripheral surface of the first heat insulating material 3.

As shown in FIG. 5, the second side plate 26 is an annular plate material and is arranged concentrically with the piping shaft (central shaft) C1. The second side plate 26 has one or more discharge ports (discharge portions) 30 in the circumferential direction. Further, the discharge port 30 discharges the cooled cooling air flowing through the inside of the space 4 to the outside. In order to obtain a uniform flow rate distribution in the space 4, it is desirable that the discharge ports 30 are arranged at equal pitches in the circumferential direction of the pipe 2.
As shown in FIG. 6, in order to prevent rainwater or the like from entering the space 4 from the outside of the discharge header 12, a check damper (inflow prevention unit) 31 may be provided at the discharge port 30. Further, in order to suppress the pressure loss in the check damper (inflow prevention unit) 31, the total flow path area of the discharge port 30 may be formed to be larger than the total flow path area of the supply port 20a.

Next, the flow of cooling air (cooling medium) in at least one embodiment will be described.
Cooling air is supplied from the cooling medium supply device to the space inside the header portion 13 of the supply header 11 via the duct 15. The cooling air supplied to the space inside the header section 13 circulates in the space inside the header section 13 and flows into the supply section 14 substantially evenly. Specifically, it circulates between the first plate material 18 and the second plate material 19 (see arrow A1 in FIG. 1). The cooling air flowing between the first plate material 18 and the second plate material 19 flows along the outer peripheral surface 2a of the pipe 2 by the curved portion 20, passes through the supply port 20a, and flows into the space 4 ( 3 (a) See arrow A7).
At this time, the cooling air is uniformly supplied along substantially the entire circumferential direction of the outer peripheral surface 2a of the pipe 2 (see FIG. 2). The cooling air that has flowed into the space 4 flows along the outer peripheral surface 2a of the pipe 2 and reaches the welded portion 5 as it is (see arrow A2 in FIG. 2 and arrow A3 in FIG. 1). The cooling air that has reached the welded portion 5 flows along the outer peripheral surface 2a of the pipe 2 with that momentum. The cooling air flowing along the outer peripheral surface 2a of the pipe 2 collides with the other end surface 3c of the first heat insulating material 3 and flows along the other end surface 3c (see arrow A4 in FIG. 1). The cooling air flowing along the other end surface 3c flows into the flow path formed between the second heat insulating material 27 and the first heat insulating material 3 (see arrow A5 in FIG. 1). The cooling air flowing through the flow path is directed toward the plurality of discharge ports 30 formed on the second side plate 26, and is evenly discharged to the atmosphere from the plurality of discharge ports 30 (see arrow A6 in FIG. 1).

According to the above configuration, the following effects are exhibited.
In the present embodiment, cooling air for cooling the welded portion 5 is supplied from the supply portion 14, and the supplied cooling air is discharged from the discharge port 30. Further, since the welded portion 5 is covered with the discharge header 12, a space 4 is formed around the welded portion 5, and this space 4 serves as a flow path for cooling air flowing from the supply portion 14 to the discharge port 30. Become. In this way, since the flow path of the cooling air can be suitably formed, the cooling air supplied from the supply unit 14 does not stagnate. Since the cooling air does not stagnate, the non-uniformity of the cooling effect in the welded portion 5 can be suppressed as compared with the case where there is no flow path in the space 4.
Further, the plurality of discharge ports 30 are provided at substantially equal pitches in the circumferential direction. As a result, the cooling air that cools the welded portion 5 is uniformly discharged to the atmosphere. With such a configuration, it is possible to more effectively prevent the flow of the cooling air flowing in the space 4 from being locally biased, and it is possible to make the flow of the cooling air uniform.
In this way, since the welded portion 5 can be cooled uniformly, the metal temperature of the welded portion 5 after cooling can be made uniform, and the life of the pipe can be extended uniformly. As a result, the life prediction accuracy of the pipe 2 can be improved, and the reliability of the plant can be improved.

The second heat insulating material 27 provided in the discharge header 12 covers the welded portion 5 while being separated from the pipe 2. As a result, even in the portion where the first heat insulating material 3 is removed, the pipe 2 that becomes hot can be configured so as not to be exposed, so that the safety can be improved. In the present embodiment, the thickness of the second heat insulating material 27 is set so that the temperature of the exterior plate 23 exposed to the outside becomes a temperature (about 50 ° C.) that does not cause burns. Therefore, the safety of the exterior plate 23 can be enhanced.
Further, since the welded portion 5 is covered, it is possible to reduce the influence of the environment in which the pipe 2 is installed when the welded portion 5 is cooled. Therefore, it is possible to suppress the influence of the installation environment of the pipe 2 and obtain stable cooling performance. Further, even when it rains or the like in an outdoor environment, the second heat insulating material 27 can block the rainwater or the like, and it is possible to prevent the rainwater or the like from reaching the welded portion 5 from the inside of the space 4. .. Therefore, since it is not necessary to separately provide a rain shield structure or the like, the cooling structure 1 can be made into a compact structure.

