Heating device and water dispenser

Abstract

The utility model relates to heating device technical field discloses a kind of heating device and water dispenser, and heating device includes: heating pipe, is equipped with water inlet and water outlet;Support inner tube, is nested in heating pipe, and annular cross section heating flow channel is formed between support inner tube and heating pipe;Spoiler, along the axial extension of heating flow channel is set in heating flow channel;From the direction of water inlet to water outlet, the turbulence intensity of spoiler is in downward trend.Heat flow channel in the heating pipe is set spoiler, increase the residence time of fluid in heating flow channel, improve heat exchange effect, reduce the temperature difference between heating pipe and water;Water temperature is gradually increased in the direction from water inlet to water outlet of heating pipe, the turbulence intensity of spoiler is set to the mode of reducing from water inlet to the direction of water outlet, adapt to different heating needs of different heating section, ensure that water enters quickly and heats up, and reduce the generation of excessive bubble due to large temperature difference in high temperature section, to avoid bubble breakage noise.

Description

Technical Field

[0001] This utility model relates to the field of heating device technology, specifically to a heating device and a water dispenser. Background Technology

[0002] In existing water dispensers, the heating element is one of the core components, used to heat the water flowing through the pipes to meet various hot beverage needs. However, in the initial stage of water heating, the temperature of the heating element is much higher than the boiling point of water, and a large number of steam bubbles are rapidly generated on the surface of the heating element. Due to the large temperature difference between the steam bubbles and the water flowing inside the pipe, the steam bubbles burst immediately after their formation, producing noticeable heating noise, which seriously affects the user experience. In addition, traditional heating devices have low heat exchange efficiency, often requiring higher heating power to reach the target temperature, further exacerbating the noise problem. Utility Model Content

[0003] In view of this, the present invention provides a heating device and a water dispenser to solve the problem that the heating element temperature is much higher than the boiling point of water, resulting in a large number of steam bubbles, and the bursting of steam bubbles causes obvious heating noise.

[0004] In a first aspect, this utility model provides a heating device, comprising: The heating element is equipped with an inlet and an outlet. The inner support tube is nested inside the heating tube, and a heating flow channel with an annular cross-section is formed between the inner support tube and the heating tube; The turbulence diffuser is installed inside the heating channel, extending axially along the channel. The turbulence intensity of the diffuser decreases from the inlet to the outlet.

[0005] Beneficial effects: By installing a baffle in the heating channel of the heating tube, the residence time of the fluid in the heating channel is increased, the heat exchange effect is improved, and the temperature difference between the heating tube and the water is reduced. The water temperature gradually increases from the inlet to the outlet of the heating tube. The baffle intensity is set to decrease from the inlet to the outlet to adapt to the different heating needs of different heating sections, ensure rapid heating of the incoming water, and reduce the generation of excessive bubbles in the high-temperature section due to the large temperature difference, thereby avoiding bubble bursting noise.

[0006] The inlet side (low-temperature section) has high turbulence intensity and high fluid turbulence, which can quickly break the laminar boundary layer of the low-temperature fluid, allowing the cold water to fully contact the inner wall of the heating pipe and avoid local underheating caused by the low thermal conductivity of the cold water. On the outlet side (high-temperature section), the turbulence intensity is reduced and the fluid flow is relatively stable, which avoids the marginal reduction of heat exchange efficiency caused by excessive turbulence of the high-temperature fluid and also prevents local overheating caused by excessive local fluid velocity.

[0007] In one optional embodiment, the heating channel includes a low-temperature section, a medium-temperature section, and a high-temperature section, wherein the heights h1 of the low-temperature section, h2 of the medium-temperature section, and h3 of the high-temperature section satisfy the relationship h1 < h2 < h3. Beneficial effects: The heights of the low-temperature, medium-temperature, and high-temperature sections of the heating channel are precisely matched to the temperature gradient, enhancing the segmented heat exchange efficiency: the height h1 of the low-temperature section is the smallest, increasing the local flow velocity and turbulence intensity, and accelerating the heating of cold water; the height h2 of the medium-temperature section is in the middle, balancing heat exchange and resistance, and avoiding energy waste in the transition section; the height h3 of the high-temperature section is the largest, reducing the flow velocity and turbulence intensity, and adapting to the heat exchange requirements of the high-temperature section.

[0008] In one alternative implementation, the spoiler is a spring-type spoiler that extends in a spiral shape.

[0009] Beneficial effects: First, the turbulence intensity of the spring-type baffle can be precisely controlled through helical parameters (pitch, wire diameter, helix angle), resulting in better heat transfer stability. The helical extension of the baffle guides the fluid to form a composite flow of axial propulsion and radial rotation within the annular flow channel. The radial rotational motion breaks the laminar boundary layer of the fluid, allowing for more sufficient contact between the fluid and the inner wall of the heating tube and the outer wall of the supporting inner tube, avoiding the problem of insufficient heat absorption by the fluid near the wall surface. When the small number of bubbles generated in the high-temperature section flow with the rotating fluid, they will rise gently along the helical surface, preventing the bubbles from directly impacting the inner wall of the heating tube or the baffle element; at the same time, the helical structure can disperse the instantaneous impact force when bubbles burst, reducing the intensity of cavitation noise.

