Heat exchange sheet and heat exchange plate

Abstract

The utility model provides a heat exchange sheet and a heat exchange plate, and belongs to the technical field of heat transfer. The technical problems that an existing heat exchange plate is irregular in welding spot structure, low in structural strength and low in heat exchange efficiency are solved. The heat exchange piece comprises a plate body, a plurality of V-shaped troughs distributed from one end to the other end are arranged on the plate body, V-shaped corrugated ridges are arranged on every two adjacent V-shaped troughs, and groove units distributed in the length direction of the V-shaped corrugated ridges are arranged on two supporting ridges of the V-shaped corrugated ridges. The groove unit comprises at least N groove groups distributed along the length direction of the branch ridge, N is greater than or equal to 1, each groove group comprises at least M grooves distributed along the length direction of the branch ridge, and M is greater than or equal to 1. The heat exchanger has the advantages of being low in production cost, not prone to damage, low in flow resistance, high in heat exchange efficiency, low in refrigerant filling amount and the like.

Description

Technical Field

[0001] The utility model belongs to the technical field of heat transfer, relates to a heat exchange device, and in particular to a heat exchange fin and a heat exchange plate. Background Art

[0002] A heat exchange plate is a heat exchange element made of sheet metal. It efficiently transfers heat through the flow of fluid between the plates, allowing for heat exchange between different media. Existing technology often uses herringbone corrugated plates, where the peaks of one plate overlap the troughs of another, forming welds. These welds are irregular, have a small overlap area, and are flat. This creates a high risk of cold welds during production, reducing product reliability. Summary of the Invention

[0003] The purpose of the utility model is to provide a heat exchange plate capable of improving welding quality in response to the above problems.

[0004] Another object of the present invention is to provide a heat exchange plate.

[0005] To achieve the above-mentioned purpose, the present invention adopts the following technical solutions: the heat exchange plate includes a plate body, the plate body is provided with a plurality of V-shaped troughs distributed from one end to the other end, two adjacent V-shaped troughs are provided with V-shaped corrugated ridges, and the two branch ridges of the V-shaped corrugated ridge are provided with groove units distributed along the length direction thereof, the groove unit includes at least N groove groups distributed along the length direction of the branch ridge, and N ≥ 1, and the groove group includes at least M grooves distributed along the length direction of the branch ridge, and M ≥ 1.

[0006] The alternating arrangement of V-shaped troughs and corrugated ridges helps to guide the flow path of the fluid, allowing the fluid to flow in a predetermined direction and reduce flow resistance. The multiple grooves spaced apart on the corrugated ridges increase the contact area between the plates during installation and use, thereby improving welding quality, increasing heat exchange efficiency, and strengthening the overall structural strength.

[0007] In the heat exchanger described above, all groove groups have the same groove depth. This uniform groove depth helps achieve more uniform heat transfer, which reduces thermal stress within the plate and reduces complexity and variability in the production process, improving production efficiency and product quality.

[0008] In the heat exchanger plate described above, when N > 1, the depth of each groove group is not unique. Groove groups of different depths can be optimized for different fluid characteristics. For fluids with higher viscosity, deeper grooves help increase the contact time between the fluid and the heat exchange plate surface, thereby improving heat exchange efficiency.

[0009] In the heat exchange plate described above, when M > 1, all grooves in each groove group have the same depth. Grooves of the same depth help achieve a more uniform heat transfer effect, and the entire heat exchange plate can still be adapted to different operating conditions by adjusting the number and distribution of groove groups.

[0010] In the heat exchanger described above, adjacent groove groups have different depths, while adjacent groove groups have the same depth. By designing groove groups of varying depths, the temperature gradient during the heat exchange process can be controlled. Deeper groove groups can handle more heat transfer, while shallower groove groups can slow the rate of temperature change to a certain extent, thereby optimizing the efficiency of the entire heat exchange process.

[0011] In the above heat exchanger plate, the groove units on the two branch ridges of the V-shaped corrugated ridge are symmetrically arranged. The symmetrical design of the groove units makes the overall mechanical structure more regular, which is conducive to improving the fit.

[0012] In the aforementioned heat exchanger, the two branch troughs of the V-shaped trough are parallel to the branch ridges of the V-shaped corrugated ridges. Grooves are provided on the outer walls of the branch troughs. The number of these troughs is equal to the number of grooves. The grooves on one plate correspond one-to-one with the grooves on another plate rotated 180 degrees horizontally, and the grooves and grooves interlock with each other. This one-to-one correspondence between the grooves and grooves facilitates control of the refrigerant charge and forms a regular flow path to reduce flow resistance.

