Modularized boiler radiation heat exchanger

Abstract

The invention relates to the technical field of boiler design, and particularly discloses a modularized boiler radiation heat exchanger which comprises a platen superheater tube panel, an inlet header assembly connected with the inlet end of the platen superheater tube panel and an outlet header assembly connected with the outlet end of the platen superheater tube panel. The platen superheater tube panel comprises a plurality of groups of heating surface modules which are respectively connected with the outlet header assembly and the inlet header assembly; and each group of heating surface module comprises a plurality of groups of heating modules which are sequentially stacked along the flow direction of flue gas. Under the condition that a throttling hole is not adopted, the steam-water resistance and the wall temperature deviation of the heating surface are reduced at the same time, the manufacturing difficulty of the heating surface and the header is reduced, and under the condition that the average mass flow rate is the same, the resistance of the heating surface can be reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of boiler design, and more specifically, to a modular boiler radiant heat exchanger. Background Art

[0002] Thermal power based on coal has always been the dual main body of China's power supply and carbon dioxide emissions. The progress of thermal power technology is one of the essential paths to reduce carbon emissions. From 2006 to 2023, the contribution rate of reducing the coal consumption for power supply in coal-fired power generation to carbon dioxide emission reduction in the power industry was 39.7%.

[0003] Increasing parameters is an important technical path to improve power generation efficiency, reduce the coal consumption for power supply and carbon emissions. At present, China's thermal power has developed from the early medium temperature and medium pressure parameters to the world-leading high-efficiency ultra-supercritical parameters, and the standard coal consumption for power supply has been reduced from about 480 g / kw.h to 250 - 280 g / kw.h. With the continuous increase of the parameters of thermal power units, the metal wall temperature of boiler components is getting higher and higher, and the design margin of materials is getting smaller and smaller. When operating at low loads and rapidly changing loads, the risk of overheating of the boiler radiant heating surface is also increasing, which greatly limits the operating flexibility of thermal power units.

[0004] With the rapid increase in the installed capacity of unstable power sources such as wind power and photovoltaic power, the power grid has put forward higher requirements for the peak shaving rate and operating flexibility of thermal power. At present, the load increase rate of domestic thermal power units generally can only reach 1 - 2%, but newly built units need to reach more than 3%, and newly built demonstration units need to reach more than 4%. A higher load change rate means a greater overheating risk. The new requirements of the new power grid for thermal power units urgently call for the progress of thermal power technology. To better play the role of thermal power as the "ballast stone" and "pillar" of energy and power security, thermal power boilers need to further strive to reduce the wall temperature deviation of the heating surface and improve operating flexibility.

[0005] The wall temperature deviation of the boiler heating surface mainly comes from the working medium flow deviation, heat load deviation and heating area deviation.

[0006] Currently, the platen superheater (radiant heat exchanger) of existing ultra (ultra)-critical pulverized coal boilers is arranged above the furnace, as Figure 7 shown. As Figure 8As shown in the figure, the tube screen 2 is arranged in multiple screens along the furnace width direction of the furnace 1 and one screen along the furnace depth direction of the furnace 1. It includes front and rear row tube screens, and the tubes in the tube screen 2 are arranged in parallel in a U shape; the outlet header of the platen superheater includes a large platen superheater outlet header 4 and a small platen superheater outlet header 6, and the inlet header of the platen superheater includes a large platen superheater inlet header 5 and a small platen superheater inlet header 7, which are respectively in a comb structure. The large platen superheater outlet header 4 is parallel to the front and rear walls of the boiler, and the small platen superheater outlet header 6 is vertically installed on the large platen superheater outlet header 4. The outlet header and the inlet header of the platen superheater are arranged vertically in the height direction; the working medium flow path is: the large platen superheater inlet header 5, the small platen superheater inlet header 7, the tube screen 2, the small platen superheater outlet header 6, and the large platen superheater outlet header 4. In this solution, the outer tubes in the tube screen 2 are long and the inner tubes are short. Especially, the outermost radiation heating surface has the largest area; at the same time, in this solution, the outer tubes have a large heat load and the inner tubes have a small heat load, and the heat load difference between the inner and outer tubes is large; this makes the heat absorption difference between the inner and outer tubes relatively large. Currently, the flow rate of each tube is mainly adjusted by setting throttle holes on the header to reduce the wall temperature deviation, but this will increase the steam-water resistance.

