A heat exchanger based on uniform cooling and multi-stage turbulent vortex heat exchanger

Abstract

This invention provides a multi-segment turbulent vortex heat exchanger based on uniform cooling, belonging to the field of heat exchanger technology. It includes a heat exchange cylinder, a cold flow slow-in zone, a front turbulent heat exchange zone, a front vortex heat exchange zone, a cold mixing homogenization zone, a rear vortex heat exchange zone, a rear turbulent heat exchange zone, and a cold flow slow-out zone. Its key features are multi-segment turbulence and vortex heat exchange of the hot and cold flows to improve heat exchange efficiency, and uniform-temperature cold flow output through inter-flow heat exchange to achieve stable heat exchange. This invention achieves buffered and stratified cold flow input through the cold flow slow-in zone, primary turbulent heat exchange of the hot and cold flows through the front turbulent heat exchange zone, primary vortex heat exchange of the hot and cold flows through the front vortex heat exchange zone, uniform-temperature cold flow output through the cold mixing homogenization zone, secondary vortex heat exchange of the hot and cold flows through the rear vortex heat exchange zone, secondary turbulent heat exchange of the hot and cold flows through the rear turbulent heat exchange zone, and stratified buffered cold flow output through the cold flow slow-out zone.

Description

Technical Field

[0001] This invention relates to a multi-stage turbulent vortex heat exchanger based on uniform cooling, and more particularly to a system that achieves buffered and stratified input of cold flow through a cold flow slow-in zone, primary turbulent heat exchange of cold and hot flow through a front turbulent heat exchange zone, primary vortex heat exchange of cold and hot flow through a front vortex heat exchange zone, output of uniformly heated cold flow through a cold mixing and equalizing zone, secondary vortex heat exchange of cold and hot flow through a rear vortex heat exchange zone, secondary turbulent heat exchange of cold and hot flow through a rear turbulent heat exchange zone, and stratified and buffered output of cold flow through a cold flow slow-out zone. This invention belongs to the field of heat exchanger technology development. Background Technology

[0002] Heat exchangers are devices that transfer part of the heat from a hot fluid to a cold fluid, playing an important role in industrial production such as chemical, petroleum, power, and food processing. However, currently used heat exchangers still have the following problems: First, the heat exchange efficiency is low. The turbulence state of the cold and hot flows inside the heat exchanger is poor, and the cold and hot flows cannot exchange heat fully and sufficiently. Only the surface heat exchange of the cold and hot flows can occur. The internal hot flow needs to pass through the heat transfer of the outer low-temperature hot flow to cool down, resulting in low heat exchange efficiency. Second, the heat exchange is uneven. The temperature of the hot flow in different areas within the same radial cross-section of the heat exchanger is different, resulting in different temperatures of the cold flow after heat exchange. Since the cold flow inside the heat exchanger is continuously flowing and exchanging heat, the different temperatures of the cold flow will cause uneven heat exchange in subsequent heat exchange. That is, the cold flow with a lower temperature rise can exchange heat better, while the cold flow with a higher temperature cannot exchange heat effectively, thus causing uneven heat exchange throughout the heat exchanger and making it impossible to achieve stable heat exchange.

[0003] Therefore, in order to address the common problems of low heat exchange efficiency and uneven heat exchange in existing heat exchangers, a heat exchanger with high heat exchange efficiency and balanced heat exchange should be designed by comprehensively considering the working mode and structure of the heat exchanger. Summary of the Invention

[0004] This invention addresses the common problems of low heat exchange efficiency and uneven heat exchange in existing heat exchangers, and provides a heat exchanger based on uniform cooling and multi-stage turbulent vortex heat exchanger that can effectively solve the above problems.

[0005] The present invention provides a multi-stage turbulent vortex heat exchanger based on uniform cooling, employing the following technical solution:

[0006] A multi-stage turbulent vortex heat exchanger based on uniform cooling includes a heat exchange cylinder, a cold flow inlet zone, a front turbulent heat exchange zone, a front vortex heat exchange zone, a cold mixing homogenization zone, a rear vortex heat exchange zone, a rear turbulent heat exchange zone, and a cold flow outlet zone. The heat exchange cylinder contains, from left to right, the following zones: cold flow inlet zone, front turbulent heat exchange zone, front vortex heat exchange zone, cold mixing homogenization zone, rear vortex heat exchange zone, rear turbulent heat exchange zone, and cold flow outlet zone. The heat exchange cylinder is welded with a cold flow inlet, a hot flow outlet, a hot flow inlet, and a cold flow outlet. The cold flow inlet and hot flow outlet are located on one side, and the hot flow inlet and cold flow outlet are located on the other side. The heat exchange cylinder contains, from left to right, a cold flow outer plate A, a cold flow inner plate A, and a support plate. The system comprises: a baffle plate A, a support baffle plate B, a support baffle plate C, an inner cold flow plate B, and an outer cold flow plate B. The cold flow slow-in zone is located between the outer cold flow plate A and the inner cold flow plate A. Buffer plates are welded onto both the outer and inner cold flow plates A. The cold flow inlet is located above the slow-in zone. The inner cold flow plate A has three sets of square holes A (upper, middle, and lower), and the inner cold flow plate B also has three sets of square holes A (upper, middle, and lower). The front turbulence heat exchange zone is located between the inner cold flow plate A and the support baffle plate A. The support baffle plate A has round holes, square holes B, and square holes C. The heat flow outlet is located above the front turbulence heat exchange zone. The front vortex heat exchange zone is located between the support baffle plate A and the support baffle plate B. The front vortex heat exchange zone contains a front cold flow box A and a front... The cold flow box B, the front cold flow box A, and the front cold flow box B are respectively provided with a convex section, a flat section, and a concave section. The front cold flow box B is formed by welding together two upper and lower baffles B, two left and right horizontal plates B, and two front and rear longitudinal plates. The front cold flow box A is formed by welding together two upper and lower baffles A, two left and right horizontal plates A, and two front and rear longitudinal plates. The length of the horizontal plate B is 2.5 times the length of the horizontal plate A. The cold mixing and equalization zone is located in the center of the heat exchange cylinder. The cold mixing and equalization zone is provided with a baffle plate B and a cooling cylinder. The baffle plate B has a round hole and an opening for installing the cooling cylinder. The cooling cylinder is welded to the opening of the baffle plate B. A mixing plate with a round hole is welded inside the cooling cylinder. The front and rear ends of the cooling cylinder are... A sealing plate with a square hole D is welded on it; the rear vortex heat exchange zone is located between support plate B and support plate C, and a rear cold flow box A and a rear cold flow box B are provided in the rear vortex heat exchange zone. A circular hole is provided on support plate C, and a convex section, a flat section, and a concave section are provided on rear cold flow box A and rear cold flow box B respectively; the rear turbulence heat exchange zone is located between support plate C and the inner cold flow plate B. A circular hole, a square hole B, and a square hole C are also provided on support plate C. The hot flow inlet is located below the rear turbulence heat exchange zone; the cold flow slow exit zone is located between the inner cold flow plate B and the outer cold flow plate B. Buffer plates are welded on the outer cold flow plate B and the inner cold flow plate B respectively, and the cold flow outlet is located below the cold flow slow exit zone.

[0007] The heat exchange cylinder has a cylindrical structure; the cold flow outer plate A and the cold flow inner plate A are welded to the inner wall of the heat exchange cylinder. The cold flow outer plate A has a circular structure. Three buffer plates are welded on the cold flow outer plate A and the cold flow inner plate A at equal intervals from top to bottom. The buffer plates of the cold flow outer plate A and the cold flow inner plate A are arranged alternately. The width of the buffer plate is 2 / 3 of the width of the cold flow buffer zone.

[0008] The support plate A is welded to the inner wall of the heat exchange cylinder. The circular holes and square holes B and C on the support plate A are arranged alternately. Square holes B are located in the middle of the support plate A. The square holes B in the middle of the support plate A are divided into upper and lower layers, with three equally spaced holes in each layer. The support plate A has a total of 23 circular holes. The upper and lower parts of the support plate A each have two layers of square holes C, with one hole in each layer. Square holes B and C are at the same height, and the length of square hole C is 2.5 times the length of square hole B. A space is provided between the cold flow inner plate A and the support plate A. Partial front cold flow boxes A and B are provided. Front cold flow box A passes through and is welded to square holes B and A in the support plate A and the inner cold flow plate A, respectively. Front cold flow box B passes through and is welded to square holes C and A in the support plate A and the inner cold flow plate A, respectively. The support plate C has 37 circular holes. The outer cold flow plate B and the inner cold flow plate B have the same structural dimensions as the outer cold flow plate A and the inner cold flow plate A, respectively. A rectangular hole is provided in the center of the horizontal plate A and the horizontal plate B. A square tube is welded to the center of the horizontal plate A and the horizontal plate B, respectively.

[0009] The front cold flow box A and the front cold flow box B are of equal length and height, as are the rear cold flow box A and the rear cold flow box B. The convex section is upward convex, the flat section is horizontal, and the concave section is downward concave. The longitudinal sections of the convex and concave sections are equilateral triangles. The square tubes are located in the center of the horizontal plate A and the horizontal plate B, respectively. The upper and lower parts of the heat exchange cylinder are provided with two equally spaced front cold flow boxes B, and the middle part of the heat exchange cylinder is provided with three sets of equally spaced upper and lower front cold flow boxes A. Support plates are provided between adjacent front cold flow boxes A and adjacent front cold flow boxes B.

[0010] The sealing plate has two square holes D arranged symmetrically from top to bottom. The square tubes of the front cold flow box A, front cold flow box B, and rear cold flow box A and rear cold flow box B are welded to the square holes D. The cooling cylinder is a cylindrical structure. The mixing plate inside the cooling cylinder is a semi-circular structure. There are four mixing plates inside the cooling cylinder, arranged symmetrically from top to bottom in groups of two. The height of the mixing plate is 3 / 4 of the radius of the cooling cylinder. The support plate B has seven rows of round holes at equal intervals from top to bottom. The round holes on the support plate B are staggered with those on the cooling cylinder.

[0011] This invention achieves buffered and stratified input of cold flow through a cold flow slow-in zone. Specifically, the buffer plate in the cold flow slow-in zone buffers and stratifies the cold flow entering through the cold flow inlet. When the cold flow enters, the buffer plate prevents a large amount of cold flow from flowing in and damaging the heat exchanger. It also causes the cold flow to be blocked, pressurized, and changed direction. The pressurized and changed direction cold flow is then easier to pressurize and input into the front cold flow box A and the front cold flow box B.

