Heat exchange plate and heat exchanger using same
By designing staggered or aligned throttling grooves and protrusions on the heat exchange plate, the thermal boundary layer is disrupted, promoting cross-flow of fluids. This solves the problem of insufficient flow disturbance in existing heat exchange plates, achieving more efficient heat exchange and structural strength.
Patent Information
- Application Number
- CN202511194147.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-08-25
- Publication Date
- 2025-11-18
Smart Images
Figure CN120970331A_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application belongs to the technical field of heat transfer, and relates to a heat exchange device, in particular to a heat exchange plate and a heat exchanger using the same. BACKGROUND
[0002] The heat exchange plate is a heat exchange element made of metal plate. It realizes efficient heat transfer through fluid flow between the plates, and is used for heat exchange between different media. In the prior art, the plates are mostly stacked in a herringbone wave shape, and the wave peaks of one plate and the wave valleys of another plate are cross-lapped to form welding points. Most of the wave peak convex surfaces and the wave valley concave surfaces have an equal width structure, and the convex surfaces and the concave surfaces are both single flat and smooth planes.
[0003] The size of the welding points is generally adjusted by adjusting the width of the waves, but the smooth convex surfaces will cause insufficient heat exchange disturbance. Moreover, simply increasing the width of the convex surfaces will indeed increase the welding point area and thus the strength when cross-lapped, but it will also reduce the effective heat exchange area and thus weaken the heat exchange effect. In addition, the smooth convex surfaces make the fluid flow only around the welding points, which causes insufficient disturbance to the fluid flow and heat exchange, and thus poor heat exchange effect. SUMMARY
[0004] The purpose of the present application is to provide a heat exchange plate with stronger heat exchange effect in view of the above problems.
[0005] Another purpose of the present application is to provide a heat exchanger in view of the above problems.
[0006] To achieve the above purposes, the present application adopts the following technical scheme: the heat exchange plate comprises a plate body, a plurality of first convex bodies are arranged on the plate body and distributed along the direction from the inlet to the outlet, a first fluid groove is formed between two adjacent first convex bodies, a second fluid groove is arranged on the back surface of the plate body at the first convex body, and at least two rows of throttling heat exchange structures are arranged on the top of the first convex body and distributed along the width direction of the first convex body; each row of throttling heat exchange structures comprises N throttling convexities which are spaced apart along the length direction of the first convex body, N≥2, a throttling groove is arranged between two adjacent throttling convexities along the length direction, a flow guide groove is arranged between two adjacent throttling convexities along the width direction and communicates with the throttling groove, and the first fluid groove communicates with the throttling groove and the flow guide groove through the throttling groove. The back surface of the first convex body is provided with an arch convexity and a strip-shaped arch which are located in the second fluid groove and correspond to the throttling groove and the flow guide groove, respectively.
[0007] By spaced throttling protrusions and grooves along the length, periodic fluid channels are formed. As the fluid flows through these channels, acceleration and deceleration effects occur, disrupting the stability of the thermal boundary layer, reducing thermal resistance, and thus improving heat transfer efficiency. Furthermore, the diversion grooves laterally connect adjacent throttling grooves, promoting fluid mixing in the width direction. This lateral mixing eliminates temperature gradients and improves overall heat transfer uniformity. The symmetrical design ensures that the fluid on both sides is simultaneously disturbed, achieving a synergistic enhancement of heat transfer on both sides.
[0008] In the aforementioned heat exchange plate, the throttling channels of adjacent rows of throttling heat exchange structures are staggered along the length of the structure. This staggered distribution forces the fluid to deflect in alternating directions, eliminating the directional flow inertia of traditional parallel channels. Eddy shearing is then utilized to improve heat exchange efficiency.
[0009] In the heat exchange plate described above, the central axes of two adjacent throttling slots in two adjacent rows of throttling heat exchange structures coincide. The aligned throttling slots form a continuous channel, keeping the fluid in a stable flow velocity state, avoiding kinetic energy dissipation caused by misalignment design, and are more suitable for low power consumption scenarios.
