Turbulence generator, heat exchanger and water heater

Abstract

The utility model discloses a turbulence generator, a heat exchanger and a water heater, and relates to the technical field of heat exchange equipment, the turbulence generator is used for being installed in a heat exchange tube, the turbulence generator comprises a turbulence plate and a turbulence generation assembly, and the turbulence plate is arranged in the length direction of the heat exchange tube in an extending mode; the turbulent flow generation assembly comprises flow deflectors and vortex plates, and the flow deflectors are arranged on the turbulent flow plates and extend in the fluid direction in the heat exchange tubes; the flow deflector is provided with two opposite ends, the first end of the flow deflector is connected with the turbulent plate, and the second end of the flow deflector inclines in the direction away from the turbulent plate. The swirl plate is arranged at the second end of the flow deflector, the length direction of the swirl plate and the length direction of the flow deflector form an included angle, and a wing protruding out of the side face of the flow deflector is formed. According to the turbulence generator, heat transfer in the heat exchange tube can be enhanced, local high temperature of the heat exchange tube is prevented, heat transfer is uniform, and gasification noise generated by the local high temperature is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchange equipment, in particular to a turbulence generator, a heat exchanger and a water heater. Background Art

[0002] In the related prior art, a turbulence generator and the like are usually arranged in a heat exchange tube to improve the heat exchange efficiency. However, the existing turbulence generators have complex structures, high manufacturing and installation costs, and low heat exchange efficiency and large vaporization noise in actual use. Summary of the Utility Model

[0003] The main purpose of the utility model is to provide a turbulence generator, a heat exchanger and a water heater, aiming to enhance the heat exchange efficiency of the heat exchange tube and reduce the noise of the heat exchanger.

[0004] To achieve the above purpose, the turbulence generator proposed by the utility model is used for being installed in a heat exchange tube, and the turbulence generator includes:

[0005] A turbulence plate extending along the length direction of the heat exchange tube; and

[0006] A turbulence generating assembly including a guide vane and a vortex vane. The guide vane is arranged on the turbulence plate and extends along the fluid direction in the heat exchange tube; the guide vane has opposite ends, the first end of the guide vane is connected to the turbulence plate, and the second end of the guide vane inclines away from the turbulence plate; the vortex vane is arranged at the second end of the guide vane, and the length direction of the vortex vane forms an angle with the length direction of the guide vane and forms a wing portion protruding from the side surface of the guide vane.

[0007] In one embodiment, the vortex vane includes a vortex main body and the wing portion. The vortex main body is connected to the guide vane, and the length direction of the vortex main body forms an angle with the length direction of the guide vane; the wing portion is arranged on the vortex main body and is located at both ends of the vortex main body along its length direction.

[0008] In one embodiment, the wing portion inclines away from the turbulence plate from its connection with the vortex main body.

[0009] In one embodiment, defining the supplementary angle between the vortex main body and the wing portion as β, then it satisfies: 0°≤β≤90°.

[0010] In one embodiment, defining the angle between the guide vane and the turbulence plate as ɑ, then it satisfies: 30°≤ɑ≤75°.

[0011] In one embodiment, the vortex vane extends along the width direction of the turbulence plate.

[0012] In one embodiment, the number of the turbulence generating components is plural, and the plural turbulence generating components are arranged at intervals along the length direction of the turbulence plate.

[0013] In one embodiment, the turbulence plate has opposite first and second sides, and the turbulence generating components are provided on both the first side and the second side;

[0014] The turbulence generating components provided on the first side and the turbulence generating components provided on the second side are alternately arranged at intervals in the length direction of the turbulence plate.

[0015] In one embodiment, a through hole penetrating in the thickness direction of the turbulence plate is provided between two adjacent turbulence generating components of the turbulence plate.

[0016] In one embodiment, the width of the turbulence plate is W, and in the width direction of the turbulence plate, the width of the through hole is D, then it satisfies: 0.80W ≤ D ≤ 0.95W; in the length direction of the turbulence plate, the length of the through hole is L, then it satisfies: 1.0D ≤ L ≤ 2.5D.

[0017] In one embodiment, the pitch between two adjacent through holes is P, then it satisfies: P ≥ L + 4.0 mm.

[0018] The present utility model further provides a heat exchanger, which includes a heat exchange tube and the turbulence generator according to any one of the foregoing embodiments, and the turbulence generator is disposed inside the heat exchange tube.

[0019] The present utility model further provides a water heater, which includes the heat exchanger according to any one of the foregoing embodiments.