[0012] The present invention arranges the buffer plates of the outer cold flow plate A and the inner cold flow plate A in an alternating manner. This design facilitates the flow of cold air in partitioned and layered manner to the front cold flow box A and the front cold flow box B. In addition, the alternating arrangement can also achieve turbulence of the cold air and heat exchange with the turbulence on the other side of the inner cold flow plate A.

[0013] The width of the buffer plate in this invention is 2 / 3 of the width of the cold flow buffer zone, and this design achieves a change in the direction of the cold flow.

[0014] This invention achieves primary turbulent heat exchange between hot and cold flows through a front turbulent heat exchange zone. Specifically, the front cold flow box A and front cold flow box B within the front turbulent heat exchange zone perform primary turbulent heat exchange on the hot flow. Specifically, the front cold flow box A and front cold flow box B change the flow direction of the hot flow in the front turbulent heat exchange zone, thereby creating turbulence and allowing the hot flow to exchange heat with the cold flow in the cold flow box A and front cold flow box B under turbulent conditions.

[0015] The present invention arranges the round holes and square holes B and C on the support plate A in an alternating manner. This design allows the heat flow to flow above and below the front cold flow box A and the front cold flow box B respectively, realizing all-round cold and heat flow exchange and improving heat exchange efficiency.

[0016] The present invention sets the number of circular holes on the support plate C to 37 and the number of circular holes on the support plate A to 23. This design allows the heat flow to quickly enter the rear turbulence heat exchange zone through the support plate C. Furthermore, due to the fewer circular holes on the support plate A, the heat flow flows slowly into the front turbulence heat exchange zone, extending the residence time of the heat flow in the front vortex heat exchange zone for sufficient heat exchange.

[0017] This invention achieves primary vortex heat exchange between hot and cold flows through a front vortex heat exchange zone. Specifically, the front cold flow box A and front cold flow box B within the front vortex heat exchange zone generate vortices in both the hot flow flowing over them and the internal cold flow. These vortices accelerate the heat exchange between the hot and cold flows, improving heat exchange efficiency. Taking the front cold flow box A as an example, when the cold flow reaches the convex section, the upward bulge of the convex section alters the flow path, causing the cold flow to change its direction. Vortices are generated before and after the convex end of the internal flow path, increasing the turbulence of the cold flow and allowing more cold flow to participate in the heat exchange with the hot flow. During heat exchange, the hot flow outside the front cold flow box A, when flowing through the convex section, generates vortices before and after the same convex section, prompting more hot flow to participate in the heat exchange with the cold flow. Similarly, when the cold and hot flows flow through the concave section, the generated vortices improve the heat exchange efficiency. A smooth transition section is provided between the convex and concave sections, so that the cold and hot flows have a smooth transition between the two vortices. This transition section can be used to make the cold and hot flows fully exchange heat under the action of the vortices, and can also prevent the direct interaction between the two vortices, so as not to reduce the heat exchange efficiency and generate vortex collision noise.

[0018] This invention features a convex section, a flat section, and a concave section sequentially arranged on the front cold flow box A and the front cold flow box B, respectively. This design causes the cold and hot flows to generate vortices.

[0019] The present invention places square tubes in the center of horizontal plates A and B respectively. This design allows the cold flow to quickly fill the front cold flow box A and the front cold flow box B through the square tubes.

[0020] The present invention sets the longitudinal sections of the convex and concave disturbance sections as equilateral triangles. This design facilitates processing and manufacturing, and also enables the generation of equal vortices in front of and behind the convex and concave disturbance sections, ensuring the uniformity of vortex heat transfer.

[0021] The present invention sets the length of the horizontal plate B to be 2.5 times the length of the horizontal plate A. This design facilitates the placement of the large-section front cold flow box B at the top and bottom of the heat exchange cylinder, while placing multiple small-section front cold flow boxes A in the middle of the heat exchange cylinder, thus achieving a reasonable layout within the limited space of the heat exchange cylinder.

[0022] The present invention provides support plates between adjacent front cold flow boxes A and B. This design can improve the rigidity of front cold flow boxes A and B, and the support plates can also turbulentize the heat flow, allowing the heat flow to participate in heat exchange in a turbulent state.

[0023] This invention achieves uniform temperature output cold flow through a cold mixing and equalization zone. Specifically, the cold flow from the adjacent front cold flow box A or front cold flow box B is collected by the cold mixing and equalization zone's equalization cylinder. Under the action of the mixing plate, the cold flow entering the equalization cylinder is fully mixed and heat exchanged, and the cold flow is output to the rear cold flow box A or rear cold flow box B in a uniform temperature state, ensuring the uniformity and stability of heat exchange for subsequent heat flow by the rear cold flow box A or rear cold flow box B.

[0024] The present invention has a mixing plate with a circular hole inside the cooling cylinder. This design achieves the mixing and turbulence of the cold flow. That is, the mixing plate blocks and turbulents the hot flow, and the circular hole on it mixes and impacts the turbulent cold flow, thereby accelerating the heat exchange between the cold flows and so that the cold flow is output in a uniform temperature state.

[0025] The present invention has a cooling equalization cylinder in the center of the heat exchange cylinder. This design collects the cold flow with different temperatures after heat exchange in the first half of the heat exchange cylinder, so that the cold flow with different temperatures can be fully heat exchanged in the cooling equalization cylinder to achieve a uniform temperature.

