Heat exchange tube and heat exchanger

Abstract

The invention relates to the technical field of heat exchangers and provides a heat exchange tube and a heat exchanger. The heat exchange pipe comprises a pipe body, a flow guide groove is formed in the outer wall face of the pipe body and extends in the circumferential direction of the pipe body, a gap exists between the two ends of the flow guide groove, and a protruding part is formed on the lower portion of the pipe body. The flow guide grooves are formed in the outer wall face of the heat exchange pipe, the wall thickness of the pipe body is reduced, and heat exchange of the heat exchange pipe is facilitated; the diversion trench is formed in the middle-upper part of the tube body, so that liquid drop gathering of a high-efficiency heat exchange area at the middle-upper part is accelerated, the heat exchange area is increased, the heat transfer advantage of the heat exchange tube is fully played, and the heat exchange efficiency of a single heat exchange tube is improved; by means of the characteristics that the steam flow is larger, the flow speed is larger, and condensate is easier to gather and separate, the problem that due to the fact that the steam flow is larger, the flow speed is larger, the liquid film thickness is increased and the condensation heat transfer coefficient is reduced at the bottom of a traditional heat exchange pipe, the contradiction between the exhaust steam condensation load and the condensation heat exchange capacity is caused is solved.

Description

Technical Field

[0001] This invention relates to the field of heat exchanger technology, and more particularly to a heat exchange tube and a heat exchanger. Background Technology

[0002] Heat exchangers are crucial equipment in power plant generator sets. Their core function is to supply the exhaust steam from the condenser unit, maintaining the continuous operation of the steam thermodynamic cycle. Shell-and-tube heat exchangers are the most commonly used type. These heat exchangers use the inner and outer surfaces of the heat exchange tubes as the heat transfer surfaces for cooling water and steam, achieving indirect heat exchange between high and low temperature media.

[0003] Traditional shell-and-tube condensers are horizontal bare tube heat exchangers, widely used due to their simple manufacturing process and reliable operation. In this type of condenser, film condensation is the main form of heat transfer on the steam side. The steam condensate forms a liquid film on the surface of the condenser tubes, which may prevent steam from effectively contacting the condenser surface in some areas.

[0004] For a single condenser heat exchanger tube, the condensate film exhibits a "thinner at the top and thicker at the bottom" distribution pattern across the tube's cross-section. The thick liquid film that accumulates at the bottom of the heat exchanger tube eventually overcomes viscous forces under its own gravity and tears into droplets (e.g., ...). Figure 1 (As shown). Therefore, such heat exchange tubes typically have a high condensation heat transfer coefficient at the top (referred to as the "high-efficiency heat transfer zone"), while the heat transfer coefficient near the bottom is extremely low (referred to as the "low-efficiency heat transfer zone"), and may even approach zero at the bottom due to the liquid film aggregation effect.

[0005] For heat exchanger tube bundles and heat exchangers composed of heat exchange tubes, the liquid film has a more significant impact on heat exchange. This is because, for tube bundles arranged according to a certain rule within a condenser, the liquid droplets condensed in the upper tube bundles fall along the central axis of the tubes to the next layer of heat exchanger tubes, causing liquid film accumulation in the upper part of the next layer of heat exchanger tubes as well (e.g., Figure 2 As shown in the diagram, the heat transfer coefficient of the entire heat exchanger tube decreases compared to the previous layer. More importantly, for some industrial heat exchangers where the condensation process is mostly in the laminar flow region, the specific operating requirements of the condenser increase with the increase in operating parameters and the increase in the exhaust steam volume of the steam-using equipment, which places higher demands on the condensation heat transfer of the heat exchanger. However, for the film condensation process of traditional heat exchangers, as the amount of condensed steam and the condensation heat load increase, the liquid film thickness increases, and the condensation heat transfer coefficient outside the tubes decreases. This results in insufficient cooling capacity of the entire heat exchanger under high load conditions, and the heat exchange capacity can only be improved by increasing the cooling water volume, which leads to a significant pump power loss.