Further, a check damper 31 may be provided at the discharge port 30. As a result, it is possible to prevent rainwater or the like from flowing in from the discharge port 30 and the rainwater or the like from the inside of the space 4 to the welded portion 5.

Further, the total flow path area of the plurality of discharge ports 30 may be formed larger than the total flow path area of the supply port 20a. As a result, the pressure loss of the discharge port 30 can be suppressed, and the cooling air supplied from the supply port can be uniformly discharged from the discharge port 30.

Further, the supply port 20a is formed in the supply header 11, and the discharge port 30 is formed in the discharge header 12. Specifically, cooling air is supplied to the supply header 11 from a cooling air supply device (not shown), and the cooling air is guided to the welded portion 5 and the cooling medium is discharged from the discharge port 30. In this way, high cooling performance can be obtained by obtaining a uniform flow of cooling air at the welded portion 5 without causing the high-temperature air after cooling to flow back.

Further, the second heat insulating material 27 has a protruding portion 29 protruding in the direction of the discharge port 30. As a result, the protrusion 29 of the second heat insulating material 27 shields the radiation from the outer peripheral surface 2a of the pipe 2 having a high temperature of about 600 ° C. to the second side plate 26 and the like, thereby suppressing the temperature rise and causing burns. It is possible to improve the safety to such things.

Further, the supply port 20a is formed by the end portion of the flat plate-shaped second plate member 19 and the outer peripheral surface 2a of the pipe 2. As a result, the velocity distribution and temperature distribution of the cooling air flowing out from the supply port 20a become large in the vicinity of the outer peripheral surface 2a of the pipe 2. Therefore, the shearing force in the vicinity of the outer peripheral surface 2a of the pipe 2 becomes large, and the heat transfer coefficient is improved, so that the welded portion 5 can be effectively cooled.

A plurality of spacers 21 may be provided between the end portion of the second plate member 19 on the pipe 2 side and the outer peripheral surface 2a of the pipe 2. As a result, deformation of the supply port 20a between the end portion of the second plate member 19 on the pipe 2 side and the outer peripheral surface 2a of the pipe 2 can be suppressed, and the reliability of the cooling structure 1 can be improved. The plurality of spacers 21 are arranged so as to be symmetrical on one side and the other side with respect to the center line C2 when the supply header 11 is viewed from the extending direction of the pipe shaft C1 (the center of gravity thereof is the center line). Matches C2 and has a balanced weight).

In addition, in at least one embodiment, the supply port 20a in which the curved portion 20 having an arc shape having a cross section of about 90 degrees is provided at the end portion of the first plate material 18 on the pipe 2 side has been described. The supply port 20a at the end of the pipe 2 on the 18th pipe 2 is not limited to the above. For example, as shown in FIG. 3B, the supply port 20a at the end of the first plate member 18 on the pipe 2 side may be formed in an arc shape having a cross section smaller than 90 degrees, and FIG. 3C may be formed. As shown in the above, the curved portion 20 may be not provided and may extend to the outer peripheral surface of the pipe 2 in a flat plate shape.
Since the first plate member 18 is arranged in the vicinity of the pipe 2 having a high temperature of about 600 ° C., heating from the pipe 2 may cause thermal deformation. In the curved portion 20 having a cross section formed in an arc shape of approximately 90 degrees, when the first plate material 18 is inclined toward one end surface 3b side of the first heat insulating material 3 due to thermal deformation or the like, it is shown in FIG. 3 (d). As described above, the downstream end of the curved portion 20 faces the outer side in the radial direction of the pipe 2 (upper side of the paper surface in FIG. 3D) by the angle at which the first plate member 18 is inclined (arrow in FIG. 3D). See A10). As a result, the cooling air flow supplied from the supply port is supplied to the outer side in the radial direction of the pipe 2 without following the outer peripheral surface 2a of the pipe 2, so that the cooling capacity is lowered.
On the other hand, by adopting the configuration shown in FIGS. 3 (b) and 3 (c), the first plate member 18 is inclined toward one end surface 3b side of the first heat insulating material 3 due to thermal deformation or the like as shown in FIG. 3 (d). Even in this case, the cooling air supplied from the supply port maintains the flow along the outer peripheral surface 2a of the pipe 2, so that the decrease in the cooling capacity can be suppressed (FIGS. 3D, arrows A8 and A9). reference).