[0010] In one alternative implementation, the pitch of the spoiler corresponding to the low-temperature, medium-temperature, and high-temperature sections satisfies the relationship P1. <P2<P3。

[0011] Beneficial effects: The low-temperature section has a small pitch P1, resulting in the highest coil density of the turbulence generator. This leads to the highest shear force and rotational guidance frequency per unit length as the fluid flows through it, achieving peak turbulence intensity. Combined with the small heating channel height h1 in the low-temperature section, the high coil density further compresses the fluid flow space, forcing the cold water to form a violent axial and radial composite flow. This quickly breaks the laminar boundary layer of the low-temperature fluid, solving the problems of low thermal conductivity and slow heat absorption in cold water, achieving rapid heating in the low-temperature section, and reducing noise caused by temperature differences. At the same time, the high turbulence intensity prevents the formation of a low-temperature dead zone near the pipe wall, ensuring uniform heat exchange. In the intermediate temperature section, as the fluid temperature increases, the viscosity decreases, and the temperature difference with the heating tube narrows. The pitch P2 increases moderately, the coil density decreases, and the turbulence intensity transitions smoothly. This avoids the resistance accumulation caused by high turbulence in the low-temperature section while maintaining stable heat exchange through moderate turbulence intensity. Combined with the centrally located heating channel height h2 in the intermediate temperature section, the fluid velocity and rotation intensity are matched, preventing fluid impact and eddy current losses caused by sudden changes in turbulence intensity or channel height, achieving a smooth transition between efficient heat exchange and low-resistance flow. In the high-temperature section, the fluid approaches the target temperature, with the minimum temperature difference with the heating tube. Excessive turbulence no longer provides significant heat exchange gain but instead exacerbates bubble formation and resistance energy consumption. The maximum pitch P3 minimizes the coil density and turbulence intensity, resulting in stable fluid flow. Combined with the large channel height h3 in the high-temperature section, the fluid velocity further decreases. This reduces the collision frequency between the high-temperature fluid and the pipe wall and turbulence generator, suppressing excessive bubble formation and avoiding bubble burst noise and cavitation corrosion. Furthermore, it significantly reduces friction loss and decreases the power consumption of the circulating pump. In one alternative implementation, the pitch of the spoiler gradually increases from the inlet to the outlet.

[0012] Beneficial effects: As the water temperature continues to rise, the amount of heat required to reach the target temperature also decreases. To ensure the water temperature while avoiding steam problems caused by excessive heat exchange, the pitch of the turbulence diffuser gradually increases, the turbulence intensity gradually weakens, and the heat exchange gradually decreases with increasing temperature. In the high-temperature section, weak turbulence and low flow velocity reduce bubble formation, and the spiral structure guides the bubbles to exit smoothly, avoiding the sharp noise generated by concentrated bubble bursts. The gradual pitch change ensures smooth fluid flow, eliminating turbulent noise caused by sudden velocity changes or eddies, further reducing the overall noise of the heating device during operation.

[0013] In one optional embodiment, the heating channel includes a low-temperature section, a medium-temperature section, and a high-temperature section, wherein the cross-sectional area A1 of the low-temperature section, the cross-sectional area A2 of the medium-temperature section, and the cross-sectional area A3 of the high-temperature section satisfy the relationship A1 > A2 > A3.

[0014] Beneficial effects: Adapting to water temperature gradients, the low-temperature section (A1), with the largest cross-sectional area, enhances turbulence at low flow rates, achieving efficient heat absorption by cold water and reducing the temperature difference between the heating pipe and the water. The medium-temperature section (A2), with a moderate cross-sectional area, balances heat transfer and resistance through medium flow rates and moderate turbulence intensity, while smoothly connecting the low-temperature and high-temperature sections. The high-temperature section (A3), with the smallest cross-sectional area, suppresses bubbles and local overheating through high flow rates and weak turbulence. Simultaneously, the weak turbulence avoids a surge in turbulent resistance at high flow rates, balancing heat transfer efficiency and energy consumption. The annular flow channel itself has a uniform flow velocity distribution. Combined with the gradient design of A1>A2>A3, the fluid is fully mixed at low flow rates in the low-temperature section and rapidly advanced at high flow rates in the medium- and high-temperature sections, with no stagnant dead zones remaining throughout. This ensures that all fluids undergo effective heat exchange, avoiding uneven heating issues where some cold water is not fully heated and some high-temperature fluid is overheated. Simultaneously, the high flow rate in the high-temperature section can quickly remove heat from local hot spots, preventing abnormal increases in local pipe wall temperature and improving overall heat transfer uniformity.

[0015] In one alternative implementation, the cross-sectional area of ​​the heating channel gradually decreases from the inlet to the outlet.