[0010] In the aforementioned heat exchange plate, the central axes of the throttling grooves of two adjacent first protrusions coincide, or they are staggered along the length of the first protrusions. Through the aforementioned flow disturbances, boundary layer disruption, and bilateral interaction, both arrangements improve the overall heat exchange effect. The staggered arrangement is more advantageous in promoting lateral mixing and temperature uniformity, resulting in a more balanced heat exchange effect. The coincident arrangement makes the fluid flow more coherent in the direction of flow. This helps the fluid to more effectively impact the lower heat exchange surface, enhancing local turbulence and heat exchange intensity.
[0011] In the aforementioned heat exchange plate, the cross-sectional area of the throttling groove gradually increases or decreases from the bottom to the top. The gradual decrease in cross-sectional area from bottom to top reduces the size of the arched top section, increasing the fluid velocity and decreasing the pressure as it passes through, enhancing turbulence intensity, disrupting the thermal boundary layer, and contributing to improved heat exchange efficiency. Furthermore, it reduces fluid retention within the channel, preventing localized fouling. Conversely, the 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 applications and avoids concentrated scouring, ensuring balanced utilization of the heat exchange surface, reducing localized wear or corrosion, and improving system operational stability. In the heat exchange plate described above, the depth of the throttling groove is 0.05-0.5 times the depth of the second fluid groove. Setting the depth of the throttling groove to 0.05-0.5 times the depth of the second fluid groove 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.
[0012] In the aforementioned heat exchange plate, the depth of the throttling groove is less than the depth of the first fluid groove and the second fluid groove, while the depth of the throttling groove is greater than, less than, or equal to the depth of the guide groove. The purpose of the throttling groove depth being less than the main groove depth is to generate a throttling effect, significantly increasing the fluid velocity and forming a high-speed jet, thereby disrupting the boundary layer, enhancing turbulence and mixing, and ultimately improving local heat transfer efficiency. Simultaneously, the design allowing the throttling groove depth to be greater than, less than, or equal to the guide groove depth provides flexibility to adapt to different operating conditions, enabling fine-tuning of heat transfer performance and pressure drop.
[0013] In the aforementioned heat exchange plate, the cross-section of the throttling groove and / or throttling protrusion is any one of rectangular, circular, elliptical, crescent-shaped, dumbbell-shaped, or S-shaped. Different cross-sectional shapes can adaptably balance the corresponding pressure-bearing capacity, heat exchange capacity, structural reliability, and manufacturing cost for different operating conditions, 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 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.
[0015] In the aforementioned heat exchange plate, the first fluid groove can be linear, curved, or a combination of both. Curved grooves can induce the fluid to generate helical flow energy perpendicular to the mainstream direction, disrupting the thermal boundary layer. This promotes radial mixing of the fluid within the channel cross-section, resulting in a more uniform temperature distribution. Furthermore, it extends the actual flow distance of the fluid on the plate, thus prolonging the heat exchange time.
[0016] In the aforementioned heat exchange plate, the distribution positions of the throttling grooves and throttling protrusions are interchangeable with those of the arched protrusions and strip arches. This interchangeability does not alter the basic working principle, ensuring the effectiveness of the design. It also allows for the selection and combination of different plates 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, with throttling protrusions on the two heat exchange plates arranged symmetrically and welded together. Alternatively, the throttling protrusions of one heat exchange plate can be staggered relative to the throttling protrusions 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 load-bearing capacity. Furthermore, it enhances heat exchange capacity while improving strength.
[0019] In the heat exchanger described above, the throttling protrusions of the two heat exchange plates may have the same or different shapes. 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. 5. It has better heat transfer uniformity and more stable heat transfer effect. Attached Figure Description
[0021] Figure 1 This is a schematic diagram of the heat exchange plate structure provided by the present invention.
[0022] Figure 2 This is a schematic diagram of the front structure of the heat exchange plate provided by the present invention.
