Cooling triangular unit of low-wind-resistance cooling tower and cooling tower

Abstract

The utility model provides a cooling triangular unit of a low-wind-resistance cooling tower and the cooling tower, and relates to the technical field of heat exchange equipment and processes. An air inlet grille used for inputting cold air is arranged on the front end face of a cooling triangular unit of the low-wind-resistance cooling tower, and a first side end face and a second side end face are two air cooling heat exchangers which are connected in a V shape. Cooling water is input into the air-cooling heat exchanger to be cooled after exchanging heat with cold air, and the cold air flows into the axis direction of the cooling tower after exchanging heat with the air-cooling heat exchanger; wherein a plurality of parallel flying wing type finned tubes are arranged in the air cooling heat exchanger, the flying wing type finned tubes are flat tubes, and flying wing type fins are arranged on two opposite wide surfaces of each flying wing type finned tube; the flying wing type finned tubes are arranged along the flowing direction of cold air; the upper sealing plate is arranged on the upper portion, and the lower sealing plate is arranged on the lower portion. According to the utility model, the reversing times of cooling air entering the cooling tower through the cooling triangle can be effectively reduced, the wind resistance is reduced, and meanwhile, the heat exchange efficiency of the cooling triangle unit is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange equipment and process technology, specifically to a low wind resistance cooling tower cooling triangle unit and a cooling tower. Background Technology

[0002] Taking thermal power plants as an example, various types of cooling towers are important equipment in the production process of thermal power plants. Their function is to exchange heat between the cooling water carrying heat and the air inside the tower, so that the heat is transferred to the air and dissipated into the atmosphere, thereby ensuring the normal operation of the equipment. According to the different contact methods between water and air, cooling towers can be divided into wet cooling towers and dry cooling towers.

[0003] Traditional cooling towers mostly use wet cooling tower systems with direct spraying, which enhance heat exchange by spraying or atomizing water. However, wet cooling towers lose 10-20% of their water through evaporation while dissipating heat, resulting in resource waste. To save water, dry cooling towers use hot water flowing inside the heat dissipation pipes, cooling the air through contact heat transfer caused by the temperature difference with the outside air, thus achieving closed-loop hot water circulation and avoiding water loss.

[0004] Existing dry cooling towers (taking natural draft towers as an example) employ a triangular arrangement of heat exchangers, including multiple rows of heat exchange tubes, around the bottom of the tower to accommodate more heat exchangers within a limited space. The outer side serves as the air inlet, and one heat exchanger is placed on each of the two inner sides, forming a cooling triangular unit. During operation, cold air enters through the air inlet of the cooling triangular unit. After heat exchange in the heat exchangers, the air flows towards the tower axis, undergoing at least two deflections between the airflow and the heat exchanger surfaces and internal heat exchange tubes before entering the cooling tower. Excessive flow resistance along the flow path can lead to insufficient cooling airflow, resulting in a decrease in the cooling performance of the air-cooled system.

[0005] Patent CN112284157A discloses a cooling triangular unit capable of achieving air-side self-rectification within a triangular space. This unit achieves precise control and distribution of the localized airflow at the outer end of the cooling columns by vertically arranging air-side self-rectification devices on both sides of the central symmetrical plane. Simultaneously, it rectifies the airflow within the triangular space, effectively eliminating lateral vortices and balancing the airflow into the cooling columns on both sides of the unit. This technical solution improves the overall heat transfer effect of the cooling triangular unit and reduces unbalanced temperature differences, thus enhancing the overall performance of the cooling triangular unit. However, it cannot effectively reduce the number of deflections required for cold air to enter the cooling tower.

[0006] Patent CN114754605A discloses a cooling triangle unit with a rotating plate-type integrated flow equalization and antifreeze device. The unit includes a cooling triangle unit and a rotating plate-type integrated flow equalization and antifreeze device. It can adjust the angle between the rotating plate and the cooling column according to the ambient wind speed and direction, thereby achieving flow equalization and antifreeze. In summer, the rotating plate's rotation angle can be adjusted to coincide with the vertical center symmetry plane of the cooling triangle unit, thus equalizing the flow. In winter, when the ambient wind speed is high and the air inlet angle is large, the rotating plate's rotation angle can be adjusted to prevent the ambient wind from directly impacting the cooling column, thus preventing the cooling triangle unit from freezing. However, this technology does not address the wind resistance issue of the cooling air during the operation of the cooling triangle unit.