[0007] Taking the platen superheater commonly used in domestic current ultra (ultra) supercritical π-type boilers as an example, the outermost tubes are about 16% longer than the innermost tubes, and the heat transfer area is about 43% larger than the innermost tubes. Coupled with a large heat load deviation, the outer tubes absorb more heat. The design has to consider enlarging the outer tube diameter and setting throttle holes on the header to forcibly increase the mass flow rate of the outer tubes. This makes the mass flow velocity of the outer tubes 25 - 40% larger than the average value, increasing the resistance of the heating surface. Summary of the Invention

[0008] The technical problem to be solved by the present invention is to provide a modular boiler radiation heat exchanger, which can reduce both the steam-water resistance and the wall temperature deviation of the heating surface without using throttle holes, and reduce the manufacturing difficulty of the heating surface and the header. Under the condition of the same average mass flow velocity, the resistance of the heating surface can be reduced;

[0009] The solution adopted by the present invention to solve the technical problem is:

[0010] A modular boiler radiation heat exchanger includes a platen superheater tube screen, an inlet header assembly connected to the inlet end of the platen superheater tube screen, and an outlet header assembly connected to the outlet end of the platen superheater tube screen;

[0011] The platen superheater tube screen includes multiple groups of heating surface modules respectively connected to the outlet header assembly and the inlet header assembly;

[0012] Each group of the heating surface modules includes multiple groups of heating modules stacked in sequence along the flue gas flow direction.

[0013] In some possible embodiments, the heat-receiving module includes multiple groups of first heat-receiving tube groups and / or second heat-receiving tube groups; the first heat-receiving tube groups are respectively connected to the outlet header assembly and the inlet header assembly; the second heat-receiving tube groups are respectively connected to the outlet header assembly and the inlet header assembly;

[0014] When the heat-receiving module includes multiple groups of first heat-receiving tube groups, the multiple groups of first heat-receiving tube groups are stacked along the flue gas flow direction;

[0015] When the heat-receiving module includes multiple groups of second heat-receiving tube groups, the multiple groups of first heat-receiving tube groups are stacked along the flue gas flow direction.

[0016] In some possible embodiments, the lengths of the multiple groups of first heat-receiving tube groups and / or second heat-receiving tube groups are the same.

[0017] In some possible embodiments, the lengths of the multiple groups of first heat-receiving tube groups and / or second heat-receiving tube groups increase from the outside to the inside.

[0018] In some possible embodiments, the first heat-receiving tube group and the second heat-receiving tube group have the same structure; the first heat-receiving tube group includes tube one, tube two arranged in an interleaved manner with tube one, and tube three arranged between tube one and tube two and in an interleaved manner with tube one and tube two.

[0019] In some possible embodiments, tube one, tube two, and tube three have the same structure and are all U-shaped structures, including a first descending section connected to the inlet header assembly, a first ascending section connected to the outlet header assembly, and an arc section for connecting the first ascending section and the first descending section.

[0020] In some possible embodiments, the second heat-receiving tube group further includes several groups of outer tubes sleeved outside the first heat-receiving tube group and having a U-shaped structure;

[0021] The outer tube has a U-shaped structure and includes a descending outer tube connected to the inlet header assembly, an ascending outer tube connected to the outlet header assembly, and an arc outer tube for connecting the ascending outer tube and the descending outer tube.

[0022] In some possible embodiments, the outlet header assembly includes a large screen superheater outlet header, and multiple groups of small screen superheater outlet headers that are perpendicularly communicated with the large screen superheater outlet header and arranged in sequence along the steam flow direction in the large screen superheater outlet header; the small screen superheater outlet headers are respectively communicated with the first ascending section and the ascending outer tube;

[0023] In some possible embodiments, the inlet header assembly includes a large screen superheater inlet header, and multiple groups of small screen superheater inlet headers that are perpendicularly communicated with the large screen superheater inlet header and arranged in sequence along the steam flow direction in the small screen superheater outlet header; the small screen superheater inlet headers are respectively communicated with the first descending section and the descending outer tube.