[0023] Figure 3 This is a schematic diagram of the reverse side structure of the heat exchange plate provided by the present invention.
[0024] Figure 4 This is a schematic diagram of the side structure of the heat exchange plate provided by the present invention.
[0025] Figure 5 This is a schematic diagram of the heat exchanger structure provided by the present invention.
[0026] Figure 6 This is a schematic diagram of the front structure of the heat exchanger provided by the present invention.
[0027] Figure 7 This is a schematic diagram of the side structure of the heat exchanger provided by the present invention.
[0028] Figure 8 This is a schematic diagram of the front structure of the heat exchange plate in Embodiment 2 of the present invention.
[0029] Figure 9 This is a schematic diagram of the heat exchange plate structure in Embodiment 3 of the present invention.
[0030] Figure 10 This is a schematic diagram of the back structure of the heat exchange plate in Embodiment 3 of the present invention.
[0031] Figure 11 This is a schematic diagram of the heat exchange plate structure in Embodiment 4 of the present invention.
[0032] Figure 12This is a schematic diagram of the front structure of the heat exchange plate in Embodiment 4 of the present invention.
[0033] Figure 13 This is a schematic diagram of the throttling protrusion connection structure of Embodiment 4 provided by the present invention.
[0034] Figure 14 This is a schematic diagram of the throttling protrusion connection structure of Embodiment 5 provided by the present invention.
[0035] Figure 15 This is a schematic diagram of the throttling protrusion connection structure of Embodiment Six provided by the present invention.
[0036] Figure 16 This is a schematic diagram of the front structure of the heat exchange plate in Embodiment 7 of the present invention.
[0037] Figure 17 This is a partial structural diagram of the heat exchanger provided in Embodiment 8 of the present invention.
[0038] Figure 18 This is a partial structural diagram of the heat exchange plate in Embodiment Nine of the present invention.
[0039] Figure 19 This is a partial structural diagram of the heat exchange plate in Embodiment 10 of the present invention.
[0040] Figure 20 This is a partial structural diagram of the heat exchange plate in Embodiment Eleven of the present invention.
[0041] In the figure, there are plate 1, first fluid groove 11, second fluid groove 12, first protrusion 13, throttling heat exchange structure 2, throttling protrusion 21, throttling groove 22, diversion groove 23, arch protrusion 24, strip arch 25, and heat exchange plate 3. Detailed Implementation Example 1
[0042] like Figures 1 to 4 As shown, this heat exchange plate includes a plate body 1. The plate body 1 is provided with a plurality of first protrusions 13 distributed along the inlet to outlet direction. A first fluid groove 11 is formed between two adjacent first protrusions 13. A second fluid groove 12 is provided on the back side of the first protrusions 13 on the plate body 1. Two rows of throttling heat exchange structures 2 are provided on the top of the first protrusions 13 along their width direction. Each row of throttling heat exchange structures 2 includes a plurality of throttling protrusions 21 spaced apart along the length direction of the first protrusions 13. A throttling groove 22 is provided between two adjacent throttling protrusions 21 along the length direction. A guide groove 23 communicating with the throttling groove 22 is provided between two adjacent throttling protrusions 21 in the width direction. The first fluid groove 11 is connected to the guide groove 23 through the throttling groove 22. The back of the first protrusion 13 is provided with an arched protrusion 24 and a strip arch 25 located in the second fluid groove 12 and corresponding to the throttling groove 22 and the diversion groove 23, respectively.
[0043] In this embodiment, two rows of throttling heat exchange structures 2 are added to the top of the first protrusion 13. The structures of the throttling protrusions 21, throttling grooves 22, and guiding grooves 23 generate additional surface area. The arched protrusions 24 and strip arches 25 on the back side further increase the heat exchange area of the second fluid groove 12. This has the effect of increasing the heat exchange area of the flow channels on both sides. Furthermore, when the fluid flows through the first fluid groove 11 between adjacent throttling protrusions 21 in the width direction and between adjacent throttling protrusions 21 in the length direction, the flow direction and velocity will continuously change. These drastic changes in flow direction and velocity will induce turbulence. Turbulence can effectively disrupt the temperature boundary layer formed between the fluid and the wall, thereby improving the heat exchange effect.