[0020] In the technical solution of the present utility model, when the turbulence generator is installed on the heat exchange tube, since the guide vane is disposed on the turbulence plate and extends along the fluid direction inside the heat exchange tube, and the first end of the guide vane is connected to the turbulence plate, and the second end of the guide vane inclines in a direction away from the turbulence plate, thus, when the fluid flows through the guide vane, the guide vane guides the oncoming fluid to the vicinity of the heat exchange tube wall, promotes the mixing of the hot fluid near the wall and the cold fluid at the center, reduces the local high-temperature area, and thereby strengthens the heat transfer; secondly, for the eddy current vane disposed at the second end of the guide vane, since the length direction of the eddy current vane forms an included angle with the length direction of the guide vane and forms a wing portion protruding from the side surface of the guide vane, the eddy current vane can form a longitudinal eddy current in the cross section of the heat exchange tube, and guide the hot fluid near the heat exchange tube wall to the center of the heat exchange tube, thereby strengthening the heat transfer.

[0021] In addition, the eddy current sheet can also confine part of the fluid near the heat exchange tube wall, maintaining a high-speed scouring of the area near the heat exchange tube wall. The subcooled boiling bubbles formed within the thermal boundary layer near the heat exchange tube wall, under the action of the guide vane, form a sidewall flow guide. Under the action of the high-speed scouring fluid, they can quickly break away from the heat exchange tube wall, inhibiting the growth of bubbles and reducing the gasification noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on the structures shown in these drawings.

[0023] Figure 1 Structural schematic diagram of the first embodiment of the turbulence generator provided by the present invention;

[0024] Figure 2 Structural schematic diagram of the second embodiment of the turbulence generator provided by the present invention;

[0025] Figure 3 Structural schematic diagram of the third embodiment of the turbulence generator provided by the present invention;

[0026] Figure 4 Structural schematic diagram of the fourth embodiment of the turbulence generator provided by the present invention;

[0027] Figure 5 Structural schematic diagram of the fifth embodiment of the turbulence generator provided by the present invention;

[0028] Figure 6 is Figure 5 side view of;

[0029] Figure 7 is Figure 6 partial enlarged view of;

[0030] Figure 8 is Figure 7 cross-sectional view taken along A-A in;

[0031] Figure 9 is Figure 5 partial enlarged view of the other side view;

[0032] Figure 10 is Figure 1 schematic diagram of the gas-liquid separation principle in the heat exchange tube in the illustrated embodiment;

[0033] Figure 11 is Figure 1In the illustrated embodiment, a schematic diagram of the main flow direction of the gas-liquid diversion;

[0034] Figure 12 It is a temperature distribution diagram of a smooth heat exchange tube and the application of the five foregoing embodiments of the present invention;

[0035] Figure 13 It is a pressure distribution diagram of a smooth heat exchange tube and the application of the five foregoing embodiments of the present invention;

[0036] Figure 14 It is a comparison diagram of the convective heat transfer coefficient and pressure drop of a smooth heat exchange tube and the application of the five foregoing embodiments of the present invention;

[0037] Figure 15 It is a flow velocity distribution diagram of a smooth heat exchange tube and the application of the five foregoing embodiments of the present invention.

[0038] Explanation of the reference numerals in the drawings:

[0039] 10. Turbulence generator;

[0040] 100. Turbulence plate; 101. Through hole;

[0041] 200. Turbulence generating assembly; 210. Flow guiding vane; 220. Eddy current vane; 221. Eddy current body; 222. Wing part;

[0042] 300. Flanging;

[0043] 20. Heat exchange tube;

[0044] The realization, functional features and advantages of the object of the present invention will be further described with reference to the embodiments and the accompanying drawings. Detailed implementation manners

[0045] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without making creative efforts shall fall within the protection scope of the present invention.

[0046] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) involved in the embodiments of the present invention, the directional indications are only used to explain the relative position relationship and movement conditions between components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0047] In addition, if descriptions such as "first" and "second" are involved in the embodiments of the present utility model, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning includes three parallel scenarios. Taking "A and / or B" as an example, it includes scenario A, or scenario B, or the scenario where both A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present utility model.

[0048] The present utility model provides a turbulence generator for installation inside a heat exchange tube, aiming to enhance the heat exchange efficiency of the heat exchange tube or reduce the noise of the heat exchanger. For the convenience of understanding and description, in the attached Figures 1 to 11 of the specification of the present utility model, the opening is indicated by the solid arrow.

[0049] Please refer to Figure 1 , in an embodiment of the present utility model, the turbulence generator 10 includes a turbulence plate 100 and a turbulence generating assembly 200. The turbulence generator 10 is for installation inside the heat exchange tube 20. The turbulence plate 100 extends along the length direction of the heat exchange tube 20, and the edge of the turbulence plate 100 generally abuts against the tube wall of the heat exchange tube 20 to support the turbulence plate 100.

