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WO2020095572A1 - Échangeur de chaleur, chaudière équipée d'un échangeur de chaleur, et procédé d'échange de chaleur - Google Patents

Échangeur de chaleur, chaudière équipée d'un échangeur de chaleur, et procédé d'échange de chaleur Download PDF

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Publication number
WO2020095572A1
WO2020095572A1 PCT/JP2019/038512 JP2019038512W WO2020095572A1 WO 2020095572 A1 WO2020095572 A1 WO 2020095572A1 JP 2019038512 W JP2019038512 W JP 2019038512W WO 2020095572 A1 WO2020095572 A1 WO 2020095572A1
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WIPO (PCT)
Prior art keywords
outlet
inlet
header
predetermined direction
heat transfer
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Ceased
Application number
PCT/JP2019/038512
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English (en)
Japanese (ja)
Inventor
直文 阿部
和宏 堂本
大輝 上野
航平 本村
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Mitsubishi Power Ltd
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Mitsubishi Hitachi Power Systems Ltd
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Publication of WO2020095572A1 publication Critical patent/WO2020095572A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/22—Drums; Headers; Accessories therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G3/00—Steam superheaters characterised by constructional features; Details or component parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates

Definitions

  • the present disclosure relates to a heat exchanger, a boiler including the heat exchanger, and a heat exchange method.
  • a large-scale boiler that constitutes a thermal power plant has a furnace that is hollow and is installed in the vertical direction, and multiple combustion burners are arranged along the circumferential direction on the furnace wall. Further, in a large-scale boiler, a flue is connected vertically above the furnace, and a heat exchanger for generating steam is arranged in the flue. Then, the combustion burner injects a mixture of fuel and air into the furnace to form a flame, and high-temperature combustion gas is generated and flows into the flue.
  • a heat exchanger is installed in a region where the combustion gas flows, and superheated steam is generated by heating water and steam flowing in the heat transfer tubes that form the heat exchanger.
  • Patent Document 1 describes a heat exchanger in which the heat transfer tubes are configured in two or more groups and two or more inlet headers and / or outlet headers are provided for each group. There is. According to this heat exchanger, since it is possible to suppress the flow rate of steam flowing through each of the outlet headers, it is said that the diameter of each outlet header can be reduced.
  • the heat exchanger has an inlet header and an outlet header connected by a plurality of heat transfer tubes.
  • the flow or temperature of the combustion gas flowing through the flue is uneven, there is a possibility that a difference will occur in the amount of heat absorption in each heat transfer tube. Then, the performance of the heat exchange amount of the heat exchanger is deteriorated, and it is necessary to raise the design temperature of each device constituting the heat exchanger, which may increase the equipment cost.
  • a dynamic pressure distribution due to the velocity difference may occur in each header. There may be a static pressure difference with the outlet. Then, a difference occurs in the flow rate of the fluid (vapor) flowing through the individual heat transfer tubes. When the flow rate of steam flowing through each heat transfer tube is uneven, a difference occurs in the amount of heat absorbed in each heat transfer tube, further reducing the heat exchange performance of the heat exchanger, and configuring the heat exchanger. It is necessary to further increase the design temperature of each device, which may further increase the equipment cost.
  • the present disclosure has been made in view of such circumstances, and provides a heat exchanger that suppresses a temperature difference between fluids near the outlet end of each heat transfer tube, a boiler including the heat exchanger, and a heat exchange method. With the goal.
  • the heat exchanger of the present disclosure includes one or a plurality of inlet headers that extend in a predetermined direction and are provided with an inlet communication pipe that communicates with the outside at an end in the predetermined direction.
  • a plurality of outlet headers extending in a predetermined direction and provided with outlet communication pipes that communicate with the outside only at one end in the predetermined direction, and the outlet headers are arranged in the predetermined direction, and the outlet ends are arranged along the predetermined direction.
  • a plurality of heat transfer pipes which are alternately connected to the header, and whose inlet end, which is the other end of the outlet end connected to the one outlet header, is connected to the one inlet header.
  • the outlet communication pipe and the inlet communication pipe associated by the common heat transfer pipe are provided on the same side in the predetermined direction.
  • the plurality of heat transfer tubes are arranged in a predetermined direction, the outlet ends are alternately connected to the respective outlet headers along the predetermined direction, and the heat transfer tubes connected to one outlet header are connected.
  • the inlet end of is connected to one inlet header.