[0044] In this embodiment, the first protrusion 13 and the first fluid groove 11 are arranged parallel to each other at intervals, and the length direction and width direction of the first protrusion 13 are the same as the length direction and width direction of the first fluid groove 11.
[0045] More specifically, the central axes of two adjacent throttling grooves 22 of two adjacent rows of throttling heat exchange structures 2 coincide. The central axes of the throttling grooves 22 of two adjacent first protrusions 13 coincide.
[0046] like Figure 4 As shown, the cross-sectional area of the throttling groove 22 gradually increases from the bottom surface to the top surface, and the depth of the throttling groove 22 is 0.17 times the depth of the second fluid groove 12.
[0047] More specifically, the depth of the throttling groove 22H1 is less than the depth H2 of the first fluid groove 11 and the depth H3 of the second fluid groove 12, and the depth of the throttling groove 22 is equal to the depth H4 of the diversion groove 23.
[0048] More specifically, the cross-sections of the throttling groove 22 and the throttling protrusion 21 are rectangular.
[0049] More specifically, the cross-sections of the first fluid groove 11 and the second fluid groove 12 are V-shaped, with straight lines on both sides of the V-shape. The first fluid groove 11 is straight.
[0050] like Figures 5 to 7 As shown, this heat exchanger includes two heat exchange plates 3 as described above. The throttling protrusions 21 of the two heat exchange plates 3 are symmetrically arranged and welded together. The throttling protrusions 21 of the two heat exchange plates 3 have the same shape. Example 2
[0051] This embodiment is basically the same as embodiment one, except that, as follows: Figure 8As shown, the throttling grooves 22 of the two adjacent rows of throttling heat exchange structures 2 are staggered along the length of the throttling heat exchange structure 2.
[0052] In this embodiment, adjacent rows of throttling grooves 22 are staggered along the length direction, forcing the fluid to frequently change direction in the width direction, breaking the inertia of directional flow and generating stronger eddies. This disordered disturbance more thoroughly destroys the thermal boundary layer, enhances turbulent mixing, and can further improve heat transfer efficiency. Example 3
[0053] This embodiment is basically the same as embodiment one, except that, as follows: Figure 9 and 10 As shown, the central axes of the throttling grooves 22 of two adjacent first protrusions 13 are staggered along the length of the first protrusion 13. Furthermore, the distribution positions of the throttling grooves 22 and the throttling protrusions 21 are interchanged with the distribution positions of the arch protrusions 24 and the strip arches 25.
[0054] In this embodiment, the throttling grooves 22 of adjacent first protrusions 13 are staggered to improve lateral fluid mixing, eliminate temperature stratification, and make heat exchange more uniform. The interchangeability of the front and back structures can provide a differentiated flow channel morphology for the second fluid concave 12 on the back side. Example 4
[0055] This embodiment is basically the same as embodiment one, except that, as follows: Figures 11 to 13 As shown, the throttling protrusions 21 of the throttling heat exchange structure 2 are distributed at intervals along the length direction of the first protrusion body 13, and the axial direction of the throttling protrusions 21 is at a certain angle to the length direction of the first protrusion body 13.
[0056] More specifically, the throttling grooves 22 of the two adjacent rows of throttling heat exchange structures 2 are staggered along the length of the throttling heat exchange structure 2.
[0057] This heat exchanger includes two heat exchange plates 3, with the throttling protrusions 21 of one heat exchange plate 3 being staggered relative to the throttling protrusions 21 of the other heat exchange plate 3.
[0058] More specifically, the beginning and end of the throttling protrusion 21 of one heat exchange plate 3 are welded to the end and beginning of the corresponding throttling protrusion 21 of another heat exchange plate 3, respectively.