[0050] Among them, the heat exchange tube 20 can be a circular tube or an elliptical tube. The turbulence plate 100 is adapted to the shape of the heat exchange tube 20. The heat exchange tube 20 is usually oblong or long elliptical. Therefore, the turbulence plate 100 is usually arranged in a long strip shape. The turbulence plate 100 has two opposite plate surfaces, and a flow passage is formed between the plate surface of the turbulence plate 100 and the tube wall of the heat exchange tube 20. In the embodiment where the heat exchange tube 20 is an elliptical tube, the turbulence plate 100 abuts against the tube wall at the position where the short axis of the elliptical tube is located, and a better strengthening effect can be achieved. The turbulence generating assembly 200 includes a guide vane 210 and a vortex vane 220. The specific structures of the guide vane 210 and the vortex vane 220 will be described below.

[0051] Generally, the guide vane 210 is arranged on the turbulence plate 100 and extends along the fluid direction inside the heat exchange tube 20; the guide vane 210 has two opposite ends. The first end of the guide vane 210 is connected to the turbulence plate 100, and the second end of the guide vane 210 inclines away from the turbulence plate 100.

[0052] The turbulator plate 100 is provided with flow guiding vanes 210. The flow guiding vanes 210 have a first end and a second end which are oppositely arranged along their length direction. Among them, the first end of the flow guiding vane 210 is connected to the turbulator plate 100, and the second end of the flow guiding vane 210 inclines away from the turbulator plate 100. That is, when the turbulator 10 is installed on the heat exchange tube 20, the second end of the flow guiding vane 210 inclines towards the tube wall of the heat exchange tube 20. In some embodiments, it can be understood that the first end of the flow guiding vane 210 is the connecting end and the second end is the free end. In this way, the flow guiding vane 210 can guide the fluid to the tube wall of the heat exchange tube 20, thereby disturbing the fluid at the tube wall of the heat exchange tube 20 and thinning the boundary layer at the tube wall.

[0053] The eddy current vane 220 is arranged at the second end of the flow guiding vane 210. The length direction of the eddy current vane 220 is arranged at an angle with the length direction of the flow guiding vane 210, and a wing part 222 protruding from the side surface of the flow guiding vane 210 is formed. Exemplarily, it can be understood that Figure 2 As shown, the flow guiding vane 210 and the eddy current vane 220 can be on one plane, and there is an angle between the length extension direction of the flow guiding vane 210 and the length extension direction of the eddy current vane 220, or it can be as Figure 1 、 Figure 3 、 Figure 4 and Figure 5 As shown, the flow guiding vane 210 and the eddy current vane 220 are not on one plane. Of course, there are many schemes for setting the angle between the eddy current vanes 220, and they will not be exemplified one by one here.

[0054] Furthermore, the eddy current vane 220 extends along the width direction of the turbulator plate 100. In this embodiment, the eddy current vane 220 extends along the width direction of the turbulator plate 100. It can be understood that an auxiliary plane perpendicular to the extension direction of the turbulator plate 100 is adopted. In the figure intercepted by the auxiliary plane on the eddy current vane 220, the extension direction of the eddy current vane 220 is substantially the same as the width direction of the turbulator plate 100, as Figure 2 shown.

[0055] Exemplarily, please refer to Figure 1 、 Figures 5 to 7 , the eddy current vane 220 includes an eddy current main body 221 and the wing part 222. The eddy current main body 221 is connected to the flow guiding vane 210, and the length direction of the eddy current main body 221 is arranged at an angle with the length direction of the flow guiding vane 210; the wing part 222 is arranged on the eddy current main body 221 and is located at both ends of the eddy current main body 221 along its length direction.

[0056] Among them, the wing part 222 is arranged on the eddy current main body 221, and the positional relationship between the wing part 222 and the eddy current main body 221 can be as Figure 2As shown, it can also be as Figure 1 As shown, the wing part 222 is inclined away from the turbulence plate 100 from its connection with the vortex body 221. In this way, in this embodiment, by inclining the wing part 222 away from the turbulence plate 100 from its connection with the vortex body 221, the longitudinal vortex formed by the vortex body 221 can be further mixed with the cold and hot fluids before and after, reducing the local high-temperature area, reducing the subcooled boiling gasification phenomenon, and playing a role in strengthening heat transfer and reducing the gasification noise.

[0057] Of course, in other embodiments, the wing part 222 can also be inclined towards the turbulence plate 100 from its connection with the vortex body 221.