[0024] In some possible embodiments, the platen superheater tube bank is provided in multiple groups and is correspondingly arranged and interconnected with the platen superheater outlet header and the platen superheater inlet header one by one.

[0025] In some possible embodiments, the lengths of the first tube, the second tube, the third tube, and the outer tube are equal or unequal, and the diameters of the first tube, the second tube, the third tube, and the outer tube are equal or unequal.

[0026] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0027] In the present invention, a heating module group is formed by multiple groups of heating modules arranged in sequence along the flue gas flow path. As a result, the rising section, the falling section, the rising outer tube, and the falling outer tube in the U-shaped tubes in each heating module will not be simultaneously located on the outermost side, thereby reducing the average heat load deviation and the difference in heating area between the heating modules, and thus reducing the heat absorption deviation.

[0028] By adjusting the lengths and diameters of the first tube, the second tube, the third tube, and the outer tube, the present invention makes the heat absorption match the flow rate. When the mass velocity deviation does not exceed 3%, a wall temperature deviation smaller than that of the prior art can be obtained, and there is no need to adopt additional measures to adjust the flow rates of different tubes, effectively reducing the resistance of the heating surface.

[0029] Without using throttle holes, the present invention simultaneously reduces the steam-water resistance and the wall temperature deviation of the heating surface, and reduces the manufacturing difficulty of the heating surface and the header. When the average mass velocity is the same, the resistance of the heating surface can be reduced by 30-40%. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 It is a schematic structural diagram of Embodiment 1 of the present invention;

[0031] Figure 2 It is a schematic structural diagram of Embodiment 2 of the present invention;

[0032] Figure 3 It is a schematic structural diagram of Embodiment 3 of the present invention;

[0033] Figure 4 It is a schematic structural diagram of Embodiment 4 of the present invention;

[0034] Figure 5 It is a schematic structural diagram of the first heating tube group in the present invention;

[0035] Figure 6 It is a schematic structural diagram of the second heating tube group in the present invention; Figure 7 It is a schematic layout diagram of a platen superheater or a radiation heat exchanger in the prior art; Figure 8 It is a schematic layout diagram of a tube bank in the prior art;

[0036] Wherein: 1. furnace; 2. tube screen; 3. heating module; 4. large header at the outlet of the platen superheater; 5. large header at the inlet of the platen superheater; 6. small header at the outlet of the platen superheater; 7. small header at the inlet of the platen superheater; 8. heating tube group one; 81. tube one; 82. tube two; 83. tube three; 9. heating tube group two; 91. outer tube. Specific embodiments

[0037] In the present invention, unless otherwise clearly defined and limited, terms such as "installed", "connected", "connected", "fixed", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be directly connected, or indirectly connected through an intermediate medium, and may be the communication inside two components or the interaction relationship between two components. The "first", "second" and similar words mentioned in this application do not indicate any order, quantity or importance, but are only used to distinguish different components. Similarly, words such as "one" or "a" do not indicate a quantity limit, but indicate the existence of at least one. In the implementation of this application, "and / or" describes the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B may indicate: A exists alone, A and B exist simultaneously, and B exists alone. In the description of the embodiments of this application, unless otherwise stated, the meaning of "a plurality" refers to two or more. For example, a plurality of positioning posts means two or more positioning posts. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0038] The present invention will be described in detail below.