[0026] This invention achieves secondary vortex heat exchange of hot and cold flows through a rear vortex heat exchange zone. Specifically, the rear cold flow box A and rear cold flow box B in the rear vortex heat exchange zone generate vortices for the hot flow flowing above and the cold flow flowing inside, respectively. The generated vortices enable the hot and cold flows to exchange heat fully, thereby improving the heat exchange efficiency.

[0027] This invention achieves secondary turbulence heat exchange of hot and cold flows through a rear turbulence heat exchange zone, that is, the heat flow is subjected to secondary turbulence heat exchange through a portion of the rear cold flow box A and rear cold flow box B within the rear turbulence heat exchange zone.

[0028] This invention achieves layered buffered output of cold flow through a cold flow slow-out zone, that is, the cold flow flowing to the cold flow outlet is layered and buffered through a buffer plate in the cold flow slow-out zone.

[0029] The beneficial effects of this invention are: the cold flow is buffered and layered input through the cold flow slow entry zone; the cold and hot flows undergo primary turbulence heat exchange through the front turbulence heat exchange zone; the cold and hot flows undergo primary vortex heat exchange through the front vortex heat exchange zone; the cold and hot flows undergo uniform temperature output through the cold mixing and equalization zone; the cold and hot flows undergo secondary vortex heat exchange through the rear vortex heat exchange zone; the cold and hot flows undergo secondary turbulence heat exchange through the rear turbulence heat exchange zone; and the cold flow is buffered and layered output through the cold flow slow exit zone. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the overall main structure of the present invention.

[0031] Figure 2 This is a schematic diagram of the arrangement of the buffer plate of the present invention on the cold flow outer plate A.

[0032] Figure 3 This is a schematic diagram of the structure of the cold flow inner plate A of the present invention.

[0033] Figure 4 This is a partial structural schematic diagram of the cold flow slow-in zone and the front turbulence heat exchange zone of the present invention.

[0034] Figure 5 This is a schematic diagram of the structure of the support plate A of the present invention.

[0035] Figure 6 This is a schematic diagram of the arrangement of the cooling cylinder on the support plate B according to the present invention.

[0036] Figure 7 This is a partial structural schematic diagram of the front cooling box B of the present invention.

[0037] Figure 8 This is a schematic diagram of the front cooling box B of the present invention.

[0038] Figure 9 This is a schematic diagram of the front cooling box A of the present invention.

[0039] Figure 10 This is a partial structural schematic diagram of the cold mixing temperature equalization zone of the present invention.

[0040] Figure 11 This is a schematic diagram of the sealing plate of the present invention.

[0041] Figure 12This is a schematic diagram of the structure of the rear cooling box B of the present invention.

[0042] Figure 13 This is a schematic diagram of the structure of the rear cooling box A of the present invention.

[0043] Figure 14 This is a schematic diagram of the structure of the support plate C of the present invention.

[0044] The components are: 1. Cold flow outlet, 2. Cold flow inner plate B, 3. Support plate C, 4. Heat exchange cylinder, 5. Support plate B, 6. Front cold flow box A, 7. Front cold flow box B, 8. Hot flow outlet, 9. Cold flow outer plate A, 10. Cold flow inlet, 11. Buffer plate, 12. Support plate A, 13. Support plate, 14. Cooling cylinder, 15. Mixing plate, 16. Rear cold flow box A, 17. Rear cold flow box B. 18. Hot flow inlet, 19. Square hole A, 20. Round hole, 21. Square hole B, 22. Square hole C, 23. Protruding section, 24. Flat section, 25. Concave section, 26. Square tube, 27. Horizontal plate B, 28. Baffle plate B, 29. Longitudinal plate, 30. Sealing plate, 31. Square hole D, 32. Horizontal plate A, 33. Baffle plate A, 34. Cold flow inner plate A, 35. Cold flow outer plate B. Detailed Implementation

[0045] like Figure 1 As shown, a multi-segment turbulent vortex heat exchanger based on uniform cooling includes a heat exchange cylinder 4, a cold flow slow inlet zone, a front turbulent heat exchange zone, a front vortex heat exchange zone, a cold mixing uniform temperature zone, a rear vortex heat exchange zone, a rear turbulent heat exchange zone, and a cold flow slow outlet zone. The heat exchange cylinder 4 is provided with the following zones sequentially from left to right: a cold flow slow inlet zone, a front turbulent heat exchange zone, a front vortex heat exchange zone, a cold mixing uniform temperature zone, a rear vortex heat exchange zone, a rear turbulent heat exchange zone, and a cold flow slow outlet zone. The heat exchange cylinder 4 is welded with a cold flow inlet 10, a hot flow outlet 8, a hot flow inlet 18, and a cold flow outlet 1. The cold flow inlet 10 and the hot flow outlet 8 are located on one side, and the hot flow inlet 18 and the cold flow outlet 1 are located on the other side. The heat exchange cylinder 4 is provided with the following layers sequentially from left to right: a cold flow outer plate A9, a cold flow inner plate A34, a support plate A33, a support plate B5, a support plate C3, a cold flow inner plate B2, and a cold flow outer plate B35.

