Turbulent flow piece, heat exchanger and water heater

Abstract

The utility model discloses a spoiler, a heat exchanger and a water heater, and relates to the technical field of heat exchange equipment, the spoiler comprises a spiral link and a side wall vortex generator; the spiral band spirally extends in the length direction of the heat exchange tube and is provided with an open hole. The side wall vortex generator is arranged on the spiral band and used for guiding fluid from the pipe wall of the heat exchange pipe to the pipe center. According to the technical scheme provided by the utility model, the flow resistance of fluid in the pipe can be reduced while heat transfer in the pipe is enhanced.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange equipment technology, and in particular to a turbulence-disrupting component, a heat exchanger, and a water heater. Background Technology

[0002] Enhanced heat transfer technology within heat exchangers is widely used in industries such as petroleum, chemical, metallurgy, transportation, and home appliances. Under the backdrop of carbon emissions and energy conservation, industrial development demands energy saving and emission reduction. Enhanced heat transfer technology within heat exchangers can effectively solve the problem of low heat transfer efficiency in smooth heat exchange tubes.

[0003] In related technologies, spiral structure baffles are used to enhance heat transfer inside the pipe. However, while enhancing heat transfer inside the pipe, spiral structure baffles also increase the resistance to fluid flow inside the pipe. Utility Model Content

[0004] The main purpose of this invention is to propose a flow-deflecting component, heat exchanger, and water heater, which aims to enhance heat transfer within the pipe while reducing the flow resistance of the fluid within the pipe.

[0005] To achieve the above objectives, this utility model proposes a flow-deflecting element for installation inside a heat exchange tube, the flow-deflecting element comprising:

[0006] A spiral ribbon extends spirally along the length of the heat exchange tube, and the spiral ribbon is provided with openings;

[0007] A sidewall vortex generator, located on the spiral band, is used to guide fluid from the tube wall of the heat exchange tube to the center of the tube.

[0008] In one embodiment, the spiral band includes:

[0009] The sidewall vortex structure extends spirally along the length of the heat exchange tube and is located close to the tube wall. The sidewall vortex structure has a first opening, and the opening includes the first opening. The sidewall vortex generator is located on the inner side of the sidewall vortex structure.

[0010] In one embodiment, the spiral band further includes:

[0011] A central vortex structure extends spirally along the length of the heat exchange tube and is located close to the center of the heat exchange tube. A first opening is formed between the central vortex structure and the sidewall vortex structure. The central vortex structure is provided with a second opening. The first opening and the second opening constitute the opening.

[0012] In one embodiment, the central vortex structure is connected to the side of the sidewall vortex generator away from the sidewall vortex structure.

[0013] In one embodiment, the central vortex structure is connected to the sidewall vortex generator via a fixed structure.

[0014] In one embodiment, the projection of the sidewall swirling structure onto the axial direction of the heat exchange tube is defined as the sidewall swirling projection structure. The minimum outer diameter of the sidewall swirling projection structure is D, and the width of the sidewall swirling structure is W. Then, the following condition is satisfied: W <D / 2。

[0015] In one embodiment, the height of the sidewall vortex generator is defined as H, then the following condition is satisfied: H <D / 2。

[0016] In one embodiment, the projection of the central vortex structure onto the axial direction of the heat exchange tube is defined as the central vortex projection structure. The minimum outer diameter of the central vortex projection structure is D1, and the diameter of the second opening is D2. Then, D2 satisfies the following condition: <D1,D1<D / 4。

[0017] In one embodiment, the maximum outer diameter of the sidewall vortex projection structure is defined as Y, and the maximum outer diameter of the central vortex projection structure is defined as Y1, then the following condition is satisfied: Y1 <Y / 4。

[0018] In one embodiment, the pitch of the sidewall swirl structure is defined as P, and the length of the heat exchange tube is L, then: P <L / 4。

[0019] In one embodiment, multiple sidewall vortex generators are provided, and the multiple sidewall vortex generators are distributed at intervals along the extension direction of the sidewall vortex structure.

[0020] To achieve the above objectives, this utility model also proposes a heat exchanger, comprising:

[0021] Heat exchanger tubes;

[0022] The aforementioned turbulence-inducing element is disposed inside the heat exchange tube.

[0023] To achieve the above objectives, this utility model also proposes a water heater, including the heat exchanger described above.

