Heat exchange plate and heat exchanger using the same

Abstract

The utility model provides a kind of heat exchange plate and the heat exchanger using it, belong to heat transfer technical field.It solves the technical problem such as weak heat exchange effect of prior art.This heat exchange plate, including plate body, the plate body is equipped with at least two first strip-shaped protrusions spaced distribution, first fluid groove is set between two adjacent first strip-shaped protrusions, the plate body is located first strip-shaped protrusion back surface is equipped with second fluid groove, the first strip-shaped protrusion top surface is equipped with heat exchange unit, the heat exchange unit includes being set in first strip-shaped protrusion top surface at least two arches spaced distribution along its length direction, two adjacent arches are equipped with for connecting two adjacent first fluid groove intercommunication groove;The arch back surface is equipped with in second fluid groove and corresponding recess of intercommunication groove.This utility model has the advantages of strong heat exchange effect, large heat exchange area, high structural strength etc..

Description

Technical Field

[0001] This utility model belongs to the field of heat transfer technology, and relates to heat exchange devices, and in particular to a heat exchange plate and a heat exchanger using the same. Background Technology

[0002] A heat exchange plate is a heat exchange element made of metal plates. It achieves efficient heat transfer through fluid flow between the plates and is used for heat exchange between different media. In the existing technology, most are herringbone-shaped plate stacks, where the crests of one plate overlap with the troughs of another plate to form solder joints. Most of the crest convex surfaces and trough concave surfaces have the same width, and both the convex and concave surfaces are single, flat, and smooth planes.

[0003] The size of the weld joint is usually adjusted by changing the corrugation width, but a smooth convex surface will result in insufficient heat transfer disturbance. Moreover, simply increasing the width of the convex surface does increase the weld joint area during overlapping, thereby increasing strength, but it also reduces the effective heat transfer area, thus weakening the heat transfer effect. In addition, a smooth convex surface causes the fluid to flow only around the weld joint, resulting in insufficient disturbance to the fluid flow and heat transfer, thus leading to poor heat transfer effect. Summary of the Invention

[0004] The purpose of this invention is to address the above-mentioned problems by providing a heat exchange plate with a stronger heat exchange effect.

[0005] Another objective of this invention is to provide a heat exchanger that addresses the aforementioned problems.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: The heat exchange plate includes a plate body, on which at least two spaced-apart first strip-shaped protrusions are provided, and a first fluid groove is provided between adjacent two first strip-shaped protrusions. A second fluid groove is provided on the back side of the first strip-shaped protrusions of the plate body. A heat exchange unit is provided on the top surface of the first strip-shaped protrusions. The heat exchange unit includes at least two arches spaced-apart along the length direction on the top surface of the first strip-shaped protrusions. A connecting groove for connecting adjacent two first fluid grooves is provided between adjacent two arches. The arched back is provided with a recess located in the second fluid groove and corresponding to the connecting groove.

[0007] By setting spaced arches on the top surface of the first strip-shaped protrusion, the effective heat transfer area can be increased, the fluid disturbance can be effectively enhanced, and the boundary layer can be broken, thereby simultaneously enhancing the flow heat transfer efficiency of the fluid on both sides.

[0008] In the aforementioned heat exchange plate, the arches on adjacent first strip-shaped protrusions are either staggered or aligned along their length. When staggered, the arches on adjacent protrusions are interleaved, forcing the fluid to generate a more complex turbulent path as it flows through the connecting channels between adjacent passages. This design significantly enhances fluid turbulence, helping to further strengthen heat transfer and improve heat exchange efficiency. When aligned, the fluid path is relatively smooth, reducing flow resistance and allowing for a better balance between heat transfer and energy consumption.

[0009] In the heat exchange plate described above, the cross-sectional area of ​​the arch gradually decreases from the bottom surface to the top surface; Alternatively, the cross-sectional area of ​​the arch gradually increases from the bottom surface to the top surface; Alternatively, the cross-sectional area of ​​the arch remains constant from the bottom to the top. A gradual decrease in cross-sectional area from bottom to top reduces the size of the top section of the arch, increasing fluid velocity and decreasing pressure, enhancing turbulence, disrupting the thermal boundary layer, and improving heat transfer efficiency. It also reduces fluid stagnation in the channel, preventing localized fouling. A gradual increase in cross-sectional area from bottom to top expands the cross-section, slowing the flow velocity, reducing localized eddies, and significantly lowering pressure drop. This is suitable for energy-sensitive scenarios and avoids concentrated scouring, ensuring balanced utilization of the heat exchange surface, reducing localized wear or corrosion, and improving system stability. A constant cross-sectional area results in pressure drop and heat transfer efficiency between the two options, with a simple structure, minimal processing requirements, suitability for standardized production, and uniform heat distribution during welding, reducing the risk of incomplete welds or deformation. It offers broad adaptability to fluid types and velocity variations, making it a more universal design solution.