[0013] In the aforementioned heat exchanger plate, the grooves have a slope angle of 70-150 degrees. Grooves designed within this slope angle range can enhance the heat exchange plate's ability to resist external impact and vibration, protecting it from damage. It also helps break up the thermal boundary layer during fluid flow, increasing the contact area between the fluid and the heat exchange plate surface, thereby improving heat exchange efficiency.

[0014] This heat exchange plate comprises several layers of stacked fins. The upper fin of two adjacent fins is connected to the lower fin, which has been rotated 180 degrees horizontally. The V-shaped troughs at the bottom of the upper fin fit within the grooves of the lower fin. This structure, in which the multiple fins are connected to the lower fin, which has been rotated 180 degrees horizontally, improves overall heat exchange efficiency, facilitates installation, and ensures structural stability.

[0015] In the aforementioned heat exchange plates, the two branch troughs of the V-shaped troughs are parallel to the branch ridges of the V-shaped corrugated ridges. Grooves are provided on the outer walls of the branch troughs. The number of troughs on the upper heat exchange plate is equal to and corresponds to the number of grooves on the lower heat exchange plate. These grooves interlock with each other. This interlocking design physically increases the connection strength between the heat exchange plates, making the entire heat exchange structure more stable. This stability helps reduce vibration and deformation caused by factors such as fluid pressure and temperature changes.

[0016] In the heat exchange plate described above, the grooves and gullies can have the same depth, or they can have different depths. Designing with the same depth helps achieve a more uniform heat exchange effect, while gullies and grooves with different depths can produce more complex fluid flow patterns, thereby improving heat exchange efficiency. Deep grooves can create greater fluid disturbances, promoting heat transfer, while shallow grooves help reduce fluid resistance and improve flow efficiency.

[0017] In the aforementioned heat exchange plate, the grooves or gullies have a depth of 0.05 to 2.0 mm. This depth range helps enhance internal heat conduction. When heat is transferred from the fluid to the heat exchange plate, it can reduce the heat diffusion path within the material, allowing heat to be transferred more quickly throughout the heat exchange plate, thereby improving overall heat exchange efficiency.

[0018] In the aforementioned heat exchange plate, the grooves or gullies may have a cross-section that is any one of trapezoidal, triangular, arc-shaped, and stepped. Specific cross-sectional shapes, such as trapezoidal and stepped, can generate turbulent flow when fluid passes through, disrupting the thermal boundary layer and enabling faster and more efficient heat transfer. Arc-shaped cross-sections can guide fluid flow more smoothly, reducing fluid resistance. Trapezoidal and triangular cross-sections, due to their geometric characteristics, offer greater structural strength.

[0019] Compared with existing technologies, the advantages are: 1. Simple and reliable structure, low production cost and not easy to damage. 2. The grooves or gullies reduce flow resistance while improving heat exchange efficiency. 3. The special structure can effectively reduce the refrigerant charge. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a structural diagram of embodiment 1 provided by the utility model.

[0021] Figure 2 It is a schematic cross-sectional structure diagram of embodiment 1 provided by the utility model.

[0022] Figure 3 This is a structural diagram of embodiment 3 provided by the present utility model.

[0023] Figure 4It is a schematic cross-sectional structure diagram of embodiment 3 provided by the present utility model.

[0024] Figure 5 This is a structural diagram of embodiment 4 provided by the present utility model.

[0025] Figure 6 It is a schematic cross-sectional structure diagram of embodiment 4 provided by the present utility model.

[0026] Figure 7 This is a structural diagram of embodiment 5 provided by the present utility model.

[0027] Figure 8 It is a schematic cross-sectional structure diagram of embodiment 5 provided by the present utility model.

[0028] Figure 9 This is a structural diagram of embodiment 6 provided by the present utility model.

[0029] Figure 10 It is a schematic cross-sectional structure diagram of embodiment 6 provided by the present utility model.

[0030] Figure 11 This is a structural diagram of embodiment 7 provided by the present utility model.

[0031] Figure 12 It is a schematic cross-sectional structure diagram of embodiment 7 provided by the present utility model.

[0032] In the figure, the plate body 1, the trough 2, the branch trough 3, the gully 31, the corrugated ridge 4, the branch ridge 5, the groove unit 51, the groove group 52, the groove 53, and the heat exchange fin 6. DETAILED DESCRIPTION

[0033] Example 1

[0034] like Figure 1 and 2 As shown, a heat exchanger plate includes a plate body 1, on which are provided a plurality of V-shaped troughs 2 distributed from one end to the other, two adjacent V-shaped troughs 2 are provided with a V-shaped corrugated ridge 4, and two branch ridges 5 of the V-shaped corrugated ridge 4 are provided with groove units 51 distributed along the length direction thereof, the groove unit 51 includes at least a plurality of groove groups 52 distributed along the length direction of the branch ridge 5, and the groove group 52 includes at least a plurality of grooves 53 distributed along the length direction of the branch ridge 5.

