Turbulence device for heat exchange structure, heat exchange structure and heat exchange device

Abstract

The present application relates to heat exchange technical field, disclose a spoiler for heat exchange structure, heat exchange structure and heat exchange device, the spoiler is located in the main oil way of heat exchange structure, and extends along the axial direction of main oil way, the spoiler extends spirally, and in a single spiral period, the projection of the spoiler along the axial direction is oval shape, the spoiler includes first section, second section and third section which are arranged in sequence along the axial direction, the first section is located at one end close to the heating part of heat exchange structure, the radial dimension of first section is greater than the radial dimension of third section, the radial dimension of second section gradually decreases from first section to third section, the present application improves the heat exchange efficiency and temperature uniformity of heat exchange structure, avoids local overheating, delays the aging speed of oil, reduces the security risk, reduces the equipment power under the premise of keeping the same heating effect, realizes energy saving and consumption reduction, improves the energy utilization rate, and can realize greater heat dissipation under the same heating power, shortens the preheating response time.

Description

Technical Field

[0001] This invention relates to the field of heat exchange technology, and more specifically to turbulence-disrupting elements, heat exchange structures, and heat exchange devices used in heat exchange structures. Background Technology

[0002] Heat transfer oil is a high-viscosity organic medium, with a viscosity typically ranging from 10 mPa·s to 100 mPa·s at room temperature. The high viscosity results in weak natural convection, and the flow is mostly laminar or transitional. This leads to a thicker boundary layer, higher thermal resistance, and a lower overall heat transfer coefficient. Consequently, the heat transfer oil near the heating zone in the oil passage heats up faster, while the temperature rise in the parts far from the heating zone is significantly delayed. This not only results in uneven overall oil temperature distribution but also prolongs the preheating time and reduces energy utilization efficiency. Summary of the Invention

[0003] In view of this, the present invention provides a turbulence-disrupting element, a heat exchange structure, and a heat exchange device for a heat exchange structure, so as to solve the problem of uneven overall oil temperature distribution in the oil passage, while prolonging the preheating time and reducing energy utilization efficiency.

[0004] In a first aspect, the present invention provides a turbulence element for a heat exchange structure, disposed within the main oil passage of the heat exchange structure and extending axially along the main oil passage, the turbulence element extending in a spiral shape, and within a single spiral cycle, the projection of the turbulence element along the axial direction is elliptical. The turbulence-disrupting element includes a first section, a second section, and a third section arranged sequentially along the axial direction. The first section is located at one end near the heating part of the heat exchange structure. The radial dimension of the first section is greater than that of the third section. The radial dimension of the second section gradually decreases from the first section to the third section.

[0005] Beneficial effects: By placing spirally extending turbulence-inducing components within the main oil channel, the heat transfer oil flows in a spiral pattern within the main oil channel. Furthermore, within a single spiral cycle, the projection of the turbulence-inducing components along the axial direction is elliptical. In this spiral flow, the non-circular structure actively induces velocity gradients and pressure changes in the heat transfer oil, effectively disrupting the laminar boundary layer formed along the flow direction, promoting turbulent mixing of hot and cold heat transfer oils, and enhancing convective heat transfer between the heat transfer oil and the main oil channel wall, thereby improving heat transfer efficiency. Simultaneously, the first section is located in the high-temperature region near the heating section. Since the heat transfer oil is initially heated here and easily forms a stable laminar boundary layer on the wall, it passes through a larger diameter... The first section generates strong swirling and turbulence, allowing the heat transfer oil to smoothly transition from axial laminar flow to a flow state with swirling characteristics. The second section, as a gradually narrowing transition section, effectively avoids local flow separation and excessive pressure loss caused by abrupt changes in cross-section due to the continuous change in the cross-sectional area of ​​the flow channel. At the same time, the narrowing of the flow channel further increases the flow velocity of the heat transfer oil, maintaining and enhancing the swirling intensity. The third section, located in the area far from the heating part, uses a smaller radial dimension to continuously maintain the turbulence on the heat transfer oil with a higher swirling intensity. This effectively improves the heat exchange efficiency and temperature uniformity of the heat exchange structure as a whole, avoids local overheating, slows down the aging rate of the oil, and reduces safety hazards. Meanwhile, due to the enhanced convective heat transfer intensity and increased heat transfer oil flow rate, the overall thermal resistance is reduced, enabling greater heat dissipation under the same heating power. This makes heat transfer more efficient and complete, allowing for a reduction in equipment power to achieve energy conservation and consumption reduction while maintaining the same heating effect, and improving energy utilization. Furthermore, it enables a greater heat dissipation under the same heating power, shortening the preheating response time and allowing users to perceive the temperature rise more quickly, thus improving the overall user experience.

[0006] In one alternative implementation, the axial length of the third segment is greater than the axial length of the first segment, and the axial length of the first segment is greater than the axial length of the second segment.

[0007] Beneficial effects: By setting the axial length of the third section to be greater than that of the first section, and the axial length of the first section to be greater than that of the second section; the first section is located in the high-temperature region near the heating part, with the largest radial dimension and moderate axial length, which can fully disrupt the thermal boundary layer in the high-temperature region, improve local heat exchange efficiency, and quickly remove the accumulated heat; the second section, as a gradually narrowing transition section, is designed with the shortest axial length to achieve a smooth transition of the flow channel cross-sectional area with minimal occupied length; while the third section, located in the heat dissipation region far from the heating part, has the smallest radial dimension but high swirling intensity, and its axial length is set to be the longest, extending the enhanced heat exchange distance of the heat transfer oil in the heat dissipation region, so that the enhanced heat exchange region can fully cover the main heat release process of the heat transfer oil, thereby improving the overall heat exchange efficiency and temperature uniformity.

[0008] In one optional implementation, the length of the first segment is L1, the length of the second segment is L2, and the length of the third segment is L3, wherein the ratio of L1:L2:L3 is in the range of (0.8~1.2)∶(0.3~0.8)∶(1.5~3).

[0009] In one optional embodiment, the agitator is a constant-pitch helical structure.