[0016] Beneficial effects: The cross-sectional area gradually decreases, meaning it decreases continuously and smoothly. The flow velocity increases synchronously and continuously from the low-temperature section to the high-temperature section, resulting in gentle changes in fluid flow direction and velocity, avoiding the formation of impact eddies and generating only low-intensity continuous flow noise. The gradually decreasing structure of the annular flow channel allows the fluid to flow smoothly along the wall, with a uniform velocity field distribution within the channel and no local velocity peaks, further suppressing turbulent noise. The gradually decreasing heating channel, combined with the gradually increasing pitch design, allows the high-velocity fluid in the high-temperature section to be quickly discharged, avoiding local overheating and the generation of a large number of bubbles. The weak turbulence reduces fluid shearing, lowering the driving force for bubble formation and reducing the number of bubbles at the source. The continuously increasing flow velocity in the gradually decreasing channel avoids local overboiling caused by sudden changes in flow velocity in the high-temperature section, further suppressing bubble formation. The fluid flow within the gradually decreasing channel is stable; even if a small number of bubbles are generated, they will move smoothly with the continuously flowing fluid, avoiding aggregation and breakage.

[0017] In one alternative implementation, the heating channel forms a tapered structure with equal annular width.

[0018] Beneficial effects: The equal annular width design ensures a constant annular gap width from the low-temperature section to the high-temperature section, meaning the radial flow distance of the fluid remains unchanged. In the low-temperature section, the equal annular width, combined with strong turbulence, ensures thorough mixing of cold water in the radial direction, avoiding radial temperature gradient differences caused by excessive annular width. In the high-temperature section, the equal annular width prevents radial flow congestion caused by excessively narrow annular width, ensuring rapid and uniform discharge of high-temperature fluid, preventing local fluid stagnation and overboiling, and further suppressing bubble formation. Furthermore, conventional conical flow channels (where the annular width gradually decreases with the cross-sectional area) tend to form narrow annular dead zones in the high-temperature section, leading to poor fluid flow and localized overheating. The equal annular width conical flow channel, however, achieves a gradual reduction in cross-sectional area through simultaneous reduction in both the outer and inner diameters. This ensures uniform fluid flow in the radial direction, eliminating dead zones and ensuring all fluid fully contacts the heating tube and the heat exchange surface supporting the inner tube, improving overall heat exchange efficiency. The equal annular width conical structure reduces abrupt flow changes and enhances noise reduction.

[0019] In one optional embodiment, the heating device further includes a diversion cap disposed at the inlet and outlet, wherein a plurality of flow holes are evenly distributed around the periphery of the diversion cap.

[0020] Beneficial effects: To address the problem of uneven heat flux density on the heating wall caused by unreasonable water distribution structure design and uneven water distribution within the pipe in related technologies, multiple flow holes are evenly distributed around the periphery of the distribution cap. This ensures uniform fluid distribution along the circumference of the flow channel, resulting in a consistent circumferential flow velocity across each annular cross-section, preventing localized overheating and reducing the probability of bubble formation. Furthermore, the multiple flow holes increase the perforation area, reducing flow resistance.

[0021] In one alternative implementation, the shunt cap includes: The flow divider is located near the edge of the flow divider cap; the flow passage is opened in the flow divider; An extension is located at the top of the splitter cap; an installation step is formed at the junction of the extension and the splitter, and the extension is deeply inserted into the inner support tube and abuts against the end face of the inner support tube through the installation step.

[0022] Beneficial effects: End caps are prone to flipping during pipeline assembly. By using a method of deep insertion of the extension into the supporting inner tube, the probability of installation failure is reduced, assembly efficiency is improved, and after-sales issues and labor costs are decreased. The combination of an installation step and deep insertion of the extension creates a dual positioning effect of axial limiting and radial centering, resulting in high positioning accuracy. In one alternative implementation, the height of the shunt cap l The relationship between the inner diameter D of the heating tube and the equation is as follows: l ≥D / 2.

[0023] Beneficial effect: Diverter cap height l≥D / 2 means that the extension is inserted deep enough into the inner tube of the support, which enhances radial centering stability, facilitates the installation of the diverter cap, avoids the diverter cap from flipping during installation, improves assembly efficiency, and also avoids problems caused by the diverter cap flipping, such as failure and affecting normal use.

[0024] Secondly, this utility model also provides a water dispenser, including any of the heating devices mentioned above.

[0025] Beneficial effects: Since the water dispenser includes the heating device of this utility model, it has the same technical effects as the heating device, which will not be described in detail here. Attached Figure Description

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

[0027] Figure 1 This is an exploded structural diagram of a heating device according to an embodiment of the present invention; Figure 2 for Figure 1 The diagram shows a cross-sectional view of the heating device after the main support frame has been concealed. Figure 3 for Figure 2 Schematic diagram of the connection structure between the inner support tube, the spoiler and the splitter cap; Figure 4 This is a schematic diagram of the structure of a shunt end cap according to an embodiment of the present utility model; Figure 5 This is a schematic diagram of the connection structure between the shunt end cap, the supporting inner tube, and the heating tube in an embodiment of this utility model. Figure 6 This is a schematic diagram illustrating the relationship between the inner tube and the support tube during the installation of the end cap in related technologies. Figure 7 A comparison chart showing the noise levels of heating devices with and without spoilers.