[0035] In this embodiment, V-shaped troughs 2 and corrugated ridges 4 are arranged at intervals on the thin sheet-like plate body 1, and multiple grooves 53 are arranged at intervals on the corrugated ridges 4. When in use, multiple heat exchange plates are stacked and arranged, and the troughs 2 of the upper heat exchange plate are arranged in the grooves 53 of the lower heat exchange plate, which can increase the contact area and thereby improve the heat exchange efficiency and structural strength.

[0036] More specifically, the depths of the grooves 53 of all groove groups 52 are the same. The groove units 51 on the two branch ridges 5 of the V-shaped corrugated ridge 4 are symmetrically arranged, and the slope angle of the grooves 53 is 70-150 degrees.

[0037] Preferably, the slope angle of the groove 53 is 90-120 degrees.

[0038] In the present application, the two branch troughs 3 of the V-shaped trough 2 and the branch ridge 5 of the V-shaped corrugated ridge 4 are parallel to each other, and grooves 31 are provided on the outer wall of the branch trough 3. The number of grooves 31 is equal to the number of grooves 53, and the grooves 53 on one plate body 1 can correspond one-to-one with the grooves 31 on another plate body 1 after horizontal rotation 180 degrees. The grooves 31 and the grooves 53 are of corresponding size and fit together.

[0039] Example 2

[0040] The content of this embodiment is basically the same as that of the first embodiment. The difference is that the depth of each groove group 52 is not unique, and groove groups 52 with grooves 53 of different depths are provided.

[0041] In this embodiment, by adjusting the depth ratio and distribution of the grooves 53 of the groove group 52, the heat exchange performance of the heat exchange plate can be flexibly controlled, thereby optimizing the groove 53 depth design according to specific application needs and heat exchange requirements to achieve the best heat exchange effect.

[0042] Example 3

[0043] The content of this embodiment is basically the same as that of the first embodiment, except that Figure 3 and 4 As shown, the dimensions of the ravine 31 are slightly smaller than the dimensions of the groove 53 .

[0044] In this embodiment, the size of the gully 31 is slightly smaller than the size of the groove 53 so that the fluid resistance of the refrigerant can be reduced when the two cooperate.

[0045] Example 4

[0046] The content of this embodiment is basically the same as that of the first embodiment, except that Figure 5 and 6 As shown, no grooves 31 are provided on the wave troughs 2 .

[0047] In this embodiment, no grooves 31 are provided on the troughs 2 , so that the structural strength can be improved and the production cost can be reduced while ensuring the function is achieved.

[0048] Example 5

[0049] like Figure 7 and 8As shown, a heat exchange plate includes two layers of stacked heat exchange fins 6. The upper heat exchange fin 6 of the two adjacent heat exchange fins 6 is connected to the lower heat exchange fin 6 after being horizontally rotated 180 degrees. The outer wall of the V-shaped trough 2 at the bottom of the upper heat exchange fin 6 is embedded in the groove 53 of the lower heat exchange fin 6.

[0050] In this embodiment, the grooves 31 and the grooves 53 correspond to each other and interlock with each other, which further enhances the overall heat exchange efficiency while reducing the refrigerant filling amount and ensuring that the flow resistance of the refrigerant in the flow channel remains at a low level.

[0051] More specifically, the two branch troughs 3 of the V-shaped trough 2 and the branch ridge 5 of the V-shaped corrugated ridge 4 are parallel to each other, and grooves 31 are provided on the outer wall of the branch trough 3. The number of grooves 31 on the upper heat exchange plate 6 is equal to and corresponds to the number of grooves 53 on the lower heat exchange plate 6, and the grooves 31 and the grooves 53 are interlocked with each other.

[0052] More specifically, the depth of the groove 53 or the gully 31 is 0.05 to 2.0 mm. Preferably, the depth of the groove 53 or the gully 31 is 0.1 to 0.5 mm.

[0053] Example 6

[0054] The content of this embodiment is basically the same as that of the fourth embodiment, except that Figure 9 and 10 As shown, no grooves 31 are provided on the trough 2 , and the outer wall of the V-shaped trough 2 at the bottom of the upper heat exchange fin 6 is directly embedded in the groove 53 of the lower heat exchange fin 6 .

[0055] In this embodiment, the design of the V-shaped corrugated ridges 4 and the troughs 2 maintains an unobstructed flow path between the two heat exchange fins 6. The outer wall of the V-shaped trough 2 at the bottom of the upper heat exchange fin 6 is embedded in the groove 53 of the lower heat exchange fin 6, thereby reducing production costs and increasing structural strength while still maintaining a large contact area, thereby ensuring heat exchange efficiency.