[0006] To address the shortcomings of film condensation, researchers and designers have proposed droplet condensation technology. This involves surface modification of the outer surface of the heat exchanger tube or coating it with a hydrophobic coating to achieve a droplet-like distribution of condensate within the heat exchanger tube (e.g., ...). Figure 3(As shown). In droplet condensation, the condensate forms droplets and rolls off rapidly, unlike film condensation which forms a continuous liquid film covering the surface. This allows for timely removal of latent heat of condensation, reducing condensate accumulation and improving heat transfer efficiency. While droplet condensation can improve the heat transfer coefficient of a single tube compared to film condensation, the natural detachment of droplets via "sliding and gathering" and "gravity stripping" is inefficient. Therefore, droplets still cover the entire surface of the heat exchanger tubes, significantly reducing the effective heat transfer area. Furthermore, conventional droplet condensation heat exchanger tube bundles still suffer from the problem of droplets accumulating on the surface of the lower heat exchanger tubes, resulting in a low heat transfer coefficient at the bottom tubes and affecting the overall heat transfer efficiency of the tube bundle and the heat exchanger. More importantly, the external condensation heat transfer coefficient of the heat exchanger still decreases with increasing steam flow rate, failing to resolve the contradiction of declining condensation heat transfer coefficient under high exhaust flow and high load conditions. Summary of the Invention

[0007] This invention provides a heat exchange tube and a heat exchanger to solve the problem in the prior art where, as the steam flow rate and velocity increase, the liquid film thickness increases at the bottom of the heat exchange tube, but the condensation heat transfer coefficient decreases, thus leading to a contradiction between the exhaust steam condensation load and the condensation heat exchange capacity.

[0008] The present invention provides a heat exchange tube, comprising: a tube body, wherein a flow guide groove is provided on the outer wall surface of the tube body, the flow guide groove extends circumferentially along the tube body, and there is a gap between the two ends of the flow guide groove, and a protrusion is formed at the lower part of the tube body.

[0009] According to a heat exchange tube provided by the present invention, the protrusion is provided with a drainage groove, which extends along a direction perpendicular to the axis of the tube body.

[0010] According to a heat exchange tube provided by the present invention, the depth of the flow guide groove is less than 1 / 2 of the thickness of the tube body.

[0011] According to a heat exchange tube provided by the present invention, the angle formed between the two ends of the flow guide groove and the center of the tube body is α, where α ≤ 60°.

[0012] According to a heat exchange tube provided by the present invention, the guide groove is an arc-shaped guide groove.

[0013] According to a heat exchange tube provided by the present invention, there are multiple flow guide grooves, which are arranged at intervals or continuously along the extension direction of the tube body.

[0014] According to a heat exchange tube provided by the present invention, when the guide grooves are spaced apart along the extension direction of the tube body, the outer wall surface of the tube body between two adjacent guide grooves is coated with a hydrophobic element.

[0015] The present invention also provides a heat exchanger, including a shell and a plurality of heat exchange tubes as described in any of the above claims, wherein the plurality of heat exchange tubes are disposed within the shell, the extending direction of the heat exchange tubes is consistent with the extending direction of the shell, the two ends of the plurality of heat exchange tubes are aligned, and the guide grooves on the plurality of heat exchange tubes are aligned one by one.

[0016] According to a heat exchanger provided by the present invention, multiple rows of heat exchange tubes are spaced apart along a first direction of the shell, and adjacent rows of heat exchange tubes are staggered, wherein the first direction is consistent with the flow direction of condensate.

[0017] According to a heat exchanger provided by the present invention, the outer diameter of the heat exchange tube is d; the distance between the centers of two adjacent heat exchange tubes along the second direction of the shell is S, where S≥1.5d; the second direction is perpendicular to the first direction.