[0028] Explanation of reference numerals in the attached figures: 1. Main support frame; 2. Sealing gasket; 3. Diverter cap; 31. Diversion section; 311. Flow orifice; 32. Extension section; 4. Support the inner tube; 5. Spoiler; 6. Heating element; 7. Thermostat; 8. Water inlet; 9. Water outlet; 10. Wearing a hat. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0030] In the description of this utility model, it should be noted that, unless otherwise stated, "a plurality of" means two or more; the terms "upper," "lower," "left," "right," "inner," "outer," "front end," "rear end," "head," "tail," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model 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, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," "third," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0031] In the description of this utility model, it should also be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" 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 this utility model according to the specific circumstances.

[0032] The following is combined Figures 1 to 6 The following describes embodiments of the present invention.

[0033] According to embodiments of the present invention, on the one hand, such as Figure 1 As shown, a heating device is provided, comprising: The heating element 6 is equipped with a water inlet 8 and a water outlet 9; The inner support tube 4 is nested inside the heating tube 6, and a heating flow channel with an annular cross-section is formed between the inner support tube 4 and the heating tube 6. The spoiler 5 is disposed in the heating flow channel, extending along the axial direction of the heating flow channel; in the direction from the water inlet 8 to the water outlet 9, the turbulence intensity of the spoiler 5 shows a downward trend.

[0034] The spoiler 5 is arranged in the heating flow channel of the heating pipe 6, which increases the residence time of the fluid in the heating flow channel, improves the heat exchange effect, and reduces the temperature difference between the heating pipe 6 and water; the water temperature gradually rises in the direction from the water inlet 8 to the water outlet 9 of the heating pipe 6, and the turbulence intensity of the spoiler 5 is set to decrease in the direction from the water inlet 8 to the water outlet 9, so as to adapt to different heating requirements of different heating sections, ensure the rapid temperature rise of inlet water, reduce the generation of excessive bubbles caused by large temperature difference in the high-temperature section, and further avoid the noise caused by bubble rupture.

[0035] The turbulence intensity on the water inlet 8 side (low-temperature section) is high, and the fluid has a high degree of turbulence, which can quickly break the laminar boundary layer of the low-temperature fluid, make the cold water fully contact with the inner wall of the heating pipe 6, and avoid local underheating caused by the low thermal conductivity of cold water; while the turbulence intensity on the water outlet 9 side (high-temperature section) is reduced, and the fluid flows relatively smoothly, which not only avoids the marginal decline of heat exchange efficiency caused by excessive turbulence of high-temperature fluid, but also prevents local overheating caused by excessive local fluid flow rate.

[0036] In some embodiments, the heating flow channel includes a low-temperature section, a medium-temperature section and a high-temperature section, and the height of the low-temperature section, the height h2 of the medium-temperature section and the height h3 of the high-temperature section satisfy the relational expression <h2<h3. The heights of the low-temperature section, medium-temperature section and high-temperature section of the heating flow channel precisely match the temperature gradient to enhance the segmented heat exchange efficiency: the height of the low-temperature section is the smallest, which increases the local flow rate and turbulence intensity to accelerate the temperature rise of cold water; the height h2 of the medium-temperature section is moderate, which balances heat exchange and resistance to avoid energy efficiency waste in the transition section; the height h3 of the high-temperature section is the largest, which reduces the flow rate and turbulence intensity to adapt to the heat exchange requirements of the high-temperature section.

[0037] In some embodiments, the spoiler 5 is a spring-type spoiler 5, which extends in a spiral shape.

[0038] First, the turbulence intensity of the spring-type spoiler 5 can be precisely adjusted and controlled through spiral parameters (pitch, wire diameter, spiral lift angle), so that the heat exchange stability is better. The spirally extending spoiler 5 will guide the fluid to form a composite flow of axial propulsion and radial rotation in the annular flow channel. The radial rotational motion can break the laminar boundary layer of the fluid, make the fluid fully contact with the inner wall of the heating pipe 6 and the outer wall of the supporting inner pipe 4, and avoid the problem of insufficient heat absorption of the fluid near the wall surface. A small number of bubbles generated in the high-temperature section will rise gently along the spiral surface when flowing with the rotating fluid, preventing the bubbles from directly hitting the inner wall of the heating pipe 6 or the spoiler element; at the same time, the spiral structure can disperse the instantaneous impact force when the bubbles rupture, reducing the intensity of cavitation noise.