Further, in the present embodiment, the spacers 21 are arranged one by one so as to be symmetrical with respect to the center line C2, but the number of spacers 21 is not limited to this. If they are arranged symmetrically with respect to the center line C2, a plurality of them may be arranged on one side and the other side. Further, it may be provided evenly in the circumferential direction regardless of the center line C2.

Further, although an example in which the check damper 31 is provided in the discharge port 30 has been described, the configuration for preventing the inflow from the discharge port 30 is not limited to this. For example, it may have a labyrinth structure or a louver may be provided.

Moreover, although the example in which a plurality of discharge ports 30 are provided at equal intervals in the circumferential direction has been described, the present invention is not limited to this. Slits may be formed in substantially the entire circumferential direction of the second side plate 26.

[Second Embodiment]
Next, the second embodiment will be described with reference to FIGS. 7 and 8.
In the present embodiment, as shown in FIG. 7, the point where the welded portion 35, which is the cooled portion, is formed so as to extend in the pipe axial direction, and the first heat insulating material 36 are removed only in a part in the circumferential direction of the pipe 2. This is mainly different from the above first embodiment. A detailed description of the same embodiment as that of the first embodiment will be omitted.
In the present embodiment, the angle θ1 in the circumferential direction formed by the supply portion 34 and the welded portion 35 is formed to be approximately 45 degrees or less. Further, the angle θ2 in the circumferential direction from which the first heat insulating material 36 is removed is formed to be approximately 90 degrees or less. The point that the supply unit 34 is provided in the supply header 37 and the discharge unit 39 is provided in the discharge header 38 is the same as in the first embodiment.

In at least one embodiment, since the welded portion 35 extends in the axial direction of the pipe, the cooling air supplied from the supply unit 34 flows along the circumferential direction of the pipe 2. The cooling air flowing along the circumferential direction of the pipe 2 is separated from the pipe 2 when the temperature reaches about 45 degrees or more from the supplied portion, and the local heat transfer coefficient decreases. This decrease in the local heat transfer coefficient will be described with reference to FIGS. 8 (a) and 8 (b). FIG. 8A shows a model in which a uniform flow of cooling air W collides with the cylindrical side surface of the pipe X. Reference numeral Z in FIG. 8A indicates a flow of cooling air. Further, FIG. 8B shows the local heat transfer coefficient on the side surface of the cylinder. As shown in FIG. 8B, the local heat transfer coefficient of the side surface of the cylinder is substantially constant from the collision point to the vicinity of 45 degrees, and thereafter, the local heat transfer coefficient gradually decreases because it gradually peels off from the outer peripheral surface. ..
In the above configuration, the angle between the supply portion 34 and the welded portion 35 in the circumferential direction is set to 45 degrees or less at which the local heat transfer coefficient is constant. As a result, the cooling air supplied from the supply unit 34 reaches the welded portion 35 before being separated from the pipe 2 and the local heat transfer coefficient is lowered, so that the welded portion 35 can be cooled without deteriorating the cooling performance.
Further, the removed portion of the first heat insulating material 36 is set to be approximately 90 degrees or less in the circumferential direction from the supply unit 14. Therefore, high cooling performance can be obtained, and the number of places where the first heat insulating material 36 is removed can be reduced as compared with the case where the first heat insulating material 36 is removed over the entire area in the circumferential direction. As a result, the safety against burns can be improved by reducing the exposed surface of the pipe 2 having a high temperature of about 600 ° C., and the decrease in plant efficiency can be suppressed by suppressing heat dissipation.

The angles of θ1 and θ2 described in this embodiment are examples, and are not limited thereto. If θ1 is 45 degrees or less, it may be any number of times, and if θ2 is an angle smaller than 360 degrees, safety can be improved as compared with the case where the first heat insulating material 36 is removed over the entire circumferential direction. can.

[Third Embodiment]
Next, the third embodiment will be described with reference to FIGS. 9 and 10.
In the present embodiment, the supply unit 49 and the discharge unit 50 are formed on the second heat insulating material 47 without using the supply header and the discharge header.