[0007] Patent CN114719664A discloses a cooling triangular unit with vertically rotatable louvers for equalizing airflow. The unit includes a cooling triangular unit and vertically rotatable louvers for equalizing airflow. The louvers can be adjusted according to ambient wind speed and direction: when the ambient wind speed is low, the louvers are closed to equalize airflow on the cooling triangular side; when the ambient wind speed is high and there is some airflow deviation, the louvers are opened at a certain angle to reduce ventilation resistance inside the cooling triangular unit, optimize the airflow distribution inside the unit, and improve the heat exchange performance. While this technology reduces wind resistance by incorporating a flow-guiding structure within the cooling triangular unit, the cooling air flowing from the outside into the cooling tower always needs to undergo several reversals, resulting in significant wind resistance. Utility Model Content

[0008] To address the shortcomings of existing technologies, this utility model proposes a low-wind-resistance cooling tower cooling triangle unit and a cooling tower, which solves the problem of high wind resistance caused by deflection of cold air after it enters the cooling tower during operation.

[0009] To achieve the above technical objectives, this utility model proposes a low-wind-resistance cooling tower cooling triangular unit. The front end of this unit is equipped with an air intake grille for inputting cold air. The first and second side ends are two air-cooled heat exchangers connected in a V-shape. Cooling water is input into the air-cooled heat exchangers and exchanges heat with the cold air to lower its temperature. The cold air then flows into the axial direction of the cooling tower after exchanging heat with the air-cooled heat exchangers. The unit also includes an upper sealing plate at the top and a lower sealing plate at the bottom. Each air-cooled heat exchanger contains multiple parallel-arranged finned tubes. These finned tubes are flat tubes with finned fins on two opposite wide surfaces. The finned tubes are arranged in the direction of the cold air flow.

[0010] In the above technical solution, in order to reduce wind resistance, the flat tube-shaped heat exchange tubes in the air-cooled heat exchanger are arranged in the direction of airflow, so that the cold air can directly exchange heat with the heat exchange tubes after entering the cooling triangular unit, and then continue to flow towards the axis of the tower. This avoids the situation in existing dry cooling towers where multiple rows of heat exchange tubes are set, which causes the cold air to be deflected multiple times between the heat exchange tubes. This allows more cold air to pass through the heat exchanger per unit time, enhancing the heat exchange between the air and the heat exchanger.

[0011] However, the reduced resistance to cold air flow leads to excessively high air velocity, which can result in insufficient contact time between the cold air and the heat exchanger, affecting localized heat exchange efficiency. Furthermore, the aforementioned technical solution uses flat-tube finned tubes instead of traditional round tube heat exchangers. The fluid channels and finned tubes are integrated, eliminating contact thermal resistance between the finned tubes and the inner channels during operation. This promotes effective heat exchange between the cold air and the air-cooled heat exchanger under low air resistance conditions, thereby comprehensively improving the heat exchange efficiency of the cooling triangle unit.

[0012] The air-cooled heat exchanger described in the above technical solution forms a stable cooling triangular unit structure with the upper and lower sealing plates. This novel cooling triangular unit can be widely used in large air-cooled equipment in power plant natural draft towers, mechanical auxiliary towers, and other application scenarios (such as oil refining, chemical plants, and metal smelting), and has broad application value.

[0013] On the other hand, this utility model proposes a low wind resistance cooling tower, which includes the aforementioned low wind resistance cooling tower cooling triangle unit.

[0014] On the other hand, this utility model proposes a cooling method for a low-wind-resistance cooling tower. Cooling water carrying waste heat from the upstream process is input into the air-cooled heat exchanger on the side end face of the cooling triangular unit of the cooling tower, where it contacts and exchanges heat with the cold air input from the front face of the cooling triangular unit. After cooling, the cooling water exits the air-cooled heat exchanger and returns to the upstream power generation process. The cold air, after heat exchange, continues to flow towards the axis of the cooling tower and is finally output from the cooling tower. The air-cooled heat exchanger is equipped with multiple parallel flying-wing finned tubes. The flying-wing finned tubes are flat tubes with flying-wing fins on their opposite wide sides. The flying-wing finned tubes are arranged in the direction of the cold air flow.

