Intermediate mixed header system for boilers and boiler water circulation system

Abstract

The application provides a boiler intermediate mixing header system and a boiler water circulation system, wherein the boiler intermediate mixing header system comprises a header structure, the header structure comprises an inlet box section and an outlet box section in communication with the inlet box section, a first channel is arranged in the inlet box section, a second channel is arranged in the outlet box section, and the cross-sectional area of the first channel is smaller than that of the second channel in the direction perpendicular to the extension direction of the first channel to the second channel; a plurality of inlet portions are arranged on the header structure at intervals and in communication with the inlet box section; and a plurality of outlet portions are arranged on the header structure at intervals and in communication with the outlet box section. Therefore, the technical scheme of the application effectively solves the problem of large outlet steam-water temperature deviation of the boiler spiral pipe ring in the related art, and further causes the uniformity of the steam-water temperature entering the vertical pipe ring water wall to be poor.

Description

Technical Field

[0001] This invention relates to the field of boiler water circulation technology, and more specifically, to an intermediate mixing header system and a boiler water circulation system for boilers. Background Technology

[0002] Traditional coal-fired power plants have limited self-regulation capabilities, long start-up times, and limited peak-shaving range, making it crucial to explore the peak-shaving potential of their generating units. Currently, ultra-supercritical thermal power units with deep peak-shaving typically employ a spiral water-cooled wall and a vertical water-cooled wall structure for their boiler water-cooled walls. With this arrangement, the safe operation of the water-cooled wall heating surfaces becomes critical during low-load boiler operation. Typically, the spiral tube coil outlet and the vertical tube coil inlet share a single header, located in the two-phase region of the working steam-water mixture. The presence of numerous bubbles in the two-phase flow can affect the uniformity of flow distribution. To prevent the unbalanced temperature difference at the spiral tube coil outlet (which can reach a maximum of 30°C) from being transmitted to the furnace vertical water-cooled wall, resulting in an excessively large steam temperature difference at the outlet of the upper furnace vertical water-cooled wall, an intermediate secondary mixing header is needed at the transition point from the spiral tube coil to the vertical tube coil. This header is used to eliminate the impact of the carryover deviation from the critical temperature rise of the steam-water mixture on the hydrodynamic safety of the vertical tube coil. Currently, ensuring the hydrodynamic safety of vertical tube coils typically involves adjusting the flow cross-section of the water-cooled wall within the vertical tube coil to improve the hydrodynamic safety margin under low-load conditions. Because the heat load distribution along the width of the furnace is uneven, and the water-cooled wall exhibits significant heat absorption unevenness in this direction, the flow distribution of the vertical water-cooled wall loop needs to be coupled with the heat load distribution within the furnace during the design process.

[0003] In related technologies, intermediate mixing headers are mostly vertically suspended headers. However, since this location is in the two-phase zone under saturation at low loads, the presence of both vapor and liquid two-phase flow in the intermediate mixing header significantly affects the flow distribution and heat transfer stability of the vapor-water mixture. In the transition header between the spiral and vertical water-cooled walls of supercritical or critical thermal power boilers, the coexistence of vapor and liquid phases leads to complex changes in local flow resistance, and the random distribution of a large number of bubbles easily causes uneven flow distribution among parallel vertical tube coils, thereby exacerbating the thermal deviation of the heating surface. Summary of the Invention

[0004] The main objective of this invention is to provide an intermediate mixing header system and a boiler water circulation system to solve the problem in related technologies where the temperature deviation between the steam and water at the outlet of the boiler spiral tube coil is large, resulting in poor uniformity of the steam and water temperature entering the water-cooled wall of the vertical tube coil.

[0005] To achieve the above objectives, according to one aspect of the present invention, an intermediate mixing header system for boilers is provided, comprising: a header structure including an inlet box section and an outlet box section communicating with the inlet box section, wherein a first channel is provided in the inlet box section and a second channel is provided in the outlet box section, and the cross-sectional area of ​​the first channel is smaller than the cross-sectional area of ​​the second channel in an extension direction perpendicular to the first channel to the second channel; a plurality of inlets are spaced apart on the header structure and communicating with the inlet box section; and a plurality of outlets are spaced apart on the header structure and communicating with the outlet box section.

[0006] Furthermore, the container structure also includes an intermediate container section disposed between the inlet container section and the outlet container section. A third channel is provided in the intermediate container section. In the extension direction perpendicular to the first channel to the second channel, the cross-sectional area of ​​the third channel is smaller than that of the first channel.

[0007] Furthermore, the container structure also includes a first transition section, which is located between the inlet container section and the intermediate container section. A first transition channel is provided in the first transition section, and the cross-sectional area of ​​the first transition section gradually decreases in the direction of extension from the first channel to the second channel.

[0008] Furthermore, the container structure also includes a second transition section, which is located between the intermediate container section and the outlet container section. A second transition channel is provided in the second transition section, and the cross-sectional area of ​​the second transition section gradually decreases in the direction of extension from the first channel to the second channel.

[0009] Furthermore, the intermediate mixing header system for boilers also includes an adjustment orifice plate, which is disposed inside the header structure and located between the inlet box section and the intermediate box section, and the adjustment orifice plate has multiple first through holes.

[0010] Furthermore, the adjusting plate includes an adjusting plate portion and a first outer edge portion disposed on the outer periphery of the adjusting plate portion, and all the first through holes are disposed on the adjusting plate portion.

[0011] Furthermore, the adjusting plate is provided with a first hole area and a second hole area. The second hole area is arranged around the outer periphery of the first hole area. Both the first hole area and the second hole area have multiple first through holes. The diameter of the first through hole in the first hole area is larger than the diameter of the first through hole in the second hole area.