[0039] Of course, in some other embodiments, the baffle 5 can also be a blade baffle 5. The radial blades of the blade baffle 5 are arranged at intervals along the axial direction of the heating pipe 6. The blades can directly cut the fluid to form multiple rotating vortices, which can more thoroughly destroy the boundary layer, improve the heat transfer coefficient, reduce the temperature difference between the fluid and the heating pipe 6, and reduce the generation of bubbles.

[0040] In other embodiments, the baffle 5 may also be a finned baffle 5, which improves heat exchange efficiency by increasing the heat exchange area. Furthermore, guide holes, grooves, or corrugated structures may be formed on the surface of the fins to further break the fluid adhesion effect.

[0041] In other embodiments, the baffle 5 may also be a perforated plate, a wire mesh, or a honeycomb structure. The perforated structure has a small obstruction effect on the fluid and a low pressure drop.

[0042] Of course, in some other embodiments, a combined turbulence diffuser 5 can also be used, such as a spiral-shaped type with blades, in which a set of radial blades is set at intervals on the basis of the spiral turbulence zone to enhance the turbulence intensity. Another example is a finned type with a perforated plate, in which a perforated plate is connected to the end of the axial fins, which increases the heat exchange area and generates micro-turbulence through the perforated plate.

[0043] In some embodiments, such as Figure 3 As shown, the pitch of the spoiler 5 corresponding to the low temperature section, medium temperature section, and high temperature section satisfies the relationship P1. <P2<P3。

[0044] The low-temperature section has a small pitch, and the coil density of the turbulence diffuser 5 is the largest. When the fluid flows through it, the shearing force and rotational guidance frequency per unit length are the highest, and the turbulence intensity reaches its peak. Combined with the small heating channel height h1 in the low-temperature section, the high coil density can further compress the fluid flow space, forcing the cold water to form a violent axial and radial composite flow, quickly breaking the laminar boundary layer of the low-temperature fluid, solving the problem of low thermal conductivity and slow heat absorption of cold water, achieving the purpose of rapid heating in the low-temperature section, and reducing the noise caused by temperature difference. At the same time, the high turbulence intensity can prevent the formation of a low-temperature dead zone near the pipe wall, ensuring heat exchange uniformity. In the intermediate temperature section, the fluid temperature increases, the viscosity decreases, and the temperature difference with the heating tube 6 narrows. The pitch P2 increases moderately, the coil density decreases, and the turbulence intensity transitions smoothly. This avoids the resistance accumulation caused by high turbulence in the low-temperature section while maintaining stable heat exchange through moderate turbulence intensity. Combined with the centrally located heating channel height h2 in the intermediate temperature section, the fluid velocity and rotation intensity are matched, preventing fluid impact and eddy current losses caused by sudden changes in turbulence intensity or channel height, achieving a smooth transition between efficient heat exchange and low-resistance flow. In the high-temperature section, the fluid approaches the target temperature, and the temperature difference with the heating tube 6 is minimal. Excessive turbulence no longer provides significant heat exchange gain but instead exacerbates bubble formation and resistance energy consumption. The maximum pitch P3 minimizes the coil density and turbulence intensity, resulting in stable fluid flow. Combined with the large channel height h3 in the high-temperature section, the fluid velocity is further reduced. This reduces the collision frequency between the high-temperature fluid and the tube wall and turbulence generator 5, suppressing excessive bubble formation and avoiding bubble burst noise and cavitation corrosion. Furthermore, it significantly reduces friction loss and decreases the power consumption of the circulating pump. In some embodiments, the pitch of the baffle 5 gradually increases from the inlet 8 to the outlet 9.

[0045] As the water temperature continues to rise, the amount of heat required to reach the target temperature decreases. To ensure the water temperature while avoiding steam problems caused by excessive heat exchange, the pitch of the turbulence diffuser 5 gradually increases, the turbulence intensity gradually weakens, and the heat exchange gradually decreases with increasing temperature. In the high-temperature section, weak turbulence and low flow velocity reduce bubble formation, and the spiral structure guides the bubbles to exit smoothly, avoiding the sharp noise generated by concentrated bubble bursts. The gradual pitch change ensures smooth fluid flow, eliminating turbulent noise caused by sudden velocity changes or eddies, further reducing the overall noise of the heating device during operation.

[0046] In some embodiments, the heating channel includes a low-temperature section, a medium-temperature section, and a high-temperature section, wherein the cross-sectional area A1 of the low-temperature section, the cross-sectional area A2 of the medium-temperature section, and the cross-sectional area A3 of the high-temperature section satisfy the relationship A1 > A2 > A3.