[0058] Regarding the shape and structure of the guide vane 210 and the vortex vane 220, the shape of the guide vane 210 can be a regular shape such as a square sheet or an oval sheet, or other irregular shapes. Preferably, the guide vane 210 is arranged as a rectangular sheet. The shape of the vortex vane 220 can be arranged as a rectangular sheet, as Figure 2 shown, or the shape of the vortex vane 220 is as Figure 5 shown, and no further examples will be given here.

[0059] Since the R & D background of this application is for gas water heaters, the heat exchange tube 20 of the gas water heater is subjected to the scouring of high-temperature flue gas outside the tube, and the temperature in the area near the wall inside the heat exchange tube 20 will rise sharply, resulting in local gasification phenomena inside the heat exchange tube 20, affecting the stability of the flow rate inside the heat exchange tube 20, and the bubbles generated by gasification generate relatively large gasification noise during the rupture process, thus affecting the quality of the entire gas water heater.

[0060] In the technical solution of the present invention, as Figure 10 shown, when the heat exchange tube 20 exchanges heat, the sidewall guiding fluid formed by the guide vane 210 forms a high-speed scouring fluid area near the wall of the heat exchange tube 20. This high-speed scouring fluid area enables the generated bubbles to be confined near the wall of the heat exchange tube 20, forming a bubble channel from generation, growth to detachment; secondly, by setting it like this, a central fluid channel is formed below the guide vane 210 and the vortex vane 220, that is to say, a gas-liquid guiding separation channel is formed inside the heat exchange tube 20, so that the bubbles and the fluid do not interfere with each other. While strengthening the heat transfer inside the tube, the influence of the bubbles on the flow rate inside the heat exchange tube 20 is reduced; in addition, the bubbles in the high-speed scouring fluid channel can increase the disappearance speed of the bubbles and reduce the gasification noise.

[0061] In the technical solution of the present utility model, when the turbulence generator 10 is installed on the heat exchange tube 20, since the guide vane 210 is provided on the turbulence plate 100 and extends along the fluid direction in the heat exchange tube 20, and the first end of the guide vane 210 is connected to the turbulence plate 100, and the second end of the guide vane 210 is inclined away from the turbulence plate 100. Thus, when the fluid flows through the guide vane 210, the guide vane 210 deflects the incoming fluid to the vicinity of the wall of the heat exchange tube 20, promoting the mixing of the hot fluid near the wall and the cold fluid in the center, thereby enhancing heat transfer. Secondly, the eddy current vane 220 provided at the second end of the guide vane 210, since the length direction of the eddy current vane 220 is arranged at an angle with the length direction of the guide vane 210 and forms a wing portion 222 protruding from the side surface of the guide vane 210, the eddy current vane 220 can form a longitudinal eddy current in the cross section of the heat exchange tube 20, deflecting the hot fluid near the wall of the heat exchange tube 20 to the center of the heat exchange tube 20, thereby enhancing heat transfer.

[0062] In addition, the eddy current vane 220 can also confine part of the fluid near the wall of the heat exchange tube 20, maintaining a high-speed scouring of the vicinity of the wall of the heat exchange tube 20. The subcooled boiling bubbles formed in the thermal boundary layer near the wall of the heat exchange tube 20, under the action of the guide vane 210, form sidewall diversion. Under the action of the fluid that can scour at high speed, the bubbles can quickly break away from the wall of the heat exchange tube 20, inhibiting the growth of the bubbles and reducing the vaporization noise.

[0063] Please refer to Figure 7 , in order to enable the heat exchange tube 20 using the turbulence generator 10 to have an enhanced heat transfer effect while reducing the resistance of the fluid and reducing the vaporization noise generated by local high temperature. In an embodiment, the included angle between the guide vane 210 and the turbulence plate 100 is defined as ɑ, and it satisfies: 30° ≤ ɑ ≤ 75°.

[0064] Exemplarily, the values of α include but are not limited to 31°, 32°, 36°, 39°, 42°, 45°, 48°, 50°, 52°, 55°, 58°, 60°, 62°, 66°, 70°, 73° or 75°, etc.

[0065] In an embodiment, wing portions 222 are respectively provided at both ends of the eddy current body 221 along its length direction. In other embodiments, it may be that a wing portion 222 is provided at one end of the eddy current body 221 along its length direction. Among them, the number of wing portions 222 provided at each end is not limited. Considering that in a gas water heater, the diameter of the heat exchange tube 20 is relatively small, in the embodiment applied to a gas water heater, one wing portion 222 is respectively provided at both ends of the eddy current body 221 along its length direction, and it can also preferably confine the fluid deflected by the guide vane 210 to the vicinity of the wall of the heat exchange tube 20, maintaining a high-speed scouring of the vicinity of the wall of the heat exchange tube 20.