[0059] In this embodiment, the inclined throttling protrusion 21 can induce lateral velocity components, significantly enhancing radial mixing and boundary layer disruption. The staggered welding method results in a more dispersed weld point distribution, more uniform stress, and higher compressive strength. Example 5
[0060] This embodiment is basically the same as embodiment four, except that, as follows: Figure 14As shown, the middle part of the throttling protrusion 21 of one heat exchange plate 3 is welded to the middle part of the corresponding throttling protrusion 21 of another heat exchange plate 3.
[0061] In this embodiment, the welding point is located in the middle of the throttling protrusion 21, making the connection more robust, especially suitable for high-voltage conditions. At the same time, the vibration risk can be constrained by the central fixing point. Example 6
[0062] This embodiment is basically the same as embodiment four, except that, as follows: Figure 15 As shown, the throttling protrusion 21 of one heat exchange plate 3 is overlapped and welded to the corresponding throttling protrusion 21 of another heat exchange plate 3.
[0063] In this embodiment, the throttling protrusions 21 connected by overlapping welding maximize the welding area, providing stronger structural rigidity and pressure resistance. Example 7
[0064] This embodiment is basically the same as embodiment one, except that, as follows: Figure 16 As shown, the cross-section of the first fluid groove 11 and the second fluid groove 12 is V-shaped, with curved sides.
[0065] In this embodiment, the side walls of the V-shaped first fluid groove 11 and the second fluid groove 12 are curved, which can better guide the fluid to smoothly change direction, reduce flow separation and eddy current dissipation, and significantly reduce pressure drop. Furthermore, it avoids scaling in right-angle areas, ensuring long-term stable operation. Example 8
[0066] This embodiment is basically the same as embodiment one, except that, as follows: Figure 17 As shown, the cross-section of the throttling protrusion 21 is S-shaped.
[0067] In this embodiment, the cross-section of the throttling protrusion 21 is S-shaped. The S-shaped profile can provide a more continuous curvature change, which is beneficial to increasing the effective heat exchange area per unit volume. Example 9
[0068] This embodiment is basically the same as embodiment one, except that, as follows: Figure 18 As shown, the cross-section of the throttling protrusion 21 is circular.
[0069] In this embodiment, the throttling protrusion 21 has a circular cross-section, the separation point is fixed when the fluid flows around it, the wake region is small, and the pressure drop is minimal. Furthermore, the stress distribution is uniform, resulting in good fatigue resistance. Example 10
[0070] This embodiment is basically the same as embodiment nine, except that, as follows: Figure 19As shown, the drainage channel 23 is an S-shaped channel.
[0071] In this embodiment, based on the circular throttling protrusion 21, the flow channel 23 is changed to an S-shape. The S-shaped flow channel 23 can drive the fluid to oscillate back and forth in the width direction, thereby enhancing lateral mixing and temperature uniformity. Example 11
[0072] This embodiment is basically the same as embodiment ten, except that, as Figure 20 As shown, the first fluid groove 11 is curved.
[0073] In this embodiment, the main flow channel of the curve can extend the flow path and increase the heat exchange time. Combined with the S-shaped guide channel 23, local lateral pulsations are further superimposed to achieve multi-scale mixing.
[0074] 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.
[0075] During the heat exchange process, the flow of fluid is regulated by the throttling protrusion 21, throttling groove 22 and flow guiding groove 23 on the front first protrusion 13 and the arched protrusion 24 and strip arch 25 in the back second fluid groove 12.
[0076] When fluid impacts the throttling protrusion 21, it disrupts the fluid boundary layer and enhances heat transfer within the first fluid groove 11. When flowing through the throttling groove 22 and the flow channel 23, the forced fluid flow separation generates turbulent vortices that disrupt the thermal boundary layer. Simultaneously, within the second fluid groove 12, the arched protrusion 24 and the strip arch 25 create flow resistance and turbulence, increasing the heat transfer area.