The cooling structure 41 of the high temperature pipe according to this embodiment will be described. As shown in FIG. 9, the welded portion 45 in this embodiment is formed at the upper end of the pipe 42.
In the first heat insulating material 43, the portion covering the welded portion 45 is removed, and a space 44 is formed so as to surround the welded portion 45. Further, the first heat insulating material 43 is removed over the entire area in the circumferential direction of the pipe 42. Further, the outer side of the space 44 in the radial direction is closed with the second heat insulating material 47. The second heat insulating material 47 is separated from the outer peripheral surface 42a of the pipe 42 by a predetermined distance outward in the radial direction. Further, the second heat insulating material 47 is formed with a supply section 49 and a discharge section 50 communicating with the space 44. As shown in FIGS. 9 and 10, the discharge portion 50 is formed directly above the welded portion 45 and opens upward with respect to the outside of the pipe 42 (vertically upward in FIG. 9). On the other hand, the supply unit 49 is formed on the opposite side of the discharge unit 50 by 180 degrees in the circumferential direction (vertically downward in FIG. 9).

Next, the flow of the cooling air (cooling medium) in one embodiment will be described.
Cooling air flows into the space 44 from the supply unit 49 by natural convection (see arrow A11 in FIG. 10). The cooling air that has flowed into the space 44 from the supply unit 49 is divided into two parts and circulates while rising along the outer peripheral surface 42a of the pipe 42 along the circumferential direction as shown by the arrow A12 in FIG. The cooling air that has flowed while rising along the outer peripheral surface 42a of the pipe 42 along the circumferential direction cools the welded portion 45 and is then discharged from the discharge portion 50 to the outside of the space 44 (see arrow A13).

According to the above configuration, the following effects are obtained.
In the present embodiment, the supply unit 49 and the discharge unit 50 are formed on the second heat insulating material 47. As a result, the supply unit 49 and the discharge unit 50 can be provided without providing a cooling device or a cooling structure to be added to the existing equipment. Therefore, it is possible to suppress the frequency of occurrence of failures and damages and improve maintainability. In addition, since it is space-saving because it does not have a cooling device or cooling structure to be added to the existing equipment, it can be applied to high-temperature piping in a situation where there is no empty space in the existing equipment.

Further, the cooling air supplied from the supply unit 49 into the space 44 and in contact with the pipe 42 raises the temperature. The heated cooling air flows vertically upward because buoyancy is generated by the density difference due to the temperature difference. In the present embodiment, since the discharge unit 50 is located vertically above the supply unit 49, the cooling air supplied from the supply unit 49 into the space 44 is directed toward the discharge unit 50 by using buoyancy. be able to. Therefore, it is possible to form a flow of cooling air from the supply unit 49 to the discharge unit 50 without using a drive source such as a fan or a blower.
Further, since the discharge portion 50 is opened vertically upward, the cooling air can be suitably discharged without stagnation of air in the cooling flow path.

In the present embodiment, an example in which the space 44 is formed over substantially the entire circumferential direction of the pipe 42 has been described, but the present invention is not limited to this. As shown in FIG. 11, the supply unit 49 may be formed at an intermediate position in the vertical direction, and the first heat insulating material 43 may be removed only in the region from the supply unit 49 in the circumferential direction of the pipe 42 to the discharge unit 50. With such an apparatus configuration, it is possible to improve safety against burns by reducing the exposed surface of the pipe 42 having a high temperature of about 600 ° C., and to suppress a decrease in plant efficiency by suppressing heat dissipation.

Further, in the present embodiment, a plurality of supply parts or discharge parts may be formed in the axial direction of the pipe. With such a configuration, the flow rate of the cooling air flowing through the space 44 can be increased, and the cooling of the welded portion 45 can be promoted.

[Fourth Embodiment]
Next, the fourth embodiment will be described with reference to FIGS. 12 and 13.
As shown in FIGS. 12 and 13, the welded portion 55 in one embodiment differs from the third embodiment only in that it is formed at the lower end of the pipe 52.
In the cooling structure 51 according to one embodiment, the supply portion 59 is formed directly below the welded portion 55. Therefore, as soon as the cooling air flows into the space 54 formed between the second heat insulating material 57 and the outer peripheral surface 52a of the pipe 52 by natural convection from the supply unit 59 (see arrow A14 in FIG. 13), the welded portion 55 To cool. The cooling air that has cooled the welded portion 55 is divided into two parts and circulates while rising along the outer peripheral surface 52a of the pipe 52 along the circumferential direction, as shown by the arrow A15 in FIG. The cooling air that has flowed while rising along the circumferential direction of the outer peripheral surface 52a of the pipe 52 is discharged from the discharge hole 60 to the outside of the space 54 (see arrow A16).