[0012] Furthermore, the adjusting plate is also provided with a third hole area, and the outer periphery of the third hole area is arranged around the first hole area. The third hole area includes at least one first through hole, and the diameter of the first through hole in the third hole area is larger than the diameter of the first through hole in the first hole area.

[0013] Furthermore, the adjusting plate protrudes gradually toward the inlet box section from its outer periphery to its center.

[0014] Furthermore, the intermediate mixing header system for boilers also includes a flow equalization orifice plate, which is disposed between the intermediate box section and the outlet box section, and has multiple second through holes.

[0015] Furthermore, the flow equalization orifice plate includes a flow equalization plate portion and a second outer edge portion disposed on the outer periphery of the flow equalization plate portion, and all the second through holes are disposed on the flow equalization plate portion.

[0016] Furthermore, the flow equalization plate is provided with multiple annular hole groups, each annular hole group including multiple second through holes, and the centers of the multiple annular hole groups are located on the same straight line.

[0017] Furthermore, in the direction from the flow equalization plate to the second outer edge, the distance between two adjacent annular hole groups gradually decreases.

[0018] Furthermore, the flow equalization orifice plate also includes a third through hole, and all the annular orifice groups are arranged around the outer periphery of the third through hole. The diameter of the third through hole is larger than the diameter of the second through hole.

[0019] Furthermore, the flow equalization plate is arranged to gradually protrude towards the inlet housing section from its outer periphery to its center.

[0020] Furthermore, the intermediate mixing header system for boilers also includes multiple first connecting pipes, which are connected to multiple inlets one by one. Each first connecting pipe is provided with a first regulating pipe section, which has a first flow passage. The first flow passage includes a first flow section, a second flow section, and a third flow section. The second flow section is located between the first flow section and the third flow section. The flow area of ​​the first flow section is greater than that of the second flow section, and the flow area of ​​the first flow section is equal to that of the third flow section.

[0021] Furthermore, the intermediate mixing header system for boilers also includes multiple second connecting pipes, which are connected to multiple outlets one by one. Each second connecting pipe is provided with a second regulating pipe section, which has a second flow passage. The second flow passage includes a fourth flow passage, a fifth flow passage, and a sixth flow passage. The fifth flow passage is located between the fourth and sixth flow passages. The flow area of ​​the fourth flow passage is greater than that of the fifth flow passage, and the flow area of ​​the fourth flow passage is equal to that of the sixth flow passage.

[0022] According to another aspect of the present invention, a boiler water circulation system is provided, including an intermediate mixing header system for a boiler, wherein the intermediate mixing header system for a boiler is the aforementioned intermediate mixing header system for a boiler.

[0023] The technical solution of this invention includes an inlet box section and an outlet box section. The inlet section is connected to the inlet box section, and the outlet section is connected to the outlet box section. The inlet box section and the outlet box section are connected. A first channel is provided within the inlet box section, and a second channel is provided within the outlet box section. The cross-sectional area of ​​the first channel is smaller than that of the second channel. Through this arrangement, a steam-water mixture can enter the inlet box section from multiple inlets. Since the temperature of the steam-water mixture entering the first channel through multiple inlets may differ, mixtures with different temperatures can mix within the first channel. Furthermore, the smaller size of the inlet box section ensures effective mixing. As the steam-water mixture moves towards the outlet box section, it can be further mixed within the second channel, thereby improving the temperature uniformity of the steam-water mixture. The mixed steam-water mixture can then flow out through the outlet. Therefore, the technical solution of this application effectively solves the problem in related technologies where the temperature deviation of the steam and water at the boiler spiral tube coil outlet is large, leading to poor temperature uniformity of the steam and water entering the water-cooled wall of the vertical tube coil. Attached Figure Description

[0024] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0025] Figure 1 A schematic diagram of the overall structure of an embodiment of the intermediate mixing header system for boilers according to the present invention is shown;

[0026] Figure 2 It shows Figure 1 A cross-sectional schematic diagram of the header structure of an intermediate mixing header system for boilers;

[0027] Figure 3 It shows Figure 1 A side view of the regulating orifice plate of the intermediate mixing header system for boilers;

[0028] Figure 4 It shows Figure 3 A top view of the regulating orifice plate;

[0029] Figure 5 It shows Figure 1 A side view of the flow equalization orifice plate of the intermediate mixing header system for boilers;

[0030] Figure 6 It shows Figure 3 A top view of the flow equalization orifice plate;

[0031] Figure 7 It shows Figure 1A schematic diagram of the transverse cross-section at the inlet of the intermediate mixing header system for boilers;

[0032] Figure 8 It shows Figure 1 A schematic diagram of the connection between the first connecting pipe and the first spiral water-cooled wall header of the intermediate mixing header system for boilers;

[0033] Figure 9 It shows Figure 1 A schematic diagram of the connection between the first connecting pipe and the second spiral water-cooled wall header of the intermediate mixing header system for boilers;

[0034] Figure 10 It shows Figure 7 A cross-sectional schematic diagram of the first regulating pipe section;

[0035] Figure 11 It shows Figure 1 A schematic diagram of the transverse cross section at the outlet of the intermediate mixing header system for boilers;

[0036] Figure 12 It shows Figure 1 A schematic diagram of the connection between the second connecting pipe and the first vertical pipe screen header of the intermediate mixing header system for boilers;

[0037] Figure 13 It shows Figure 1 A schematic diagram of the connection between the second connecting pipe and the second vertical pipe screen header in the intermediate mixing header system for boilers;

[0038] Figure 14 It shows Figure 11 A cross-sectional schematic diagram of the second regulating pipe section;

[0039] Figure 15 A partial structural schematic diagram of an embodiment of a boiler system according to the present invention is shown.