[0039] As Figures 1 - 6 shown:

[0040] A modular boiler radiant heat exchanger includes a platen superheater tube screen, an outlet header assembly connected to the inlet end of the platen superheater tube screen, and an inlet header assembly connected to the outlet end of the platen superheater tube screen;

[0041] The platen superheater tube screen includes multiple groups of heating surface modules respectively connected to the outlet header assembly and the inlet header assembly; specifically, multiple groups of the heating surface modules are arranged along the furnace width direction of the furnace in the boiler;

[0042] Each group of the heating surface modules includes multiple groups of heating modules 3 stacked in sequence along the flue gas flow direction;

[0043] As Figures 1 - 4 shown, the heating module 3 includes multiple groups of heating tube group one 8 and / or heating tube group two 9; the heating tube group one 8 is respectively connected to the outlet header assembly and the inlet header assembly; the heating tube group two 9 is respectively connected to the outlet header assembly and the inlet header assembly;

[0044] When the heat receiving module 3 includes multiple groups of first heat receiving tube groups 8, the multiple groups of first heat receiving tube groups 8 are stacked along the flue gas flow direction; specifically, they can be stacked in parallel or symmetrically in sequence;

[0045] When the heat receiving module 3 includes multiple groups of first heat receiving tube groups 8 and second heat receiving tube groups 9, preferably, there are two groups of the second heat receiving tube groups 9 and they are located on both sides of the multiple groups of first heat receiving tube groups 8 along the flue gas flow direction;

[0046] When the heat receiving module 3 includes multiple groups of second heat receiving tube groups 9, the multiple groups of first heat receiving tube groups 8 are stacked along the flue gas flow direction; specifically, they can be stacked in parallel or symmetrically in sequence;

[0047] Through the arrangement of the first heat receiving tube groups 8 and the second heat receiving tube groups 9, each heat receiving surface module is modularly arranged; for the heat absorption deviation of different heat receiving surface modules, the overall length or pipe diameter of the first heat receiving tube groups 8 or the first heat receiving tube groups 8 can be appropriately changed to match the heat absorption amount with the flow rate.

[0048] In some possible implementation manners, the lengths of multiple groups of the first heat receiving tube groups 8 and / or the second heat receiving tube groups 9 are the same; that is:

[0049] When multiple groups of the first heat receiving tube groups 8 are used as the heat receiving module 3, the lengths of the multiple groups of first heat receiving tube groups 8 are the same;

[0050] When multiple groups of the second heat receiving tube groups 9 are used as the heat receiving module 3, the lengths of the multiple groups of second heat receiving tube groups 9 are the same;

[0051] When multiple groups of the first heat receiving tube groups 8 and the second heat receiving tube groups 9 are used as the heat receiving module 3, the lengths of the multiple groups of first heat receiving tube groups 8 and the second heat receiving tube groups 9 of the heat receiving module 3 are the same.

[0052] In some possible implementation manners, the lengths of multiple groups of the first heat receiving tube groups 8 and / or the second heat receiving tube groups 9 increase from the outside to the inside;

[0053] That is, when multiple groups of the first heat receiving tube groups 8 are used as the heat receiving module 3, the lengths of the two outermost groups of first heat receiving tube groups 8 are the same and the shortest, and the lengths of the first heat receiving tube groups 8 in the middle are the same and the longest. When multiple groups of the second heat receiving tube groups 9 are used as the heat receiving module 3, the structure is the same as above;

[0054] When multiple groups of the first heat receiving tube groups 8 and the second heat receiving tube groups 9 are used as the heat receiving module 3, the lengths of the two outermost groups of second heat receiving tube groups 9 are the same and the shortest, and the lengths of the first heat receiving tube groups 8 in the middle are the same and the longest.

[0055] In some possible implementation manners, such as Figure 5As shown, the structure of the first heated tube group 8 is the same as that of the second heated tube group 9; the first heated tube group 8 includes a first tube 81, a second tube 82 arranged in an interleaved manner with the first tube 81, and a third tube 83 arranged between the first tube 81 and the second tube 82 and in an interleaved manner with the first tube 81 and the second tube 82.

[0056] In some possible implementation manners, the first tube 81, the second tube 82, and the third tube 83 have the same structure and are all U-shaped structures, including a first descending section connected to the inlet header assembly, a first ascending section connected to the outlet header assembly, and an arc section for connecting the first ascending section and the first descending section.