[0046] Combination Figure 2 , Figure 3 and Figure 4 As shown, the cold flow slow inlet zone is located between the cold flow outer plate A9 and the cold flow inner plate A34. Buffer plates 11 are welded on the cold flow outer plate A9 and the cold flow inner plate A34. The cold flow inlet 10 is located above the cold flow slow inlet zone. The cold flow inner plate A34 is provided with three sets of square holes A19 (upper, middle, and lower). The cold flow inner plate B2 is also provided with three sets of square holes A19 (upper, middle, and lower).

[0047] The cold flow outer plate A9 and the cold flow inner plate A34 are welded to the inner wall of the heat exchange cylinder 4. The cold flow outer plate A9 is a circular structure. Three buffer plates 11 are welded on the cold flow outer plate A9 and the cold flow inner plate A34 at equal intervals from top to bottom. The buffer plates 11 of the cold flow outer plate A9 and the buffer plates 11 of the cold flow inner plate A34 are arranged alternately. The width of the buffer plate 11 is 2 / 3 of the width of the cold flow buffer zone.

[0048] This invention achieves buffered and stratified input of cold flow through a cold flow slow-entry zone. Specifically, the buffer plate 11 in the cold flow slow-entry zone buffers and stratifies the cold flow entering through the cold flow inlet 10. When the cold flow enters, the buffer plate 11 prevents a large amount of cold flow from flowing in and damaging the heat exchanger. It also causes the cold flow to be blocked, pressurized, and changed direction. The pressurized and changed direction cold flow is then easier to pressurize and input into the front cold flow box A6 and the front cold flow box B7.

[0049] The present invention arranges the buffer plate 11 of the cold flow outer plate A9 and the buffer plate 11 of the cold flow inner plate A34 in an alternating manner. This design facilitates the cold flow to flow in sections and layers to the front cold flow box A6 and the front cold flow box B7. In addition, the alternating arrangement can also achieve the turbulence of the cold flow and exchange heat with the turbulence on the other side of the cold flow inner plate A34.

[0050] The width of the buffer plate 11 in this invention is 2 / 3 of the width of the cold flow buffer zone, and this design achieves a change in the direction of the cold flow.

[0051] Combination Figure 5 As shown, the front turbulence heat exchange zone is located between the cold flow inner plate A34 and the support plate A12. The support plate A12 is provided with round holes 20, square holes B21 and square holes C22. The hot flow outlet 8 is located above the front turbulence heat exchange zone. The number of round holes 20 on the support plate A12 is 23.

[0052] Support plate A12 is welded to the inner wall of heat exchange cylinder 4. The circular holes 20 and square holes B21 and C22 on support plate A12 are arranged alternately. Square hole B21 is located in the middle of support plate A12, and the square holes B21 in the middle of support plate A12 are divided into upper and lower layers, with three equally spaced holes in each layer. The upper and lower parts of support plate A12 each have two layers of square holes C22, with one hole in each layer. Square holes B21 and C22 are at the same height. The length of hole C22 is 2.5 times the length of square hole B21; a portion of front cold flow box A6 and front cold flow box B7 are provided between cold flow inner plate A34 and support plate A12. Front cold flow box A6 passes through and is welded to square hole B21 of support plate A12 and square hole A19 of cold flow inner plate A34, respectively. Front cold flow box B7 passes through and is welded to square hole C22 of support plate A12 and square hole A19 of cold flow inner plate A34, respectively.

[0053] This invention achieves primary turbulent heat exchange between hot and cold flows through a front turbulent heat exchange zone. Specifically, the front cold flow boxes A6 and B7 within the front turbulent heat exchange zone perform primary turbulent heat exchange on the hot flow. The front cold flow boxes A6 and B7 change the flow direction of the hot flow in the front turbulent heat exchange zone, thereby creating turbulence and allowing the hot flow to exchange heat with the cold flow in the cold flow boxes A and B7 under turbulent conditions.

[0054] The present invention arranges the round holes 20 and square holes B21 and C22 on the support plate A12 in an alternating manner. This design allows the heat flow to flow above and below the front cold flow box A6 and the front cold flow box B7 respectively, realizing all-round cold and heat flow exchange and improving heat exchange efficiency.

[0055] The present invention sets the number of circular holes 20 on the support plate C3 to 37 and the number of circular holes 20 on the support plate A12 to 23. This design allows the heat flow to quickly enter the rear turbulence heat exchange zone through the support plate C3. Furthermore, due to the design of fewer circular holes 20 on the support plate A12, the heat flow flows slowly into the front turbulence heat exchange zone, extending the residence time of the heat flow in the front vortex heat exchange zone for sufficient heat exchange.

[0056] Combination Figure 6 , Figure 7 , Figure 8 and Figure 9 As shown, the front vortex heat exchange zone is located between support plate A12 and support plate B5. The front cold flow box A6 and front cold flow box B7 are provided in the front vortex heat exchange zone. The front cold flow box A6 and front cold flow box B7 are of equal length and height. The front cold flow box A6 and front cold flow box B7 are respectively provided with a convex section 23, a flat section 24 and a concave section 25.

[0057] The front cold flow box B7 is welded together by two upper and lower baffles B28, two left and right horizontal plates B27, and two front and rear vertical plates 29. The front cold flow box A6 is welded together by two upper and lower baffles A33, two left and right horizontal plates A32, and two front and rear vertical plates 29. A rectangular hole is provided in the center of the horizontal plate A32 and the horizontal plate B27. A square tube 26 is welded in the center of the horizontal plate A32 and the horizontal plate B27 respectively. The length of the horizontal plate B27 is 2.5 times the length of the horizontal plate A32.