[0010] Beneficial effects: Because the flow-turbing component is a helical structure with equal pitch, the heat transfer oil is subjected to centrifugal force and inertial force with consistent periodicity and amplitude when flowing through each helical ring, forming a stable helical flow trajectory and avoiding flow field turbulence and local flow separation caused by sudden pitch changes.

[0011] In one optional embodiment, the pitch of the spoiler ranges from 5 mm to 6.7 mm.

[0012] Beneficial effects: By controlling the pitch within the range of 5mm to 6.7mm, the heat transfer oil is ensured to undergo sufficient disturbance in each spiral cycle, effectively breaking the thermal boundary layer, while avoiding increased flow resistance due to excessively small pitch. Thus, the heat transfer effect of the heat transfer oil is enhanced while ensuring flow stability.

[0013] In one alternative embodiment, the ratio of the major axis to the minor axis of the ellipse ranges from 1.25:1 to 2.5:1.

[0014] Beneficial effects: By controlling the ratio of the major axis to the minor axis of the ellipse within the range of 1.25:1 to 2.5:1, the heat transfer oil is subjected to asymmetric wall constraints in the spiral flow, inducing the formation of a velocity gradient and pressure difference distributed along the circumference. This effectively disrupts the laminar boundary layer formed by the heat transfer oil along the wall and reduces the thickness of the thermal boundary layer. At the same time, this ratio range ensures that the ellipticity is sufficient to induce flow instability and vortex generation, but it will not cause flow separation or local backflow due to its excessive elongation. Thus, the flow stability is maintained while enhancing the heat transfer effect.

[0015] In one alternative implementation, the major axis of the ellipse in the first segment ranges from 3 mm to 12 mm.

[0016] Beneficial effects: By setting the major axis of the ellipse in the first section to 3mm to 12mm, the heat transfer oil can flow smoothly and begin to rotate and agitate under the guidance of the spiral when it first enters the turbulence-inducing component. This avoids flow obstruction or sudden increase in local pressure due to the narrow channel, and also prevents the gap between the spiral and the oil passage wall from being too large due to the spiral being too thin, thus weakening the agitation effect on the oil flow. Under the premise of ensuring smooth flow, the turbulence-inducing process is effectively started.

[0017] In one alternative implementation, the major axis of the ellipse in the third segment ranges from 3 mm to 12 mm.

[0018] Beneficial effects: By setting the major axis of the ellipse of the third section to 3mm to 12mm, a moderate gap is maintained between the third section and the inner wall of the main oil passage. This allows the heat transfer oil to pass through and maintain rotation and agitation, avoiding excessive flow resistance or even blockage due to the narrow passage. It also ensures that the gap between the turbulence-inducing component and the oil passage wall is not too large, thereby maintaining sufficient turbulence intensity.

[0019] In an alternative embodiment, a rib is further included, which protrudes from the surface of the spoiler.

[0020] Beneficial effects: By setting ribs on the surface of the turbulence-inducing element, the spiral structure generates main-scale swirling disturbances in the heat transfer oil during its flow. The ribs, as local turbulence-inducing elements, induce additional vortex secondary flows when the heat transfer oil flows through them. The synergistic effect of the spiral structure and the ribs creates a strong turbulent mixing effect in the main oil channel, effectively disrupting the laminar boundary layer and promoting full contact between the heat transfer oil and the heating wall, further improving the overall heat exchange efficiency.

[0021] In one optional embodiment, the ribs are provided in multiples, and the multiple ribs are evenly spaced along the spiral direction of the spoiler; and the ribs extend radially along the spoiler.

[0022] Beneficial effects: By uniformly spacing multiple ribs along the spiral path of the turbulence-disrupting component, the heat transfer oil can be subjected to periodic and continuous disturbances during its flow along the spiral channel, thereby effectively breaking down and thinning the thermal boundary layer and reducing convective thermal resistance. At the same time, the radial extension of the ribs can penetrate the fluid center region and the near-wall region, enhancing the radial mixing and heat transfer of hot and cold fluids and improving the uniformity of temperature distribution within the oil passage cross-section.

[0023] In one alternative embodiment, the number of ribs provided in each pitch includes 2 to 6.

[0024] Beneficial effects: By setting 2 to 6 ribs in each helical pitch, the heat transfer oil is subjected to multiple local disturbances in each spiral flow path. This avoids the problem of excessive spacing between adjacent ribs due to an insufficient number of ribs, which would cause the thermal boundary layer to re-establish stable development in the interval zone, thus weakening the continuous effectiveness of the disturbance. At the same time, controlling the number of ribs per spiral to within 6 avoids the problem of excessive rib density on the flow cross section and increased flow resistance due to an excessive number of ribs. Through the reasonable density setting of 2 to 6 ribs, a uniformly distributed disturbance node is formed in each spiral cycle, so that the heat transfer oil is subjected to continuous and stable disturbance throughout the entire flow path, effectively disrupting the continuous development of the laminar boundary layer along the flow direction, while keeping the flow resistance within an acceptable range.

[0025] In one alternative embodiment, the cross-section of the rib is rectangular.

[0026] Beneficial effects: Because the rectangle has clear edges, it can form a more obvious turbulence edge when the heat transfer oil flows through it, thereby enhancing the shearing and stripping effect on the heat transfer oil, effectively destroying the laminar sublayer near the wall, promoting the turbulent flow of the heat transfer oil, and strengthening heat exchange.

[0027] In one alternative implementation, the height and width of the rib are both equal to the wall thickness of the spoiler.

[0028] Beneficial effects: By setting the height and width of the ribs to be equal to the wall thickness of the baffle, the ribs are prevented from being completely submerged in the viscous layer near the baffle wall due to excessive size, thus failing to effectively interfere with the boundary layer; conversely, excessive size will not cause increased flow resistance and pressure loss. At this size ratio, the heat transfer oil flowing over the ribs exhibits stable flow separation and re-adhesion, forming a periodically detached vortex structure that continuously erodes and disrupts the thermal boundary layer developing along the wall. Furthermore, since the rib size is consistent with the thickness of the baffle body, integral molding with the same material thickness can be achieved, reducing processing costs and improving product consistency.