[0057] Specifically, as Figure 5 shown, the interleaved arrangement of the second tube 82 and the first tube 81 can be understood as that the descending section of the second tube 82 is located between the descending section and the ascending section of the first tube 81, and the ascending section of the second tube 82 is located outside the first tube 81 and on the side where the ascending section of the first tube 81 is far from the descending section of the second tube 82;

[0058] The ascending section of the third tube 83 is arranged between the ascending section and the descending section of the first tube 81, and the ascending section of the third tube 83 is arranged between the ascending section and the descending section of the second tube 82;

[0059] With this setting, when the above structure is used as the platen superheater tube screen, the first tube 81 and the third tube 83 will have the ascending section or the descending section located on the outermost side, and not the entire pipe will be located on the outermost side, so that the average heat load deviation between tubes and the difference in heating area are both reduced, which reduces the heat absorption deviation of each tube;

[0060] With this setting, the ascending section and the descending section of each tube in the first heated tube group 8 are exactly arranged at intervals, and the connection of each tube (the first tube 81, the second tube 82, and the third tube 83) to the header can adopt the same structure. Under the reference conditions, the lengths of each circle of tubes (the first tube 81, the second tube 82, and the third tube 83) are basically the same, and the number of tubes in a single first heated tube group 8 is only an optimal value and can be adjusted as needed;

[0061] When using at least the first heated tube 81 and two groups of the second heated tube groups 9, and when the same specifications are used for all tubes in the above setting, the heating area of the tubes in the outermost two groups of the second heated tube groups 9 is only 7% larger than that of other tubes, and the heating areas of the remaining tubes are the same; for the first heated tube group 8, the heating areas of the internal tubes are basically the same.

[0062] In some possible implementation manners, as Figure 6 shown, the second heated tube group 9 further includes several groups of outer tubes 91 sleeved outside the first heated tube group 8 and having a U-shaped structure;

[0063] The outer tube 91 has a U-shaped structure and includes a descending outer tube connected to the inlet header assembly, an ascending outer tube connected to the outlet header assembly, and an arc-shaped outer tube for connecting the ascending outer tube and the descending outer tube;

[0064] With this arrangement, the outer tube 91, the descending outer tube, the ascending section, and the descending section of the heating tube group two 9 are exactly arranged at intervals. The connection of each tube (tube one 81, tube two 82, tube three 83, outer tube 91) to the header can adopt the same structure, and the lengths of each tube are similar; the number of tubes in a single module is only an optimal value and can be adjusted as needed.

[0065] In some possible implementation manners, the lengths of the tube one 81, tube two 82, tube three 83, and outer tube 91 are equal or unequal, and the diameters of the tube one 81, tube two 82, tube three 83, and outer tube 91 are equal or unequal.

[0066] Further, the length of the outer tube 91 is H, and the lengths of the tube one 81, tube two 82, and tube three 83 are h, and h is approximately 0.97H; in the heating tube group two 9 with the outer tube 91, the difference in the average heat load of the tubes is smaller, the heat absorption deviation is smaller, and it is more convenient to adjust the overall length of the heating tube group two 9 with the outer tube 91 to absorb heat;

[0067] If it is necessary to further reduce the deviation in the heating tube group one 8 or the heating tube group two 9, the relative diameters or relative lengths of the corresponding tubes in the corresponding tube group can be further adjusted.

[0068] In some possible implementation manners, the outlet header assembly and the inlet header assembly are arranged at the lower part in the height direction;

[0069] The outlet header assembly includes a platen superheater outlet header 4 and multiple groups of platen superheater outlet headers 6 that are perpendicularly connected to the platen superheater outlet header 4 and are arranged in sequence along the steam flow direction in the platen superheater outlet header 4; the platen superheater outlet headers 6 are respectively connected to the ascending section one and the ascending outer tube;

[0070] The inlet header assembly includes a platen superheater inlet header 5 and multiple groups of platen superheater inlet headers 7 that are perpendicularly connected to the platen superheater inlet header 5 and are arranged in sequence along the steam flow direction in the platen superheater outlet header 6; the platen superheater inlet headers 7 are respectively connected to the descending section one and the descending outer tube; the platen superheater outlet header 4 and the platen superheater inlet header 5 are arranged on the same side;