[0018] The heat exchange tube and heat exchanger provided by this invention reduce the wall thickness of the tube by setting a guide groove on the outer wall surface of the heat exchange tube, which is beneficial to heat exchange. The guide groove is set in the middle and upper part of the tube to accelerate the accumulation of liquid droplets in the "high-efficiency heat exchange zone" in the middle and upper part, increase the heat exchange area, give full play to the heat transfer advantage of the heat exchange tube, and improve the heat exchange efficiency of a single heat exchange tube. Steam is used to blow the condensate in the guide groove to the bottom of the groove to accumulate. The larger the steam flow rate, the stronger the steam blowing and carrying capacity, and the higher the flow velocity, the easier it is for the condensate to accumulate and detach. The condensate has a weaker impact on the heat transfer of the heat exchange tube. This solves the problem that in traditional heat exchange tubes, as the steam flow rate and flow velocity increase, the liquid film thickness increases and the condensation heat transfer coefficient decreases at the bottom of the heat exchange tube, which leads to a contradiction between the exhaust steam condensation load and the condensation heat exchange capacity. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in this invention 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 some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the dripping of condensate on the outer membrane of a heat exchanger tube in existing technology.

[0021] Figure 2 This diagram illustrates the effect of condensate dripping from the upper heat exchange tube on the liquid film on the surface of the lower heat exchange tube, using existing technology.

[0022] Figure 3 This is a schematic diagram of bead-like condensate dripping from the outer wall of a heat exchange tube in existing technology.

[0023] Figure 4This is a side view of the heat exchange tubes provided by the present invention, which are spaced apart along the extension direction of the tube body by means of the flow guide groove.

[0024] Figure 5 This invention provides Figure 4 Cross-sectional view at point AA.

[0025] Figure 6 This is a side view of the heat exchange tube provided by the present invention, in which the guide groove is continuously arranged along the extension direction of the tube body.

[0026] Figure 7 This is a side view of the heat exchanger provided by the present invention.

[0027] Figure 8 This is a front view of the heat exchanger provided by the present invention.

[0028] Figure 9 This is a schematic diagram of the arrangement of heat exchange tubes within a heat exchanger provided by the present invention.

[0029] Figure 10 This is a schematic diagram of the circumferential distribution of the film-like condensation heat transfer coefficient on the outer wall of the heat exchange tube provided by the present invention.

[0030] Figure 11 This is a schematic diagram of the condensation heat transfer coefficient of the outer wall of the heat exchange tube as a function of Reynolds number, provided by the present invention.

[0031] Figure label: 10. Heat exchange tube; 11. Tube body; 111. Flow guide groove; 112. Protrusion; 113. Flow channel; 20. Shell; 21. Cooling water inlet; 22. Cooling water outlet; 23. Steam inlet; 24. Condensate outlet. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0033] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0034] In the description of the embodiments of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of the present invention.

[0035] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0036] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0037] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. Additionally, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0038] The following is combined with Figures 4-11 The heat exchange tube 10 and heat exchanger of the present invention are described.

[0039] The heat exchange tube 10 provided in this embodiment of the invention includes: a tube body 11. A flow guide groove 111 is provided on the outer wall surface of the tube body 11. The flow guide groove 111 extends circumferentially along the tube body 11. There is a gap between the two ends of the flow guide groove 111. A protrusion 112 is formed at the lower part of the tube body 11.

[0040] The tube body 11 is a high thermal conductivity hollow tube made of drawn metal. The flow guide groove 111 extends circumferentially along the tube body 11, and there is a gap between the two ends of the flow guide groove 111, such as... Figure 4 As shown, when the pipe body 11 is placed horizontally, a protrusion 112 is formed at the lower part of the pipe body 11, wherein the protrusion 112 is the wall of the guide channel 111. Under the purging action of steam, the steam condensate in the guide channel 111 can quickly accumulate at the bottom of the guide channel 111 and flow towards the lower part of the pipe body 11 along the extension direction of the guide channel 111 until it flows to both ends of the guide channel 111 and separates along the junction of the guide channel 111 wall and the protrusion 112.