[0015] Furthermore, the included angle between the two side end faces of the cooling triangular unit is the vertex angle θ, and the included angle α between the flying wing finned tube and the side end face satisfies: α=1 / 2θ±5°.

[0016] Furthermore, α = 1 / 2θ.

[0017] Compared with the prior art, the beneficial effects of this utility model are as follows:

[0018] The air-cooled heat exchanger of the cooling triangle unit of this utility model low-wind-resistance cooling tower uses flat-tube flying-wing finned tubes as heat exchange tubes. The flying-wing finned tubes are arranged in the direction of cold air flow, which effectively reduces wind resistance. This allows the cold air entering the cooling triangle to exchange heat with the flying-wing finned tubes and then continuously flow towards the tower axis. This avoids the situation in existing dry cooling towers where multiple rows of heat exchange tubes are set, which causes the cold air to be deflected multiple times between the heat exchange tubes. This improves the cold air circulation efficiency, thereby providing sufficient cooling capacity for the cooling of the materials flowing in the air-cooled heat exchanger and improving the heat exchange efficiency of the cooling triangle unit.

[0019] This utility model of a low-wind-resistance cooling tower can reduce the number of reversals in the process of cooling air entering the cooling tower through the cooling triangle, thereby reducing wind resistance, increasing the cooling air volume of the natural ventilation dry air cooling system, and achieving high overall heat exchange efficiency of the cooling tower.

[0020] The cooling method of this low-wind-resistance cooling tower has a convenient process flow, sufficient cold air supply, high heat exchange efficiency, low equipment processing and maintenance costs, wide applicability, and significant application and promotion value. Attached Figure Description

[0021] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0022] Figure 1 This diagram shows a structural diagram of a cooling triangular unit of the low wind resistance cooling tower of this utility model;

[0023] Figure 2 Show Figure 1 An exploded structural diagram of a cooling triangular unit in a low-resistance cooling tower.

[0024] Figure 3 This is a schematic diagram of the operation of a cooling triangular unit of the low wind resistance cooling tower of this utility model;

[0025] Figure 4 The curves showing the variation of the heat transfer coefficient of the air-cooled heat exchanger under different operating parameters in Example 1 are shown.

[0026] Figure 5 A structural diagram of the hollow heat exchanger in the cooling triangular unit of the low wind resistance cooling tower of this utility model;

[0027] Figure 6 This diagram illustrates a structural design of a wing-type finned tube in a triangular cooling unit of a low-wind-resistance cooling tower.

[0028] Figure 7This is a schematic cross-sectional view of a cooling triangular unit in the low-resistance cooling tower of this utility model. Note that, for the sake of brevity... Figures 1-3 , Figure 5 , Figure 7 The flying fins on the flying fin tube are not shown in the diagram.

[0029] The above figures include the following reference numerals:

[0030] 1-Air-cooled heat exchanger, 11-Flying finned tube, 12-Flying fin, 13-Upper tube sheet, 14-Lower tube sheet, 15-Upper tube cap, 16-Lower tube cap, 17-Side beam, 2-Inlet grille, 31-Upper sealing plate, 32-Lower sealing plate. Detailed Implementation

[0031] To facilitate understanding of this utility model, a more comprehensive description of it will be provided below, along with preferred embodiments. However, it should be understood that these embodiments are merely for more detailed explanation and should not be construed as limiting the utility model in any way, i.e., not limiting the scope of protection of this utility model.

[0032] Unless otherwise defined, the technical terms used in the following embodiments have the same meanings as commonly understood by those skilled in the art to which this invention pertains. Unless otherwise specified, the experimental reagents used in the following embodiments are conventional biochemical reagents; and the experimental methods described are conventional methods.