[0047] Adapting to the water temperature gradient, the low-temperature section (A1), with the largest cross-sectional area, enhances turbulence with low flow velocity to achieve efficient heat absorption by cold water and reduce the temperature difference between heating pipe 6 and the water. The medium-temperature section (A2), with a medium flow velocity and medium turbulence intensity, balances heat transfer and resistance while smoothly connecting the low-temperature and high-temperature sections. The high-temperature section (A3), with the smallest cross-sectional area, suppresses bubbles and local overheating with high flow velocity and weak turbulence. At the same time, the weak turbulence avoids a surge in turbulent resistance at high flow velocity, balancing heat transfer efficiency and energy consumption. The annular flow channel itself has a uniform flow velocity distribution. Combined with the gradient design of A1>A2>A3, the fluid is fully mixed at low flow velocity in the low-temperature section and rapidly advanced at high flow velocity in the medium- and high-temperature sections. There are no stagnant dead zones throughout the entire process, ensuring that all fluids can undergo effective heat exchange and avoiding uneven heating problems such as some cold water not being fully heated and some high-temperature fluids being overheated. At the same time, the high flow velocity in the high-temperature section can quickly remove heat from local hot spots, preventing abnormal local temperature rises in the pipe wall and improving overall heat transfer uniformity.

[0048] In some embodiments, the cross-sectional area of ​​the heating channel gradually decreases from the inlet 8 to the outlet 9.

[0049] The cross-sectional area gradually decreases, meaning it decreases smoothly and continuously. The flow velocity increases synchronously and continuously from the low-temperature section to the high-temperature section, resulting in a gradual change in fluid flow direction and velocity. This avoids the formation of impact eddies and only generates low-intensity continuous flow noise. The gradually decreasing structure of the annular flow channel ensures smooth fluid flow along the wall, with a uniform velocity field distribution within the channel and no local velocity peaks, further suppressing turbulent noise. The gradually decreasing heating channel, combined with the gradually increasing pitch design, allows for rapid fluid discharge at high velocities in the high-temperature section, preventing local overheating and the generation of numerous bubbles. Weak turbulence reduces fluid shearing, lowering the driving force for bubble formation and reducing the number of bubbles at the source. The continuously increasing velocity in the gradually decreasing channel prevents local overboiling caused by sudden velocity changes in the high-temperature section, further suppressing bubble formation. The fluid flow within the gradually decreasing channel is stable; even if a small number of bubbles are generated, they will move smoothly with the continuously flowing fluid, preventing aggregation and breakage.

[0050] In some embodiments, the heating channel forms a tapered structure with equal annular width.

[0051] The constant annular width design ensures a constant annular gap width from the low-temperature section to the high-temperature section, meaning the radial flow distance of the fluid remains unchanged. In the low-temperature section, the constant annular width, combined with strong turbulence, ensures thorough mixing of cold water in the radial direction, avoiding radial temperature gradient differences caused by excessive annular width. In the high-temperature section, the constant annular width prevents radial flow congestion caused by excessively narrow annular width, ensuring rapid and uniform discharge of high-temperature fluid, preventing local fluid stagnation and overboiling, and further suppressing bubble formation. Furthermore, conventional conical flow channels (where the annular width gradually decreases with the cross-sectional area) tend to form narrow annular dead zones in the high-temperature section, leading to poor fluid flow and localized overheating. The constant annular width conical flow channel, however, achieves a gradual reduction in cross-sectional area through simultaneous reduction in both the outer and inner diameters. This ensures uniform fluid flow in the radial direction, eliminating dead zones and ensuring all fluid fully contacts the heat exchange surfaces of the heating tube 6 and the supporting inner tube 4, improving overall heat exchange efficiency. The constant annular width conical structure reduces abrupt flow changes and enhances noise reduction.

[0052] In some embodiments, the heating device further includes a diversion cap 3 disposed at the inlet 8 and the outlet 9, wherein a plurality of flow holes 311 are evenly distributed around the periphery of the diversion cap 3.

[0053] To address the issue of uneven heat flux density on the heating wall caused by an unreasonable water distribution structure design and uneven water distribution within the pipe in related technologies, multiple flow holes 311 are evenly distributed around the periphery of the distribution end cap 3. This ensures uniform fluid distribution along the circumference of the flow channel, resulting in a consistent circumferential flow velocity across each annular section. This avoids localized overheating and reduces the probability of bubble formation. Furthermore, the multiple flow holes 311 increase the water passage area and reduce flow resistance.

[0054] In some embodiments, the shunt cap 3 includes: The flow divider 31 is located near the edge of the flow divider cap 3; the flow passage 311 is formed in the flow divider 31; The extension 32 is located at the top of the diversion cap 3; an installation step is formed at the junction of the extension 32 and the diversion part 31, and the extension 32 is deeply inserted into the inner support tube 4 and abuts against the end face of the inner support tube 4 through the installation step.

[0055] To address the issue of the shunt cap 3 easily flipping during pipeline assembly, an extension 32 is deeply inserted into the supporting inner tube 4. This reduces the likelihood of installation failures, improves assembly efficiency, and minimizes after-sales issues and labor costs. The combination of the installation step and the deep insertion of the extension 32 creates a dual positioning effect of axial limiting and radial centering, resulting in high positioning accuracy. In some embodiments, the height of the shunt cap 3 l The relationship between the inner diameter D of heating tube 6 and the equation is: l ≥D / 2.