[0029] Secondly, the present invention also provides a heat exchange structure, comprising: Heat exchange fins, equipped with main oil passages; The aforementioned turbulence-inducing element for the heat exchange structure is disposed within the main oil passage and extends axially along the main oil passage.

[0030] Beneficial effects: By placing the turbulence-disrupting element inside the main oil passage, when the heat transfer oil is heated and rises inside the main oil passage, it is affected by the turbulence-disrupting element, which breaks the laminar boundary layer and enhances the heat transfer intensity between the heat transfer oil and the wall of the main oil passage.

[0031] In one optional embodiment, the main oil passage includes a first equal-diameter section, a tapering section, and a second equal-diameter section arranged sequentially along the axial direction; the first equal-diameter section is located at the end of the main oil passage closer to the heating part, and the second equal-diameter section is located at the end of the main oil passage farther from the heating part. The radial dimension of the first equal-diameter section is greater than the radial dimension of the second equal-diameter section; the radial dimension of the tapering section gradually decreases from the first equal-diameter section to the second equal-diameter section; The first section of the spoiler is located within the first constant diameter section, the second section of the spoiler is located within the tapering section, and the third section of the spoiler is located within the second constant diameter section.

[0032] Beneficial effects: By setting the main oil passage as a first equal-diameter section, a tapering section, and a second equal-diameter section arranged sequentially along the axial direction, and by setting the first section of the baffle in the first equal-diameter section, the second section in the tapering section, and the third section in the second equal-diameter section, the outer diameter of each section of the baffle and the inner diameter of the corresponding section of the main oil passage are matched to each other. This ensures that the gradual change trend of the inner diameter of the oil passage and the change trend of the outer diameter of the baffle are completely coordinated along the axial direction, forming a flow gap and flow state consistent with the expectation in each section. This enhances the heat exchange effect between the heat transfer oil and the wall of the main oil passage while ensuring the stability of the natural circulation of the heat transfer oil.

[0033] In one alternative embodiment, the baffle is interference-fitted with the inner wall of the main oil passage.

[0034] Beneficial effects: By setting the baffle to an interference fit with the inner wall of the main oil passage, the baffle is tightly attached to the inner wall of the main oil passage, ensuring that the flow path of the heat transfer oil must bypass the spiral structure of the baffle, forming a spiral flow. This ensures that all heat transfer oil undergoes sufficient contraction, expansion, and vortex disturbance. Compared with traditional smooth oil passages, simple baffles, or wavy oil passages, it can achieve a higher heat transfer enhancement effect. At the same time, because the baffle is an elliptical spiral structure, it has a certain degree of elasticity. The baffle can be interference-fitted with the inner wall of the main oil passage by its own elastic deformation, without the need for welding, bonding, or additional connecting structures. This achieves bidirectional fixation of the baffle in both the axial and circumferential directions, preventing the baffle from shifting due to oil flow impact during use, and simplifying the assembly process and overall structure of the baffle.

[0035] In one alternative embodiment, a limiting member is further included, the limiting member being disposed at the end of the deflector.

[0036] Beneficial effects: By setting a limiting component at the end of the turbulence component, it is possible to effectively prevent the turbulence component from moving or displacing axially under conditions such as heat transfer oil flow impact, thermal expansion and contraction due to temperature changes, or equipment vibration. This ensures that the turbulence component and the main oil passage always maintain an accurate axial correspondence, further enhancing the stability and reliability during long-term use.

[0037] Thirdly, the present invention also provides a heat exchange device, including the heat exchange structure described above.

[0038] In one alternative embodiment, the heat exchange device includes an electric oil radiator. Attached Figure Description

[0039] To more clearly illustrate the technical solutions in the specific embodiments or related technologies of the present invention, 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 the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0040] Figure 1 This is a side view of the heat exchange structure according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the assembly of the turbulence-disrupting element and the heat exchange plate according to an embodiment of the present invention; Figure 3 This is a top view of the heat exchange structure according to an embodiment of the present invention; Figure 4 This is a schematic diagram of the overall structure of the baffle element according to an embodiment of the present invention; Figure 5 This is a top view of the spoiler according to an embodiment of the present invention; Figure 6 This is a schematic diagram illustrating the variable diameter feature of the aerodynamic component according to an embodiment of the present invention; Figure 7 This is a schematic diagram of the first section of the spoiler in an embodiment of the present invention; Figure 8 This is a schematic diagram of the second section of the spoiler in an embodiment of the present invention; Figure 9 This is a schematic diagram of the third section of the aerodynamic component according to an embodiment of the present invention; Figure 10 This is a partial structural schematic diagram of the baffle element according to an embodiment of the present invention; Figure 11 This is a schematic diagram of a single spiral cycle of the turbulence-disrupting component according to an embodiment of the present invention; Figure 12 This is a schematic diagram of the simulation results of steady-state temperature rise on the surface of the heat exchanger plate according to an embodiment of the present invention; Figure 13This is a schematic diagram of the simulation results of steady-state temperature rise on the surface of a heat exchanger with a traditional structure.

[0041] Explanation of reference numerals in the attached figures: 1. Spoiler; 111. First section; 112. Second section; 113. Third section; 12. Rib; 2. Heat exchanger fins; 21. Main oil passage; 22. Return oil passage; 23. Upper oil reservoir; 24. Lower oil reservoir. Detailed Implementation

[0042] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] In the description of this invention, it should be noted that the terms "upper," "lower," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for 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 invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0044] In the description of this 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; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0045] Furthermore, the technical features involved in the different embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0046] Oil-filled electric radiators, widely used in southern regions without centralized heating, are a mainstream household heating device. Their core structure includes multiple interconnected metal heat exchange fins 2, high-boiling-point heat-conducting oil filling the interior, an electric heating element assembly, and temperature control and safety protection devices. When powered on, the electric heating element converts electrical energy into heat energy, directly heating the surrounding heat-conducting oil. The heated oil, due to its reduced density, flows upwards along the vertical main oil channel 21 under buoyancy, while simultaneously forming a natural convection circulation through the side return oil channel 22. Finally, heat is transferred to the room through radiation and natural convection via the outer surface of the heat exchange fins 2, thus raising the room temperature. Their advantages, such as quiet operation, no open flame, high safety, and continued heat release after power failure, have made them a market mainstream choice.