[0041] The heat exchange tube provided in this embodiment of the invention reduces the wall thickness of the tube body 11 by setting a guide groove 111 on the outer wall surface of the heat exchange tube 10, which is beneficial to heat exchange. The guide groove 111 is also set in the upper middle part of the tube body 11 to accelerate the accumulation of liquid droplets in the upper middle "high-efficiency heat exchange zone", increasing the heat exchange area and fully utilizing the heat transfer advantages of the heat exchange tube 10, thereby improving the heat exchange efficiency of a single heat exchange tube 10. Furthermore, under the action of steam, the condensate in the guide groove 111 can be blown to the bottom of the groove and accumulate. Therefore, the greater the steam flow rate and velocity, the stronger the steam blowing and carrying capacity, making it easier for the condensate to accumulate and detach, and the weaker the impact of the condensate on the heat transfer of the heat exchange tube 10. This solves the problem in traditional heat exchange tubes where, with increasing steam flow rate and velocity, the liquid film thickness increases at the bottom of the heat exchange tube 10, leading to a decrease in the condensation heat transfer coefficient and a contradiction between the exhaust steam condensation load and the condensation heat exchange capacity.

[0042] The structure of the flow guide trough 111 in this embodiment of the invention is not specifically limited, as long as it facilitates condensate aggregation. The backflow trough 111 has the characteristic of being high on both sides and low in the middle, resulting in good aggregation effect. In some embodiments of the invention, such as... Figure 4 and Figure 5 As shown, the guide channel 111 is an arc-shaped guide channel. The structural feature of the guide channel 111, which is high on both sides and low in the middle, can divide and collect the steam. Under the action of the steam, the condensate in the guide channel 111 can be blown to the bottom of the channel and collect. The arc-shaped guide channel not only utilizes the collection of steam condensate at the bottom of the arc-shaped guide channel, but also avoids stress concentration.

[0043] In some embodiments of the present invention, the protrusion 112 is provided with a drainage groove 113, which extends in a direction perpendicular to the axis of the tube body 11. For example... Figure 5 As shown, in this embodiment of the invention, by providing a drainage groove 113 in the protrusion 112, the condensate gathered in the drainage groove 111 can further gather along the drainage groove 113 and flow downward and detach faster, that is, prevent the condensate in the drainage groove 111 from being dispersed in the protrusion 112, thereby accelerating the detachment.

[0044] In one embodiment of the present invention, the drainage channel 113 is disposed at the junction of the guide channel 111 and the protrusion 112, which facilitates the entry of condensate in the guide channel 111 into the drainage channel 113. In some embodiments of the present invention, the surface of the protrusion 112 near the guide channel 111 is an inclined surface, wherein the wall of the drainage channel 113 is the lowest surface of the inclined surface, which helps the condensate in the guide channel 111 to flow into the drainage channel 113 and detach via the inclined surface.

[0045] The heat exchange tube 10 provided in this embodiment of the invention utilizes the flow trend of condensate in the guide channel 111, and simultaneously uses the steam scouring drag to collect the condensate at the bottom of the guide channel 111. The steam scouring shearing action and the convergence effect of the guide channel 111 on the condensate accelerate the condensate collection and its detachment through the guide channel 113. This embodiment of the invention accelerates condensate detachment through a "guide channel convergence + shear detachment" mode, avoiding the adverse effects of the liquid film on the condensation heat transfer of the heat exchange tube 10. Furthermore, the higher the steam flow rate and velocity, the stronger the steam blowing and carrying capacity, the easier it is for the condensate to collect and detach, and the weaker the impact of the condensate on the heat transfer of the heat exchange tube. This solves the problem that in traditional heat exchange tubes 10, the condensation heat transfer coefficient decreases with increasing steam flow rate and condensation load, leading to a contradiction between the exhaust steam condensation load and the condensation heat transfer capacity. This allows the condensation heat transfer coefficient to increase with the Reynolds number, such as... Figure 11 As shown, this improves the condensation heat transfer characteristics of the condenser under commonly used low flow rate conditions.

[0046] In some embodiments of the present invention, the depth of the guide channel 111 is uniform in the extending direction. The depth of the guide channel 111 is less than the thickness of the pipe body 11. In one embodiment, the depth of the guide channel 111 is less than 1 / 2 of the thickness of the pipe body 11. While ensuring the structural strength of the pipe body 11, this not only helps to collect condensate but also reduces the thickness of the pipe body 11, decreasing the thermal resistance of the local wall surface at the bottom of the guide channel 111. This makes the tendency of steam to condense and release heat in the guide channel 111 more obvious, accelerating the aggregation of condensate in the guide channel. In one embodiment, the depth of the guide channel 111 is 1 / 3 of the thickness of the pipe body 11. In another embodiment, the depth of the guide channel 111 is 1 / 4 of the thickness of the pipe body 11.