[0040] The above figures include the following reference numerals:

[0041] 10. Container structure; 11. Inlet box section; 111. First channel; 12. Outlet box section; 121. Second channel; 13. Intermediate box section; 131. Third channel; 14. First transition section; 141. First transition channel; 15. Second transition section; 151. Second transition channel; 20. Inlet section; 30. Outlet section; 40. Adjusting orifice plate; 41. First through hole; 42. Adjusting plate section; 43. First outer edge section; 50. Flow equalization orifice plate; 51. Second through hole; 52. Flow equalization plate section; 53. Second outer edge section; 5 4. Third through hole; 60. First connecting pipe; 61. First regulating pipe section; 611. First flow passage; 6111. First flow section; 6112. Second flow section; 6113. Third flow section; 70. Second connecting pipe; 71. Second regulating pipe section; 711. Second flow passage; 7111. Fourth flow section; 7112. Fifth flow section; 7113. Sixth flow section; 81. First spiral water-cooled wall header; 82. Second spiral water-cooled wall header; 83. First vertical tube panel header; 84. Second vertical tube panel header. Detailed Implementation

[0042] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0044] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0045] like Figure 1 and Figure 2 As shown, in some embodiments, a boiler intermediate mixing header system includes: a header structure 10, an inlet section 20, and an outlet section 30. The header structure 10 includes an inlet box section 11 and an outlet box section 12 communicating with the inlet box section 11. The inlet box section 11 has a first channel 111, and the outlet box section 12 has a second channel 121. In the extension direction perpendicular to the first channel 111 to the second channel 121, the cross-sectional area of ​​the first channel 111 is smaller than the cross-sectional area of ​​the second channel 121. The inlet section 20 is disposed on the header structure 10 and communicates with the inlet box section 11. The outlet section 30 is disposed on the header structure 10 and communicates with the outlet box section 12.

[0046] Applying the technical solution of this embodiment, the container structure 10 includes an inlet box section 11 and an outlet box section 12. The inlet part 20 is connected to the inlet box section 11, and the outlet part 30 is connected to the outlet box section 12. The inlet box section 11 and the outlet box section 12 are connected. A first channel 111 is provided inside the inlet box section 11, and a second channel 121 is provided inside the outlet box section 12. The cross-sectional area of ​​the first channel 111 is smaller than the cross-sectional area of ​​the second channel 121. With the above configuration, the steam-water mixture can enter the inlet housing section 11 from multiple inlets 20. Since the temperature of the steam-water mixture entering the first channel 111 through the multiple inlets 20 may differ, the mixtures with different temperatures can mix within the first channel 111. Furthermore, due to the small size of the inlet housing section 11, the mixing effect is ensured. As the steam-water mixture moves towards the outlet housing section 12, it can be further mixed in the second channel 121, thereby improving the temperature uniformity of the steam-water mixture. The mixed steam-water mixture can then flow out through the outlet 30. Therefore, the technical solution of this embodiment effectively solves the problem in related technologies where the steam-water temperature deviation at the boiler spiral tube coil outlet is large, leading to poor uniformity of the steam-water temperature entering the vertical tube coil water-cooled wall.

[0047] Specifically, the technical solution of this embodiment achieves mixing of the steam-water mixture inside the header structure 10 by setting a difference in the cross-sectional area between the inlet section 11 and the outlet section 12. Specifically, the cross-sectional area of ​​the first channel 111 is smaller than that of the second channel 121. During the process of the steam-water mixture flowing from the inlet 20 to the outlet 30, a flow path from a small diameter to a large diameter is formed. In the small-diameter section, the flow velocity of the steam-water mixture increases, which is beneficial for the breakup and vaporization of droplets in the two-phase flow, thus improving the mixing effect of the steam-water mixture. The multiple spaced inlets 20 and outlets 30 further promote the uniform distribution and mixing of the steam-water mixture throughout the header structure 10, effectively reducing the carryover deviation of the steam-water mixture and improving the temperature uniformity of the steam-water mixture entering the first vertical tube screen header 83 and the second vertical tube screen header 84.

[0048] The technical solution of this embodiment can effectively reduce the carryover deviation of the steam-water mixture at the outlet of the spiral water-cooled wall when the boiler is operating under low load and rapid load change conditions. By optimizing the steam-water distribution characteristics, it can significantly improve the hydrodynamic stability and safety of the vertical tube screen and avoid local water circulation abnormalities caused by load fluctuations.

[0049] When the boiler is operating at low load, the dryness of the steam-water mixture within the header structure 10 is 0.8 (located in the steam-liquid two-phase flow region, still containing liquid working fluid), which can easily lead to flow deviation due to uneven steam-liquid distribution. To address this, the header structure 10 employs a three-stage droplet vaporization synergistic approach: using a tapered and expanding structure, and incorporating a regulating orifice plate 40 and a flow equalization orifice plate 50. By enhancing steam-liquid mixing and vaporization, the influence of the steam-liquid two-phase state on flow deviation is effectively reduced.

[0050] like Figure 1 and Figure 2 As shown, in some embodiments, the header structure 10 further includes an intermediate section 13 disposed between the inlet section 11 and the outlet section 12. A third channel 131 is provided within the intermediate section 13. In the extension direction perpendicular to the first channel 111 to the second channel 121, the cross-sectional area of ​​the third channel 131 is smaller than that of the first channel 111. This tapering channel design increases the velocity of the water-air mixture as it passes through the intermediate section 13, thereby enhancing the agitation and mixing of the water-air mixture inside the header structure 10. The increased velocity of the water-air mixture in the third channel 131 enables the breakup and vaporization of large droplets, further improving mixing efficiency.