[0024] The technical solution of this utility model involves setting openings on the spiral ribbon. These openings reduce the flow resistance of the fluid flowing through the spiral ribbon, thereby effectively reducing the flow resistance of the fluid inside the tube. Furthermore, the openings reduce the guiding area of ​​the spiral ribbon. Therefore, by combining the spiral ribbon with a sidewall vortex generator, the spiral ribbon generates swirling flow within the heat exchange tube, guiding the swirling fluid from front to back. This ensures that the hot fluid at the front of the heat exchange tube is thoroughly mixed with the cold fluid at the rear, preventing localized high temperatures and enhancing heat transfer within the tube. Simultaneously, the sidewall vortex generator guides the fluid from the tube wall to the center of the tube, allowing the fluid to thoroughly mix the hot fluid near the tube wall with the cold fluid at the center, similarly preventing localized high temperatures and further enhancing heat transfer within the tube.

[0025] Therefore, this solution, by combining an open spiral ribbon with a sidewall vortex generator, can enhance heat transfer within the pipe while reducing the flow resistance of the fluid inside the pipe. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0027] Figure 1 A schematic diagram of the structure of an embodiment of the baffle provided by this utility model;

[0028] Figure 2 A side view of an embodiment of the spoiler provided by this utility model;

[0029] Figure 3 for Figure 2 A magnified view of a portion of the image;

[0030] Figure 4 A front view of an embodiment of the baffle provided by this utility model;

[0031] Figure 5 A front view of another embodiment of the spoiler provided by this utility model;

[0032] Figure 6 A side view of another embodiment of the spoiler provided by this utility model;

[0033] Figure 7 A schematic diagram of a heat exchanger embodiment provided by this utility model;

[0034] Figure 8 The heat transfer coefficient distribution diagrams for smooth heat exchange tubes, existing spiral structures, and two embodiments of this utility model are shown.

[0035] Figure 9 Pressure drop distribution diagrams for smooth heat exchange tubes, existing spiral structures, and two embodiments of this utility model;

[0036] Figure 10 A comparison diagram of heat transfer coefficients and pressure drops of a smooth heat exchange tube compared to existing spiral structures and two embodiments of this utility model.

[0037] Explanation of icon numbers:

[0038]

[0039]

[0040] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0041] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0042] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0043] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0044] Enhanced heat transfer technology within heat exchangers is widely used in industries such as petroleum, chemical, metallurgy, transportation, and home appliances. Under the backdrop of carbon emissions and energy conservation, industrial development demands energy saving and emission reduction. Enhanced heat transfer technology within heat exchangers can effectively solve the problem of low heat transfer efficiency in smooth heat exchange tubes.

[0045] In related technologies, spiral structure baffles are used to enhance heat transfer inside the pipe. However, while enhancing heat transfer inside the pipe, spiral structure baffles also increase the resistance to fluid flow inside the pipe.

[0046] Based on the above problems, this utility model proposes a flow-deflecting element 10, which aims to enhance heat transfer within the tube while reducing the flow resistance of the fluid inside the tube. This flow-deflecting element 10 is applied in a heat exchanger 100, which includes a heat exchange tube 20 and the flow-deflecting element 10 installed within the heat exchange tube 20. The spiral ribbon 11 of the flow-deflecting element 10 extends spirally along the length of the heat exchange tube 20, and an opening 11a is provided on the spiral ribbon 11. The opening 11a reduces the flow resistance of the fluid flowing through the spiral ribbon 11, thereby effectively reducing the flow resistance of the fluid inside the tube. The sidewall vortex generator 12 of the flow-deflecting element 10 guides the fluid from the tube wall of the heat exchange tube 20 to the center of the tube. The combination of the spiral ribbon 11 with the opening 11a and the sidewall vortex generator 12 can enhance heat transfer within the tube while reducing the flow resistance of the fluid inside the tube. The structure of the flow-deflecting element 10 will be described below by way of an embodiment.

[0047] Please see Figures 1 to 7 In one embodiment of the present invention, the turbulence-disrupting element 10 is installed inside the heat exchange tube 20. The turbulence-disrupting element 10 includes a spiral ribbon 11 and a sidewall vortex generator 12. The spiral ribbon 11 extends spirally along the length of the heat exchange tube 20 and has an opening 11a. The sidewall vortex generator 12 is disposed on the spiral ribbon 11 and is used to guide the fluid from the tube wall of the heat exchange tube 20 to the center of the tube.