  • the heat transfer tubes arranged in the low temperature side region are alternately connected to the outlet headers along the predetermined direction. Therefore, the total amount of heat from the heat transfer tubes arranged in the regions on the respective temperature sides into the respective outlet headers is substantially equal, and the fluid (for example, steam) can be collected so that the temperature difference between the outlet headers is reduced. Therefore, it is possible to suppress the temperature difference that occurs in the fluid flowing through the outlet communication pipes of the outlet headers after flowing through the heat transfer pipes and collected in the outlet headers. Further, since it is possible to suppress the temperature difference between the fluids flowing out from the respective outlet communication pipes, it is possible to suppress the occurrence of temperature non-uniformity even in the equipment on the downstream side connected to the outlet communication pipes, and thus to improve the performance of the entire plant. The decrease can be suppressed.
  • the outlet communication pipe of the outlet header and the inlet communication pipe of the inlet header which are associated with the connection relationship in the common heat transfer pipe, are provided on the same side in the predetermined direction.
  • the differential pressure distribution due to the static pressure distribution along the predetermined direction in the inlet header and the static pressure distribution along the predetermined direction in the outlet header can be made substantially uniform along the predetermined direction. Since the flow velocity of the fluid flowing through the heat transfer tubes depends on the static pressure difference between the inlet header and the outlet header at the position where the heat transfer tubes are connected, it is possible to suppress the flow velocity difference between the fluid flowing through the heat transfer tubes. ..
  • the inlet header at a position connecting each heat transfer pipe
  • the static pressure difference between the outlet header and the outlet header increases (or decreases) along a predetermined direction. Therefore, the fluid flowing in each heat transfer tube has a difference in flow velocity along the predetermined direction. Then, a difference occurs in the heat absorption amount of the fluid flowing through each heat transfer tube. In addition to this difference in the amount of heat absorption, the unevenness in the temperature of the combustion gas described above causes the temperature difference in the fluid near the outlet end of each heat transfer tube to increase further.
  • the performance of the heat exchange amount of the heat exchanger is deteriorated, and it is necessary to raise the design temperature of each device constituting the heat exchanger, which may increase the facility cost.
  • the number of heat transfer tubes connected to each outlet header can be reduced. As a result, it is possible to reduce the diameter of each outlet header as the flow rate of each outlet header is reduced, and also to reduce the space occupied by the heat transfer pipes extending from the outlet header, thereby reducing the flue gas inside the boiler. Placement of the heat exchanger in the is easy.
  • the number of the inlet headers is the same as the number of the outlet headers, and the outlet communication pipes provided in the outlet headers are on the same side in the predetermined direction. It is provided.
  • the number of inlet headers is the same as the number of outlet headers.
  • the diameter of each inlet header can be reduced with a decrease in the flow rate flowing into each inlet header, and the space occupied by the heat transfer tubes protruding from the inlet header can be reduced, so that the flue gas inside the boiler can be reduced. Placement of the heat exchanger in the is easy.
  • the outlet communication pipes provided in each outlet header are provided on the same side in the predetermined direction. As a result, the inlet communication pipe and the outlet communication pipe are gathered on one side in the predetermined direction, so that workability at the time of assembling the heat exchanger can be improved.
  • the outer diameter of the inlet header must be increased in order to obtain an appropriate flow velocity.
  • the wall thickness may be increased to increase the strength and the number of manufacturing processes may increase. Since the diameter of the inlet header can be reduced as described above by using a plurality of inlet headers, such a manufacturing problem does not occur. This also applies to the exit header.
  • one of the outlet communication pipes provided in each of the outlet headers has one of the outlet communication pipes and the other at least one of the outlet communication pipes in the predetermined direction. Located on different sides.
  • the number of inlet headers is the same as the number of outlet headers.
  • one of the outlet connecting pipes provided in each outlet header is provided on the side different from the other at least one inlet connecting pipe in the predetermined direction. For example, when there are two inlet headers and two outlet headers, the direction of the inlet connecting pipe of one inlet header and the outlet connecting pipe of one outlet header connected to the one inlet header is different from that of the other inlet header.
  • the inlet communication pipe and the outlet communication pipe are not aggregated on one side in the predetermined direction, it becomes easy to arrange the pipes connected to them, the increase of the occupied space is suppressed, and the heat exchanger is arranged. It will be easier.
  • the outer diameter of the inlet header must be increased. As it becomes larger, the wall thickness becomes thicker to increase the strength and the manufacturing process thereof may increase. Since the diameter of the inlet header can be reduced as described above by using a plurality of inlet headers, such a manufacturing problem does not occur.
  • the number of the inlet headers is one
  • the number of the outlet headers is two
  • the inlet communication pipes are provided at both ends of the inlet header
  • the one inlet is provided.