[0010] In the aforementioned heat exchange plate, the depth of the connecting groove is less than the depth of the first fluid groove and the second fluid groove. The shallower depth of the connecting groove compared to the main channel avoids excessive cutting of the first strip-shaped protrusion, preserving the integrity of its main structure and ensuring resistance to deformation under high-pressure fluid. Furthermore, when the two plates are welded together using an arched design, the shallow groove reduces weakening of the weld area, improving overall sealing and pressure-bearing reliability.

[0011] In the aforementioned heat exchange plate, the depth of the connecting groove is 0.05-0.5 times the depth of the second fluid groove. Setting the shallow groove depth to 0.05-0.5 times the main channel depth ensures necessary inter-channel connectivity while avoiding a sudden drop in flow velocity due to an excessively large flow cross-sectional area, thus reducing ineffective pressure drop losses. Furthermore, excessively deep grooves are prone to generating backflow vortices at the bottom; this design also suppresses vortex formation, reducing energy loss.

[0012] In the aforementioned heat exchange plate, the axis C of the connecting groove is inclined or perpendicular to the axis D of the first fluid groove. When the fluid passes through the inclined groove, it rotates, forming secondary eddies that can disrupt the thermal boundary layer on the channel wall, thus improving the heat transfer coefficient. The jet impacts the opposite channel wall perpendicularly, forming a high-turbulence stagnation zone, suitable for enhanced cooling in areas with localized high heat loads.

[0013] In the heat exchange plate described above, the arched cross-section is any one of rectangular, circular, elliptical, crescent-shaped, dumbbell-shaped, or S-shaped. When the cross-section of the arch is rectangular, crescent-shaped, or S-shaped, the axis A of the arch is parallel to or inclined to the axis B of the first strip-shaped protrusion. Different cross-sectional shapes of the arch can adapt to different working conditions, balancing the corresponding pressure-bearing capacity, heat exchange capacity, structural reliability, and manufacturing cost, thereby enabling the product to have good heat exchange performance in different application scenarios.

[0014] In the aforementioned heat exchange plate, the first and second fluid grooves are either straight or corrugated. Fluid encounters less resistance when flowing in straight channels, reducing operating costs. Furthermore, straight channels are easier to process and shape, simplifying mold design and manufacturing, which helps reduce production costs. The corrugated groove structure disrupts the laminar boundary layer of the fluid within the channel, promoting more efficient heat transfer from the fluid core and thus improving heat transfer efficiency. Additionally, the corrugated structure creates additional crests and troughs within the channel, providing more heat exchange surface area.

[0015] In the aforementioned heat exchange plate, the first and second fluid grooves have V-shaped cross-sections, with the sides of the V-shape being straight, curved, or a combination of straight and curved lines. When two heat exchange plates with V-shaped channels are welded together, a V-shaped flow channel network is formed. This structure allows the heat exchange plate as a whole to maintain a large average temperature difference, thereby significantly improving the overall heat exchange efficiency.

[0016] In the aforementioned heat exchange plates, the locations of the raised and recessed sections are interchangeable. Even after interchange, the fundamental working principle—using the raised structures to turbulent the flow and the connecting grooves to create channels—remains unchanged, ensuring the effectiveness of the design. This allows for the selection of different plate combinations during assembly, providing greater flexibility to better adapt to different flow patterns and efficiency requirements.

[0017] This heat exchanger includes two heat exchange plates as described above. The two heat exchange plates are connected by welding through arches, and the arches of one heat exchange plate are arranged symmetrically or crosswise with respect to the arches of the other heat exchange plate. Alternatively, the two ends of the arch of one heat exchange plate are respectively set on the two adjacent arches of another heat exchange plate.