[Fifth Embodiment]
Next, the fifth embodiment will be described with reference to FIGS. 14 and 15.
As shown in FIGS. 14 and 15, the welded portion 65 in one embodiment is provided along the circumferential direction of the pipe 62.
In one embodiment, cooling air flows from the supply unit 69 by natural convection into the space 64 formed between the second heat insulating material 67 and the outer peripheral surface 62a of the pipe 62 (see arrow A17 in FIG. 15). The cooling air that has flowed into the space 64 from the supply unit 69 is divided into two parts, and as shown by the arrow A18 in FIG. Cool 65. The cooling air that circulates while rising along the outer peripheral surface 62a of the pipe 62 along the circumferential direction and cools the welded portion 65 is discharged from the discharge portion 70 to the outside of the space 64 (see arrow A19).

In the present embodiment, an example in which the space 64 is formed over substantially the entire circumferential direction of the pipe has been described, but the present invention is not limited to this. For example, as shown in FIG. 16, the supply portion 69 may be formed at an intermediate position in the vertical direction, and the first heat insulating material 63 may be removed only in the circumferential direction region of the pipe in which the welded portion 65 is formed. With such an apparatus configuration, it is possible to improve safety against burns by reducing the exposed surface of the pipe 62 having a high temperature of about 600 ° C., and to suppress a decrease in plant efficiency by suppressing heat dissipation.

[Sixth Embodiment]
Next, the sixth embodiment will be described with reference to FIG.
In the high-temperature pipe cooling system 100 according to the present embodiment, cooling air is provided in the first cooled portion 70a and the second cooled portion 70b provided in the pipe 74, and in the first cooled portion 70a and the second cooled portion 70b. It is provided with a blower (cooling medium supply device) 71 for supplying the air, and a duct 72 for communicating the blower 71 with the first cooled portion 70a and the second cooled portion 70b.
The duct 72 branches into a first duct 72a and a second duct 72b between the blower 71 and the cooled portion. The first duct 72a communicates with the first cooled portion 70a, and the second duct 72b communicates with the second cooled portion 70b. Further, the first duct 72a is provided along the pipe 74 and is fixed to the pipe 74.
Further, the first duct 72a and the second duct 72b are provided with a flow rate adjusting valve 73 for adjusting the flow rate of the cooling air flowing through the inside.
Since the cooling structure of the pipes in the first cooled portion 70a and the second cooled portion 70b is the same as that in the first embodiment, the description thereof will be omitted.

According to the above configuration, it has the following effects.
In the present embodiment, even if the blower 71 and the cooled portion are separated from each other, the cooling medium can be supplied to the cooled portion by the duct 72 without leaking. Therefore, since it is not necessary to arrange the blower 71 in the vicinity of the cooled portion, the pipe 74 can be cooled even when there is no space for installing the blower 71 in the vicinity of the cooled portion. Further, since the first duct 72a is provided along the pipe 74, it is not necessary to provide a special support tool or the like for supporting the first duct 72a, and the installation cost can be reduced.

Further, cooling air can be supplied from one blower 71 to a plurality of units to be cooled. As a result, even when there are a plurality of cooled portions, the installation cost can be reduced and the space can be saved as compared with the case where one blower is provided for each cooled portion.

The present invention is not limited to the invention according to each of the above embodiments, and can be appropriately modified without departing from the gist thereof.
For example, each of the above embodiments may be combined as appropriate.

1 Cooling structure 2 Piping (high temperature piping)
2a Outer peripheral surface 3 First heat insulating material 3a Outer peripheral surface 3b One end surface 3c Other end surface 4 Space 5 Welded part (cooled part)
11 Supply header 12 Discharge header 13 Header part 14 Supply part 15 Duct 16 1st flange 17 2nd flange 18 1st plate material 19 2nd plate material 20 Curved part 21 Spacer 23 Exterior plate 24 Interior plate 25 1st side plate 26 2nd side plate 27 Second heat insulating material 28 Base 29 Protruding part 30 Exhaust port (exhaust part)
31 Check damper (inflow prevention part)
34 Supply part 35 Welded part 36 First heat insulating material 37 Supply header 38 Discharge header 42, 52, 62 Piping 42a, 52a, 62a Outer peripheral surface 43, 63 First heat insulating material 44, 54, 64 Space 45, 55, 65 Welded part 47, 57, 67 Second heat insulating material 49, 59, 69 Supply unit 50, 60, 70 Discharge unit 71 Blower (cooling medium supply device)
72, 72a, 72b Duct 73 Flow control valve 74 Piping 100 Cooling system A1 to A19 Cooling air flow C2 Center line W Cooling air X Piping Z Cooling air flow θ1, θ2 Angle