  • the connecting pipe and the outlet connecting pipe of the one outlet header are provided on one side in the predetermined direction, and the other inlet connecting pipe and the outlet connecting pipe of the other outlet header are in the predetermined direction. In the other side, the flow passage area of the inlet header is larger than the flow passage area of the outlet header.
  • the inlet communication pipes are provided at both ends of one inlet header, and one inlet communication pipe and one outlet header's outlet communication pipe are provided on one side in a predetermined direction.
  • the other inlet communication pipe and the other outlet header outlet communication pipe are provided on the other side in the predetermined direction.
  • the inlet connection pipe of one inlet header and the outlet connection pipe of one outlet header are in a pair
  • the inlet connection pipe of the other inlet header and the outlet connection pipe of another outlet header are in a pair
  • each pair is It is equivalent to a heat exchanger located on the opposite side in a given direction.
  • the inlet header is configured in common, and the inlet header has a larger flow passage area than the outlet header.
  • the inlet communication pipe and the outlet communication pipe are not aggregated on one side in the predetermined direction, so that the piping connected to them can be easily handled.
  • the number of heat transfer tubes connected to each outlet header can be reduced.
  • a boiler according to one aspect of the present disclosure includes the heat exchanger described above.
  • a heat exchange method includes one or a plurality of inlet headers that extend in a predetermined direction and are provided with an inlet communication pipe that communicates with the outside at an end portion in the predetermined direction.
  • a plurality of outlet headers extending in a predetermined direction and provided with outlet communication pipes that communicate with the outside only at one end in the predetermined direction, and the outlet headers are arranged in the predetermined direction, and the outlet ends are arranged along the predetermined direction.
  • the outlet communication pipe and the inlet communication pipe which are associated with each other in the common heat transfer pipe, are heat exchange methods using a heat exchanger provided on the same side in the predetermined direction, Through the pipe Flowing a fluid into the inlet header, circulating the fluid into the heat transfer tube to heat the fluid, and flowing out the heated fluid from the outlet header via the outlet communication tube.
  • the boiler including the same, and the heat exchange method according to the present disclosure, it is possible to suppress the temperature difference of the fluid near the outlet end of each heat transfer tube.
  • FIG. 1 is a partial schematic diagram of a coal-fired boiler 100 (hereinafter, simply referred to as “boiler 100”) as an example of a thermal power generation plant in which a heat exchanger according to an embodiment of the present disclosure is adopted. Is shown in.
  • the boiler 100 uses pulverized coal obtained by pulverizing coal by a pulverizer (mill) (not shown) as pulverized fuel (carbon-containing solid fuel), combusts the pulverized coal with a combustion burner, and supplies combustion gas generated by the combustion to water supply or It is a coal-fired (pulverized coal-fired) boiler capable of exchanging heat with steam to generate superheated steam.
  • pulverized fuel carbon-containing solid fuel
  • the boiler 100 has a furnace 110, a combustion device 114, and a flue 102.
  • the furnace 110 has a hollow rectangular shape and is installed along the vertical direction.
  • the furnace wall (heat transfer tube) that constitutes the furnace 110 is composed of a plurality of evaporation tubes and fins that connect them, and suppresses the temperature rise of the furnace wall by exchanging heat with water or steam.
  • the combustion device 114 is provided on the lower side of the furnace wall forming the furnace 110.
  • the combustion device 114 has a plurality of combustion burners 108 mounted on the furnace wall.
  • the combustion burners 108 are arranged at equal intervals along the circumferential direction as one set, and are arranged in a plurality of stages along the vertical direction.
  • the shape of the furnace, the number of combustion burners in one stage, and the number of stages are not limited to this form.
  • Each combustion burner 108 is connected to the mill via a pulverized coal supply pipe (not shown).
  • a rotary table is rotatably supported in a housing, and a plurality of rollers are rotatably supported above the rotary table in association with the rotation of the rotary table.
  • the carrier gas primary air
  • a wind box 116 is provided at a mounting position of each combustion burner 108.
  • the air box 116 is connected to the other end of an air duct 118 having a blower (not shown) at one end.
  • the flue 102 is connected to the upper part of the furnace 110.
  • the flue 102 is provided with a superheater 104, a reheater 106, and a economizer 112 as heat exchangers for recovering the heat of the combustion gas, and the combustion gas generated by the combustion in the furnace 110. And heat is exchanged between the feed water and steam flowing through each heat exchanger.
  • the heat exchanger 1A is adopted as a superheater 104 and a reheater 106 arranged in the flue 102 of the boiler 100 shown in FIG. 1, for example, and is a suitable heat exchanger.