[0066] Preferably, in order to better confine the fluid deflected by the deflector 210 near the wall of the heat exchange tube 20 near the wall of the heat exchange tube 20 and maintain a high-speed scouring near the wall of the heat exchange tube 20, the supplementary angle of the angle between the eddy current body 221 and the wing portion 222 is defined as β, and it satisfies: 0° ≤ β ≤ 90°.

[0067] Among them, the β angle is as Figure 8 shown, and this angle can be understood as the angle at which the wing portion 222 is Figure 1 shown, and is inclined in the direction away from the side of the turbulence plate 100. Exemplarily, the values of β include but are not limited to 2°, 5°, 8°, 10°, 12°, 15°, 17°, 20°, 23°, 25°, 28°, 30°, 35°, 40°, 45°, 50°, 55°, 60°, 65°, 70°, 75°, 80°, 85° or 90°.

[0068] In one embodiment, in order to further improve the heat exchange uniformity of the heat exchange tube 20 and enhance the heat exchange efficiency, the number of the turbulence generating assemblies 200 is multiple, and the multiple turbulence generating assemblies 200 are arranged at intervals along the length direction of the turbulence plate 100; further, the turbulence plate 100 has opposite first and second sides, and the turbulence generating assemblies 200 are provided on both the first side and the second side; the turbulence generating assemblies 200 provided on the first side and the turbulence generating assemblies 200 provided on the second side are alternately arranged at intervals in the length direction of the turbulence plate 100. Thus, in this embodiment, since the turbulence generating assemblies 200 are arranged alternately up and down, the flow path of the fluid in the heat exchange tube 20 is extended, thereby enhancing heat transfer.

[0069] In one embodiment, the turbulence plate 100 is provided with a through hole 101 penetrating along its thickness direction between two adjacent turbulence generating assemblies 200. Thus, in this embodiment, the through hole 101 cooperates with the arrangement of the turbulence generating assemblies 200 arranged alternately up and down, so that the fluid forms a zigzag flow path flowing up and down, that is, Figure 11 the zigzag flow shown, further extending the flow path of the fluid in the heat exchange tube 20, thereby enhancing heat transfer.

[0070] Among them, the through hole 101 can be a rectangular hole or other polygonal holes. Preferably, the through hole 101 is a rectangular hole, and the rectangular hole is convenient for processing and reduces the difficulty of the production process. It should be noted that the rectangular hole includes a rectangular opening and a square opening.

[0071] In one embodiment, please refer to Figure 8 and Figure 9, the width of the turbulence plate 100 is W. In the width extension direction of the turbulence plate 100, the width of the through-hole 101 is D, and the following is satisfied: 0.80W ≤ D ≤ 0.95W.

[0072] In the fluid channel, the proportional relationship between the width D of the through-hole 101 and the width W of the turbulence plate 100 can affect the flow characteristics of the fluid. First of all, setting 0.80W ≤ D ≤ 0.95W can enable the fluid to have better flow velocity and pressure distribution when passing through the through-hole 101, avoiding poor flow or turbulence caused by too large or too small orifices. Secondly, the through-hole 101 is arranged in cooperation with the alternately arranged turbulence generating components 200 up and down, so that the fluid forms a zigzag flow path flowing up and down. If the through-hole 101 is too small, the flow area is insufficient, and the flow area of this zigzag flow path is small, resulting in poor heat transfer enhancement effect; while too large an orifice may cause the turbulence plate 100 to lose the necessary support in some application scenarios, affecting the strength and stability of the structure; therefore, the setting of this range helps to balance the hydrodynamic performance and the structural stability.

[0073] Among them, the turbulence plate 100 is adapted to the shape of the heat exchange tube 20. Generally speaking, the width of the turbulence plate 100 is related to the diameter of the heat exchange tube 20. Since the heat exchange tube 20 can be a circular tube or an elliptical tube, in the case of the heat exchange tube 20 being a circular tube, the width of the turbulence plate 100 is equal to the diameter of the heat exchange tube 20, and in the case of the heat exchange tube 20 being an elliptical tube, the width of the turbulence plate 100 is equal to the minor axis diameter of the heat exchange tube 20. The width of the through-hole 101 is D, which can be 0.80W, 0.82W, 0.85W, 0.88W, 0.90W, 0.92W or 0.95W.

[0074] Furthermore, in the length extension direction of the turbulence plate 100, the length of the through-hole 101 is L, and the following is satisfied: 1.0D ≤ L ≤ 2.5D. When the length of the through-hole 101 is 2.5D, a larger flow area can be provided, which helps the smooth flow of the fluid. The length of the through-hole 101 is greater than 1.0D to prevent the flow from being too narrow. Among them, the length L of the through-hole 101 can be 1.0D, 1.2D, 1.5D, 1.6D, 1.8D, 2.0D, 2.2D, 2.4D or 2.5D.