[0033] Example 1

[0034] A low-drag cooling tower cooling triangular unit, combined with Figures 1-2 The front end face of the cooling triangular unit is provided with an air intake grille 2 for inputting cold air, and the first and second side ends are two air-cooled heat exchangers 1 connected in a V-shape; cooling water is input into the air-cooled heat exchanger 1 and cooled down after exchanging heat with the cold air, and the cold air flows into the axial direction of the cooling tower after exchanging heat with the air-cooled heat exchanger 1; it also includes an upper sealing plate 31 at the top and a lower sealing plate 32 at the bottom; wherein, the air-cooled heat exchanger 1 is provided with multiple parallel flying wing finned tubes 11, the flying wing finned tubes 11 are flat tubes, and flying wing fins 12 are provided on two opposite wide surfaces; the flying wing finned tubes 11 are arranged in the direction of cold air flow.

[0035] Understandably, the flat tube-shaped heat exchange tubes are set with the airflow direction, which will reduce the resistance encountered by the cold air after it enters the cooling triangular unit. The reduction of obstacles encountered by the air during the flow usually means an increase in airflow velocity. Furthermore, the higher airflow velocity will lead to a reduction in the residence time of the cold air in the heat exchanger and insufficient contact time with the heat exchanger, thereby affecting the local heat exchange effect.

[0036] Based on extensive experimental results, this invention employs a wing-shaped finned tube 11 as the heat exchange tube of the air-cooled heat exchanger 1, and innovatively arranges the flat tubular wing-shaped finned tube 11 in a direction with the airflow, combined with... Figure 3 It can be seen that during actual operation, the cooling air can be guided to enter from the air intake grille 2 and exchange heat with the wing-shaped finned tube 11, and then flow towards the axis of the cooling tower. This not only avoids the increase in flow resistance caused by other pipes, steps and other obstacles during the flow of cooling air towards the center of the tower, but also improves the heat exchange efficiency of the cooling triangle unit under low wind resistance conditions.

[0037] Specific experiments include:

[0038] On the one hand, this embodiment tested the structure and heat transfer efficiency parameters of the traditional aluminum tube-aluminum finned heat exchanger tube and the aluminum wing-shaped finned tube 11. The test results are shown in Table 1.

[0039] Table 1

[0040] parameter Aluminum tube-aluminum fin heat exchanger tube Flying finned tube 11 <![CDATA[Contact thermal resistance (m 2 ·K / W)]]> <![CDATA[7×10 -5 ~3×10 -4 ]]> 0 <![CDATA[Body density (kg / m 3 )]]> 60～85 30～35 <![CDATA[Fin area (m 2 / m)]]> 1.7811 3.67 <![CDATA[Heat transfer coefficient on the wind side (W / (m 2 ·K))]]> <![CDATA[479U N 0.718 ]]> <![CDATA[≈1031U N 0.8 ]]> Hydraulic diameter (mm) 20 12.7

[0041] In traditional radiators, the connection between the tube body and fins of the finned heat exchanger tube is achieved by welding or fastening, such as steel tube-aluminum finned heat exchanger tubes or aluminum tube-aluminum finned heat exchanger tubes. The resulting thermal resistance is the primary factor affecting heat dissipation performance. This utility model's air-cooled heat exchanger 1 in a cooling triangular unit uses a wing-shaped finned tube 11, with the wing-shaped fins 12 on the tube body manufactured by a cutting process. Therefore, the heat dissipation fins and heat dissipation tubes are integrated, achieving body-based heat dissipation and contactless thermal resistance.

[0042] As shown in Table 1, the heat dissipation performance of traditional finned heat exchange tubes is limited by contact thermal resistance, while the wing-type finned tube 11 used in this invention achieves zero contact thermal resistance, greatly improving the heat transfer efficiency of the air-cooled heat exchanger 1. The fin area and windage heat transfer coefficient of the wing-type finned tube 11 are significantly better than those of traditional finned heat exchange tubes, further confirming the excellent heat exchange performance of the wing-type finned tube 11. In addition, the wing-type finned tube 11 of the same material has a lower bulk density than traditional finned heat exchange tubes, thus having higher thermal conductivity. Its lightweight characteristics make it easy to design and install, and can adapt to various complex space and structural requirements. Furthermore, the relatively small hydraulic diameter of the wing-type finned tube 11 can increase the flow velocity of the fluid inside the tube, making it easier to achieve turbulence and further improve heat transfer efficiency.