[0077] Furthermore, by connecting the first fluid grooves 11 on both sides through the throttling groove 22 and the diversion groove 23, the fluid is promoted to flow laterally between adjacent first fluid grooves 11, the heat exchange process is extended, the three-dimensional mixing of the fluid is realized to eliminate temperature stratification, enhance the uniformity of heat exchange, and ultimately achieve a stronger heat exchange effect.
[0078] The specific embodiments described herein are merely illustrative of the spirit of the invention. Those skilled in the art to which this invention 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 the invention or exceeding the scope defined by the appended claims.
[0079] Although this document frequently uses terms such as plate, first fluid groove, second fluid groove, first protrusion, throttling heat exchange structure, throttling protrusion, throttling groove, diversion groove, arched protrusion, strip arch, 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 the invention, and interpreting them as any additional limitation would contradict the spirit of the invention.
Claims
1. A heat exchange plate, comprising a plate body (1), wherein the plate body (1) is provided with a plurality of first protrusions (13) distributed along the inlet to outlet direction, a first fluid groove (11) is formed between two adjacent first protrusions (13), and a second fluid groove (12) is provided on the back side of the first protrusions (13) of the plate body (1), characterized in that, The top of the first protrusion (13) is provided with at least two rows of throttling heat exchange structures (2) distributed along its width direction; each row of throttling heat exchange structures (2) includes N throttling protrusions (21) spaced apart along the length direction of the first protrusion (13), N≥2, a throttling groove (22) is provided between two adjacent throttling protrusions (21) along the length direction, and a flow guide groove (23) communicating with the throttling groove (22) is provided between two adjacent throttling protrusions (21) in the width direction, and the first fluid groove (11) is connected to the flow guide groove (23) through the throttling groove (22); The back of the first protrusion (13) is provided with an arch protrusion (24) and a strip arch (25) located in the second fluid groove (12) and corresponding to the throttling groove (22) and the diversion groove (23) respectively.
2. The heat exchange plate according to claim 1, characterized in that, The throttling grooves (22) of the two adjacent rows of throttling heat exchange structures (2) are staggered along the length of the throttling heat exchange structure (2).
3. The heat exchange plate according to claim 1, characterized in that, The central axes of the two adjacent throttling grooves (22) of the two adjacent rows of throttling heat exchange structures (2) coincide.
4. The heat exchange plate according to claim 3, characterized in that, The central axes of the throttling grooves (22) of two adjacent first protrusions (13) coincide or are staggered along the length of the first protrusion (13).
5. The heat exchange plate according to claim 1, characterized in that, The cross-sectional area of the throttling groove (22) gradually increases or decreases from the bottom surface to the top surface.
6. The heat exchange plate according to claim 1, characterized in that, The depth of the throttling groove (22) is 0.05-0.5 times the depth of the second fluid groove (12).
7. The heat exchange plate according to any one of claims 1-6, characterized in that, The depth of the throttling groove (22) is less than the depth of the first fluid groove (11) and the second fluid groove (12), and the depth of the throttling groove (22) is greater than, less than or equal to the depth of the diversion groove (23).
8. The heat exchange plate according to any one of claims 1-6, characterized in that, The cross-section of the throttling groove (22) and / or throttling protrusion (21) is any one of rectangular, circular, elliptical, crescent-shaped, dumbbell-shaped or S-shaped.
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 first fluid groove (11) is a straight line, a curved line, or a hybrid of straight lines and curves.
11. The heat exchange plate according to any one of claims 1-6, characterized in that, The distribution positions of the throttling groove (22) and throttling protrusion (21) can be interchanged with the distribution positions of the arch protrusion (24) and strip arch (25).
12. A heat exchanger, characterized in that, It includes two heat exchange plates (3) as described in any one of claims 1-11, wherein the throttling protrusions (21) of the two heat exchange plates (3) are symmetrically arranged and welded together; Alternatively, the throttling protrusions (21) of one heat exchange plate (3) are staggered relative to the throttling protrusions (21) of another heat exchange plate (3).
13. The heat exchanger according to claim 12, characterized in that, The throttling protrusions (21) of the two heat exchange plates (3) may have the same or different shapes.