  • the heat exchanger 1A includes one inlet header 10, two outlet headers 20 and a plurality of heat transfer tubes 40.
  • the inlet header 10 is, for example, a tubular member having a cylindrical shape that extends in a predetermined direction that corresponds to the left-right direction on the paper surface of FIG.
  • the inlet header 10 is made of metal such as low alloy steel, high alloy steel, and stainless steel.
  • an inlet communication pipe 12 that connects the inlet passage 14 formed in the inlet header 10 and the outside of the inlet header 10 is provided.
  • the inlet communication pipe 12 is provided only at one end in the predetermined direction (the left end on the paper surface). On the other hand, the other end (the right end on the paper surface) where the inlet communication pipe 12 is not provided is closed.
  • the outlet header 20 is a cylindrical tubular member extending in a predetermined direction that corresponds to the left-right direction on the paper surface of the same figure.
  • the outlet header 20 is made of metal such as low alloy steel, high alloy steel, and stainless steel.
  • the outlet header 20 is provided above the sheet surface of the inlet header 10. In the figure, there are two outlet headers 20. In the following description, reference numerals 20a and 20b are used when it is necessary to distinguish them, and reference numeral 20 is simply used in the case of matters common to each outlet header 20.
  • an outlet communication pipe 22 that connects the outlet flow path 24 formed in the outlet header 20 and the outside of the outlet header 20 is provided.
  • each outlet communication pipe 22 of the first outlet header 20a and the second outlet header 20b is provided only at one end on the same side as the side where the inlet communication pipe 12 is provided in the predetermined direction. On the other hand, the other end (right end in the drawing) where the outlet communication pipe 22 is not provided is closed.
  • the above-mentioned inlet header 10 and each outlet header 20 are connected by a plurality of heat transfer tubes 40.
  • the heat transfer tube 40 is a tubular member extending in the vertical direction on the paper surface of the figure.
  • the heat transfer tube 40 is made of metal such as low alloy steel, high alloy steel, and stainless steel.
  • the upper end portion of the heat transfer tube 40 (that is, the end portion on the outlet header 20 side) is open and serves as an outlet end.
  • the lower end portion of the heat transfer tube 40 (that is, the end portion on the inlet header 10 side) is also open and serves as an inlet end.
  • a heat exchange channel 41 is formed in the heat transfer tube 40, and a fluid flows therethrough.
  • the circulating fluid is, for example, water or steam, and is steam in the present embodiment.
  • the plurality of heat transfer tubes 40 are arranged along the predetermined direction at predetermined intervals. Although eight heat transfer tubes 40 are arranged in a predetermined direction in the same drawing, in reality, about 100 to 1000 heat transfer tubes 40 may be arranged.
  • the outlet ends of the plurality of heat transfer tubes 40 are alternately connected to the first outlet header 20a and the second outlet header 20b along a predetermined direction.
  • the heat transfer pipes 40 on the left side in the figure are alternately connected in order such as a first outlet header 20a, a second outlet header 20b (hereinafter the same).
  • a first outlet header 20a a second outlet header 20b
  • the first outlet header 20a, the second outlet header 20b, the third outlet header 20c (hereinafter the same) in order from the left heat transfer tube 40. In order) ... will be connected alternately.
  • the outlet end of one heat transfer tube 40 is configured to be connected to an outlet header 20 different from the outlet header 20 to which the adjacent heat transfer tube 40 is connected. That is, when the number of the outlet headers 20 is three, for example, from the heat transfer tube 40 on the left side, the second outlet header 20b, the first outlet header 20a, the third outlet header 20c (hereinafter the same) are alternately arranged. May be connected, or any other combination may be used.
  • each inlet end of the plurality of heat transfer tubes 40 is connected to the inlet header 10 along a predetermined direction as shown in FIG.
  • all the heat transfer tubes 40 connected to the two outlet headers 20 are connected to the inlet header 10. That is, the first outlet header 20a and the second outlet header 20b are associated with the connection relationship by the inlet header 10 and the heat transfer tube 40, respectively.
  • the heat exchanger 1A is installed in the flue 102 through which the high temperature combustion gas generated in the furnace 110 flows. Therefore, the steam flowing through the heat exchange flow passage 41 in each heat transfer tube 40 is heated by the heat exchange with the combustion gas flowing around the heat transfer tube 40, and the temperature rises.
  • the heated steam flows from the heat transfer tube 40 into the outlet passage 24 in each outlet header 20 and is collected.
  • the collected steam is taken out from each outlet connecting pipe 22 provided in each outlet header 20.