[0043] On the other hand, the heat exchange performance of the air-cooled heat exchanger 1 used in this embodiment was tested using a standard wind tunnel test rig. During the test, the heat exchange medium flowing inside the heat exchange tube was water, and the flat tube-shaped flying fin tube 11 was arranged in the direction of airflow. Specifically, the flow channel between the flat tube-shaped flying fin tube 11 tended to be parallel to the airflow direction. Under this condition, the airflow resistance was small, which correspondingly promoted the increase of airflow rate.

[0044] Based on this, this embodiment tested the heat transfer and air-side and water-side flow resistance at four water flow rates of 438 L / min, 626 L / min, 817 L / min, and 1001 L / min, respectively, for different oncoming air flow rates. The corresponding in-pipe velocities were 0.7, 1.0, 1.3, and 1.6 m / s, respectively, thus exploring the influence of oncoming mass air velocity on the heat transfer coefficient of the heat exchanger. The test results are as follows: Figure 4 As shown in the figure. The windward side refers to the surface area that the cold air first comes into contact with when it flows through the air-cooled heat exchanger 1.

[0045] Based on the test results, data fitting using the least squares method confirms that the relationship between the heat transfer coefficient of the air-cooled heat exchanger 1 containing the finned tube 11 and the air mass velocity at the windward side and the water velocity inside the tube can be expressed as Equation (1):

[0046] K = 38.7466v a 0.212 v w 0.088 Equation (1);

[0047] Where, 1.0≤v a ≤5.0, 0.7≤v w ≤1.6; v a The frontal wind velocity of the heat exchanger is in m / s; v w The velocity of the water flow inside the pipe is m / s; K is the heat transfer coefficient of the radiator, W / (m³). 2 ·℃).

[0048] Combination Figure 4 It can be seen that the heat transfer coefficient of the air-cooled heat exchanger 1, which includes the wing-shaped finned tube 11, increases with the increase of air mass wind speed and also with the increase of water flow velocity in the tube. This reflects that in the cooling triangle unit of the low wind resistance cooling tower of this utility model, by setting the flat tube-shaped wing-shaped finned tube 11 in the direction of air flow, the flow resistance of cold air is reduced and the wind speed is increased. At the same time, the convective heat transfer between the air and the heat exchange surface is enhanced, avoiding the condition of uneven local heat transfer of the heat exchanger due to the increase of wind speed, and improving the overall heat transfer efficiency of the air-cooled heat exchanger 1.

[0049] Figure 5A structural diagram of an air-cooled heat exchanger 1 is shown. The air-cooled heat exchanger 1 includes a heat exchanger core, which includes an upper tube sheet 13, a lower tube sheet 14, and multiple finned tubes 11. The finned tubes 11 are flat tubes with finned fins 12 on two opposite wide surfaces. The multiple finned tubes 11 are arranged in parallel between the upper tube sheet 13 and the lower tube sheet 14. It also includes an upper tube cap 15 and a lower tube cap 16 connected to the upper and lower tube sheets. The space formed by the tube sheet and the corresponding tube cap is used to collect and distribute the heat exchange medium. Side beams 17 are also provided on both sides of the heat exchanger core in the air-cooled heat exchanger 1.

[0050] Figure 6 A schematic diagram of an optional structure of the wing-shaped finned tube 11 in the heat exchange core is shown. The wing-shaped fins are thin sheet-like metal sheets formed by shaving the surface of the wing-shaped finned tube 11. Therefore, the fluid pipe and the wing-shaped fins 12 are integrally formed. There is no contact thermal resistance between the wing-shaped fins and the inner channel, which maximizes the internal heat transfer capacity and enhances the overall structural strength of the wing-shaped finned tube 11. This is beneficial for the low wind resistance cooling tower cooling triangle unit of this embodiment to maintain a high heat exchange efficiency even under low wind resistance conditions.