[0047] In some embodiments of the present invention, the angle formed by the two ends of the guide groove 111 and the center of the pipe body 11 is α, such as... Figure 5 As shown, α≤60°, that is, the angle between the two side walls of the protrusion 112 and the center of the tube 11 is less than or equal to 60°. This area is different from the inefficient heat exchange area of ​​the heat exchange tube 10 (such as...). Figure 10 Correspondingly, while concentrating the condensate and allowing it to flow away to form a beaded curtain, the space wastage in the effective heat exchange zone is reduced. In one embodiment, the angle α formed between the two ends of the guide channel 111 and the center of the tube body 11 can be 60°, 45°, 30°, 15°, 10°, etc.

[0048] In some embodiments of the present invention, there are multiple guide channels 111, and the multiple guide channels 111 are spaced apart along the extension direction of the pipe body 11, such as... Figure 4 As shown, increasing the effective heat exchange area improves heat exchange efficiency.

[0049] In some embodiments of the present invention, the outer wall surfaces of the tube bodies 11 of two adjacent guide channels 111 are coated with hydrophobic elements. Under the action of the hydrophobic elements, the condensate on the outer wall surfaces of the tube bodies 11 between the two adjacent guide channels 111 flows into the guide channels 111, reducing the condensate on the outer wall surfaces of the tube bodies 11, thereby improving the heat exchange efficiency. The hydrophobic elements in the embodiments of the present invention can be hydrophobic materials, or the surface can be modified to be hydrophobic.

[0050] In some embodiments of the present invention, there are multiple guide channels 111, and the multiple guide channels 111 are continuously arranged along the extension direction of the pipe body 11, such as... Figure 6 As shown, this can prevent condensate from accumulating on the outer wall of the pipe body 11 and help the condensate to collect in the guide groove 111.

[0051] This invention also provides a heat exchanger, including a housing 20 and a plurality of heat exchange tubes 10 as described in any of the above embodiments. The plurality of heat exchange tubes 10 are disposed inside the housing 20, the extension direction of the heat exchange tubes 10 is consistent with the extension direction of the housing 20, the two ends of the plurality of heat exchange tubes 10 are aligned, and the guide grooves 111 on the plurality of heat exchange tubes 10 are aligned one by one.

[0052] like Figure 7 As shown, the shell 20 is provided with a cooling water inlet 21 and a cooling water outlet 22, which are located at opposite ends of the shell 20's extension direction. Multiple heat exchange tubes 10 are disposed within the shell 20. Cooling water enters the heat exchange tubes 10 through the cooling water inlet 21, exchanges heat within the tubes, and then exits through the cooling water outlet 22. A steam inlet 23 is located at the top of the shell 20, and a condensate outlet 24 is located at the bottom. The axes of both the steam inlet 23 and the condensate outlet 24 are perpendicular to the axis of the shell 20, i.e., perpendicular to the heat exchange tubes 10. Under the shearing action of steam, the condensate on the outer wall of the heat exchange tubes 10 is accelerated to collect in the guide groove 111 and finally drawn out through the guide groove 113, and finally flows out through the condensate outlet 24.

[0053] Furthermore, the guide grooves 111 on the outer wall of the tube body 11 of the multiple heat exchange tubes 10 inside the shell 20 are in the same position. That is, when the two ends of the multiple heat exchange tubes 10 are aligned, the guide grooves 111 on the multiple heat exchange tubes 10 are aligned one by one. That is, the guide grooves 111 on any two heat exchange tubes 10 are aligned one by one. This is conducive to the condensate detaching and collecting into a beaded curtain. The condensate detached from the upper layer can fall directly into the lower guide groove 111, which accelerates the collection and detachment of the lower layer of condensate and improves the heat exchange efficiency.