[0047] However, since the viscosity of heat transfer oil at room temperature is typically between 10 mPa·s and 100 mPa·s, it belongs to a high-viscosity organic medium. Its internal natural convection intensity is weak, and the flow is mostly in a laminar or transitional state. This results in a thick boundary layer, high thermal resistance, and rapid temperature rise near the heating area, while the temperature rise in areas farther from the heating area lags significantly. The overall heat transfer coefficient is low, the temperature gradient is large, leading to uneven oil temperature distribution, which can easily cause localized overheating, accelerate oil aging, and increase safety hazards. Furthermore, due to the low overall heat transfer coefficient, it usually takes 10 to 30 minutes or even longer to reach a comfortable human body temperature, resulting in a long preheating time and impacting energy utilization efficiency.

[0048] To address the aforementioned issues, current improvements primarily involve increasing the number and surface area of ​​heat exchange fins 2, optimizing the cross-sectional shape of the oil passages, selecting oils with high thermal conductivity, or adding external convection fins. However, these measures mainly focus on external heat dissipation or overall structural adjustments, failing to fundamentally enhance the internal flow and hot-cold mixing of the heat-transfer oil within the main oil passage 21. Furthermore, while related technologies mention wave-shaped oil passages or baffle structures to extend the flow path, these designs primarily target the air side or external convection enhancement, making it difficult to shorten preheating time and improve overall heat exchange efficiency.

[0049] The following is combined Figures 1 to 13 The following describes embodiments of the present invention.

[0050] According to an embodiment of the present invention, in one aspect, a baffle 1 for a heat exchange structure is provided, which is disposed in the main oil passage 21 of the heat exchange structure and extends along the axial direction of the main oil passage 21. The baffle 1 extends in a spiral shape, and in a single spiral cycle, the projection of the baffle 1 along the axial direction is elliptical. The baffle 1 includes a first section 111, a second section 112 and a third section 113 arranged sequentially along the axial direction. The first section 111 is located at one end near the heating part. The radial dimension of the first section 111 is greater than the radial dimension of the third section 113. The radial dimension of the second section 112 gradually decreases from the first section 111 to the third section 113.

[0051] In the above embodiment, by placing the spirally extending baffle 1 inside the main oil passage 21, the heat transfer oil flows in a spiral state within the main oil passage 21. Furthermore, since the projection of the baffle 1 along the axial direction is elliptical within a single spiral cycle, the non-circular structure actively induces velocity gradients and pressure changes in the heat transfer oil during the spiral flow. This effectively disrupts the laminar boundary layer formed along the flow direction of the heat transfer oil, promotes turbulent mixing of hot and cold heat transfer oils, and enhances convective heat transfer between the heat transfer oil and the wall of the main oil passage 21, thereby improving heat transfer efficiency. Simultaneously, the first section 111 is located in a high-temperature region near the heating section. Since the heat transfer oil is initially heated here and easily forms a stable laminar boundary layer on the wall, it... The larger radial dimension creates strong swirling and turbulence, allowing the heat transfer oil to smoothly transition from axial laminar flow to a flow state with swirling characteristics. The second section 112, as a gradually narrowing transition section, effectively avoids local flow separation and excessive pressure loss caused by abrupt changes in cross-section due to the continuous change in the cross-sectional area of ​​the flow channel. At the same time, the narrowing of the flow channel further increases the flow velocity of the heat transfer oil, maintaining and enhancing the swirling intensity. The third section 113, located in the area far from the heating part, adopts a smaller radial dimension and maintains the turbulence on the heat transfer oil with a higher swirling intensity. This effectively improves the heat exchange efficiency and temperature uniformity of the heat exchange structure as a whole, avoids local overheating, slows down the aging rate of the oil, and reduces safety hazards. Meanwhile, due to the enhanced convective heat transfer intensity and increased heat transfer oil flow rate, the overall thermal resistance is reduced, enabling greater heat dissipation under the same heating power. This makes heat transfer more efficient and complete, allowing for a reduction in equipment power to achieve energy conservation and consumption reduction while maintaining the same heating effect, and improving energy utilization. Furthermore, it enables a greater heat dissipation under the same heating power, shortening the preheating response time and allowing users to perceive the temperature rise more quickly, thus improving the overall user experience.

[0052] Specifically, by enhancing the disturbance and mixing of the heat transfer oil through the turbulence component 1, the convective heat transfer intensity between the heat transfer oil and the wall of the main oil channel 21 is enhanced, thereby increasing the convective heat transfer coefficient and the Nusselt number. This results in a greater heat dissipation under the same heating power, and the heat transfer process is more thorough and efficient. As a result, users can perceive the temperature rise more quickly after turning on the equipment.

[0053] Specifically, due to the difference in radial dimensions between the major and minor axes of the ellipse, when the turbulence-inducing component 1 rotates and propels within the main oil passage 21, the gap between the major axis end and the inner wall of the main oil passage 21 is smaller, while the gap between the minor axis end and the inner wall of the main oil passage 21 is larger. During the axial spiral flow, the heat transfer oil will alternately pass through flow areas of different widths, causing periodic contraction and expansion effects to form inside the main oil passage 21. This can induce strong secondary flow, centrifugal force, and velocity gradient changes, effectively disrupting the laminar boundary layer and enhancing the convective heat transfer intensity between the heat transfer oil and the wall of the main oil passage 21.

[0054] Specifically, the heating section is located in the area below the heat exchange plate 2. The first section 111, the second section 112 and the third section 113 are arranged vertically from low to high, so that the heat transfer oil in the main oil passage 21 flows through the first section 111, the second section 112 and the third section 113 in sequence when heated and rising.

[0055] Specifically, the heating element is an electric heating tube.