[0051] Example 2

[0052] Based on the low-resistance cooling tower cooling triangle unit shown in Example 1, this example explores and optimizes the flying-wing finned tube 11 in the cooling triangle unit at multiple angles along the direction of cold air flow to further reduce the resistance of the cooling zone triangle unit to cold air flow and improve heat exchange efficiency. Specifically:

[0053] Optionally, the angle between the first side end face and the second side end face is the apex angle θ, and the angle α between the flying wing finned tube 11 and the first side end face or the second side end face satisfies: α = 1 / 2θ ± 5°. (Combined with...) Figure 7 The adjacent finned tubes 11 form a heat exchange path for the flow of cold air in the air-cooled heat exchanger 1. When α is within this angle range, the flow channel between the finned tubes 11 in the air-cooled heat exchanger 1 is nearly parallel or parallel to the flow channel of the air input from the air intake grille 2. This optimizes the cold air flow path from the air intake grille 2 to the cooling tower axis, reduces the formation of turbulence and eddies, significantly reduces wind resistance, and promotes heat exchange between the cold air and the finned tubes 11.

[0054] It should be noted that the included angle α in this utility model refers to the included angle between the wing-type finned tube 11 in the first side end face or the corresponding side end face. In this utility model, the included angle is the smaller of the complementary angles when two planes intersect.

[0055] Optionally, the angle α between the wing-shaped finned tube 11 and the first or second side end face is 1 / 2θ, so that the flow channel between the wing-shaped finned tubes 11 in the air-cooled heat exchanger 1 is parallel to the flow channel of the air entering from the air intake grille 2, forming an unobstructed flow path from the air intake grille to the cooling tower axis, guiding the cold air to flow rapidly towards the center of the cooling tower.

[0056] Optionally, the apex angle θ can be set to 60°≤θ≤90°, with the air-cooled heat exchanger arranged in a V-shape. The included angle θ (60°≤θ≤90°) synergizes with the finned tube arrangement angle α (α=1 / 2θ±5°). Through angle matching, the finned tubes and airflow direction tend to be parallel, allowing cold air to flow in a straight line towards the tower axis after entering through the inlet grille, avoiding multiple deflections in traditional multi-row tube layouts. This design not only reduces wind resistance but also extends the effective contact time between air and finned tubes by optimizing the flow path, thus improving overall heat exchange efficiency. Correspondingly, the selectable range for α is 25°≤α≤50°, and an appropriate α angle can be set as needed in actual operating conditions.

[0057] Example 3

[0058] Based on the low wind resistance cooling tower cooling triangle unit shown in Embodiment 1, this embodiment further optimizes the structure of the flying wing finned tube 11.

[0059] Understandably, the relative positional relationship between multiple wing-shaped fins 12 on the wing-shaped finned tube 11 also affects the overall heat transfer effect of the wing-shaped finned tube 11. In this embodiment, the multiple wing-shaped fins 12 can be selected to be evenly spaced and parallel to each other, so that cold air or other fluids can flow between the fins, thereby promoting uniform heat transfer, reducing local overheating or overcooling, and improving heat exchange efficiency.

[0060] Furthermore, the radiant heat between the wing-shaped fins 12 and the wing-shaped finned tube 11 is related to the three-dimensional angle between them. Based on the low-resistance cooling tower cooling triangle unit shown in Embodiment 1, the included angle between the wing-shaped fins 12 and the wing-shaped finned tube 11 can be an acute angle or a right angle. In this embodiment, the wing-shaped fins 12 of the wing-shaped finned tube 11 can be perpendicular to the wing-shaped finned tube 11, which not only improves the radiative heat transfer effect but also further reduces the airflow resistance of cold air.

[0061] It should be noted that the specific shape of the wing-shaped fins 12 is not limited in this embodiment. For example, it can be selected as a straight, arc-shaped, or wavy type, and the choice can be made according to the specific working conditions. The material of the wing-shaped finned tube 11 is not limited in this embodiment. It can be selected as an aluminum alloy wing-shaped finned tube 11, such as a wing-shaped finned tube 11 made of 1-6 series industrial aluminum profiles, which reduces the overall weight of the air-cooled heat exchanger 1 and reduces the processing difficulty of the wing-shaped fins 11.