[0051] The steam-water mixture enters the second channel 121. Due to the increased cross-sectional area of ​​the second channel 121, the speed of the steam-water mixture slows down, which helps to convert the kinetic energy of the mixed steam-water mixture into pressure energy. This ensures that the steam-water mixture enters the first vertical tube header 83 and the second vertical tube header 84 with a more uniform temperature and pressure, thereby reducing the temperature deviation and hydrodynamic instability at the first vertical tube header 83 and the second vertical tube header 84, and improving the operating efficiency and safety of the boiler under low load and rapid load change conditions.

[0052] like Figure 1 and Figure 2 As shown, in some embodiments, the header structure 10 further includes a first transition section 14, which is disposed between the inlet section 11 and the intermediate section 13. A first transition channel 141 is provided within the first transition section 14. The cross-sectional area of ​​the first transition section 14 gradually decreases in the extension direction from the first channel 111 to the second channel 121. The first transition section 14 is designed to taper, allowing for gradual speed and pressure adjustment of the carbonated water mixture before it enters the intermediate section 13. When the carbonated water mixture, carrying a large number of bubbles, enters from the first channel 111, the flow channel of the first transition section 14 contracts, effectively increasing the speed of the carbonated water mixture and promoting better mixing and dispersion of the bubbles and liquid, thereby accelerating the breakup and vaporization of large droplets. After the carbonated water mixture successfully passes through the first transition section 14, it is further accelerated by the third channel 131 and finally enters the second channel 121, thus achieving mixing of the carbonated water mixture within the header structure 10.

[0053] The above-mentioned configuration not only enhances the flow efficiency of the steam-water mixture, but also ensures that the temperature of the steam-water mixture entering the first vertical tube header 83 and the second vertical tube header 84 is more balanced, thereby improving the operational stability and peak-shaving capability of the intermediate mixing header system for boilers.

[0054] In addition, the tapering design of the first transition section 14 can reduce the changes in local flow resistance caused by uneven distribution of the steam-water mixture, which is beneficial to maintaining the hydrodynamic safety of the system under low load and rapid load change conditions.

[0055] like Figure 1 and Figure 2 As shown, in some embodiments, the header structure 10 further includes a second transition section 15, which is disposed between the intermediate casing section 13 and the outlet casing section 12. A second transition channel 151 is provided within the second transition section 15, and the cross-sectional area of ​​the second transition section 15 gradually decreases in the extension direction from the first channel 111 to the second channel 121. This design allows the water-air mixture to be further accelerated and its turbulence increased after passing through the first channel 111 and the third channel 131, thereby achieving a more efficient mixing effect before entering the second channel 121. The gradual narrowing of the second transition channel 151 stabilizes the velocity of the water-air mixture, facilitating droplet breakup and vaporization, while also enhancing momentum exchange between the water-air mixture, ultimately ensuring the uniformity of the water-air mixture temperature at the outlet 30.

[0056] like Figures 1 to 4 As shown, in some embodiments, the intermediate mixing header system for boilers also includes an adjusting orifice plate 40. The adjusting orifice plate 40 is disposed inside the header structure 10 and located between the inlet box section 11 and the intermediate box section 13. The adjusting orifice plate 40 has multiple first through holes 41. The arrangement of the adjusting orifice plate 40, combined with the characteristics of the inlet steam-water mixture in the inlet box section 11 and the gradually narrowing and expanding structure of the intermediate box section 13, jointly achieves the function of improving the mixing effect. When the steam-water mixture passes through the first through holes 41, according to the distribution law of the orifice diameter of the first through holes 41, the large orifice diameter area is conducive to the passage of high flow rate steam-water mixture, while the smaller orifice diameter area helps to control the steam-water mixture under low flow rate conditions.

[0057] Specifically, before the gas-liquid mixture enters the third channel 131, the gas and liquid phases inside are initially homogenized, reducing the presence of large droplets, thereby improving the hydrodynamic safety and thermal load uniformity of the entire system when operating at low load.

[0058] like Figures 1 to 4As shown, in some embodiments, the regulating orifice plate 40 includes an regulating plate portion 42 and a first outer edge portion 43 disposed on the outer periphery of the regulating plate portion 42, with all the first through holes 41 disposed on the regulating plate portion 42. Through this arrangement, when the steam-water mixture passes through the regulating orifice plate 40, it first undergoes initial flow rate adjustment and flow distribution through the first through holes 41 in the central region of the regulating orifice plate 40. Then, the steam-water mixture diffuses towards the edge of the first outer edge portion 43, further enhancing the uniform dispersion and pressure balance of the steam-water mixture. Furthermore, it can effectively control the pressure loss of the steam-water mixture in different areas, ensuring a more uniform pressure distribution of the steam-water mixture across the entire header cross-section, thereby enhancing the stability and efficiency of the water circulation.

[0059] In addition, the presence of the first outer edge 43 can improve the structural strength of the regulating orifice plate 40, reduce the risk of deformation under the impact of high-pressure steam-water mixture, and ensure the reliability of long-term operation.

[0060] The regulating plate 42 is provided with a first orifice area and a second orifice area, with the second orifice area surrounding the outer periphery of the first orifice area. Both the first and second orifice areas have multiple first through holes 41, and the diameter of the first through holes 41 in the first orifice area is larger than the diameter of the first through holes 41 in the second orifice area. This design enables the regulation of the flow rate of the steam-water mixture passing through the regulating plate 42. By coordinating the first through holes 41 of different diameters, the steam-water mixture is dispersed as it passes through the regulating orifice plate 40, and large water droplets are broken up, thereby accelerating the mixing of the gas phase flow and the liquid phase flow and improving the uniformity of the steam-water mixture vaporization.