[0056] In one embodiment, the axial length of the third segment 113 is greater than the axial length of the first segment 111, and the axial length of the first segment 111 is greater than the axial length of the second segment 112.

[0057] In the above embodiment, the axial length of the third section 113 is set to be greater than that of the first section 111, and the axial length of the first section 111 is greater than that of the second section 112. The first section 111 is located in the high-temperature region near the heating part, with the largest radial dimension and a moderate axial length, which can fully disrupt the thermal boundary layer in the high-temperature region, improve local heat exchange efficiency, and quickly remove the accumulated heat. The second section 112, as a gradually narrowing transition section, is designed with the shortest axial length to achieve a smooth transition of the flow channel cross-sectional area with minimal occupied length. The third section 113, located in the heat dissipation region far from the heating part, has the smallest radial dimension but a high swirling intensity. Its axial length is set to be the longest, which extends the enhanced heat exchange distance of the heat transfer oil in the heat dissipation region, so that the enhanced heat exchange region can fully cover the main heat release process of the heat transfer oil, thereby improving the overall heat exchange efficiency and temperature uniformity.

[0058] In one embodiment, the length of the first segment 111 is L1, the length of the second segment 112 is L2, and the length of the third segment 113 is L3, wherein the ratio of L1:L2:L3 is in the range of (0.8~1.2)∶(0.3~0.8)∶(1.5~3).

[0059] In one implementation, the ratio of L1:L2:L3 can be 0.8:0.3:1.5.

[0060] In another implementation, the ratio of L1:L2:L3 can be 1.2:0.8:3.

[0061] In another implementation, the ratio of L1:L2:L3 can be 1:0.5:2.

[0062] In one embodiment, the deflector 1 is a constant pitch spiral structure.

[0063] In the above embodiments, since the turbulence-disrupting element 1 is a helical structure with equal pitch, the heat transfer oil is subjected to centrifugal force and inertial force with consistent periodicity and amplitude when flowing through each helical coil, forming a stable helical flow trajectory and avoiding flow field turbulence and local flow separation caused by sudden pitch changes.

[0064] In one embodiment, the pitch range of the spoiler 1 includes 5 mm to 6.7 mm.

[0065] In the above embodiments, the pitch is controlled within the range of 5mm to 6.7mm, which ensures that the heat transfer oil undergoes sufficient disturbance in each spiral cycle to effectively destroy the thermal boundary layer, while avoiding the increase in flow resistance caused by too small a pitch. Thus, the heat transfer effect of the heat transfer oil is enhanced while ensuring flow stability.

[0066] In one embodiment, the pitch of the spoiler 1 is set to 5 mm, that is, 4 turns of spiral are provided within every 20 mm of length. In another embodiment, the pitch of the spoiler 1 can also be set to 6.7 mm, corresponding to 3 turns of spiral are provided within every 20 mm of length.

[0067] In one embodiment, the ratio of the major axis to the minor axis of the ellipse ranges from 1.25:1 to 2.5:1.

[0068] In the above embodiments, by controlling the ratio of the major axis to the minor axis of the ellipse to be within the range of 1.25:1 to 2.5:1, the heat transfer oil is subjected to asymmetric wall constraints in the spiral flow, inducing the formation of a velocity gradient and pressure difference distributed along the circumference, effectively disrupting the laminar boundary layer formed by the heat transfer oil along the wall, and reducing the thickness of the thermal boundary layer; at the same time, this ratio range ensures that the ellipticity is sufficient to induce flow instability and vortex generation, but does not cause flow separation or local backflow due to its excessive elongation, thereby maintaining flow stability while enhancing the heat transfer effect.

[0069] Specifically, since the size of the main oil passage 21 directly determines the installation space of the turbulence component 1 and the flow cross-sectional area of ​​the heat transfer oil, and the viscosity of the heat transfer oil affects the flow resistance and turbulence effect, in practical applications, the ratio of the major axis to the minor axis of the ellipse needs to be adjusted according to the size of the main oil passage 21 and the viscosity of the heat transfer oil; specifically, the ratio of the major axis to the minor axis of the ellipse can be set to 2:1.

[0070] In one embodiment, the major axis of the ellipse of the first segment 111 ranges from 3 mm to 12 mm.

[0071] In the above embodiment, by setting the major axis of the ellipse of the first section 111 to 3mm to 12mm, the heat transfer oil can flow smoothly and start to rotate and agitate under the guidance of the spiral when it enters the turbulence member 1. This avoids flow obstruction or sudden increase in local pressure due to the channel being too narrow, and also prevents the gap between the spiral and the oil passage wall from being too large due to the spiral being too thin, thereby weakening the agitation effect on the oil flow. Under the premise of ensuring smooth flow, the turbulence process is effectively started.

[0072] In one embodiment, the major axis of the ellipse in the third segment 113 ranges from 3 mm to 12 mm.

[0073] In the above embodiment, by setting the major axis of the ellipse of the third section 113 to 3mm to 12mm, a moderately sized gap is maintained between the third section 113 and the inner wall of the main oil passage 21. This allows the heat transfer oil to pass through and maintain rotation and agitation, avoiding excessive flow resistance or even blockage due to the narrow passage. It also ensures that the gap between the turbulence-disrupting element 1 and the oil passage wall is not too large, thereby maintaining sufficient turbulence intensity.

[0074] For example, the major axis of the ellipse in the first segment 111 is 9mm, the major axis of the ellipse in the second segment 112 is uniformly reduced from 9mm to 4.5mm, and the major axis of the ellipse in the third segment 113 is 4.5mm.

[0075] In one embodiment, a rib 12 is also included, which protrudes from the surface of the spoiler 1.

[0076] In the above embodiment, by providing ribs 12 on the surface of the turbulence-disrupting element 1, the spiral structure causes the heat transfer oil to generate main-scale swirling disturbances during the flow process, while the ribs 12 act as local turbulence-disrupting elements to induce additional vortex secondary flows when the heat transfer oil flows through. The spiral structure and the ribs 12 work together to form a strong turbulent mixing effect in the main oil channel 21, effectively destroying the laminar boundary layer and promoting full contact between the heat transfer oil and the heating wall, further improving the overall heat exchange efficiency.