[0048] In this embodiment, the heat exchange tube 20 can be a circular tube, an elliptical tube, a flat tube, a rectangular tube, etc. The outer contour of the spiral ribbon 11 is adapted to the shape of the heat exchange tube 20. The heat exchange tube 20 is usually oblong or oblong. Therefore, the outer contour of the projection of the spiral ribbon 11 on the axial direction of the heat exchange tube 20 is usually circular or elliptical. The turbulence-inducing element 10 includes the spiral ribbon 11 and the sidewall vortex generator 12. The specific structure of the spiral ribbon 11 and the sidewall vortex generator 12 will be described below.

[0049] The spiral ribbon 11 can be a single spiral ribbon structure with an opening 11a located in the middle, outer, or inner part of the spiral ribbon structure. Alternatively, the spiral ribbon 11 can consist of two or more spiral ribbon structures, each extending spirally along the length of the heat exchange tube 20, and at least one spiral ribbon structure having an opening 11a located in the middle, outer, or inner part of the spiral ribbon structure. In some embodiments, the spiral ribbon 11 has an opening 11a in the middle, extending along the length of the heat exchange tube 20 through the entire spiral ribbon structure, thus dividing the spiral ribbon 11 into two spiral ribbon structures. Specifically, the shape of the opening 11a includes, but is not limited to, circular, annular, elliptical, etc. Thus, the opening 11a reduces the flow resistance of fluid flowing through the spiral ribbon 11, thereby effectively reducing the flow resistance of the fluid inside the tube.

[0050] The sidewall vortex generator 12 is connected to the spiral ribbon 11. When the fluid flows through the interior of the heat exchange tube 20, the sidewall vortex generator 12 guides the fluid from the tube wall to the center of the tube, thereby achieving thorough mixing of the hot and cold fluids and improving the heat transfer performance inside the tube. Specifically, the sidewall vortex generator 12 can be, but is not limited to, elliptical, triangular, or circular shapes. The sidewall vortex generator 12 and the spiral ribbon 11 can be integrally formed or connected by welding, bonding, or other methods.

[0051] In summary, the technical solution of this utility model reduces the flow resistance of fluid flowing through the spiral ribbon 11 by setting an opening 11a on the spiral ribbon 11, thereby effectively reducing the flow resistance of the fluid inside the pipe. In addition, the setting of the opening 11a reduces the guiding area of ​​the spiral ribbon 11. Therefore, by combining the spiral ribbon 11 with the sidewall vortex generator 12, the spiral ribbon 11 can generate swirling flow inside the heat exchange tube 20 and guide the swirling fluid generated inside the heat exchange tube 20 from front to back. This allows the hot fluid at the front of the heat exchange tube 20 to be guided to the cold fluid at the rear for thorough mixing, preventing local high temperature phenomena and achieving the effect of enhancing heat transfer inside the tube. At the same time, the sidewall vortex generator 12 can guide the fluid from the tube wall of the heat exchange tube 20 to the center of the tube, allowing the fluid to fully mix the hot fluid near the tube wall with the cold fluid at the center of the tube. This also prevents local high temperature phenomena and further enhances the effect of heat transfer inside the tube.

[0052] Therefore, by combining the spiral ribbon 11 with the opening 11a and the sidewall vortex generator 12, this solution can enhance heat transfer inside the pipe while reducing the flow resistance of the fluid inside the pipe.

[0053] Please see Figures 1 to 6 In one embodiment of the present invention, the spiral ribbon 11 includes a sidewall vortex structure 111. The sidewall vortex structure 111 extends spirally along the length of the heat exchange tube 20 and is disposed close to the tube wall of the heat exchange tube 20. The sidewall vortex structure 111 is provided with a first opening 11a1. The opening 11a includes the first opening 11a1. The sidewall vortex generator 12 is disposed on the inner side of the sidewall vortex structure 111.

[0054] In this embodiment, the inner side of the sidewall swirl structure 111 refers to the side closer to the center of the tube.

[0055] With this configuration, the sidewall vortex structure 111 can generate a swirling fluid flowing from front to back near the tube wall of the heat exchange tube 20. This swirling fluid can effectively guide the hot fluid near the front tube wall to the cold fluid behind for thorough mixing, preventing localized high temperatures. In addition, the sidewall vortex generator 12 can generate a longitudinal vortex fluid from the tube wall to the tube center near the tube wall. This longitudinal vortex fluid can effectively guide the hot fluid near the tube wall to the cold fluid in the tube center for thorough mixing, preventing localized high temperatures. Furthermore, the first opening 11a1 on the sidewall vortex structure 111 can reduce the flow resistance of the fluid flowing through the sidewall vortex structure 111, thereby effectively reducing the flow resistance of the fluid inside the tube. Therefore, this solution combines the sidewall vortex structure 111 with the first opening 11a1 and the sidewall vortex generator 12, which can enhance heat transfer inside the tube while reducing the flow resistance of the fluid inside the tube.