  • each temperature side Steam can be collected from the heat transfer tubes 40 arranged in the area into the outlet headers 20 so that the total amount of heat becomes substantially equal. Because the heat transfer tubes 40 arranged along the predetermined direction are alternately connected to each outlet header 20 (in order with regularity), the plurality of heat transfer tubes 40 located in each temperature side region are This is because the outlet headers 20 are connected to each other in an approximately equal number. In the case of FIG. 2, of the four heat transfer tubes 40 located in the high temperature side region, two are connected to the first outlet header 20a and two are connected to the second outlet header 20b. The same applies to the four heat transfer tubes 40 located in the low temperature region.
  • the cross-sectional area of the inlet channel 14 of the inlet header 10 in the flow direction and the cross-sectional area of the two outlet channels 24 of each outlet header 20 in the flow direction are set according to the flow rate of the passing steam.
  • the cross-sectional area of the inlet channel 14 may be smaller than the total cross-sectional area of the two outlet channels 24.
  • the steam existing in the outlet flow path 24 of the outlet header 20 has a higher temperature by the amount of heat that is heated by the heat exchange with the combustion gas, and the volume of the steam increases. The flow rate also increases.
  • the total cross-sectional area of the two outlet flow passages 24 is larger than the cross-sectional area of the inlet flow passage 14 (that is, the cross-sectional area of the inlet flow passage 14 is larger than that of the two outlet flow passages 24) in consideration of an increase in volume flow rate.
  • the flow velocity distribution of steam along a predetermined direction which will be described later, is likely to be substantially uniform.
  • the cross-sectional areas of the outlet flow paths 24 may be configured to be substantially the same.
  • the flow velocity of the steam along the predetermined direction in the inlet flow path 14 of the inlet header 10 becomes slower from one end where the inlet communication pipe 12 is provided to the other end (from the left end to the right end on the paper surface shown in the figure). This is because the steam that has flowed into the inlet header 10 flows out into the outlet header 20 via the heat transfer tube 40, so that the steam in the inlet passage 14 from one end where the inlet communication pipe 12 is provided to the other end. This is due to the gradual decrease in the flow rate of. With the change of the flow velocity, the dynamic pressure distribution of the steam along the predetermined direction in the inlet passage 14 decreases from one end to the other end (solid line shown in graph (a)).
  • the flow velocity of steam in the outlet flow path 24 increases from the other end toward one end where the outlet communication pipe 22 is provided (from the right end to the left end on the paper surface shown in the figure). This is because the amount of vapor in the outlet flow path 24 gradually increases from the other end toward one end where the outlet communication pipe 22 is provided.
  • the dynamic pressure distribution of the steam along the predetermined direction in the outlet passage 24 decreases from one end to the other end (solid line shown in graph (b)).
  • the total pressure of the outlet flow path 24 is constant regardless of the position, and the steam flow rate gradually increases from the other end toward the one end. Taking this into consideration, the static pressure distribution of steam along the predetermined direction in the outlet flow path 24 rises from one end to the other end (dotted line shown in graph (b)).
  • the flow velocity of the steam flowing through each heat transfer tube 40 depends on the differential pressure between the static pressure of the inlet passage 14 and the static pressure of the outlet passage 24. Specifically, the flow velocity of the steam flowing through the plurality of heat transfer tubes 40 arranged along the predetermined direction is the static pressure distribution of the inlet passage 14 and the static pressure distribution of the outlet passage 24 along the predetermined direction. Depends on the differential pressure of. The static pressure distribution of the inlet passage 14 and the static pressure distribution of the outlet passage 24 along the predetermined direction both rise from one end to the other end as described above. Therefore, the distribution of the static pressure difference is a distribution in which the uniformity is improved along the predetermined direction and a large difference is eliminated (graph (c)).
  • the flow velocity difference of the steam passing through each heat transfer tube 40 due to the position of each heat transfer tube 40 along the predetermined direction is suppressed, and the flow velocity distribution of the steam passing through each heat transfer tube 40 along the predetermined direction is suppressed.
  • the dynamic pressure distribution and the static pressure distribution of the steam along the predetermined direction in the inlet passage 14 of the inlet header 10 are the same as those in the graph (a) of FIG. Decreases from one end to the other end (solid line shown in graph (a)).
  • the static pressure distribution of the steam along the predetermined direction in the inlet flow path 14 rises from one end to the other end (dotted line shown in graph (a)).
  • the dynamic pressure distribution and the static pressure distribution of the steam along the predetermined direction in the outlet passage 24 show a tendency opposite to that in FIG. 4 in the predetermined direction, unlike the graph (b) of FIG. That is, the dynamic pressure distribution of steam rises from one end to the other end (solid line shown in graph (b)).