[0077] In one embodiment, a plurality of ribs 12 are provided, and the plurality of ribs 12 are evenly spaced along the spiral direction of the deflector 1; and the ribs 12 extend radially along the deflector 1.

[0078] In the above embodiments, by uniformly spacing multiple ribs 12 on the spiral path of the turbulence-disrupting element 1, the heat transfer oil can be subjected to periodic and continuous disturbance during the flow along the spiral channel, thereby effectively destroying and thinning the thermal boundary layer and reducing the convective thermal resistance; at the same time, the radial extension of the ribs 12 can penetrate the fluid center region and the near-wall region, enhance the radial mixing and heat transfer of hot and cold fluids, and improve the uniformity of temperature distribution within the oil passage cross section.

[0079] In one embodiment, the number of ribs 12 provided in each pitch includes 2 to 6.

[0080] In the above embodiments, by setting 2 to 6 ribs 12 in each pitch, the heat transfer oil is subjected to multiple local disturbances in each spiral flow path. This avoids the excessive spacing between adjacent ribs 12 due to an insufficient number of ribs 12, which would cause the thermal boundary layer to re-establish stable development in the interval area, thereby weakening the continuous effectiveness of the disturbance. At the same time, the number of ribs 12 per spiral is controlled to within 6 to avoid excessive density of ribs 12 on the flow cross section and increased flow resistance due to an excessive number of ribs 12. Through the reasonable density setting of 2 to 6 ribs 12, a uniformly distributed disturbance node is formed in each spiral cycle, so that the heat transfer oil is subjected to continuous and stable disturbance throughout the entire flow path, effectively disrupting the continuous development of the laminar boundary layer along the flow direction, while keeping the flow resistance within an acceptable range.

[0081] In one embodiment, two ribs 12 are provided in each pitch, resulting in low flow resistance but relatively limited disturbance intensity. In another embodiment, four ribs 12 are provided in each pitch, achieving a good balance between disturbance effect and flow resistance. In yet another embodiment, six ribs 12 are provided in each pitch, which can further enhance local disturbance, but the degree of flow channel blockage increases accordingly, leading to an increase in pressure drop. Therefore, it is preferable to provide four ribs 12 in each pitch to ensure that a reasonable heat transfer oil flow rate is maintained while effectively disrupting the boundary layer.

[0082] In one embodiment, the cross-section of the rib 12 is rectangular.

[0083] In the above embodiments, since the rectangle has clear edges, it can form a more obvious turbulence edge when the heat transfer oil flows through it, thereby enhancing the shearing and stripping effect on the heat transfer oil, effectively destroying the laminar sublayer near the wall, promoting the turbulent flow of the heat transfer oil, and strengthening heat exchange.

[0084] In one embodiment, the height and width of the rib 12 are both equal to the wall thickness of the spoiler 1.

[0085] In the above embodiments, by setting the height and width of the rib 12 to be equal to the wall thickness of the baffle 1, the rib 12 is neither too small and completely submerged in the viscous layer near the wall of the baffle 1, thus failing to effectively interfere with the boundary layer; nor too large and causing increased flow resistance and pressure loss. At this size ratio, when the heat transfer oil flows through the rib 12, it can generate stable flow separation and re-attachment phenomena, forming a periodically detached vortex structure, thereby continuously eroding and destroying the thermal boundary layer developing along the wall. At the same time, since the size of the rib 12 is consistent with the thickness of the main body of the baffle 1, it can be integrally molded using the same material thickness, reducing processing costs and improving product consistency.

[0086] For example, the power P of the electric heating tube is set to 2200W; the height H of the main oil channel 21 is 600mm; the heat transfer oil is mineral oil, and the inlet temperature is set to 20℃; the heating method is constant heat flux density heating, and the flow state is forced circulation under the dominance of natural convection, that is, the inside of the electric oil heater is a closed natural convection environment.

[0087] In this embodiment, the ratio of L1:L2:L3 is selected as 0.8:0.3:1.5, and four ribs 12 are provided in each spiral cycle. The ratio of the major axis to the minor axis of the ellipse is set to 2:1. The simulation results of the steady-state temperature rise of the heat exchanger on both sides are as follows. Figure 12 As shown. Using heat exchanger 2 of the same specifications but without any internal turbulence structures as a comparative example, the simulation results of the steady-state temperature rise of heat exchanger 2 are as follows. Figure 13 As shown.

[0088] according to Figure 12 and Figure 13 Compared with the simulation results, the steady-state temperature rise of heat exchanger 2 in this experiment is lower than that in the comparative example. The maximum temperature rise is reduced from about 138K to about 118K. The temperature difference between the upper and lower plates is small, local hot spots are effectively suppressed, the temperature distribution is more uniform, and the overall heat exchange efficiency is better.

[0089] Figure 12 and Figure 13 The simulation results show that the turbulence component 1 in this embodiment, through the synergistic effect of the elliptical variable diameter spiral structure and the periodically arranged protruding ribs 12, can dynamically match the flow characteristics according to the flow rate and temperature changes of the heat transfer oil in the main oil passage 21, forming a multi-directional secondary flow and swirling superposition effect. This effectively avoids the formation of local high temperature zones or low temperature dead zones, making the surface temperature distribution of the heat exchange plate 2 more uniform and improving the heat exchange efficiency of the heat exchange plate 2. This reduces the risk of burns and improves user comfort and safety. At the same time, the reduction in overall temperature difference helps to reduce the damage of thermal stress to the heating part, seals and heat exchange plate 2, thereby extending the service life of the equipment while ensuring reliable operation.

[0090] According to an embodiment of the present invention, another aspect provides a heat exchange structure, including a heat exchange plate 2 and the aforementioned baffle 1 for the heat exchange structure; the heat exchange plate 2 is provided with a main oil passage 21; the baffle 1 is disposed in the main oil passage 21 and extends along the axial direction of the main oil passage 21.