[0075] Exemplarily, taking the inner diameter of the heat exchange tube 20 as 20 mm as an example, the width W of the turbulence plate 100 is 20 mm, and the value of the width D of the through-hole 101 ranges from 16 mm to 19 mm. Then the value of the length L of the through-hole 101 ranges from 16 mm to 47.5 mm.

[0076] In one embodiment, please refer to Figure 8If the pitch between two adjacent through-holes 101 is P, then P≥L + 4.0 mm. It can be understood that if the pitch between two adjacent through-holes 101 is too large, the number of turbulent sound generators set will be too small, and insufficient flow rate can be directed to the tube wall of the heat exchange tube 20, resulting in a poor effect of enhanced heat transfer. This needs to be determined in combination with the diameter of the heat exchange tube 20 and will not be limited here. If the pitch between two adjacent through-holes 101 is too small, the number of turbulent sound generators set will be too large, thus increasing the resistance to the fluid.

[0077] Regarding the length direction, width direction, and thickness direction of the turbulent plate 100, reference can be made to Figures 7 to 9 , which is determined based on the fact that the turbulent plate 100 is arranged in a long plate shape.

[0078] To prove the superiority of the present invention, the present invention selects the smooth heat exchange tube 20 of the prior art and five schemes applying the technical concept of the present invention as cases for numerical simulation. Among them, the boundary conditions of the simulation cases are the same, and the overall dimensions are the same.

[0079] Using Ansys Fluent to perform numerical calculations on the flow and heat transfer performance of the smooth heat exchange tube 20 of the prior art and five schemes applying the technical concept of the present invention. The calculation conditions are as follows: the fluid is water, the inlet mass flow rate is 0.7 kg / s, the inlet temperature is 20 °C, the outlet pressure is 0, and the convective heat transfer coefficient of the wall is 1500 kW / m2·K; the steady state is adopted, and the Realizable k-ε model is used. The SIMPLE algorithm is used for pressure and velocity. For the momentum and energy equations, the central difference format is used for the diffusion term, and the second-order upwind difference format is used for the convective term. When the residuals of the continuity equation, momentum equation, and energy equation are all less than 10 -6 , it is considered that the numerical calculation converges. The specific experimental data are as Figures 12 to 15 shown.

[0080] Figure 12 is the temperature distribution diagram of the smooth heat exchange tube 20 and the five foregoing embodiments of the present invention, Figure 13 is the pressure distribution diagram of the smooth heat exchange tube 20 and the five foregoing embodiments of the present invention, Figure 14 is the comparison diagram of the convective heat transfer coefficient and pressure drop of the smooth heat exchange tube 20 and the five foregoing embodiments of the present invention; Figure 15 is the flow velocity distribution diagram of the smooth heat exchange tube 20 and the five foregoing embodiments of the present invention.

[0081] The above Figures 12 to 15 Among them, (a) corresponds to the smooth heat exchange tube 20; (b) corresponds to the first embodiment ( Figure 1 shown), where α = 35°, β = 30°; (c) corresponds to the second embodiment (Figure 2 as shown, where α = 35° and β = 0°; (d) corresponding to the third embodiment ( Figure 3 as shown, where α = 35° and β = 60°; (e) corresponding to the fourth embodiment ( Figure 4 as shown, where α = 45° and β = 60°; and (f) corresponding to the fifth embodiment ( Figure 5 as shown, where α = 45° and β = 45°).

[0082] Referring to Figures 12 to 15 , the numerical simulation results show that, compared with the smooth heat exchange tube 20, all five solutions applying the technical concept of the present utility model can effectively reduce the surface temperature of the heat exchange tube 20 and enhance the heat transfer inside the tube; from the perspective of the surface temperature distribution of the heat exchange tube 20, the heat exchange tube 20 in the first embodiment ( Figure 1 as shown) and the second embodiment ( Figure 2 as shown) has a lower surface temperature, indicating that these two structures have a stronger improvement in the heat exchange performance inside the heat exchange tube 20. From the perspective of the surface pressure distribution of the heat exchange tube 20, the pressure drop in the first embodiment ( Figure 1 as shown) is smaller than that in the second embodiment ( Figure 2 as shown). In addition, from the velocity distribution diagram, the side wall flow velocity in the first embodiment ( Figure 1 as shown) is faster, and the scouring velocity for the bubbles is greater. Considering temperature, pressure, and velocity comprehensively, the first embodiment ( Figure 1 as shown) has a stronger comprehensive heat transfer enhancement performance.