[0018] By using weld points arranged at intervals, welding stress can be dispersed, reducing the risk of localized deformation and improving the overall structural rigidity and pressure resistance. This simultaneously enhances both co-current and counter-current flow, resulting in improved strength while further enhancing heat transfer capacity.

[0019] In the heat exchanger described above, the arched shapes of the two heat exchange plates may be the same or different. By welding the same or different heat exchange plates together to form the heat exchanger, a wider variety of flow channel shapes can be created, allowing the heat exchanger to adapt to more diverse operating conditions and further enhancing its flexibility and applicability.

[0020] Compared with existing technologies, the advantages of this heat exchange plate and the heat exchanger using it are: 1. It can enhance fluid turbulence, resulting in better heat transfer between the fluids on both sides. 2. It effectively balances structural strength and heat transfer effect, further enhancing heat transfer while improving strength. 3. It has a larger effective heat transfer area. 4. The special structure increases vaporization nuclei, promoting the boiling heat transfer of the refrigerant. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the heat exchange plate structure provided by this utility model.

[0022] Figure 2 This is a schematic diagram of the front structure of the heat exchange plate provided by this utility model.

[0023] Figure 3 This is a schematic diagram of the reverse side structure of the heat exchange plate provided by this utility model.

[0024] Figure 4 This is a schematic diagram of the side structure of the heat exchange plate provided by this utility model.

[0025] Figure 5 This is a schematic diagram of the heat exchanger structure provided by this utility model.

[0026] Figure 6 This is a schematic diagram of the side structure of the heat exchanger provided by this utility model.

[0027] Figure 7 This is a schematic diagram of the heat exchange plate structure in Embodiment 2 of this utility model.

[0028] Figure 8 This is a schematic diagram of the heat exchanger structure according to Embodiment 2 of this utility model.

[0029] Figure 9 This is a schematic diagram of the arched connection structure of Embodiment 3 provided by this utility model.

[0030] Figure 10 This is a schematic diagram of the arched connection structure of Embodiment 4 provided by this utility model.

[0031] Figure 11 This is a schematic diagram of the arched connection structure of Embodiment 5 provided by this utility model.

[0032] In the figure, there is a plate 1, a first fluid groove 11, a second fluid groove 12, a first strip protrusion 13, a heat exchange unit 2, an arch 21, a connecting groove 22, a recess 23, and a heat exchange plate 3. Detailed Implementation Example 1

[0033] like Figures 1 to 4 As shown, this heat exchange plate includes a plate body 1. The plate body 1 is provided with at least two spaced first strip-shaped protrusions 13. A first fluid groove 11 is provided between two adjacent first strip-shaped protrusions 13. A second fluid groove 12 is provided on the back side of the plate body 1 on the first strip-shaped protrusions 13. A heat exchange unit 2 is provided on the top surface of the first strip-shaped protrusions 13. The heat exchange unit 2 includes a plurality of arches 21 spaced along the length direction on the top surface of the first strip-shaped protrusions 13. A connecting groove 22 for connecting two adjacent first fluid grooves 11 is provided between two adjacent arches 21. The back of the arch 21 is provided with a recess 23 located in the second fluid groove 12 and corresponding to the connecting groove 22.

[0034] In this embodiment, adjacent first fluid grooves 11 are separated on the front side of the plate 1 by a first strip-shaped protrusion 13, and a heat exchange unit 2 is provided on the top surface. The effective heat transfer area is further expanded by the alternating arches 21 and connecting grooves 22, and the fluid boundary layer is broken to enhance fluid disturbance. On the back side of the plate 1, the sidewalls of the first fluid grooves 11 and the first strip-shaped protrusion 13 together form the outer wall of the second fluid groove 12. The arches 21 on the front side and the recesses 23 on the back side, located in the second fluid groove 12 and corresponding to the connecting grooves 22, simultaneously disturb the fluid on both sides, thereby enhancing the overall heat exchange effect on both sides.

[0035] More specifically, the arches 21 on the two adjacent first strip-shaped protrusions 13 are aligned and distributed along the length direction.

[0036] More specifically, the cross-sectional area of ​​the arch 21 gradually decreases from the bottom surface to the top surface.

[0037] like Figure 4 As shown, the depth of the connecting groove 22 is less than the depth of the first fluid groove 11 and the second fluid groove 12. The depth H1 of the connecting groove 22 is 0.17 times the depth H2 of the second fluid groove 12.