[0061] like Figures 1 to 4 As shown, in some embodiments, the regulating plate 42 is further provided with a third hole area, with the outer periphery of the third hole area surrounding the first hole area. The third hole area includes at least one first through hole 41, and the diameter of the first through hole 41 in the third hole area is larger than the diameter of the first through hole 41 in the first hole area. The above design achieves graded regulation and mixing of the air-water mixture flowing through the header structure 10 through the distribution of different hole diameters.

[0062] like Figures 1 to 4 As shown, in some embodiments, the regulating plate 42 gradually protrudes towards the inlet housing section 11 from its outer periphery to its center. The regulating orifice plate 40, through its gradually protruding design from its outer periphery to its center, effectively alters the flow state of the steam-water mixture at the inlet of the third channel 131. As the steam-water mixture approaches the central region of the regulating orifice plate 40, the degree of protrusion gradually increases, enabling the steam-water mixture to undergo a stepwise pressurization process as it passes through the regulating plate 42, thereby ensuring the breakup and vaporization of large droplets in the two-phase state.

[0063] The diameter of the first through hole 41 in the third hole area is d1, the diameter of the first through hole 41 in the first hole area is d2, and the diameter of the first through hole 41 in the second hole area is d3. d2 is between 0.6d1 and 0.8d1, and d3 is between 0.3d1 and 0.5d1.

[0064] The flow rate is high and the flow capacity is strong in the third orifice area, while the pressure loss is relatively controllable.

[0065] The first orifice zone can balance flow and pressure loss, providing a stable range for regular flow regulation, and is the core regulation area.

[0066] The second orifice area is used for precise control of small flow rates. Through the throttling effect of dense micro-orifices, stable output is achieved at low flow rates.

[0067] like Figure 1 , Figure 2 , Figure 5 as well as Figure 6 As shown, in some embodiments, the intermediate mixing header system for boilers further includes a flow equalization orifice plate 50, which is disposed between the intermediate housing section 13 and the outlet housing section 12. The flow equalization orifice plate 50 has multiple second through holes 51. This arrangement further enhances the distribution of the steam-water mixture within the header structure 10, ensuring that after acceleration through the first channel 111 and the third channel 131, the steam-water mixture reaches a highly uniform state before the second channel 121. The flow equalization orifice plate 50, through its second through holes 51, redistributes the steam-water mixture, effectively reducing flow velocity inconsistencies and thus improving the uniformity of the steam-water mixture.

[0068] This not only promotes the uniform distribution of the steam-water mixture inside the header structure 10, but also provides a more stable flow and temperature uniformity for the steam-water mixture entering the first vertical tube header 83 and the second vertical tube header 84, thereby improving the operating efficiency and reliability of the entire system.

[0069] Specifically, by setting the flow equalization orifice plate 50, the uniformity of the steam-water mixture at the first vertical tube header 83 and the second vertical tube header 84 can be maintained, avoiding hydrodynamic instability caused by insufficient or excessive local flow, reducing the risk of equipment failure, and extending the service life of the boiler.

[0070] like Figure 1 , Figure 2 , Figure 5 as well as Figure 6As shown, in some embodiments, the flow equalization orifice plate 50 includes a flow equalization plate portion 52 and a second outer edge portion 53 disposed on the outer periphery of the flow equalization plate portion 52, with all the second through holes 51 disposed on the flow equalization plate portion 52. The above design achieves uniform distribution of the steam-water mixture through the second through holes 51 on the flow equalization plate portion 52, while the second outer edge portion 53 provides stable support, ensuring the positioning stability of the flow equalization orifice plate 50 within the header structure 10. The distribution of the second through holes 51 allows the steam-water mixture to enter the second channel 121 at a more consistent speed and pressure after passing through the third channel 131, which not only enhances the uniformity of the steam-water mixture but also improves the temperature mixing effect.

[0071] like Figure 1 , Figure 2 , Figure 5 as well as Figure 6 As shown, in some embodiments, the flow equalization plate 52 is provided with multiple annular hole groups, each annular hole group including multiple second through holes 51, and the centers of the multiple annular hole groups are located on the same straight line. The above structural design realizes the uniform distribution and allocation of the steam-water mixture inside the header structure 10.

[0072] The distance between any two adjacent second through holes 51 in each annular hole group is a preset distance in the circumferential direction. From the center of the flow equalization plate 52 to the outer periphery of the flow equalization plate 52, the preset distance of the multiple annular hole groups first decreases and then increases.

[0073] like Figure 1 , Figure 2 , Figure 5 as well as Figure 6 As shown, in some embodiments, the distance between two adjacent annular hole groups gradually decreases in the direction from the flow equalization plate portion 52 to the second outer edge portion 53. This arrangement improves the flow equalization effect, thus ensuring the flow efficiency of the carbonated water mixture.

[0074] like Figure 1 , Figure 2 , Figure 5 as well as Figure 6 As shown, in some embodiments, the flow equalization orifice plate 50 further includes a third through hole 54, with all the annular holes surrounding the outer periphery of the third through hole 54. The diameter of the third through hole 54 is larger than the diameter of the second through hole 51. This configuration further optimizes the distribution of the carbonated water mixture on the flow equalization orifice plate 50. By configuring different orifice sizes, the velocity and flow rate distribution of the carbonated water mixture can be controlled more effectively. The third through hole 54, as an additional flow channel, provides a larger flow area and reduces the resistance of the carbonated water mixture as it passes through the orifice plate.

[0075] like Figure 1 , Figure 2 , Figure 5as well as Figure 6 As shown, in some embodiments, the flow equalization plate portion 52 gradually protrudes towards the inlet housing section 11 from its outer periphery to its center. This arrangement enables uniform flow of the air-water mixture inside the header structure 10. The protruding design of the flow equalization plate portion 52 improves the structural strength, thus ensuring structural and positional stability even when impacted by the air-water mixture.