[0083] In an exemplary embodiment, the turbulence generator 10 includes a turbulence plate 100 and a plurality of turbulence generating components 200, which are arranged to extend along the length direction of the heat exchange tube 20; the plurality of turbulence generating components 200 are arranged on the turbulence plate 100, and the plurality of turbulence generating components 200 are arranged at intervals along the length direction of the turbulence plate 100. The turbulence plate 100 is provided with a through hole 101 penetrating in its thickness direction between two adjacent turbulence generating components 200; the turbulence generating component 200 includes a guide vane 210 and a vortex vane 220; the guide vane 210 is arranged on the turbulence plate 100 and extends along the fluid direction inside the heat exchange tube 20; the guide vane 210 has opposite ends, the first end of the guide vane 210 is connected to the turbulence plate 100, and the second end of the guide vane 210 is inclined in a direction away from the turbulence plate 100; the vortex vane 220 is arranged at the second end of the guide vane 210 and is arranged at an angle with the guide vane 210.

[0084] In an embodiment, when the turbulence generator 10 is installed on the heat exchange tube 20, fluid flows through the guide vane 210. The guide vane 210 guides the oncoming fluid to the vicinity of the wall of the heat exchange tube 20, promoting the mixing of the hot and cold fluids of the hot fluid near the tube wall and the cold fluid in the center, thereby enhancing heat transfer. The eddy current vane 220 provided on the guide vane 210 and arranged at an angle to the guide vane 210 confines the fluid guided to the vicinity of the wall of the heat exchange tube 20 near the wall of the heat exchange tube 20, maintaining a high-speed scouring of the vicinity of the wall of the heat exchange tube 20. The eddy current vane 220 can form a longitudinal eddy current structure on the cross-section of the heat exchange tube 20, guiding the hot fluid near the wall of the heat exchange tube 20 to the center of the heat exchange tube 20, thereby enhancing heat transfer. In addition, as Figure 10 shown, the subcooled boiling bubbles formed in the thermal boundary layer near the wall of the heat exchange tube 20, under the action of the guide vane 210, form a side-wall diversion. Under the action of the fluid that can scour at high speed, the bubbles can quickly break away from the wall of the heat exchange tube 20, inhibiting the growth of the bubbles and reducing the gasification noise.

[0085] As Figure 11 shown, the guide vane 210 divides the fluid into two flow directions. One is the flow direction of the side-wall diversion to the vicinity of the wall of the heat exchange tube 20 mentioned above. Due to the arrangement of the guide vanes 210 that alternate up and down, the fluid forms a zigzag flow path that flows up and down, that is, Figure 11 the zigzag flow shown, increasing the flow path of the fluid in the heat exchange tube 20, thereby enhancing heat transfer. The other is the fluid that is confined to flow in the center of the heat exchange tube 20 by the guide vane 210. The fluid in this flow direction can mix the hot and cold fluids before and after the longitudinal eddy current formed by the eddy current vane 220, reduce the local high temperature, reduce the subcooled boiling gasification phenomenon, and play a role in enhancing heat transfer. During the flow of the two main flow direction fluids formed under the action of the guide vane 210, they are continuously mixed, and at the same time, the turbulence intensity of the fluid in the heat exchange tube 20 is enhanced, thereby enhancing the heat transfer in the tube.

[0086] In one embodiment, the turbulence plate 100 is provided with flanges 300, and the two flanges 300 extend along the length direction of the heat exchange tube 20; in the width direction of the turbulence plate 100, the turbulence generating assembly 200 is arranged between the two flanges 300. In this way, the setting of the flanges 300 can facilitate the insertion of the turbulence generator 10 into the heat exchange tube 20, avoiding the cutting surface of the turbulence plate 100 from fitting with the tube wall of the heat exchange tube 20. The cutting surface of the turbulence plate 100 may have a relatively large roughness compared to its plate surface. The direct contact between the turbulence plate 100 and the tube wall may introduce thermal stress, resulting in mechanical stress concentration. In addition, when the turbulence plate 100 and the heat exchange tube 20 are connected by welding, the setting of the flanges 300 can increase the connection area (such as the welding area) between the turbulence plate 100 and the tube wall of the heat exchange tube 20, that is, the turbulence plate 100 can be better fixedly connected to the tube wall of the heat exchange tube 20 through the flanges 300. Of course, the flanges 300 cannot be too large, otherwise it will affect the heat transfer of the heat exchange tube 20.

[0087] The present utility model further provides a heat exchanger, which includes a heat exchange tube 20 and a turbulence generator 10. The specific structure of the turbulence generator 10 refers to the above embodiments. Since this heat exchanger adopts all the technical solutions of the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated herein one by one.