[0056] The height of the shunt end cap 3 l≥D / 2, which means the extension part 32 is inserted into the inner support tube 4 with a sufficient depth, enhancing the radial centering stability, facilitating the installation of the split end cap 3, preventing the split end cap 3 from turning over during installation, improving the assembly efficiency, and avoiding the problems of failures and impact on normal use caused by the turning over of the split end cap 3.

[0057] As shown in Figure 1 and Figure 2 , the heating device is composed of a main body bracket 1, a sealing gasket 2, a split end cap 3, an inner support tube 4, a turbulator 5, a heating tube 6 and a temperature controller 7. Normal-temperature inlet water enters the heating tube from the bottom inlet, passes through the water diversion holes of the split end cap 3 and enters the annular cross-section heating flow channel formed by the nesting of the inner support tube 4 and the heating tube. The heating tube 6 generates heat to heat the flowing water in the flow channel. After reaching the outlet water temperature, the water flows out through the holes of the split end cap 3 at the water outlet end; the temperature controller 7 controls the outlet water temperature within the target value range to prevent safety problems caused by steam injection due to overheating.

[0058] In order to improve the heat exchange efficiency between the flowing water and the heating wall surface, a spiral turbulator 5 is added in the flow channel. The turbulator 5 can extend the residence time of the inlet water in the heating tube 6 path and increase the turbulence intensity, accelerate the temperature rise rate of the inlet water, shorten the length of the low-temperature water end in the heating tube 6 path, minimize the temperature difference between steam bubbles and the flowing water, thereby reducing the breaking probability of steam bubbles and lowering the heating noise. The outer wall of the heating tube 6 is attached with a heating film. As the flowing water travels deeper in the heating tube 6, it is gradually heated up, so there are a low-temperature water section at the water inlet side and a high-temperature water section at the water outlet side. Improving turbulence to enhance heat exchange efficiency allows the water in the water inlet section to heat up rapidly, thus shortening the length of the low-temperature water section.

[0059] As shown in Figure 3 , since the low-temperature water section in the heating tube 6 path is shortened and the high-temperature water section is lengthened after the turbulence structure is added to enhance heat exchange, the high-temperature water is very prone to generating excessive superheated steam, causing steam injection problems; frequent operation of the temperature limiter for control will cause water cutoff problems. In order to reduce steam generation, lower the operation frequency of the temperature limiter, and ensure continuous and uniform flowing water, the turbulator 5 adopts a variable pitch design; the entire turbulent flow pipeline is divided into a low-temperature section, a medium-temperature section and a high-temperature section. The low-temperature section has a small pitch, the turbulator 5 has a large number of winding turns, the turbulence is more sufficient, the temperature rise is fast, the low-temperature section is shortened as much as possible to reduce heating noise; as the water temperature continues to rise, the heat required to reach the target temperature also continues to decrease. In order to maintain the water temperature while avoiding steam problems caused by excessive heat exchange, the pitch of the turbulator 5 gradually increases, the turbulence intensity gradually weakens, and the heat exchange amount gradually decreases with the temperature rise, that is, P1<P2<P3 and h1<h2<h3 must be satisfied.

[0060] In some embodiments, the pitch of the turbulator 5 is a fixed value, P=7mm, the wire diameter d of the turbulator 5 is 2mm, and the cross-sectional width w of the heating flow channel is 2.2mm.

[0061] Furthermore, the pitch can be designed to be infinitely variable, and the baffle 5 is not segmented. From the water inlet to the water outlet, the pitch gradually increases, making the water temperature rise transition more continuous. When the water flow decreases, the accumulated heat will cause the water to produce excessive steam. If the temperature rises too quickly, splashing problems can easily occur at the water outlet 9. This utility model provides continuous heating, and the outlet temperature fluctuates less due to changes in water flow, thus preventing splashing.

[0062] Furthermore, the water pipe can adopt a tapered, uniform thickness, variable cross-section design. The inlet water temperature rise section has a large ring cross-section diameter, which slows down the flow velocity and increases the water residence time, rapidly increasing the water temperature within the short pipe length range at the inlet end. The flow channel area of ​​the high-temperature section at the rear end gradually decreases, accelerating the outflow of high-temperature water and avoiding overheating and excessive steam generation.

[0063] like Figures 3-5 As shown, the diversion caps 3 at the inlet 8 and outlet 9 are designed with height and side flow holes 311. On the one hand, this can solve the problem of easy flipping of the diversion caps 3 during pipeline assembly, reduce the failure rate, improve assembly efficiency, and reduce after-sales risks and labor costs.