  • the static pressure distribution of the steam along the predetermined direction in the outlet channel 24 decreases from one end to the other end (dotted line shown in graph (b)).
  • the distribution of the static pressure difference between the static pressure distribution in the inlet passage 14 and the static pressure distribution in the outlet passage 24 is a distribution that greatly increases along a predetermined direction (graph (c)). Therefore, due to the position of each heat transfer tube 40 along the predetermined direction, a difference in the flow velocity of the steam flowing through each heat transfer tube 40 occurs. In the case of the same figure, the flow velocity of the steam flowing in the heat transfer tube 40 on the right side becomes faster than that of the heat transfer tube 40 on the left side of the drawing.
  • the heat exchanger 1A is provided in the flue 102 of the boiler 100, as shown in FIG. 2, when the flow velocity and temperature of the combustion gas flowing through the flue 102 are uneven and uneven in a predetermined direction (for example, Even if it is divided into two regions of a high temperature side region and a low temperature side region), the total amount of heat becomes substantially even from the heat transfer tubes 40 arranged in each temperature side region into each outlet header 20, The steam can be collected so that the temperature difference between the headers 20 is reduced. Therefore, it is possible to suppress the temperature difference generated in the steam flowing out from each outlet communication pipe 22 after flowing through each heat transfer pipe 40 and being collected in each outlet header 20.
  • each heat transfer tube 40 it is possible to suppress the difference in the flow rate of the steam flowing through the heat exchange flow passage 41 in each heat transfer tube 40. Further, for example, if a flow velocity difference occurs in the steam flowing through the heat exchange flow passage 41, a difference occurs in the heat absorption amount of the steam flowing through the individual heat transfer tubes 40. In addition to this difference in the amount of heat absorption, if the unevenness in the temperature of the combustion gas described above is added, the difference in the temperature of the steam near the outlet end of each heat transfer tube 40 is further increased. Therefore, the performance of the heat exchange amount as the heat exchanger is deteriorated, and it is necessary to raise the design temperature of each device configured as the heat exchanger, which may increase the equipment cost.
  • the heat exchanger 1A of the present embodiment by suppressing the difference in the flow rate of the steam flowing through the heat exchange flow passages 41 in each heat transfer tube 40, it occurs between the steam near the outlet end of each heat transfer tube 40.
  • the temperature difference can be suppressed.
  • the flow rate of steam collected in each outlet header 20 can be made substantially uniform.
  • the number of heat transfer tubes 40 connected to each outlet header 20 can be reduced.
  • the diameter of the outlet header 20 can be reduced as the flow rate introduced to each outlet header 20 decreases.
  • the space occupied by the heat transfer tube 40 protruding from the outlet header 20 can be reduced.
  • the number of heat transfer tubes 40 connected to each outlet header 20 can be halved as shown in the cross-sectional view of FIG. 7.
  • the space occupied by the heat transfer tubes 40 protruding from each outlet header 20 becomes smaller. Therefore, the heat exchanger 1A can be easily arranged in the flue 102 of the boiler 100.
  • the heat exchanger 1B according to the second embodiment of the present disclosure will be described.
  • the present embodiment is different from the first embodiment in the form relating to the inlet header, and is the same in other respects. Therefore, only the points different from the first embodiment will be described, and other elements will be denoted by the same reference numerals and the description thereof will be omitted.
  • the heat exchanger 1B includes two inlet headers 10.
  • the symbols 10a and 10b are used when it is necessary to distinguish them from each other, and the symbol 10 is simply used when the items are common to the respective entrance headers 10.
  • the respective inlet communication pipes 12 of the first inlet header 10a and the second inlet header 10b are provided only at one end on the same side as the side where the outlet communication pipe 22 is provided in the predetermined direction. In the case of the same drawing, all the inlet communication pipes 12 and the outlet communication pipes 22 are provided on the same side (left side in the drawing of the drawing) in a predetermined direction.
  • the inlet ends of the plurality of heat transfer tubes 40 are alternately connected to the first inlet header 10a and the second inlet header 10b.
  • the heat transfer tubes 40 on the left side of the drawing in the figure are sequentially connected in an alternating manner (order having regularity) such as a first inlet header 10a, a second inlet header 10b (hereinafter the same order). ing.