[0091] In the above embodiment, the turbulence element 1 is disposed in the main oil passage 21. When the heat transfer oil is heated and rises in the main oil passage 21, it is affected by the turbulence element 1, which disrupts the laminar boundary layer and enhances the heat transfer intensity between the heat transfer oil and the wall of the main oil passage 21.

[0092] In a specific implementation, the turbulence-disrupting element 1 can be arranged along the entire axial length of the main oil passage 21, or selectively arranged in key heat exchange areas according to heat exchange requirements. Taking a single heat exchange plate 2 as an example, the heat exchange plate 2 forms a closed-loop oil circuit consisting of the main oil passage 21 and the two side return oil passages 22. The main oil passage 21 and the two side return oil passages 22 are interconnected through the upper oil reservoir 23 at the top of the heat exchange plate 2 and the lower oil reservoir 24 at the bottom. The main oil passage 21 is located in the middle of the heat exchange plate 2 and is adjacent to the electric heating tube, forming the main upward channel for the heat transfer oil after it is heated. The two side return oil passages 22 are located on both sides of the heat exchange plate 2, forming the return channel for the heat transfer oil after it is heated.

[0093] During operation, the electric heating element first heats the heat transfer oil in the main oil channel 21. After being heated, the heat transfer oil's temperature rises and its density decreases. Under the action of buoyancy, it flows upward along the main oil channel 21 and continuously transfers heat to the wall of the heat exchange plate 2 during the upward process. When the heat transfer oil flows to the top of the heat exchange plate 2, it flows into the return oil channels 22 on both sides through the top oil inlet 23. As the heat transfer oil continuously releases heat to the heat exchange plate 2 in the oil channels on both sides, its temperature gradually decreases and its density increases accordingly. Thus, under the action of gravity, it flows back downward along the oil channels on both sides and finally merges back into the heating area of ​​the main oil channel 21 through the bottom oil inlet 24. This forms a continuous natural circulation flow pattern in which the main oil channel 21 rises and the oil channels on both sides descend.

[0094] Specifically, the turbulence-inducing element 1 is arranged in the main oil channel 21 so that the heat transfer oil enters the enhanced turbulence zone immediately after being heated by the electric heating tube. The turbulence-inducing element 1 induces the heat transfer oil to generate strong swirling, secondary flow and periodic vortex through its spiral shape and surface ribs 12, which effectively improves the mixing degree of the heat transfer oil, thereby promoting the rapid and uniform transfer of heat to the entire heat exchange plate 2.

[0095] In one embodiment, the main oil passage 21 includes a first equal-diameter section, a tapering section, and a second equal-diameter section arranged sequentially along the axial direction; the first equal-diameter section is located at one end of the main oil passage 21 near the heating part, and the second equal-diameter section is located at one end of the main oil passage 21 away from the heating part; the radial dimension of the first equal-diameter section is greater than the radial dimension of the second equal-diameter section; the radial dimension of the tapering section gradually decreases from the first equal-diameter section to the second equal-diameter section; the first section 111 of the turbulence member 1 is disposed in the first equal-diameter section, the second section 112 of the turbulence member 1 is disposed in the tapering section, and the third section 113 of the turbulence member 1 is disposed in the second equal-diameter section.

[0096] In the above embodiment, by setting the main oil passage 21 as a first equal diameter section, a tapering section and a second equal diameter section arranged sequentially along the axial direction, and by setting the first section 111 of the baffle 1 to the first equal diameter section, the second section 112 to the tapering section and the third section 113 to the second equal diameter section, the outer diameter of each section of the baffle 1 and the inner diameter of the corresponding section of the main oil passage 21 are mutually adapted to each other, so that the gradual change trend of the inner diameter of the oil passage and the change trend of the outer diameter of the baffle 1 are completely coordinated along the axial direction, and a flow gap and flow state consistent with the expectation are formed in each section, thereby enhancing the heat exchange effect between the heat transfer oil and the wall of the main oil passage 21 while ensuring the stability of the natural circulation of the heat transfer oil.

[0097] In one embodiment, the baffle 1 is interference-fitted with the inner wall of the main oil passage 21.

[0098] In the above embodiment, by setting the baffle 1 and the inner wall of the main oil passage 21 to an interference fit, the baffle 1 is tightly attached to the inner wall of the main oil passage 21, thereby ensuring that the flow path of the heat transfer oil must bypass the spiral structure of the baffle 1 to form a spiral flow, ensuring that all heat transfer oil undergoes sufficient contraction and expansion and vortex disturbance; compared with traditional smooth oil passages, simple baffles or wavy oil passages, a higher heat transfer enhancement effect can be achieved. At the same time, since the baffle 1 is an elliptical spiral structure, it has a certain degree of elasticity, so the baffle 1 can be interference-fitted with the inner wall of the main oil passage 21 by its own elastic deformation, without the need for welding, bonding or additional connection structures, thus achieving bidirectional fixation of the baffle 1 in both the axial and circumferential directions, preventing the baffle 1 from shifting due to oil flow impact during use, simplifying the assembly process and overall structure of the baffle 1.

[0099] In specific embodiments, the baffle 1 can be integrally molded within the main oil passage 21 or installed by insertion. This eliminates the need to adjust the structure of the heat exchanger 2, the shape of the oil passage, or the power parameters of the equipment. Therefore, it facilitates large-scale mass production and is beneficial for upgrading existing equipment, resulting in low overall additional costs and good economic efficiency and applicability. In this embodiment, the baffle 1 is installed by insertion and is interference-fitted with the inner wall of the main oil passage 21.

[0100] Specifically, in this embodiment, the major axis of the baffle 1 is less than or equal to the inner diameter of the main oil passage 21, and the fit tolerance between the two is controlled within the range of -0.2mm to 0mm, so that the baffle 1 and the inner wall of the main oil passage 21 form an interference fit.

[0101] In one embodiment, a limiting member is also included, which is disposed at the end of the deflector 1.

[0102] In the above embodiments, by setting a limiting member at the end of the turbulence member 1, it is possible to effectively prevent the turbulence member 1 from moving or displacing axially under conditions such as heat transfer oil flow impact, thermal expansion and contraction due to temperature changes, or equipment vibration, so as to ensure that the turbulence member 1 and the main oil passage 21 always maintain an accurate axial correspondence, and further enhance the stability and reliability in long-term use.