[0064] For the related technology, see the cap flipping state. Figure 6 On the assembly line, the heating tube needs to be installed on the main support first, and one side needs to be fixed to form a deep cylinder structure with one end open. The assembly position of the end cap 10 at the bottom of the deep cylinder is not visible and needs to be installed manually blindly. The metal end cap 10 is pushed into the installation position by the heating inner tube. Because the height of the end cap 10 and the circumference diameter of the middle protrusion are too small, the freedom of movement is too large, and the inner and outer tubes cannot form an effective constraint. During the installation process, the end cap 10 will deflect and get stuck in the corresponding position. Because the heating tube has a rubber gasket sealing structure, even if the deflection eats up part of the assembly size, the elastic deformation margin of the rubber parts can still allow the entire heating device to be assembled. This will affect the normal use of the heating device.

[0065] The installation of the shunt cap 3 of this utility model is as follows: Figure 5 As shown, the height of the diversion cap 3 is increased, and the flow hole 311 is punched on the inclined side wall of the metal diversion cap 3 to form a side water outlet structure. The circumferential diameter of the protrusion in the middle of the diversion cap 3 is not much different from the diameter of the heating inner tube. During the installation of the tube, it can form an effective constraint and is not easy to fall off or flip over. The two arrows in the figure show the constraint of the heating tube 6 and the constraint of the supporting inner tube 4, respectively. The height of the diversion cap 3 is much greater than the inner diameter of the heating tube 6. Even if there is a slight deflection, it will be constrained by the tube wall and return to its position.

[0066] To ensure that the shunt cap 3 is not easily overturned during assembly within the pipeline, the height of the shunt cap 3 must be at least greater than the inner diameter of the heating tube 6, i.e. l≥D / 2; On the other hand, the diameter Φ of the side flow hole 311 is not limited by the width of the flow cross-section of the heating tube 6, and the flow area can be made very large, effectively reducing flow resistance loss. In this embodiment, the height of the diversion end cap 3 l =11mm, the inner diameter D of the heating tube 6 is 18.4mm, and the diameter Φ of the flow hole 311 on the flow divider cap 3 is 2.3mm.

[0067] like Figure 7 As shown, compared with the heating device without a spoiler, the heating device with spoiler 5 has a noise reduction of more than 7dB in each heating function, which is a significant effect.

[0068] According to an embodiment of the present invention, another aspect is provided: a water dispenser including a heating device.

[0069] Since the water dispenser includes the heating device of this utility model, it has the same technical effect as the heating device, which will not be described in detail here.

[0070] Although embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations all fall within the scope defined by this application.

Claims

1. A heating device, characterized in that, include: The heating element (6) is provided with an inlet (8) and an outlet (9); A supporting inner tube (4) is nested inside the heating tube (6), and a heating flow channel with an annular cross-section is formed between the supporting inner tube (4) and the heating tube (6); A flow disruptor (5) is provided in the heating channel, extending along the axial direction of the heating channel; the flow disruption intensity of the flow disruptor (5) decreases from the inlet (8) to the outlet (9).

2. The heating device according to claim 1, characterized in that, The heating channel includes a low-temperature section, a medium-temperature section, and a high-temperature section. The heights h1 of the low-temperature section, h2 of the medium-temperature section, and h3 of the high-temperature section satisfy the relationship h1 < h2 < h3.

3. The heating device according to claim 2, characterized in that, The spoiler (5) is a spring-type spoiler (5) that extends in a spiral shape.

4. The heating device according to claim 3, characterized in that, The pitch of the spoiler (5) corresponding to the low temperature section, the medium temperature section, and the high temperature section satisfies the relationship P1. <P2<P3。 5. The heating device according to claim 3, characterized in that, The pitch of the turbulence diffuser (5) gradually increases from the inlet (8) to the outlet (9).

6. The heating device according to claim 1, characterized in that, The heating channel includes a low-temperature section, a medium-temperature section, and a high-temperature section. The cross-sectional area A1 of the low-temperature section, the cross-sectional area A2 of the medium-temperature section, and the cross-sectional area A3 of the high-temperature section satisfy the relationship A1 > A2 > A3.

7. The heating device according to claim 6, characterized in that, The cross-sectional area of ​​the heating channel gradually decreases from the inlet (8) to the outlet (9).

8. The heating device according to claim 7, characterized in that, The heating channel forms a conical structure with equal annular width.

9. The heating device according to any one of claims 1 to 8, characterized in that, The heating device also includes a diversion cap (3) disposed at the inlet (8) and the outlet (9), and the diversion cap (3) has a plurality of flow holes (311) evenly distributed around its periphery.

10. The heating device according to claim 9, characterized in that, The shunt cap (3) includes: The flow divider (31) is located near the edge of the flow divider cap (3); the flow passage (311) is opened in the flow divider (31). An extension (32) is located at the top of the diversion cap (3); an installation step is formed at the junction of the extension (32) and the diversion part (31); the extension (32) is deeply inserted into the inner support tube (4) and abuts against the end face of the inner support tube (4) through the installation step.

11. The heating device according to claim 9, characterized in that, The height of the shunt cap (3) l The inner diameter D of the heating tube (6) satisfies the following relationship: l ≥D / 2.

12. A water dispenser, characterized in that, The heating device includes any one of claims 1 to 11.

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