[0054] The heat exchanger provided in this embodiment of the invention uses the guide channel 111 to guide the droplets, forming a "water curtain" that is parallel and spaced along the radial direction of the heat exchanger. The shear force of the high-speed steam flow on the droplets collected in the guide channel 111 is enhanced, which improves the condensation heat transfer performance of the heat exchanger under high-flow exhaust and high-load condensation conditions and reduces the power consumption burden of the cooling pump. At the same time, the droplets of the upper heat exchange tube 10 fall into the lower guide channel 111, accumulate in the guide channel 111 and quickly detach, avoiding dripping onto the top of the lower layer and causing the heat transfer performance of the lower heat exchange tube 10 to deteriorate, thereby improving the heat exchange efficiency and compactness of the entire heat exchanger.

[0055] In some embodiments of the present invention, such as Figure 8 As shown, multiple rows of heat exchange tubes 10 are spaced apart along the first direction of the shell 20. The heat exchange tubes 10 in adjacent rows are staggered to form a triangular arrangement, which can accelerate the detachment of liquid droplets on the heat exchange tubes 10. The first direction is consistent with the flow direction of condensate.

[0056] In this embodiment of the invention, the outer diameter of the heat exchange tube 10 is d. Along the second direction of the shell 20, the distance between the centers of two adjacent heat exchange tubes 10 is S, where S≥1.5d; the second direction is perpendicular to the first direction.

[0057] like Figure 8 and Figure 9 As shown, in this embodiment of the invention, the distance S between the centers of two adjacent heat exchange tubes 10 in the second direction is greater than or equal to 1.5 times the outer diameter of the heat exchange tube 10. That is, in the second direction, the distance between the outer diameters of two adjacent heat exchange tubes 10 is greater than 0.5 times the outer diameter of the heat exchange tube 10. This allows the condensate on the heat exchange tubes 10 to drip across layers, accelerating its detachment and improving the heat exchange effect. In addition, it also eliminates the problem of upper condensate dripping onto the outer wall of the lower heat exchange tube 10 between two adjacent layers, reducing the adverse effect of upper condensate on the heat transfer of the lower heat exchange tube 10. In one embodiment, the distance S between the centers of two adjacent heat exchange tubes 10 in the second direction is 1.5d, but it can also be 2d, 2.5d, etc.

[0058] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A heat exchange tube, characterized in that, include: The tube body has a flow guide groove on its outer wall surface. The flow guide groove extends circumferentially along the tube body and there is a gap between the two ends of the flow guide groove, forming a protrusion at the lower part of the tube body.

2. The heat exchange tube according to claim 1, characterized in that, The protrusion is provided with a drainage groove, which extends along the axis perpendicular to the tube body.

3. The heat exchange tube according to claim 1, characterized in that, The depth of the guide groove is less than 1 / 2 of the thickness of the pipe body.

4. The heat exchange tube according to claim 1, characterized in that, The angle between the two ends of the guide channel and the center of the pipe body is α, where α ≤ 60°.

5. The heat exchange tube according to claim 1, characterized in that, The guide channel is an arc-shaped guide channel.

6. The heat exchange tube according to any one of claims 1 to 5, characterized in that, There are multiple guide channels, which are spaced apart or continuous along the extension direction of the pipe body.

7. The heat exchange tube according to claim 6, characterized in that, When the guide channels are spaced apart along the extension direction of the pipe body, the outer wall surface of the pipe body between two adjacent guide channels is coated with a hydrophobic element.

8. A heat exchanger, characterized in that, The device includes a housing and a plurality of heat exchange tubes as described in any one of claims 1 to 7, wherein the plurality of heat exchange tubes are disposed within the housing, the extension direction of the heat exchange tubes is consistent with the extension direction of the housing, the two ends of the plurality of heat exchange tubes are aligned, and the guide grooves on the plurality of heat exchange tubes are aligned one by one.

9. The heat exchanger according to claim 8, characterized in that, Multiple rows of heat exchange tubes are spaced apart along a first direction of the shell, with adjacent rows of heat exchange tubes staggered. The first direction is consistent with the flow direction of the condensate.

10. The heat exchanger according to claim 9, characterized in that, The outer diameter of the heat exchange tube is d; the distance between the centers of two adjacent heat exchange tubes along the second direction of the shell is S, where S≥1.5d; the second direction is perpendicular to the first direction.

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