[0056] Please see Figures 1 to 4 In one embodiment of the present invention, the spiral ribbon 11 may further include a central swirl structure 112. The central swirl structure 112 extends spirally along the length of the heat exchange tube 20 and is located close to the center of the heat exchange tube 20. A first opening 11a1 is formed between the central swirl structure 112 and the sidewall swirl structure 111. The central swirl structure 112 is provided with a second opening 11a2. The first opening 11a1 and the second opening 11a2 constitute the opening 11a.

[0057] This configuration, in addition to the sidewall vortex structure 111 near the wall of the heat exchange tube 20, also includes a central vortex structure 112 at the center of the tube. This central vortex structure 112 generates swirling fluid at the center of the tube and guides this swirling fluid from front to back, ensuring thorough mixing of the hot fluid in front of the tube center with the cold fluid behind, preventing localized high temperatures and enhancing heat transfer within the tube. Therefore, this scheme combines the sidewall vortex structure 111, the sidewall vortex generator 12, and the central vortex structure 112. The sidewall vortex structure 111 is responsible for mixing the hot and cold fluids near the tube wall, the sidewall vortex generator 12 is responsible for thoroughly mixing the hot fluid near the tube wall and the cold fluid at the center of the tube, and the central vortex structure 112 is responsible for mixing the hot and cold fluids near the center of the tube. The coupling effect of these three components ensures thorough mixing of the hot and cold fluids within the tube, preventing localized high temperatures and effectively improving the overall heat transfer performance of the fluids within the tube. Furthermore, the first opening 11a1 can reduce the flow resistance of fluid flowing through the sidewall swirl structure 111, while the second opening 11a2 can reduce the flow resistance of fluid flowing through the central swirl structure 112. Thus, the flow resistance of the fluid in the pipe can be sufficiently reduced under the action of the first opening 11a1 and the second opening 11a2.

[0058] Furthermore, by changing the shape or cross-sectional area of ​​the central swirling structure 112, the intensity of the central swirling flow can be effectively improved, thereby further improving the mixing degree of the hot and cold fluids inside the tube and further improving the surface temperature of the heat exchange tube 20.

[0059] In this embodiment, the first opening 11a1 is an annular hole formed between the sidewall swirling structure 111 and the central swirling structure 112, and the second opening 11a2 is a hole of the shape of a circle, an ellipse, a rectangle, etc., formed in the middle of the central swirling structure 112.

[0060] In practical applications, the outer contour shape of the projection of the central swirl structure 112 onto the heat exchange tube 20 in the axial direction can be circular, elliptical, rectangular, etc. The outer contour shapes of the projections of the central swirl structure 112 and the sidewall swirl structure 111 onto the heat exchange tube 20 in the axial direction can be the same or different. Furthermore, the helix angle of the central swirl structure 112 and the helix angle of the sidewall swirl structure 111 can be the same or different.

[0061] Please see Figures 1 to 3 In one embodiment of the present invention, the central vortex structure 112 is connected to the side of the sidewall vortex generator 12 away from the sidewall vortex structure 111.

[0062] This configuration, by connecting the central vortex structure 112 to the sidewall vortex generator 12, establishes a connection between the central vortex structure 112 and the sidewall vortex generator 12. The sidewall vortex generator 12 guides the hot fluid near the pipe wall to the central vortex structure 112 located at the center of the pipe, ensuring thorough mixing with the cold fluid near the central vortex structure 112. This prevents localized high temperatures within the pipe and effectively improves the overall heat transfer performance of the fluid inside the pipe. Furthermore, it enhances the installation reliability of the central vortex structure 112, preventing its position from shifting due to fluid flow.

[0063] In practical applications, the central vortex structure 112 can be directly connected to the sidewall vortex generator 12, or it can be indirectly connected to the sidewall vortex generator 12 using other auxiliary structures.

[0064] Please see Figures 1 to 3 In one embodiment of this utility model, the central vortex structure 112 is connected to the sidewall vortex generator 12 via a fixing structure 121.