[0056] Example 7

[0057] The content of this embodiment is basically the same as that of the fourth embodiment, except that Figure 11 and 12 As shown, the heat exchange fins 6 arranged at the top are not provided with the grooves 31 and the channels 53 .

[0058] In this embodiment, the heat exchange plate 6 arranged at the top is not provided with the gully 31 and the groove 53, which can further reduce the flow resistance of the refrigerant in the flow channel, and at the same time improve the structural strength and reduce the production cost while ensuring the function is realized.

[0059] The specific embodiments described herein are merely illustrative of the spirit of the present invention. Persons skilled in the art may make various modifications, additions, or substitutions to the described specific embodiments without departing from the spirit of the present invention or exceeding the scope defined by the appended claims.

[0060] Although this document frequently uses terms such as plate, trough, sub-trough, gully, corrugated ridge, sub-ridge, groove unit, groove group, groove, and heat exchanger fin, the use of other terms is not excluded. These terms are used solely to more conveniently describe and explain the essence of the present invention. Any interpretation of them as additional limitations is contrary to the spirit of the present invention.

Claims

1. A heat exchange plate, comprising a plate body (1), characterized in that: The plate body (1) is provided with a plurality of V-shaped troughs (2) distributed from one end to the other end, two adjacent V-shaped troughs (2) are provided with V-shaped corrugated ridges (4), and two branch ridges (5) of the V-shaped corrugated ridge (4) are provided with groove units (51) distributed along the length direction thereof, and the groove units (51) include at least N groove groups (52) distributed along the length direction of the branch ridge (5), and N ≥ 1, and the groove groups (52) include at least M grooves (53) distributed along the length direction of the branch ridge (5), and M ≥ 1.

2. The heat exchange plate according to claim 1, characterized in that: The depths of the grooves (53) of all groove groups (52) are the same.

3. The heat exchange fin according to claim 1, characterized in that: When N>1, the depth of each groove group (52) is not unique.

4. The heat exchange plate according to claim 1 or 3, characterized in that: When M>1, the depths of all the grooves (53) in each groove group (52) are the same.

5. The heat exchange fin according to claim 1, characterized in that: The depths of adjacent groove groups (52) are different, and the depths of separated groove groups (52) are the same.

6. The heat exchange fin according to claim 5, characterized in that: The groove units (51) on the two branch ridges (5) of the V-shaped corrugated ridge (4) are symmetrically arranged.

7. The heat exchange fin according to claim 5, characterized in that: The two branch troughs (3) of the V-shaped trough (2) and the branch ridge (5) of the V-shaped corrugated ridge (4) are parallel to each other, and grooves (31) are provided on the outer wall of the branch trough (3). The number of the grooves (31) is equal to the number of the grooves (53), and the grooves (53) on one plate (1) can correspond one to one with the grooves (31) on another plate (1) after being horizontally rotated 180 degrees, and the grooves (31) and the grooves (53) are interlocked with each other.

8. The heat exchange fin according to claim 1, 2 or 3, characterized in that: The slope angle of the groove (53) is 70-150 degrees.

9. A heat exchange plate, characterized in that: The invention comprises a plurality of stacked layers of heat exchange fins (6) as described in any one of claims 1 to 8, wherein the upper heat exchange fin (6) of two adjacent heat exchange fins (6) is connected to the lower heat exchange fin (6) after being horizontally rotated 180 degrees, and the outer wall of the V-shaped trough (2) at the bottom of the upper heat exchange fin (6) is embedded in the groove (53) of the lower heat exchange fin (6).

10. The heat exchange plate according to claim 9, characterized in that: The two branch troughs (3) of the V-shaped trough (2) and the branch ridge (5) of the V-shaped corrugated ridge (4) are parallel to each other, and grooves (31) are provided on the outer wall of the branch trough (3). The number of grooves (31) of the upper heat exchange plate (6) is equal to and corresponds to the number of grooves (53) on the lower heat exchange plate (6), and the grooves (31) and grooves (53) are interlocked.

11. The heat exchange plate according to claim 10, characterized in that: The groove (53) has the same depth as the gully (31); Alternatively, the groove (53) and the gully (31) have different depths.

12. The heat exchange plate according to claim 10, characterized in that The depth of the groove (53) or gully (31) is 0.05 to 2.0 mm.

13. The heat exchange plate according to claim 10, characterized in that The cross section of the groove (53) or gully (31) is any one of a trapezoidal, triangular, arc-shaped, and stepped shape.

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