[0076] The diameter of the third through hole 54 is d4, and the diameter of the second through hole 51 is d5, with d4 ranging from 0.6d5 to 0.8d5.

[0077] The above settings can force the fluid to redistribute within the cross section, making the flow velocity distribution more uniform.

[0078] like Figure 1 , Figures 7 to 14 As shown, in some embodiments, the intermediate mixing header system for boilers further includes multiple first connecting pipes 60, which are connected one-to-one with multiple inlet sections 20. Each first connecting pipe 60 is provided with a first regulating pipe section 61, which has a first flow passage 611. The first flow passage 611 includes a first flow section 6111, a second flow section 6112, and a third flow section 6113. The second flow section 6112 is located between the first flow section 6111 and the third flow section 6113. The flow area of ​​the first flow section 6111 is larger than that of the second flow section 6112, and the flow area of ​​the first flow section 6111 is equal to that of the third flow section 6113. The above arrangement, by changing the flow areas of the first flow section 6111, the second flow section 6112, and the third flow section 6113, creates a gradual flow resistance, thereby achieving the regulation of the steam-water mixture flow rate. When the steam-water mixture flows through the first connecting pipe 60 and its first regulating pipe section 61, the mixture first enters the first flow section 6111. Due to the large flow area in this section, the resistance of the steam-water mixture is relatively small, maintaining a stable flow velocity. Subsequently, when the mixture passes through the second flow section 6112, the flow area decreases, the resistance increases, and the flow velocity accelerates. This process disturbs the flow state of the mixture, thus achieving uniform mixing. Finally, the mixture enters the third flow section 6113, where the flow area increases again, the resistance decreases, and the flow velocity stabilizes. During this process, the flow of the mixture tends to be smooth, while maintaining the uniform mixing state generated in the second flow section 6112. This gradually narrowing and expanding flow channel design of the first regulating pipe section 61 not only effectively controls the flow distribution of the steam-water mixture in the first connecting pipe 60 but also improves the mixing effect, thereby ensuring the stability and efficiency of the water circulation system and reducing the temperature deviation between the first vertical pipe screen header 83 and the second vertical pipe screen header 84.

[0079] The length of the first regulating pipe section 61 is L1, and the length of the second flow passage section 6112 is L2. The ratio between L2 and L1 is greater than or equal to 0.15 and between 0.35. The length of L2 is greater than or equal to 0.25m.

[0080] The orifice diameter of the first flow section 6111 is B1, and the orifice diameter of the second flow section 6112 is A1. The ratio between A1 and B1 is greater than or equal to 0.2 and between 0.6.

[0081] Specifically, there are eight first connecting pipes 60. Four of the eight first connecting pipes 60 are connected to the first spiral water-cooled wall header 81, and the remaining four first connecting pipes 60 are connected to the second spiral water-cooled wall header 82.

[0082] like Figure 1 , Figures 7 to 14 As shown, in some embodiments, the intermediate mixing header system for boilers further includes a plurality of second connecting pipes 70, which are connected one-to-one with a plurality of outlets 30. Each second connecting pipe 70 is provided with a second regulating pipe section 71, which has a second flow passage 711. The second flow passage 711 includes a fourth flow section 7111, a fifth flow section 7112, and a sixth flow section 7113. The fifth flow section 7112 is located between the fourth flow section 7111 and the sixth flow section 7113. The flow area of ​​the fourth flow section 7111 is greater than that of the fifth flow section 7112, and the flow area of ​​the fourth flow section 7111 is equal to that of the sixth flow section 7113. The above-described structural design allows the steam-water mixture flowing through the second connecting pipe 70 to be accelerated and throttled at the fifth flow section 7112, and then decelerated and pressurized in the fourth flow section 7111 and the sixth flow section 7113. This achieves effective conversion of the kinetic energy of the steam-water mixture and restoration of its pressure. At the same time, by adjusting the size of the fifth flow section 7112, the flow rate and pressure loss of the steam-water mixture can be controlled, thereby achieving the purpose of fine-tuning the flow rate. This ensures the uniformity of the steam-water mixture distribution in the vertical pipe screen inlet header, reduces the thermal stress at the first vertical pipe screen header 83 and the second vertical pipe screen header 84, and improves the safety and efficiency of the water circulation system.

[0083] The length of the second regulating pipe section 71 is L3, and the length of the fifth flow passage section 7112 is L4. The ratio between L4 and L3 is greater than or equal to 0.15 and between 0.35. The length of L4 is greater than or equal to 0.25m.

[0084] The orifice diameter of the fifth flow section 7112 is B2, and the orifice diameter of the fourth flow section 7111 is A2. The ratio between A2 and B2 is greater than or equal to 0.2 and between 0.6.

[0085] Specifically, there are eight second connecting pipes 70. Four of the eight second connecting pipes 70 are connected to the first vertical tube screen header 83, and the remaining four second connecting pipes 70 are connected to the second vertical tube screen header 84.