[0103] Specifically, the limiting component can be a positioning ring or an end retaining ring, and both ends of the turbulence-disrupting component 1 can be provided with limiting components. During installation, the two limiting components abut against the end faces of the two ends of the main oil passage 21, or are connected to the heat exchange plates 2 respectively, thereby achieving axial limiting of the turbulence-disrupting component 1.

[0104] According to an embodiment of the present invention, a third aspect provides a heat exchange device including the heat exchange structure described above.

[0105] In one embodiment, the heat exchange device includes an electric oil heater.

[0106] The baffle 1 is installed inside the main oil passage 21 of the heat exchange fins 2 of the oil radiator. In one specific embodiment, a commercially available oil radiator with 13 to 15 heat exchange fins 2 is used as the application object. Its electric heating tube power is 1500 watts to 2500 watts, and the total height of the main oil passage 21 is 400 mm to 600 mm. The structural parameters such as the pitch, radial dimension, and section length of the baffle 1 can be adapted and designed accordingly. Since the oil passage size and the physical properties of the heat transfer oil such as density, viscosity, and specific heat capacity vary among different models, the above structural parameters can be adjusted and optimized proportionally in actual applications. This allows for the improvement of heat exchange efficiency and the reduction of preheating time without changing the external dimensions, overall weight, and safety performance of the oil radiator.

[0107] It should be noted that the turbulence-disrupting element 1 of this application is not only applicable to the above-mentioned electric oil heater, but can also be applied to oil-filled heat exchange devices or in-tube flow heat exchange devices such as industrial oil coolers, generator oil cooling pipelines, shell and tube heat exchangers, and cold plate radiators.

[0108] Although embodiments of the 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 invention, and such modifications and variations all fall within the scope defined by the appended application.

Claims

1. A turbulence-disrupting element for a heat exchange structure, disposed within the main oil passage (21) of the heat exchange structure and extending axially along the main oil passage (21), characterized in that, The spoiler (1) extends in a spiral shape, and within a single spiral cycle, the projection of the spoiler (1) along the axial direction is elliptical. The turbulence-disrupting element (1) includes a first section (111), a second section (112), and a third section (113) arranged sequentially along the axial direction. The first section (111) is located at one end close to the heating part of the heat exchange structure. The radial dimension of the first section (111) is greater than that of the third section (113). The radial dimension of the second section (112) gradually decreases from the first section (111) to the third section (113).

2. The turbulence-disrupting element for a heat exchange structure according to claim 1, characterized in that, The length of the third segment (113) is greater than the length of the first segment (111), and the length of the first segment (111) is greater than the length of the second segment (112).

3. The turbulence-disrupting element for a heat exchange structure according to claim 2, characterized in that, The length of the first segment (111) is L1, the length of the second segment (112) is L2, and the length of the third segment (113) is L3, wherein the ratio of L1:L2:L3 is (0.8~1.2)∶(0.3~0.8)∶(1.5~3).

4. The turbulence-disrupting element for a heat exchange structure according to any one of claims 1 to 3, characterized in that, The turbulence-disrupting component (1) is a constant pitch spiral structure.

5. The turbulence-disrupting element for a heat exchange structure according to claim 4, characterized in that, The pitch range of the spoiler (1) includes 5mm to 6.7mm.

6. The turbulence-disrupting element for a heat exchange structure according to any one of claims 1 to 3, characterized in that, The ratio of the major axis to the minor axis of the ellipse ranges from 1.25:1 to 2.5:1; And / or, the major axis of the ellipse of the first segment (111) ranges from 3 mm to 12 mm; And / or, the major axis of the ellipse of the third segment (113) ranges from 3 mm to 12 mm.

7. The turbulence-disrupting element for a heat exchange structure according to any one of claims 1 to 3, characterized in that, It also includes a rib (12) that protrudes from the surface of the spoiler (1).

8. The turbulence-disrupting element for a heat exchange structure according to claim 7, characterized in that, The ribs (12) are provided in multiple ways, and the multiple ribs (12) are evenly spaced along the spiral direction of the spoiler (1); and the ribs (12) extend radially along the spoiler (1). And / or, the number of said ribs (12) provided in each pitch includes 2 to 6.

9. The turbulence-disrupting element for a heat exchange structure according to claim 7, characterized in that, The cross-section of the convex rib (12) is rectangular.

10. The turbulence-disrupting element for a heat exchange structure according to claim 9, characterized in that, The height and width of the rib (12) are both equal to the wall thickness of the spoiler (1).

11. A heat exchange structure, characterized in that, include: The heat exchange plate (2) is equipped with a main oil passage (21); The turbulence member (1) for the heat exchange structure according to any one of claims 1 to 10 is disposed in the main oil passage (21) and extends axially along the main oil passage (21).

12. The heat exchange structure according to claim 11, characterized in that, The main oil passage (21) includes a first equal diameter section, a tapering section and a second equal diameter section arranged sequentially along the axial direction; the first equal diameter section is located at the end of the main oil passage (21) near the heating part, and the second equal diameter section is located at the end of the main oil passage (21) away from the heating part. The radial dimension of the first equal-diameter section is greater than the radial dimension of the second equal-diameter section; the radial dimension of the tapering section gradually decreases from the first equal-diameter section to the second equal-diameter section; The first section (111) of the spoiler (1) is located in the first equal diameter section, the second section (112) of the spoiler (1) is located in the tapered section, and the third section (113) of the spoiler (1) is located in the second equal diameter section.

13. The heat exchange structure according to claim 11, characterized in that, The turbulence-inducing component (1) is interference-fitted with the inner wall of the main oil passage (21).

14. The heat exchange structure according to claim 11, characterized in that, It also includes a limiting member, which is located at the end of the turbulence member (1).

15. A heat exchange device, characterized in that, The heat exchange structure includes any one of claims 11 to 14.

16. The heat exchange device according to claim 15, characterized in that, The heat exchange device includes an electric oil heater.

Images