  • all the heat transfer tubes 40 connected to the first outlet header 20a are connected to one inlet header 10 (the first inlet header 10a in the figure) and the connection relationships are associated. Further, all the heat transfer tubes 40 connected to the second outlet header 20b are connected to the other inlet header 10 (the second inlet header 10b in the figure) to be associated with the connection relationship. That is, all the heat transfer tubes 40 connected to the one outlet header 20 are connected to the one inlet header 10 without being connected to the plurality of inlet headers 10, and the connection relationships are associated with each other. All the heat transfer tubes 40 connected to the other outlet headers 20 are not connected to the plurality of inlet headers 10 but are connected to the other inlet headers 10 and the connection relationships are associated.
  • the total amount of heat is approximately equalized into each outlet header 20, and the steam can be collected so that the temperature difference between the outlet headers 20 is reduced. Therefore, it is possible to suppress the temperature difference that occurs in the steam flowing out of the outlet communication pipes 22 after flowing through the heat transfer pipes 40 and collected in the outlet headers 20.
  • each outlet header 20 can be made substantially uniform.
  • each outlet header 20 can be made smaller as the flow rate introduced to each outlet header 20 decreases, and the heat transfer tube 40 protruding from each outlet header 20 can be provided. Can occupy less space. Therefore, the heat exchanger 1B can be easily arranged in the flue 102 of the boiler 100.
  • each inlet header 10 can be reduced as the flow rate flowing through each inlet header 10 decreases, and the heat transfer tube 40 that extends from each inlet header 10 can be achieved. Can occupy less space. Therefore, the heat exchanger 1B can be easily arranged in the flue 102 of the boiler 100.
  • the outlet communication pipes 22 provided in the respective outlet headers 20 are provided on the same side in the predetermined direction, the inlet communication pipes 12 and the outlet communication pipes 22 are integrated on the same side in the predetermined direction, so The workability when assembling the exchanger can be improved.
  • the inlet connecting pipe 22 is provided on one side in the predetermined direction. Since the connecting pipe 12 and the outlet connecting pipe 22 are not integrated, it becomes easy to arrange the pipes connected to them.
  • the outer diameter of the inlet header 10 should be set to be an appropriate flow rate. Although it must be made larger, there is a possibility that the larger the outer diameter, the thicker the wall thickness to increase the strength and the more manufacturing steps therefor. Since the diameter of the inlet header 10 can be reduced by using a plurality of inlet headers 10 as described above, such a manufacturing problem does not occur.
  • the heat exchanger 1C according to the third embodiment of the present disclosure will be described.
  • the present embodiment is different from the first embodiment and the second embodiment in the form relating to the inlet header, and is the same in other points. Therefore, only the points different from the first and second embodiments will be described, and other elements will be denoted by the same reference numerals and description thereof will be omitted.
  • the heat exchanger 1C includes one third inlet header 10c. Similar to the first embodiment, the two outlet headers 20 are connected to the third inlet header 10c by the heat transfer tubes 40. That is, the first exit header 20a and the second entrance header 10b are associated with the third entrance header 10c, respectively.
  • the outlet communication pipe 22 of the first outlet header 20a is provided in a direction different from the outlet communication pipe 22 of the second outlet header 20b in a predetermined direction. Further, the inlet communication pipes 12 of the third inlet header 10c are provided at both ends in the predetermined direction so that the connection relations correspond to the respective outlet communication pipes 22.
  • the inlet connecting pipe 12 at one end of the third inlet header 10c is the outlet of the outlet header 20b connected to the third inlet header 10c.
  • the direction of the connecting pipe 22 is on the same side.
  • the direction of the outlet communication pipe 22 of the outlet header 20a connected to the third inlet header 10c is the same on the inlet communication pipe 12 at the other end of the third inlet header 10c (on the right side of the drawing). It is a thing.
  • the third inlet header 10c is configured in common.
  • the inlet connecting pipe 12 at one end of the third inlet header 10c and the outlet connecting pipe 22 of the outlet header 20b are in a pair, and the inlet connecting pipe 12 at the other end of the third inlet header 10c and the outlet header 20a are connected.
  • the outlet connecting pipe 22 is in a pair. This is because the inlet connection pipe of one inlet header and the outlet connection pipe of one outlet header are in a pair, the inlet connection pipe of the other inlet header and the outlet connection pipe of another outlet header are in a pair, and each pair is It is equivalent to a heat exchanger located on the opposite side in a given direction.
  • the first inlet header 10a and the second inlet header 10b of the heat exchanger 1B according to the second embodiment shown in FIG. 9 are provided as one common inlet header, the third inlet header 10c. Is equivalent to
  • the flow passage area of the third inlet header 10c may be larger than the flow passage area of the outlet header 20.