[0071] Further, the platen superheater outlet header 4 and the platen superheater outlet headers 6 are relatively perpendicular and arranged in a comb shape, and all the platen superheater outlet headers 6 will be arranged on the same side; the platen superheater inlet header 5 and the platen superheater inlet headers 7 are relatively perpendicular and arranged in a comb shape, and all the platen superheater outlet headers 6 will be arranged on the same side; the platen superheater outlet header 4 and the platen superheater inlet header 5 are arranged in parallel, and the platen superheater inlet headers 7 and the platen superheater outlet headers 6 are arranged in parallel.

[0072] In some possible embodiments, the platen superheater tube bank is provided in multiple groups and is correspondingly arranged and interconnected with the platen superheater outlet header 6 and the platen superheater inlet header 7 one by one.

[0073] Embodiment 1:

[0074] Refer to Figure 1 , when 6 groups of heating tube groups 8 and 2 groups of heating tube groups 9 with the same structure as the heating tube groups 8 are used as a platen superheater tube bank, each group of heating tube groups 8 includes a group of tubes 81, a group of tubes 82, and a group of tubes 83. By parallel stacking, a platen superheater tube bank formed by 24 turns of tubes can be obtained. Among the 6 groups, the lengths of the 4 middle groups of heating tube groups 8 are A, the lengths of the heating tube groups 8 on both sides of the 4 groups of heating tube groups 8 are B, and the length of the heating tube group 9 is C. A - C = 1500 mm, A - B = 500 mm; through the above settings, a uniform wall temperature can be obtained.

[0075] Of course, the specific length change can be adjusted according to the actual situation.

[0076] Furthermore, in this example, the wall temperature deviation can be further reduced by adjusting the pipe diameter of the heating tube group 9.

[0077] Embodiment 2:

[0078] Refer to Figure 2 , when 6 groups of heating tube groups 8 and 2 groups of heating tube groups 9 with the same structure and size as the heating tube groups 8 are used as a platen superheater tube bank, a platen superheater tube bank formed by 24 turns of tubes can be obtained by parallel stacking. By enlarging the pipe diameters of the two groups of heating tube groups 9, a relatively uniform wall temperature can be obtained.

[0079] Furthermore, in this example, on the basis of the pipe diameter change, the lengths of the heating tube group 8 and the heating tube group 9 can be adjusted to further improve the wall temperature uniformity; the ranges of enlarging the pipe diameter and adjusting the length can be determined according to the needs during actual design.

[0080] Embodiment 3:

[0081] Refer to Figure 3 , when 4 groups of heating tube groups 9 are used as a platen superheater tube bank, each group of heating tube groups 9 includes a group of tubes 81, a group of tubes 82, a group of tubes 83, and three groups of outer tubes 91; among them, the lengths of the two outer groups of heating tube groups 9 are F, and the lengths of the other two groups of heating tube groups 8 are E. E - F = 1500 mm; a platen superheater tube bank formed by 24 turns of tubes can be obtained by parallel stacking, and a relatively uniform wall temperature can be obtained. The specific length change can be adjusted according to the actual situation;

[0082] Furthermore, the diameter of the outermost outer tube 91 of the outer heat-receiving tube group two 9 can be changed to further reduce the deviation.

[0083] Embodiment 4:

[0084] See the appendix Figure 4 When using 4 groups of heat-receiving tube groups one 8 and 2 groups of heat-receiving tube groups two 9 as a group of platen superheater tube screens, a group of platen superheater tube screens with 24 turns of tubes can be obtained by parallel stacking. The length of the two groups of heat-receiving tube groups two 9 is J, and the length of the two middlemost groups of heat-receiving tube groups one 8 is K. The length of the heat-receiving tube groups one 8 between the two middlemost groups of heat-receiving tube groups one 8 and the heat-receiving tube groups two 9 is L, K - J = 1500 mm, K - L = 300 mm; a relatively uniform wall temperature can be obtained.

[0085] Furthermore, by reasonably adjusting the diameter of the heat-receiving tube group two 9 and the relative length between the tube groups, the deviation can be further reduced.