[0065] With this configuration, the fixed structure 121 makes it easier to connect the central vortex structure 112 and the sidewall vortex generator 12. At the same time, it can increase the area of ​​the first opening 11a1 between the central vortex structure 112 and the sidewall vortex structure 111, which can significantly reduce the flow resistance of the fluid flowing through the spiral ribbon 11, thereby effectively reducing the flow resistance of the fluid in the pipe.

[0066] In practical applications, the central vortex structure 112 can be integrally formed and connected to the sidewall vortex structure 111 using a fixed structure 121, or it can be connected to the sidewall vortex structure 111 by means of bonding, plugging, or other methods using the fixed structure 121. Specifically, the fixed structure 121 includes, but is not limited to, structural components such as connecting rods, connecting buckles, and connecting screws.

[0067] Please see Figure 2, in an embodiment of the present utility model, the projection of the sidewall swirl structure 111 on the axial direction of the heat exchange tube 20 is defined as the sidewall swirl projection structure. The minimum outer diameter of the sidewall swirl projection structure is D, and the width of the sidewall swirl structure 111 is W. Then, it satisfies: W < D / 2.

[0068] With such a setting, in the fluid channel, the proportional relationship between the minimum outer diameter D of the sidewall swirl projection structure and the width W of the sidewall swirl structure 111 can affect the flow characteristics of the fluid. Setting W < D / 2 can enable the fluid to have good flow guiding effect and pressure distribution when flowing through the sidewall swirl structure 111, and avoid poor flow or poor flow guiding effect caused by the width W of the sidewall swirl structure 111 being too large or too small. When the width W of the sidewall swirl structure 111 is too large, the resistance to the fluid flowing through the sidewall swirl structure 111 will be large; while when the width W of the sidewall swirl structure 111 is too small, the flow guiding effect of the sidewall swirl structure 111 will be poor, and it cannot better guide the swirl fluid generated in the heat exchange tube 20 from front to back, resulting in poor heat transfer enhancement effect. Therefore, the setting of this range helps to balance the hydrodynamic performance, while enhancing the heat transfer in the tube, reducing the flow resistance of the fluid in the tube.

[0069] In some embodiments, when the outer contour of the sidewall swirl projection structure is an ellipse, the minimum outer diameter D of the sidewall swirl projection structure is the minor diameter of the ellipse. The width W of the sidewall swirl structure 111 refers to the distance of the sidewall swirl structure 111 in the direction from the tube wall to the center of the heat exchange tube 20.

[0070] As some examples, the width W of the sidewall swirl structure 111 can be D / 6, D / 5, D / 3, etc. Exemplarily, taking the heat exchange tube 20 as an elliptical tube, the inner minor diameter of the heat exchange tube 20 is 30 mm. Therefore, the minimum outer diameter D of the sidewall swirl projection structure is 30 mm, and the width W of the sidewall swirl structure 111 can be 5 mm, 6 mm, 10 mm, etc.

[0071] Please refer to Figure 2 , in an embodiment of the present utility model, the height of the sidewall vortex generator 12 is defined as H. Then, it satisfies: H < D / 2.

[0072] With such a setting, in the fluid channel, the proportional relationship between the minimum outer diameter D of the sidewall swirl projection structure and the height H of the sidewall vortex generator 12 can also affect the flow characteristics of the fluid. Setting H < D / 2 can enable the fluid to have a better flow guiding effect when flowing through the sidewall vortex generator 12 and the central swirl structure 112, and avoid poor flow guiding effects caused by the height H of the sidewall vortex generator 12 being too large or too small. When the height H of the sidewall vortex generator 12 is too large, the space for setting the central swirl structure 112 will be too small, resulting in the outer diameter of the central swirl structure 112 being too small, thus affecting the effect of guiding the fluid generated near the tube center from front to back by the central swirl structure 112 and resulting in poor heat transfer enhancement effect; while when the height H of the sidewall vortex generator 12 is too small, it cannot better guide the hot fluid near the tube wall to the tube center, and will also result in poor heat transfer enhancement effect. Therefore, setting within this range helps to balance the hydrodynamic performance and can effectively enhance the heat transfer inside the tube.

[0073] The height H of the sidewall vortex generator 12 refers to the distance of the sidewall vortex generator 12 in the direction from the tube wall to the tube center of the heat exchange tube 20.