[0038] like Figure 2 As shown, the axis C of the connecting groove 22 is inclined to the axis D of the first fluid groove 11. The cross-section of the arch 21 is rectangular, and the axis A of the arch 21 is parallel to or inclined to the axis B of the first strip protrusion 13.

[0039] More specifically, the first fluid groove 11 and the second fluid groove 12 are straight. The cross-section of the first fluid groove 11 and the second fluid groove 12 is V-shaped, and the two sides of the V-shape are straight, curved, or a combination of straight and curved shapes.

[0040] like Figure 5 and 6 As shown, this heat exchanger includes two heat exchange plates 3 as described above. The two heat exchange plates 3 are welded together by arches 21, and the arches 21 of one heat exchange plate 3 are symmetrically arranged relative to the arches 21 of the other heat exchange plate 3. The arches (21) of the two heat exchange plates (3) have the same shape.

[0041] In this embodiment, two heat exchange plates 3 are arranged symmetrically, and the top surfaces of the arches 21 of the two heat exchange plates 3 are in contact with each other and welded together, forming a closed flow channel between the two heat exchange plates 3. Example 2

[0042] This embodiment is basically the same as embodiment one, except that, as follows: Figure 7 and 8 As shown, the cross-section of the arch 21 of this heat exchange plate is S-shaped. This heat exchanger includes two heat exchange plates 3 as described above. The two heat exchange plates 3 are welded together by the arch 21, and the arch 21 of one heat exchange plate 3 is arranged to cross the arch 21 of the other heat exchange plate 3.

[0043] In this embodiment, the S-shaped arch 21, through its structural design, extends the fluid residence time and disperses impact loads via a curved flow channel, preventing breakage and extending service life. The zigzag flow channel formed by the staggered arch 21 forces the fluid to change direction multiple times, further disrupting the boundary layer and improving heat transfer efficiency. Example 3

[0044] This embodiment is basically the same as embodiment two, except that, as follows: Figure 9 As shown, this heat exchanger includes two heat exchange plates 3, and the two ends of the arch 21 of one heat exchange plate 3 are respectively set on the two adjacent arches 21 of the other heat exchange plate 3.

[0045] In this embodiment, the two ends of the S-shaped arch 21 are welded to the adjacent arch, which extends the flow channel and makes the pressure-bearing capacity stronger. Example 4

[0046] This embodiment is basically the same as embodiment one, except that, as follows: Figure 10 As shown, this heat exchanger includes two heat exchange plates 3, with the arches 21 of one heat exchange plate 3 arranged crosswise relative to the arches 21 of the other heat exchange plate 3.

[0047] In this embodiment, the staggered arrangement of the intersecting arches 21 allows the fluid to continuously redirect and impact the wall, improving heat exchange efficiency. Furthermore, the intersecting arches 21 can disperse stress, resist vibration fatigue, and extend service life. Example 5

[0048] This embodiment is basically the same as embodiment one, except that, as follows: Figure 11 As shown, this heat exchanger includes two heat exchange plates 3, and the two ends of the arch 21 of one heat exchange plate 3 are respectively set on the two adjacent arches 21 of the other heat exchange plate 3.

[0049] In this embodiment, the two ends of the arch 21 are welded to the beginning and end of the adjacent arch 21. Under the action of external forces such as thermal expansion and contraction, this structure can suppress the displacement between the plates and improve the sealing reliability.

[0050] The working principle of the above embodiment is that the fluid enters the closed flow channel in the gap between the two heat exchange plates 3 through the edge of the heat exchanger. Inside the closed flow channel, the first fluid groove 11 is located on the front side of the plate 1, and the second fluid groove 12 is located on the back side of the plate 1, respectively guiding the fluid flow and exchanging heat through the wall of the plate 1.

[0051] During the heat exchange process, the flow of fluid is regulated by the arch 21, the connecting groove 22 and the depression 23.

[0052] When fluid impacts the arch 21, it disrupts the fluid boundary layer and enhances heat transfer within the first fluid groove 11. When flowing through the depression 23, the forced fluid flow separation generates turbulent vortices that disrupt the thermal boundary layer, creating flow resistance and turbulence within the second fluid groove 12, thus increasing the heat transfer area. Simultaneously, the special structures of the arch 21 and depression 23 form vaporization nuclei, promoting boiling heat transfer of the refrigerant and further enhancing heat transfer efficiency.