[0088] In this embodiment, the heat exchanger may have one heat exchange tube 20 or multiple heat exchange tubes 20. The multiple heat exchange tubes 20 may be arranged in parallel or in series, and at least one heat exchange tube 20 is installed with a turbulence generator 10. Preferably, all the heat exchange tubes 20 are installed with turbulence generators 10.

[0089] In one embodiment, the turbulence generator 10 may be fixedly connected to the tube wall of the heat exchange tube 20 by welding. In other embodiments, the turbulence generator 10 is also connected to the tube wall of the heat exchange tube 20 by interference fit.

[0090] The present utility model further provides a water heater, which includes a heat exchanger. The specific structure of the heat exchanger refers to the above embodiments. Since this water heater adopts all the technical solutions of the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated herein one by one.

[0091] In this embodiment, the water heater is usually a gas water heater. The water heater may further include an outer shell, an inner shell, a burner and a heat exchanger. The burner and the heat exchanger are arranged inside the inner shell to form a combustion chamber. The inner shell is arranged inside the outer shell. The burner is used to burn gas to generate high-temperature flue gas in the combustion chamber. The high-temperature flue gas flows towards the heat exchanger and exchanges heat with the water in the heat exchange tube 20 of the heat exchanger to heat the water flowing through the heat exchange tube 20.

[0092] The above is only an exemplary embodiment of the present utility model, and does not limit the patent scope of the present utility model. Any equivalent structural transformation made under the technical concept of the present utility model by using the content of the specification and drawings of the present utility model, or any direct / indirect application in other related technical fields is included in the patent protection scope of the present utility model.

Claims

1. A turbulence generator for installation inside a heat exchange tube, characterized in that, Comprising: A turbulence plate, extending along the length direction of the heat exchange tube; And A turbulence generating assembly, including a guide vane and a vortex vane. The guide vane is arranged on the turbulence plate and extends along the fluid direction in the heat exchange tube; the guide vane has opposite two ends, the first end of the guide vane is connected to the turbulence plate, and the second end of the guide vane is inclined in a direction away from the turbulence plate; the vortex vane is arranged at the second end of the guide vane, and the length direction of the vortex vane is arranged at an angle with the length direction of the guide vane, and a wing portion protruding from the side surface of the guide vane is formed.

2. The turbulence generator according to claim 1, characterized in that, The vortex vane includes a vortex main body and the wing portion. The vortex main body is connected to the guide vane, and the length direction of the vortex main body is arranged at an angle with the length direction of the guide vane; the wing portion is arranged on the vortex main body and is located at both ends of the vortex main body along its length direction.

3. The turbulence generator according to claim 2, wherein, The wing portion is inclined in a direction away from the turbulence plate from its connection portion with the vortex main body.

4. The turbulence generator according to claim 2, wherein Defining the supplementary angle between the vortex main body and the wing portion as β, then it satisfies: 0° ≤ β ≤ 90°.

5. The turbulence generator according to claim 1, wherein Defining the angle between the guide vane and the turbulence plate as ɑ, then it satisfies: 30° ≤ ɑ ≤ 75°.

6. The turbulator according to any one of claims 1 to 5, characterized in that, The vortex vane extends along the width direction of the turbulence plate.

7. The turbulator according to any one of claims 1 to 5, characterized in that The number of the turbulence generating assemblies is multiple, and the multiple turbulence generating assemblies are arranged at intervals along the length direction of the turbulence plate.

8. The turbulence generator according to claim 7, characterized in that, The turbulence plate has opposite first and second sides, and the turbulence generating assemblies are arranged on both the first side and the second side; The turbulence generating assembly arranged on the first side and the turbulence generating assembly arranged on the second side are alternately and spacedly distributed in the length direction of the turbulence plate.

9. The turbulator according to claim 8, characterized in that, The turbulence plate is provided with a through hole penetrating along its thickness direction between two adjacent turbulence generating assemblies.

10. The turbulator according to claim 9, characterized in that, The width of the turbulence plate is W. In the width extension direction of the turbulence plate, the width of the through hole is D, then it satisfies: 0.80W ≤ D ≤ 0.95W; in the length direction of the turbulence plate, the length of the through hole is L, then it satisfies: 1.0D ≤ L ≤ 2.5D.

11. The turbulator according to claim 10, characterized in that, The pitch between two adjacent through holes is P, then it satisfies: P ≧ L + 4.0 mm.

12. A heat exchanger, characterized in that, Comprising: A heat exchange tube; The turbulence generator according to any one of claims 1 to 11, arranged in the heat exchange tube.

13. A water heater, characterized in that, Including the heat exchanger according to claim 12.

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