Claims (15)

It is a cooling structure of a high temperature pipe that cools the cooled part of the high temperature pipe whose outer peripheral surface is covered with the first heat insulating material.
A second heat insulating material that is separated from the outer peripheral surface of the high temperature pipe from which a part of the first heat insulating material has been removed and that covers the cooled portion of the high temperature pipe.
A supply unit that supplies a cooling medium that cools the cooled unit,
A cooling structure for a high-temperature pipe including a discharge unit that discharges the cooling medium supplied from the supply unit to the outer peripheral surface side of the first heat insulating material. The cooling structure for high-temperature piping according to claim 1, wherein the discharge unit is provided with an inflow prevention unit for preventing inflow from the discharge unit. The cooling structure for high-temperature piping according to claim 1 or 2, wherein the discharge unit is uniformly open to a space for discharging the cooling medium. The cooling structure for a high-temperature pipe according to any one of claims 1 to 3, wherein the total opening area of the discharge portion is larger than the total opening area of the supply portion. The cooling structure for high-temperature piping according to any one of claims 1 to 4, wherein the discharge unit is located above the supply unit. The cooled portion extends in the direction of the central axis of the high temperature pipe.
The cooling structure for high-temperature piping according to any one of claims 1 to 5, wherein the angle between the supply unit and the cooled unit in the circumferential direction is 45 degrees or less. The cooling structure for a high-temperature pipe according to any one of claims 1 to 6, wherein the supply unit and the discharge unit are formed on the second heat insulating material. A supply header into which the cooling medium is introduced from the cooling medium supply device, and
A discharge header into which the cooling medium in which the cooled portion is cooled is introduced, is provided.
The supply unit is formed in the supply header.
The cooling structure for a high-temperature pipe according to any one of claims 1 to 6, wherein the discharge unit is formed on the discharge header. The discharge portion is formed between the first heat insulating material and the second heat insulating material.
The high-temperature pipe according to claim 8, wherein the second heat insulating material projects in the direction of the discharge portion so as to block radiation from the outer peripheral surface of the high-temperature pipe toward the outer peripheral surface side of the second heat insulating material. Cooling structure. The first heat insulating material has an end face that intersects with the high temperature pipe.
The supply unit has a first plate material provided along the end face and a flat plate-shaped second plate material facing the first plate material.
The end portion of the first plate material on the high temperature pipe side is located closer to the high temperature pipe side than the end portion of the second plate material on the high temperature pipe side.
At the end of the first plate material on the high temperature pipe side, a curved portion curved so as to be separated from the end face as it approaches the high temperature pipe is formed.
The cooling structure for a high-temperature pipe according to claim 8 or 9, wherein the cooling medium is supplied from between the end of the second plate material on the high-temperature pipe side and the outer peripheral surface of the high-temperature pipe. The cooling structure for a high-temperature pipe according to claim 10, wherein the curved portion is formed in an arc shape having a cross section smaller than 90 degrees. The first heat insulating material has an end face that intersects with the high temperature pipe.
The supply unit has a flat plate-shaped first plate material provided along the end face and a flat plate-shaped second plate material facing the first plate material.
The end portion of the first plate material on the high temperature pipe side is located closer to the high temperature pipe side than the end portion of the second plate material on the high temperature pipe side.
The cooling structure for a high-temperature pipe according to claim 8 or 9, wherein the cooling medium is supplied from between the end of the second plate material on the high-temperature pipe side and the outer peripheral surface of the high-temperature pipe. The cooling structure for a high-temperature pipe according to any one of claims 10 to 12, wherein a spacer is provided between the end of the second plate material on the high-temperature pipe side and the outer peripheral surface of the high-temperature pipe. A duct for supplying the cooling medium from the cooling medium supply device to the supply header is provided.
The cooling structure for a high-temperature pipe according to any one of claims 8 to 13, wherein the duct is arranged along the high-temperature pipe. In the cooling structure for high temperature piping according to any one of claims 8 to 14.
A plurality of the parts to be cooled are formed.
A cooling system for high-temperature piping in which the cooling medium is supplied from one cooling medium supply device to a plurality of cooled portions.

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