[0058] The convex section 23 is upwardly protruding, the flat section 24 is horizontal, and the concave section 25 is downwardly concave. The longitudinal sections of the convex section 23 and the concave section 25 are equilateral triangles respectively. The square tube 26 is located in the center of the horizontal plate A32 and the horizontal plate B27 respectively. The upper and lower parts of the heat exchange cylinder 4 are provided with two equally spaced front cold flow boxes B7 respectively. The middle part of the heat exchange cylinder 4 is provided with three sets of upper and lower equally spaced front cold flow boxes A6. Support plates 13 are provided between adjacent front cold flow boxes A6 and adjacent front cold flow boxes B7 respectively.

[0059] This invention achieves primary vortex heat exchange between hot and cold flows through a front vortex heat exchange zone. Specifically, the front cold flow box A6 and front cold flow box B7 within the front vortex heat exchange zone generate vortices in both the hot flow flowing over them and the internal cold flow. These vortices accelerate the heat exchange between the hot and cold flows, improving heat exchange efficiency. Taking the front cold flow box A6 as an example, when the cold flow reaches the convex section 23, the upward convexity of the convex section 23 alters the flow path, causing the cold flow to change its direction. Vortices are generated before and after the convex end of the internal flow path, increasing the turbulent motion of the cold flow and allowing more cold flow to participate in the heat exchange with the hot flow. The hot flow outside the front cold flow box A6, when flowing through the convex section 23, also generates vortices before and after the convex section 23, prompting more hot flow to participate in the heat exchange with the cold flow. Similarly, when the cold and hot flows flow through the concave section 25, the generated vortices improve the heat exchange efficiency. A smooth transition section 24 is provided between the convex section 23 and the concave section 25, so that the cold and hot flows have a smooth transition section between the two vortices. This transition section can be used to make the cold and hot flows fully exchange heat under the action of the vortex, and can also prevent the direct interaction between the two vortices, so as not to reduce the heat exchange efficiency and generate vortex collision noise.

[0060] The present invention provides a convex section 23, a flat section 24, and a concave section 25 sequentially on the front cold flow box A6 and the front cold flow box B7, respectively. This design causes the cold and hot flows to generate vortices respectively.

[0061] In this invention, the square tube 26 is located in the center of the horizontal plate A32 and the horizontal plate B27 respectively. This design allows the cold flow to quickly fill the front cold flow box A6 and the front cold flow box B7 through the square tube 26.

[0062] The present invention sets the longitudinal sections of the convex disturbance section 23 and the concave disturbance section 25 as equilateral triangles. This design facilitates processing and manufacturing, and also enables the generation of equal vortices in front of and behind the convex disturbance section 23 and the concave disturbance section 25, respectively, to ensure the uniformity of vortex heat transfer.

[0063] The present invention makes the length of the horizontal plate B27 2.5 times the length of the horizontal plate A32. This design makes it easy to place the large cross-section front cold flow box B7 at the top and bottom of the heat exchange cylinder 4, while placing multiple small cross-section front cold flow boxes A6 in the middle of the heat exchange cylinder 4, thus achieving a reasonable layout within the limited space of the heat exchange cylinder 4.

[0064] The present invention provides support plates 13 between adjacent front cold flow boxes A6 and B7. This design can improve the rigidity of front cold flow boxes A6 and B7, and the support plates 13 can also turbulentize the heat flow, so that the heat flow participates in heat exchange in a turbulent state.

[0065] Combination Figure 10 and Figure 11As shown, the cold mixing and temperature equalization zone is located in the center of the heat exchange cylinder 4. The cold mixing and temperature equalization zone is provided with a baffle plate B5 and a cooling cylinder 14. The baffle plate B5 is provided with a round hole 20 and an opening for installing the cooling cylinder 14. The cooling cylinder 14 is welded to the opening of the baffle plate B5. A mixing plate 15 with a round hole 20 is welded inside the cooling cylinder 14. Sealing plates 30 with square holes D31 are welded to the front and rear ends of the cooling cylinder 14.

[0066] There are two square holes D31 on the sealing plate 30, which are arranged symmetrically from top to bottom. The square tubes 26 of the front cold flow box A6, front cold flow box B7, and rear cold flow box A16 and rear cold flow box B17 are welded to the square holes D31 respectively. The cooling cylinder 14 is a cylindrical structure. The mixing plate 15 inside the cooling cylinder 14 is a semi-circular structure. There are four mixing plates 15 inside the cooling cylinder 14, which are arranged symmetrically from top to bottom in groups of two. The height of the mixing plate 15 is 3 / 4 of the radius of the cooling cylinder 14. The support plate B5 has seven rows of round holes 20 at equal intervals from top to bottom. The round holes 20 on the support plate B5 are staggered with the cooling cylinder 14.

[0067] This invention achieves uniform temperature output cold flow through a cold mixing and equalization zone. Specifically, the cold flow from the adjacent front cold flow box A6 or front cold flow box B7 is collected by the cold mixing and equalization zone's cooling cylinder 14. Under the action of the mixing plate 15, the cold flow entering the cooling cylinder 14 is fully mixed and heat exchanged, and the cold flow is output to the rear cold flow box A16 or rear cold flow box B17 in a uniform temperature state, ensuring the uniformity and stability of heat exchange for subsequent heat flow in the rear cold flow box A16 or rear cold flow box B17.