[0062] Furthermore, based on the low wind resistance cooling tower cooling triangle unit shown in Embodiment 1, the flying finned tubes 11 are arranged in one or more rows along the width direction of the heat exchanger, thereby meeting the heat exchange requirements of more operating conditions.

[0063] Based on the low wind resistance cooling tower cooling triangle unit shown in Embodiment 1, the relative positional relationship of adjacent wing-shaped finned tubes 11 in the air-cooled heat exchanger 1 is not limited and can be staggered, thereby adapting to more medium-duty heat exchange requirements through the staggered arrangement of adjacent wing-shaped finned tubes 11.

[0064] Based on the low wind resistance cooling tower cooling triangle unit shown in Embodiment 1, the narrow surface of the wing-type finned tube 11 in the air-cooled heat exchanger 1 is a plane or an arc surface, that is, the cross-section of the wing-type finned tube 11 can be a square flat tube or a round flat tube, which can be selected as needed in the specific process.

[0065] Example 4

[0066] Based on the low wind resistance cooling tower cooling triangle unit shown in Embodiment 1, the structure of the air intake grille 2 was also explored and optimized in this embodiment.

[0067] Optionally, the air intake grille 2 is a louver. The louver has two states: open and closed. In actual operation of the cooling triangle unit, the open louver guides the cold air to flow towards the center of the cooling tower after passing through the air intake grille 2.

[0068] Optionally, the louvers can be horizontal or vertical, with horizontal louvers being more preferred. This means the louver blades are horizontally positioned. The louvered air intake grille (preferably horizontal) can adjust the airflow distribution, reduce local turbulence, and complement the finned tubes arranged in the direction of airflow. Simultaneously, the upper sealing plate 31 and lower sealing plate 32 enclose the non-flow channel area of ​​the cooling triangular unit, preventing cold air leakage and ensuring concentrated airflow through the heat exchange area. This combined design improves both air utilization efficiency and structural stability.

[0069] It should be noted that the above description is a further detailed explanation of the present invention in conjunction with specific embodiments, and should not be construed as limiting the specific implementation of the present invention to these descriptions; the dimensional data in this embodiment do not limit the technical solution, but merely illustrate one specific working condition. For those skilled in the art to which this invention pertains, several simple improvements and modifications can be made without departing from the concept of the present invention, and all such improvements and modifications should be considered to fall within the scope of protection of the present invention.

Claims

1. A low-draught cooling tower cooling delta cell, characterized in that, The front end surface of the cooling triangle unit is provided with an air inlet grille for inputting cold air, the first side end surface and the second side end surface are two air-cooled heat exchangers connected in a V shape; the cooling water input air-cooled heat exchanger is cooled after heat exchange with the cold air, and the cold air flows into the axial direction of the cooling tower after heat exchange with the air-cooled heat exchanger; further comprising an upper sealing plate arranged at the upper portion and a lower sealing plate arranged at the lower portion; The air-cooled heat exchanger is provided with a plurality of parallel arranged flying wing finned tubes, the flying wing finned tube is a flat tube, and two opposite wide surfaces thereof are provided with flying wing fins; the flying wing finned tube is arranged along the cold air flow direction.

2. The low-draught cooling tower cooling delta cell defined in claim 1, wherein The included angle between the first side end surface and the second side end surface is a top angle θ, and the included angle α between the flying wing finned tube and the first side end surface or the second side end surface satisfies: α = 1 / 2 θ ± 5°.

3. The low-draught cooling tower cooling delta cell defined in claim 2, wherein, α = 1 / 2 θ.

4. A low-draught cooling tower cooling delta cell according to claim 2 or 3, characterised in that, The value range of the top angle θ satisfies 60° ≤ θ ≤ 90°.

5. The low-draught cooling tower cooling delta cell defined in claim 1, wherein, The flying wing fin is perpendicular to the flying wing finned tube.

6. The low-draught cooling tower cooling delta cell defined in claim 1, wherein, The air inlet grille is a louver; the louver is a horizontal louver or a vertical louver.

7. A low-wind- resistance cooling tower characterized by The low wind resistance cooling tower cooling triangle unit comprises the low wind resistance cooling tower cooling triangle unit according to any one of claims 1-6.

Images