[0053] Furthermore, the connecting groove 22 promotes the lateral flow of fluid between adjacent first fluid grooves 11, extends the heat exchange process, realizes three-dimensional mixing of fluid to eliminate temperature stratification, enhances the uniformity of heat exchange, and ultimately achieves a stronger heat exchange effect.

[0054] The specific embodiments described herein are merely illustrative examples illustrating the spirit of this utility model. Those skilled in the art to which this utility model pertains may make various modifications or additions to the described specific embodiments or use similar methods to substitute them, without departing from the spirit of this utility model or exceeding the scope defined by the appended claims.

[0055] Although this document frequently uses terms such as plate, first fluid groove, second fluid groove, first strip protrusion, heat exchange unit, arch, connecting groove, recess, and heat exchange plate, the possibility of using other terms is not excluded. These terms are used merely for the convenience of describing and explaining the essence of this utility model; interpreting them as any additional limitation would contradict the spirit of this utility model.

Claims

1. A heat exchange plate, comprising a plate body (1), wherein the plate body (1) is provided with at least two spaced-apart first strip-shaped protrusions (13), a first fluid groove (11) is provided between adjacent two first strip-shaped protrusions (13), and a second fluid groove (12) is provided on the back side of the first strip-shaped protrusions (13) of the plate body (1), characterized in that, The top surface of the first strip protrusion (13) is provided with a heat exchange unit (2). The heat exchange unit (2) includes at least two arches (21) that are spaced apart along the length direction on the top surface of the first strip protrusion (13). A connecting groove (22) for connecting two adjacent first fluid grooves (11) is provided between two adjacent arches (21). The arch (21) has a recess (23) on its back side located in the second fluid groove (12) and corresponding to the connecting groove (22).

2. The heat exchange plate according to claim 1, characterized in that, The arches (21) on the two adjacent first strip protrusions (13) are staggered or aligned along the length direction.

3. The heat exchange plate according to claim 1, characterized in that, The cross-sectional area of ​​the arch (21) gradually decreases from the bottom surface to the top surface; Alternatively, the cross-sectional area of ​​the arch (21) gradually increases from the bottom surface to the top surface; Alternatively, the cross-sectional area of ​​the arch (21) remains constant from the bottom to the top.

4. The heat exchange plate according to claim 1, characterized in that, The depth of the connecting groove (22) is less than the depth of the first fluid groove (11) and the second fluid groove (12).

5. The heat exchange plate according to claim 4, characterized in that, The depth of the connecting groove (22) is 0.05-0.5 times the depth of the second fluid groove (12).

6. The heat exchange plate according to claim 1, characterized in that, The axis C of the connecting groove (22) is inclined or perpendicular to the axis D of the first fluid groove (11).

7. The heat exchange plate according to any one of claims 1-6, characterized in that, The cross-section of the arch (21) or the connecting groove (22) is any one of rectangular, circular, elliptical, crescent-shaped, dumbbell-shaped or S-shaped; When the cross-section of the arch (21) is rectangular, crescent-shaped or S-shaped, the axis A of the arch (21) is parallel or inclined to the axis B of the first strip protrusion (13).

8. The heat exchange plate according to any one of claims 1-6, characterized in that, The first fluid groove (11) and the second fluid groove (12) are either straight or corrugated.

9. The heat exchange plate according to any one of claims 1-6, characterized in that, The first fluid groove (11) and the second fluid groove (12) have V-shaped cross sections, with the two sides of the V-shape being straight, curved, or a combination of straight and curved lines.

10. The heat exchange plate according to any one of claims 1-6, characterized in that, The locations of the arch (21) and the depression (23) can be interchanged.

11. A heat exchanger, characterized in that, It includes two heat exchange plates (3) as described in any one of claims 1-10, the two heat exchange plates (3) are welded together by arches (21), and the arches (21) of one heat exchange plate (3) are symmetrically or crosswise arranged with respect to the arches (21) of the other heat exchange plate (3); Alternatively, the two ends of the arch (21) of one heat exchange plate (3) are respectively set on the two adjacent arches (21) of another heat exchange plate (3).

12. The heat exchanger according to claim 11, characterized in that, The arches (21) of the two heat exchange plates (3) may have the same or different shapes.

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