[0068] The present invention provides a mixing plate 15 with a circular hole 20 inside the cooling cylinder 14. This design achieves the mixing and turbulence effect on the cold flow. That is, the mixing plate 15 blocks and turbulents the hot flow, and the circular hole 20 on it mixes and impacts the turbulent cold flow, thereby accelerating the heat exchange between the cold flows so that the cold flow is output in a uniform temperature state.

[0069] The present invention has a cooling cylinder 14 in the center of the heat exchange cylinder 4. This design collects the cold flow with different temperatures after the heat exchange in the first half of the heat exchange cylinder 4, so that the cold flow with different temperatures can be fully heat exchanged in the cooling cylinder 14 to achieve a uniform temperature.

[0070] Combination Figure 12 , Figure 13 and Figure 14 As shown, the rear vortex heat exchange zone is located between support plate B5 and support plate C3. The rear vortex heat exchange zone is provided with rear cold flow box A16 and rear cold flow box B17. Support plate C3 is provided with a circular hole 20. The rear cold flow box A16 and rear cold flow box B17 are of equal length and height. The rear cold flow box A16 and rear cold flow box B17 are respectively provided with a convex section 23, a flat section 24 and a concave section 25.

[0071] This invention achieves secondary vortex heat exchange of hot and cold flows through a rear vortex heat exchange zone. Specifically, the rear cold flow box A16 and rear cold flow box B17 in the rear vortex heat exchange zone generate vortices for the hot flow flowing above and the cold flow flowing inside, respectively. The generated vortices enable the hot and cold flows to exchange heat fully, thereby improving the heat exchange efficiency.

[0072] The rear turbulence heat exchange zone is located between the support plate C3 and the cold flow inner plate B2. The support plate C3 is also provided with round holes 20, square holes B21 and square holes C22. The heat flow inlet 18 is located below the rear turbulence heat exchange zone. The number of round holes 20 on the support plate C3 is 37.

[0073] The present invention achieves secondary turbulence heat exchange of hot and cold flow through the rear turbulence heat exchange zone, that is, the heat flow is subjected to secondary turbulence heat exchange through part of the rear cold flow box A16 and rear cold flow box B17 in the rear turbulence heat exchange zone.

[0074] The cold flow slow-out zone is located between the inner cold flow plate B2 and the outer cold flow plate B. The outer cold flow plate B35 and the inner cold flow plate B have the same structural dimensions as the outer cold flow plate A9 and the inner cold flow plate A34, respectively. Buffer plates 11 are welded on the outer cold flow plate B35 and the inner cold flow plate B, respectively. The cold flow outlet 1 is located below the cold flow slow-out zone.

[0075] The present invention achieves layered buffered output of cold flow through a cold flow slow-out zone, that is, the cold flow flowing to the cold flow outlet 1 is layered and buffered through the buffer plate 11 of the cold flow slow-out zone.

[0076] The assembly process of the entire heat exchanger is as follows: (1) Weld the mixing plate 15 into the cooling cylinder 14 and the sealing plate 30 into both ends of the cooling cylinder 14; (2) Weld the cold flow inlet 10, the hot flow outlet 8, the hot flow inlet 18 and the cold flow outlet 1 to the side walls at both ends of the heat exchange cylinder 4 respectively, and weld the support plate B5 to the inner wall in the center of the heat exchange cylinder 4; (3) Weld the cooling cylinder 14 into the opening of the support plate B5; (4) Weld the front cold flow box A6, the front cold flow box B7 and the rear cold flow box A16 and the rear cold flow box B17, which are welded with the support plate 13. (5) Weld the support plate A12 to the front cold flow box A6 and the front cold flow box B7, and weld the support plate C3 to the rear cold flow box A16 and the rear cold flow box B17; (6) Weld the cold flow inner plate A34 with the buffer plate 11 to the front cold flow box A6 and the front cold flow box B7, and weld the cold flow inner plate B2 with the buffer plate 11 to the rear cold flow box A16 and the rear cold flow box B17; (7) Weld the cold flow outer plate A9 and the cold flow outer plate B35 with the buffer plate 11 to the outermost end of the heat exchange cylinder 4 respectively.