[0074] As some examples, the height H of the sidewall vortex generator 12 can be D / 6, D / 5, D / 3, etc. Exemplarily, taking the heat exchange tube 20 as an elliptical tube, the inner minor diameter of the heat exchange tube 20 is 30 mm. Therefore, if the minimum outer diameter D of the sidewall swirl projection structure is 30 mm, the height H of the sidewall vortex generator 12 can be 5 mm, 6 mm, 10 mm, etc.

[0075] Please refer to Figure 2 、 Figure 3 In an embodiment of the present invention, it is defined that the projection of the central swirl structure 112 in the axial direction of the heat exchange tube 20 is the central swirl projection structure, the minimum outer diameter of the central swirl projection structure is D1, and the diameter of the second opening 11a2 is D2, then it satisfies: D2 < D1, D1 < D / 4.

[0076] With such settings, in the fluid channel, the proportional relationship among the minimum outer diameter D1 of the central swirl projection structure, the minimum outer diameter D of the sidewall swirl projection structure, and the diameter D2 of the second opening 11a2 can also affect the flow characteristics of the fluid. Setting D2 < D1 and D1 < D / 4 can enable the fluid to have a better flow guiding effect when flowing through the central swirl structure 112. When the diameter D2 of the second opening 11a2 is too large, the distance between the central swirl structure 112 and the second opening 11a2 will be too small, thus affecting the effect of the central swirl structure 112 to guide the fluid generated near the tube center from front to back, resulting in poor heat transfer enhancement effect; while when the minimum outer diameter D1 of the central swirl projection structure is too large, the distance between the central swirl structure 112 and the sidewall swirl structure 111 will be too small, making the height H of the sidewall vortex generator 12 too small to better guide the hot fluid near the tube wall to the tube center, and also resulting in poor heat transfer enhancement effect. Therefore, the setting of this range helps to balance the hydrodynamic performance and can effectively enhance the heat transfer inside the tube.

[0077] In some embodiments, the outer contour of the central swirl projection structure is an ellipse, and the minimum outer diameter D1 of the central swirl projection structure is the minor axis of the ellipse. The second opening 11a2 is circular, and the diameter D2 of the second opening 11a2 is the diameter of the circle.

[0078] As some examples, the diameter D2 of the second opening 11a2 can be 0.5D1, 0.55D1, 0.6D1, 0.65D1, 0.7D1, 0.75D1, 0.8D1, 0.85D1, 0.9D1, 0.95D1, etc. The minimum outer diameter D1 of the central swirl projection structure can be D / 10, D / 6, D / 5, etc.

[0079] Exemplarily, taking the heat exchange tube 20 as an elliptical tube, the inner minor axis of the heat exchange tube 20 is 30 mm. Therefore, the minimum outer diameter D of the sidewall swirl projection structure is 30 mm, and the minimum outer diameter D1 of the central swirl projection structure can be 3 mm, 5 mm, 6 mm, etc. The diameter D2 of the second opening 11a is 1.5 mm, 1.8 mm, 3 mm, 3.6 mm, 5.4 mm, etc. <…>Please refer to Figure 2 、[[ID=…]] Figure 3 In an embodiment of the present invention, defining the maximum outer diameter of the sidewall swirl projection structure as Y and the maximum outer diameter of the central swirl projection structure as Y1, then it satisfies: Y1 < Y / 4.

[0081] With such a setting, in the fluid channel, the proportional relationship between the maximum outer diameter Y of the sidewall swirl projection structure and the maximum outer diameter Y1 of the central swirl projection structure can also affect the flow characteristics of the fluid. Setting Y1 < Y / 4 can enable the fluid to have a better resistance reduction effect when flowing through the first opening 11a1 between the sidewall swirl projection structure and the central swirl projection structure. When the maximum outer diameter Y1 of the central swirl projection structure is too large, it will cause the area of the first opening 11a1 between the sidewall swirl projection structure and the central swirl projection structure to be too small, making the first opening 11a1 unable to achieve a good resistance reduction effect. Therefore, the setting of this range helps to balance the hydrodynamic performance, can reduce the flow resistance of the fluid flowing through the sidewall swirl structure 111, and thus can effectively reduce the flow resistance of the fluid in the pipe.

[0082] In some embodiments, when the outer contour of the sidewall swirl projection structure is a first ellipse and the outer contour of the central swirl projection structure is a second ellipse, the maximum outer diameter Y of the sidewall swirl projection structure is the major axis of the first ellipse, and the maximum outer diameter Y1 of the central swirl projection structure is the major axis of the second ellipse.