  • the flow passage area of the third inlet header 10c is appropriate depending on the size of the heat exchanger 1C, the steam flow rate, the flow passage cross-sectional area of the heat exchange flow passage 41 of each heat transfer tube 40, the predetermined length of the third inlet header 10c, and the like.
  • the flow passage area of the third inlet header 10c is 1 to 2 times the flow passage area of the outlet header 20.
  • each outlet header 20 can be made smaller as the flow rate introduced to each outlet header 20 decreases, and the heat transfer tube 40 protruding from each outlet header 20 can be provided. Can occupy less space. Therefore, the heat exchanger 1C can be easily arranged in the flue 102 of the boiler 100.
  • the outlet communication pipe 22 provided in the first outlet header 20a is provided on the side different from the outlet communication pipe 22 provided in the second outlet header 20b in a predetermined direction, and the inlet communication pipe 12 is the third inlet header 10 Are provided at both ends of. For this reason, since the inlet communication pipe 12 and the outlet communication pipe 22 are not gathered on one side in the predetermined direction, it becomes easy to arrange the pipes connected to them. Therefore, the heat exchanger 1C can be easily arranged in the flue 102 of the boiler 100.
  • the flow passage area in the third inlet header 10c is increased, it is possible to suppress the flow velocity difference of the steam flowing through the heat exchange flow passage 41 in each heat transfer tube 40. Therefore, it is possible to suppress the temperature difference generated in the steam near the outlet end of each heat transfer tube 40. Further, the flow rate of steam collected in each outlet header 20 can be made substantially uniform.
  • the present disclosure is not limited to the invention according to each of the above-described embodiments, and can be appropriately modified without departing from the gist thereof.
  • the present disclosure is a gas-fired boiler, an oil-fired boiler, an exhaust heat recovery boiler (HRSG: Heat). Recovery Steam Generator), fluidized bed boiler (BFB: Bubbling Fluidized Bed) may be applied to equipment provided with a heat exchanger.
  • HRSG Heat. Recovery Steam Generator
  • BFB Bubbling Fluidized Bed

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur destiné à supprimer une différence de température de fluides autour des extrémités de sortie de tubes de transfert de chaleur respectifs, une chaudière équipée de l'échangeur de chaleur et un procédé d'échange de chaleur. Cet échangeur de chaleur comprend : un ou plusieurs collecteurs d'entrée (10) qui s'étendent dans une direction prescrite et qui comportent des tubes de raccordement d'entrée (12) disposés aux extrémités dans la direction prescrite de façon à être reliés à l'extérieur ; une pluralité de collecteurs de sortie (20) qui s'étendent dans la direction prescrite et qui comportent des tubes de raccordement de sortie (22) disposés uniquement aux extrémités dans la direction prescrite de façon à être reliés à l'extérieur ; et une pluralité de tubes de transfert de chaleur (40) qui sont disposés en réseau dans la direction prescrite, comportent des extrémités de sortie reliées en alternance aux collecteurs de sortie (20) le long de la direction prescrite, et comportent des extrémités d'entrée, qui sont les autres extrémités par rapport aux extrémités de sortie reliées à un collecteur de sortie (20), reliées à un collecteur d'entrée (10). Les tubes de raccordement de sortie (22) et les tubes de raccordement d'entrée (12) corrélés les uns aux autres par les tubes de transfert de chaleur (40) communs sont disposés sur le même côté dans la direction prescrite.
PCT/JP2019/038512 2018-11-05 2019-09-30 Échangeur de chaleur, chaudière équipée d'un échangeur de chaleur, et procédé d'échange de chaleur Ceased WO2020095572A1 (fr)

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JP2018208046A JP7202851B2 (ja) 2018-11-05 2018-11-05 熱交換器及びそれを備えたボイラ、並びに熱交換方法
JP2018-208046 2018-11-05

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996023187A1 (fr) * 1995-01-27 1996-08-01 Ail Research, Inc. Ensemble echangeur thermique
WO2012017681A1 (fr) * 2010-08-05 2012-02-09 三菱電機株式会社 Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération
JP2018009762A (ja) * 2016-07-15 2018-01-18 株式会社Ihi 熱交換器及びボイラ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5843391A (ja) * 1981-09-07 1983-03-14 Nissan Motor Co Ltd 多管式熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996023187A1 (fr) * 1995-01-27 1996-08-01 Ail Research, Inc. Ensemble echangeur thermique
WO2012017681A1 (fr) * 2010-08-05 2012-02-09 三菱電機株式会社 Échangeur de chaleur et dispositif de conditionnement d'air et de réfrigération
JP2018009762A (ja) * 2016-07-15 2018-01-18 株式会社Ihi 熱交換器及びボイラ

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