[0086] It should be noted that the inlet box section 11, the intermediate box section 13, and the outlet box section 12 are three independent parts, which are connected by welding. The interior of the inlet box section 11, the intermediate box section 13, and the outlet box section 12 forms a mixed cavity, namely the first channel 111, the second channel 121, and the third channel 131. A square hanging lug is welded on the inlet box section 11. The adjusting orifice plate 40 is arranged between the inlet box section 11 and the intermediate box section 13 and is connected by welding. The flow equalization orifice plate 50 is arranged between the intermediate box section 13 and the outlet box section 12 and is connected by welding. A first connecting pipe 60 is arranged on the inlet box section 11, circumferentially entering the first spiral water-cooled wall header 81 and the second spiral water-cooled wall header 82, and a first adjusting pipe section 61 is arranged on the first connecting pipe 60. A second connecting pipe 70 is arranged on the outlet box section 12, circumferentially leading out the first vertical tube screen header 83 and the second vertical tube screen header 84, and a second adjusting pipe section 71 is arranged on the second connecting pipe 70. The first spiral water-cooled wall header 81 and the second spiral water-cooled wall header 82 are connected to the first connecting pipe 60, and the first vertical tube screen header 83 and the second vertical tube screen header 84 are connected to the second connecting pipe 70.

[0087] In this embodiment, the first connecting pipe 60 and the first channel 111 are introduced into the same plane in a circumferential direction, and the second connecting pipe 70 and the second channel 121 are led out in the same plane in a circumferential direction. The first channel 111 is located above the second channel 121. The method of introducing from the top and leading out from the bottom can enhance the convection and turbulence mixing within the header structure 10.

[0088] Preferably, the regulating orifice plate 40 is arranged at the inlet of the second transition channel 151. The orifice plate 40 is divided into three regions along the radial direction. The middle region (including seven first through holes 41, the third orifice region and part of the first orifice region) is the main region. The two middle rings (that is, the outer side of the seven first through holes 41 and the rest of the first orifice region) are the first-level pressurization region. The outermost four rings (the second orifice region) are the second-level pressurization region. The main purpose is to vaporize the droplets, accelerate mixing, and improve the dryness of the gas-water mixture in the header structure 10 by pressurizing the first, second and third orifice regions when the gas and liquid are in two phases.

[0089] Preferably, the first transition channel 141 is a contraction section, the third channel is a mixing straight section, and the second transition channel 151 is a diffusion section. After passing through the regulating orifice plate 40, the steam-water mixture enters the first transition channel 141, where it is accelerated and then passes through the flow equalization orifice plate 50 before entering the second channel 121. This process converts the kinetic energy of the high-speed fluid into pressure energy, increasing the outlet pressure of the steam-water mixture, and outputting high-pressure fluid through the second connecting pipe 70.

[0090] In this embodiment, the adjusting orifice plate 40 and the flow equalizing orifice plate 50 are protruding orifice plates with their axial center lines coinciding and the protrusion angle forming an 18° angle with the horizontal.

[0091] The technical solution of this embodiment has the following advantages:

[0092] 1. The technical solution of this embodiment can improve the flexibility of the boiler itself, reduce the steam temperature carryover deviation at the spiral water-cooled wall outlet during low load and rapid load changes, and improve the hydrodynamic safety of the vertical water-cooled wall. The system described above directly realizes the redistribution of boiler steam and water heat, reduces stress losses caused by temperature differences in each vertical tube panel, and reduces the lifespan of the water-cooled wall.

[0093] 2. The technical solution of this embodiment uses an adjusting orifice plate 40 to achieve the breaking and vaporization of large droplets. At the same time, the header structure 10 adopts a gradually shrinking-expanding structure to achieve secondary vaporization of droplets in the third channel 131. After passing through the flow equalization orifice plate 50 for three breaking and vaporization, the droplets enter the second channel 121 for mixing. The kinetic energy of the high-speed fluid is converted into pressure energy, which increases the outlet pressure of the steam-water mixture and improves the uniformity of the fluid.

[0094] 3. The inlet of the first connecting pipe 60 and the outlet of the second connecting pipe 70 are introduced by opposing flow and are in the same plane, which enhances the mixing of the steam-water mixture. At the same time, the high-temperature steam flow is in the upper part of the header structure 10, which can enhance the convection and turbulence within the header structure 10 and fully mix them.

[0095] 4. The first regulating pipe section 61 and the second regulating pipe section 71 can reduce the flow deviation between the first connecting pipe 60 and the second connecting pipe 70.

[0096] According to another aspect of this application, a boiler water circulation system is provided, such as... Figure 15As shown, the boiler water circulation system of this embodiment includes a boiler intermediate mixing header system, which is the aforementioned boiler intermediate mixing header system. The aforementioned boiler intermediate mixing header system can effectively improve hydrodynamic safety under low load and rapid load change conditions. Specifically, by setting up the first channel, the second channel, and the third channel, the temperature mixing effect of the steam-water mixture can be improved. Therefore, the boiler water circulation system with the aforementioned boiler intermediate mixing header system also has the aforementioned advantages.

[0097] In the description of this invention, it should be understood that "a plurality of" means two or more. Directional terms such as "front, back, up, down, left, right," "horizontal, vertical, perpendicular, horizontal," and "top, bottom" indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. These terms are used solely for the convenience of describing the invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the scope of protection of this invention. The directional terms "inner" and "outer" refer to the inner or outer contours relative to the outline of each component itself.

[0098] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0099] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0100] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An intermediate mixing header system for boilers, characterized in that, include: The container structure (10) includes an inlet container section (11) and an outlet container section (12) connected to the inlet container section (11). The inlet container section (11) is provided with a first channel (111), and the outlet container section (12) is provided with a second channel (121). In the extension direction perpendicular to the first channel (111) to the second channel (121), the cross-sectional area of ​​the first channel (111) is smaller than the cross-sectional area of ​​the second channel (121). Multiple inlet sections (20) are spaced apart on the header structure (10) and communicate with the inlet box section (11); Multiple outlet sections (30) are spaced apart on the header structure (10) and communicate with the outlet box section (12).