[0083] As some examples, the maximum outer diameter Y1 of the central swirl projection structure can be 0.1Y, 0.12Y, 0.15Y, 0.16Y, 0.18Y, 0.2Y, 0.22Y, etc.

[0084] Exemplarily, taking the heat exchange tube 20 as an elliptical tube, the inner major axis of the heat exchange tube 20 is 40 mm. Therefore, the maximum outer diameter Y of the sidewall swirl projection structure is 40 mm, and the maximum outer diameter Y1 of the central swirl projection structure can be 4 mm, 4.8 mm, 6 mm, 6.4 mm, 7.2 mm, 8 mm, 8.8 mm, etc.

[0085] Please refer to Figure 4 、 Figure 5 、 Figure 7 , in an embodiment of the present invention, the pitch of the sidewall swirl structure 111 is defined as P, and the length of the heat exchange tube 20 is L, then it satisfies: P < L / 4.

[0086] With such a setting, in the fluid channel, the proportional relationship between the pitch P of the sidewall swirl structure 111 and the length L of the heat exchange tube 20 can also affect the flow characteristics of the fluid. Setting P < L / 4 can enable the fluid to have a better flow guiding effect when flowing through the sidewall swirl structure 111. When the pitch P of the sidewall swirl structure 111 is too large, it will cause the helical lift angle of the sidewall swirl structure 111 to be too large, thus affecting the effect of the sidewall swirl structure 111 to guide the fluid generated near the pipe wall from front to back, resulting in a poor heat transfer enhancement effect. Therefore, the setting of this range helps to balance the hydrodynamic performance and can effectively enhance the heat transfer in the pipe.

[0087] It should be noted that pitch refers to thread pitch, which is the distance between corresponding points on two adjacent thread profiles.

[0088] As some examples, the pitch P of the sidewall vortex structure 111 can be 0.1L, 0.12L, 0.15L, 0.16L, 0.18L, 0.2L, 0.22L, etc.

[0089] For example, taking the heat exchange tube 20 as an elongated elliptical tube, the length L of the heat exchange tube 20 is 200mm, and the pitch P of the sidewall swirl structure 111 can be 20mm, 24mm, 30mm, 32mm, 36mm, 40mm, 44mm, etc.

[0090] Please see Figure 1 , Figure 4 , Figure 5 In one embodiment of this utility model, multiple sidewall vortex generators 12 are provided, and the multiple sidewall vortex generators 12 are distributed at intervals along the extension direction of the sidewall vortex structure 111.

[0091] With this configuration, the multiple sidewall vortex generators 12 can guide the hot fluid near the tube wall at each location to the center of the tube in the direction from the front to the rear of the heat exchange tube 20, so as to fully mix with the cold fluid near the center of the tube and effectively enhance the heat transfer effect.

[0092] Please see Figure 7 This utility model also proposes a heat exchanger 100, which includes a heat exchange tube 20 and a flow-deflecting element 10. The specific structure of the flow-deflecting element 10 is as described in the above embodiments. Since this heat exchanger 100 adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The flow-deflecting element 10 is disposed inside the heat exchange tube 20.

[0093] In this embodiment, the heat exchanger 100 may include multiple heat exchange tubes 20, which may be arranged in parallel or in series, and at least one heat exchange tube 20 is equipped with a baffle 10. For two adjacent heat exchange tubes 20, a space for high-temperature flue gas to flow can be formed between the two adjacent heat exchange tubes 20.

[0094] In one embodiment, the turbulence-disrupting element 10 can be fixedly connected to the wall of the heat exchange tube 20 by welding using a spiral ribbon 11. Of course, in other embodiments, the spiral ribbon 11 can also be fixedly connected to the wall of the heat exchange tube 20 by means of adhesive bonding, screw connection, or other methods.