Claims

1. A multi-stage turbulent vortex heat exchanger based on uniform cooling, characterized in that: The heat exchanger includes a heat exchange cylinder, a cold flow inlet zone, a front turbulence heat exchange zone, a front vortex heat exchange zone, a cold mixing and homogenizing zone, a rear vortex heat exchange zone, a rear turbulence heat exchange zone, and a cold flow outlet zone. From left to right, the heat exchanger tube contains these zones in sequence. The heat exchange cylinder is welded with a cold flow inlet, a hot flow outlet, a hot flow inlet, and a cold flow outlet. The cold flow inlet and hot flow outlet are located on one side, and the hot flow inlet and cold flow outlet are located on the other side. From left to right, the heat exchange cylinder contains a cold flow outer plate A, a cold flow inner plate A, a support plate A, a support plate B, and a support plate C. The system comprises: an inner cold flow plate A and an outer cold flow plate B; a cold flow buffer zone is located between the outer cold flow plate A and the inner cold flow plate A, with buffer plates welded onto both plates; a cold flow inlet is located above the buffer zone; the inner cold flow plate A and the inner cold flow plate B have three sets of square holes A (upper, middle, and lower); a front turbulence heat exchange zone is located between the inner cold flow plate A and a support plate A, with round holes, square holes B, and square holes C on the support plate A; a hot flow outlet is located above the front turbulence heat exchange zone; and a front vortex heat exchange zone is located between the support plates A and B, containing a front cold flow box A and a front cold flow box B. A and the front cold flow box B are respectively provided with a convex section, a flat section, and a concave section. The front cold flow box B is formed by welding together two upper and lower baffles B, two left and right horizontal plates B, and two front and rear longitudinal plates. The front cold flow box A is formed by welding together two upper and lower baffles A, two left and right horizontal plates A, and two front and rear longitudinal plates. The length of the horizontal plate B is 2.5 times the length of the horizontal plate A. The cold mixing and equalization zone is located in the center of the heat exchange cylinder. The cold mixing and equalization zone is provided with a baffle plate B and a cooling cylinder. The baffle plate B has a round hole and an opening for installing the cooling cylinder. The cooling cylinder is welded to the opening of the baffle plate B. A mixing plate with a round hole is welded inside the cooling cylinder. The front and rear ends of the cooling cylinder are welded with openings. A sealing plate with a square hole D is provided; the rear vortex heat exchange zone is located between support plates B and C, and a rear cold flow box A and a rear cold flow box B are provided in the rear vortex heat exchange zone. A circular hole is provided on support plate C, and a convex section, a flat section, and a concave section are provided on rear cold flow box A and rear cold flow box B respectively; the rear turbulence heat exchange zone is located between support plates C and between the inner cold flow plate B, and a circular hole, a square hole B, and a square hole C are also provided on support plate C. The hot flow inlet is located below the rear turbulence heat exchange zone; the cold flow slow-out zone is located between the inner cold flow plate B and the outer cold flow plate B, and a buffer plate is welded on the outer cold flow plate B and the inner cold flow plate B respectively. The cold flow outlet is located below the cold flow slow-out zone.

2. The heat exchanger based on uniform cooling and multi-stage turbulent vortex heat exchanger as described in claim 1, characterized in that: The heat exchange cylinder has a cylindrical structure; the cold flow outer plate A and the cold flow inner plate A are welded to the inner wall of the heat exchange cylinder. The cold flow outer plate A has a circular structure. Three buffer plates are welded on the cold flow outer plate A and the cold flow inner plate A at equal intervals from top to bottom. The buffer plates of the cold flow outer plate A and the cold flow inner plate A are arranged alternately. The width of the buffer plate is 2 / 3 of the width of the cold flow buffer zone.

3. The heat exchanger based on uniform cooling and multi-stage turbulent vortex heat exchanger as described in claim 1, characterized in that: The support plate A is welded to the inner wall of the heat exchange cylinder. The circular holes and square holes B and C on the support plate A are arranged alternately. Square holes B are located in the middle of the support plate A. The square holes B in the middle of the support plate A are divided into upper and lower layers, with three equally spaced holes in each layer. The support plate A has a total of 23 circular holes. The upper and lower parts of the support plate A each have two layers of square holes C, with one hole in each layer. Square holes B and C are at the same height, and the length of square hole C is 2.5 times the length of square hole B. A space is provided between the cold flow inner plate A and the support plate A. Partial front cold flow boxes A and B are provided. Front cold flow box A passes through and is welded to square holes B and A in the support plate A and the inner cold flow plate A, respectively. Front cold flow box B passes through and is welded to square holes C and A in the support plate A and the inner cold flow plate A, respectively. The support plate C has 37 circular holes. The outer cold flow plate B and the inner cold flow plate B have the same structural dimensions as the outer cold flow plate A and the inner cold flow plate A, respectively. A rectangular hole is provided in the center of the horizontal plate A and the horizontal plate B. A square tube is welded to the center of the horizontal plate A and the horizontal plate B, respectively.

4. A multi-stage turbulent vortex heat exchanger based on uniform cooling as described in claim 1, characterized in that: The front cold flow box A and the front cold flow box B are of equal length and height, as are the rear cold flow box A and the rear cold flow box B. The convex section is upward convex, the flat section is horizontal, and the concave section is downward concave. The longitudinal sections of the convex and concave sections are equilateral triangles. The square tubes are located in the center of the horizontal plate A and the horizontal plate B, respectively. The upper and lower parts of the heat exchange cylinder are provided with two equally spaced front cold flow boxes B, and the middle part of the heat exchange cylinder is provided with three sets of equally spaced upper and lower front cold flow boxes A. Support plates are provided between adjacent front cold flow boxes A and adjacent front cold flow boxes B.

5. A multi-stage turbulent vortex heat exchanger based on uniform cooling as described in claim 1, characterized in that: The sealing plate has two square holes D arranged symmetrically from top to bottom. The square tubes of the front cold flow box A, front cold flow box B, and rear cold flow box A and rear cold flow box B are welded to the square holes D. The cooling cylinder is a cylindrical structure. The mixing plate inside the cooling cylinder is a semi-circular structure. There are four mixing plates inside the cooling cylinder, arranged symmetrically from top to bottom in groups of two. The height of the mixing plate is 3 / 4 of the radius of the cooling cylinder. The support plate B has seven rows of round holes at equal intervals from top to bottom. The round holes on the support plate B are staggered with those on the cooling cylinder.

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