2. The intermediate mixing header system for boilers according to claim 1, characterized in that, The container structure (10) further includes an intermediate container section (13) disposed between the inlet container section (11) and the outlet container section (12). A third channel (131) is disposed in the intermediate container section (13). In the extension direction perpendicular to the first channel (111) to the second channel (121), the cross-sectional area of ​​the third channel (131) is smaller than the cross-sectional area of ​​the first channel (111).

3. The intermediate mixing header system for boilers according to claim 2, characterized in that, The container structure (10) further includes a first transition section (14), which is located between the inlet container section (11) and the intermediate container section (13). A first transition channel (141) is provided in the first transition section (14), and the cross-sectional area of ​​the first transition section (14) gradually decreases in the extension direction from the first channel (111) to the second channel (121).

4. The intermediate mixing header system for boilers according to claim 2, characterized in that, The container structure (10) further includes a second transition section (15), which is disposed between the intermediate container section (13) and the outlet container section (12). A second transition channel (151) is provided in the second transition section (15). The cross-sectional area of ​​the second transition section (15) gradually decreases in the extension direction from the first channel (111) to the second channel (121).

5. The intermediate mixing header system for boilers according to claim 2, characterized in that, The intermediate mixing header system for boilers also includes an adjustment orifice plate (40), which is disposed inside the header structure (10) and located between the inlet box section (11) and the intermediate box section (13). The adjustment orifice plate (40) has a plurality of first through holes (41).

6. The intermediate mixing header system for boilers according to claim 5, characterized in that, The adjusting plate (40) includes an adjusting plate portion (42) and a first outer edge portion (43) disposed on the outer periphery of the adjusting plate portion (42), and all the first through holes (41) are disposed on the adjusting plate portion (42).

7. The intermediate mixing header system for boilers according to claim 6, characterized in that, The adjustment plate (42) is provided with a first hole area and a second hole area. The second hole area is arranged around the outer periphery of the first hole area. Both the first hole area and the second hole area have a plurality of first through holes (41). The diameter of the first through hole (41) in the first hole area is larger than the diameter of the first through hole (41) in the second hole area.

8. The intermediate mixing header system for boilers according to claim 7, characterized in that, The adjustment plate (42) is also provided with a third hole area, and the outer periphery of the third hole area is arranged around the first hole area. The third hole area includes at least one first through hole (41), and the diameter of the first through hole (41) in the third hole area is larger than the diameter of the first through hole (41) in the first hole area.

9. The intermediate mixing header system for boilers according to claim 6, characterized in that, The adjustment plate (42) protrudes gradually toward the inlet box section (11) from its outer periphery to its center.

10. The intermediate mixing header system for boilers according to claim 2, characterized in that, The intermediate mixing header system for boilers also includes a flow equalization orifice plate (50), which is disposed between the intermediate box section (13) and the outlet box section (12), and the flow equalization orifice plate (50) is provided with a plurality of second through holes (51).

11. The intermediate mixing header system for boilers according to claim 10, characterized in that, The flow equalization plate (50) includes a flow equalization plate portion (52) and a second outer edge portion (53) disposed on the outer periphery of the flow equalization plate portion (52), and all the second through holes (51) are disposed on the flow equalization plate portion (52).

12. The intermediate mixing header system for boilers according to claim 11, characterized in that, The flow equalization plate (52) is provided with a plurality of annular hole groups, each of the annular hole groups including a plurality of second through holes (51), and the centers of the plurality of annular hole groups are located on the same straight line.

13. The intermediate mixing header system for boilers according to claim 12, characterized in that, In the direction from the flow equalization plate portion (52) to the second outer edge portion (53), the distance between two adjacent annular hole groups gradually decreases.

14. The intermediate mixing header system for boilers according to claim 12, characterized in that, The flow equalization plate (50) also includes a third through hole (54), and all the annular hole groups are arranged around the outer periphery of the third through hole (54). The diameter of the third through hole (54) is larger than the diameter of the second through hole (51).

15. The intermediate mixing header system for boilers according to claim 11, characterized in that, The flow equalization plate (52) protrudes gradually toward the inlet box section (11) from its outer periphery to its center.

16. The intermediate mixing header system for boilers according to any one of claims 1 to 15, characterized in that, The intermediate mixing header system for the boiler also includes a plurality of first connecting pipes (60), which are connected to a plurality of inlet sections (20) in a one-to-one correspondence. Each first connecting pipe (60) is provided with a first regulating pipe section (61). The first regulating pipe section (61) has a first flow passage (611). The first flow passage (611) includes a first flow section (6111), a second flow section (6112), and a third flow section (6113). The second flow section (6112) is located between the first flow section (6111) and the third flow section (6113). The flow area of ​​the first flow section (6111) is greater than the flow area of ​​the second flow section (6112), and the flow area of ​​the first flow section (6111) is equal to the flow area of ​​the third flow section (6113).

17. The intermediate mixing header system for boilers according to any one of claims 1 to 15, characterized in that, The intermediate mixing header system for the boiler also includes a plurality of second connecting pipes (70), which are connected one-to-one with a plurality of outlets (30). Each second connecting pipe (70) is provided with a second regulating pipe section (71). The second regulating pipe section (71) has a second flow passage (711). The second flow passage (711) includes a fourth flow section (7111), a fifth flow section (7112), and a sixth flow section (7113). The fifth flow section (7112) is located between the fourth flow section (7111) and the sixth flow section (7113). The flow area of ​​the fourth flow section (7111) is greater than that of the fifth flow section (7112). The flow area of ​​the fourth flow section (7111) is equal to that of the sixth flow section (7113).

18. A boiler water circulation system, comprising an intermediate mixing header system for the boiler, characterized in that, The intermediate mixing header system for boilers is the intermediate mixing header system for boilers as described in any one of claims 1 to 17.

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