[0095] Ansys Fluent was used to numerically calculate the flow and heat transfer performance of the spatially staggered sinusoidal wave plate-type turbulence element 10, its deformed structure, and the corresponding smooth heat exchange tube 20. The calculation conditions were: fluid was water, inlet mass flow rate was 0.7 kg / s, inlet temperature was 20℃, outlet pressure was 0, and the wall convective heat transfer coefficient was 1500 kW / m²˙K. A steady-state, Realizable k-ε model was used, and the SIMPLE algorithm was employed for pressure and velocity. For the momentum and energy equations, the diffusion term used a central difference scheme, and the convection term used a second-order upwind difference scheme. The numerical calculation was considered convergent when the residuals of the continuity, momentum, and energy equations were all less than 10⁻⁶. Figures 8 to 10 It is known that adding a spiral structure to the smooth heat exchange tube 20 can effectively reduce the surface temperature of the heat exchange tube 20, but at the same time greatly increases the resistance inside the tube. However, the turbulence element 10 using a sidewall swirl structure 111 + sidewall vortex generator 12 can effectively reduce the resistance inside the tube while increasing the heat transfer coefficient, thereby improving the overall heat transfer performance inside the tube. According to... Figure 9 By adding a central swirl structure 112, the fluid inside the tube can be effectively mixed, resulting in a lower surface temperature of the smooth heat exchange tube 20 and a more uniform fluid temperature inside the tube, thus preventing localized high temperatures.

[0096] This utility model also proposes a water heater, which includes a heat exchanger 100. The specific structure of the heat exchanger 100 is as described in the above embodiments. Since this water heater adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0097] In this embodiment, the water heater may further include a shell, a burner, and a combustion chamber. Both the burner and the heat exchanger 100 are disposed inside the shell. The burner is used to burn gas to generate high-temperature flue gas in the combustion chamber. The high-temperature flue gas flows to the heat exchanger 100 and exchanges heat with the water in the heat exchange tube 20 of the heat exchanger 100 to heat the water flowing through the heat exchange tube 20.

[0098] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A flow-deflecting element for installation inside a heat exchanger tube, characterized in that, The baffle includes: A spiral ribbon extends spirally along the length of the heat exchange tube, and the spiral ribbon is provided with openings; A sidewall vortex generator, located on the spiral band, is used to guide fluid from the tube wall of the heat exchange tube to the center of the tube.

2. The aerodynamic component as described in claim 1, characterized in that, The spiral band includes: The sidewall vortex structure extends spirally along the length of the heat exchange tube and is located close to the tube wall. The sidewall vortex structure has a first opening, and the opening includes the first opening. The sidewall vortex generator is located on the inner side of the sidewall vortex structure.

3. The aerodynamic component as described in claim 2, characterized in that, The spiral band also includes: A central vortex structure extends spirally along the length of the heat exchange tube and is located close to the center of the heat exchange tube. A first opening is formed between the central vortex structure and the sidewall vortex structure. The central vortex structure is provided with a second opening. The first opening and the second opening constitute the opening.

4. The aerodynamic component as described in claim 3, characterized in that, The central vortex structure is connected to the side of the sidewall vortex generator away from the sidewall vortex structure.

5. The aerodynamic component as described in claim 4, characterized in that, The central vortex structure is connected to the sidewall vortex generator via a fixed structure.

6. The aerodynamic component as described in claim 3, characterized in that, Define the projection of the sidewall vortex structure onto the axial direction of the heat exchange tube as the sidewall vortex projection structure. Let the minimum outer diameter of the sidewall vortex projection structure be D, and the width of the sidewall vortex structure be W. Then, the following condition must be met: W <D / 2。 7. The aerodynamic component as described in claim 6, characterized in that, Define the height of the sidewall vortex generator as H, then the following condition is satisfied: H <D / 2。 8. The aerodynamic component as described in claim 6, characterized in that, The projection of the central vortex structure onto the axial direction of the heat exchange tube is defined as the central vortex projection structure. The minimum outer diameter of the central vortex projection structure is D1, and the diameter of the second opening is D2. Then, the following condition is satisfied: D2 <D1,D1<D / 4。 9. The aerodynamic component as described in claim 8, characterized in that, Let Y be the maximum outer diameter of the sidewall vortex projection structure and Y1 be the maximum outer diameter of the central vortex projection structure. Then, the following condition is satisfied: Y1 <Y / 4。 10. The aerodynamic component as described in claim 2, characterized in that, Let P be the pitch of the sidewall vortex structure and L be the length of the heat exchange tube, then: P <L / 4。 11. The aerodynamic component as described in claim 2, characterized in that, The sidewall vortex generator is provided in multiple ways, and the multiple sidewall vortex generators are distributed at intervals along the extension direction of the sidewall vortex structure.

12. A heat exchanger, characterized in that, include: Heat exchanger tubes; The turbulence-disrupting element as described in any one of claims 1 to 11 is disposed inside the heat exchange tube.

13. A water heater, characterized in that, Including the heat exchanger as described in claim 12.

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