[0086] In summary, the platen superheater tube screen in the present invention is composed of the heat-receiving tube group one 8 and / or the heat-receiving tube group two 9; the structures are similar, and the flow rate and heat load uniformity are good; during implementation, according to the working conditions and design requirements, the wall temperature uniformity inside the module can be further improved by changing the relative length and diameter of the tubes.

[0087] For the deviation between the heat-receiving tube groups in the same platen superheater tube screen, the deviation can be reduced by adjusting the overall relative length and the relative size of the tube diameters of each heat-receiving tube group. During actual use, different heat-receiving tube groups can be arbitrarily combined to form a platen superheater tube screen.

[0088] The present invention is not limited to the foregoing specific embodiments. The present invention extends to any new feature or any new combination disclosed in this specification, as well as any new method or process step or any new combination disclosed.

Claims

1. A modular boiler radiation heat exchanger, characterized in that: It includes a platen superheater tube panel, an inlet header assembly connected to the inlet end of the platen superheater tube panel, and an outlet header assembly connected to the outlet end of the platen superheater tube panel; The platen-type superheater tube plate comprises a plurality of groups of heating surface modules respectively connected to the outlet header assembly and the inlet header assembly; each group of the heating surface modules comprises a plurality of groups of heating modules stacked in sequence along the flue gas flow direction.

2. A modular boiler radiation heat exchanger according to claim 1, characterized in that: The heating module comprises a plurality of groups of heating tube groups 1 and / or heating tube groups 2; the heating tube groups 1 are respectively connected to the outlet header assembly and the inlet header assembly; the heating tube groups 2 are respectively connected to the outlet header assembly and the inlet header assembly.

3. A modular boiler radiation heat exchanger according to claim 2, characterized in that: When the heating module includes multiple groups of heating tube groups one, the multiple groups of heating tube groups one are stacked along the flue gas flow direction.

4. A modular boiler radiation heat exchanger according to claim 2, characterized in that: When the heating module includes multiple groups of heating tube groups 2, the multiple groups of heating tube groups 1 are stacked along the flue gas flow direction.

5. A modular boiler radiation heat exchanger according to claim 2, characterized in that: The lengths of the plurality of groups of heated tube groups 1 and / or heated tube groups 2 are the same.

6. A modular boiler radiation heat exchanger according to claim 2, characterized in that: The lengths of the plurality of groups of heated tube groups 1 and / or heated tube groups 2 increase from outside to inside.

7. A modular boiler radiation heat exchanger according to any one of claims 2 to 6, characterized in that: The structure of the heated tube group 1 is the same as that of the heated tube group 2; the heated tube group 1 includes tube 1, tube 2 arranged alternately with tube 1, and tube 3 arranged between tube 1 and tube 2 and arranged alternately with tube 1 and tube 2; the structures of tube 1, tube 2 and tube 3 are the same and are all U-shaped structures; they include a descending section 1 connected to the inlet header assembly, an ascending section 1 connected to the outlet header assembly, and an arc section for connecting the ascending section 1 and the descending section 1.

8. A modular boiler radiation heat exchanger according to claim 7, characterized in that: The second heat receiving tube group also includes a plurality of outer tubes which are sleeved on the outside of the first heat receiving tube group and have a U-shaped structure; The outer tube has a U-shaped structure and includes a descending outer tube connected to the inlet header assembly, an ascending outer tube connected to the outlet header assembly, and an arc-shaped outer tube used to connect the ascending outer tube and the descending outer tube.

9. A modular boiler radiation heat exchanger according to claim 8, characterized in that: The lengths of the first tube, the second tube, the third tube and the outer tube are equal or unequal, and the diameters of the first tube, the second tube, the third tube and the outer tube are equal or unequal.

10. A modular boiler radiation heat exchanger according to claim 1, characterized in that: The platen-type superheater tube plates are multiple groups and are arranged one-to-one with the platen-through outlet small header in the outlet header assembly and the platen-through inlet small header in the inlet header assembly and are interconnected.

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