Vortex type heat exchanger based on uniform cooling and provided with multiple sections of disturbances

Abstract

The invention provides a multi-section turbulence vortex type heat exchanger based on uniform cooling, and belongs to the technical field of heat exchangers, the multi-section turbulence vortex type heat exchanger comprises a heat exchange cylinder, a cold flow slow-in area, a front turbulence heat exchange area, a front vortex heat exchange area, a cold mixing uniform temperature area, a rear vortex heat exchange area, a rear turbulence heat exchange area and a cold flow slow-out area. The heat exchanger is characterized in that the heat exchange efficiency is improved through cold and hot flow multi-section turbulent flow and vortex heat exchange, and uniform-temperature cold flow is output through heat exchange between the cold flows so as to achieve stable heat exchange. Buffering layered input of cold flow is achieved through the cold flow slow inlet area, primary turbulent flow heat exchange of cold and hot flow is achieved through the front turbulent flow heat exchange area, primary vortex heat exchange of the cold and hot flow is achieved through the front vortex heat exchange area, uniform-temperature cold flow output is achieved through the cold mixing uniform-temperature area, and secondary vortex heat exchange of the cold and hot flow is achieved through the rear vortex heat exchange area. Secondary turbulent flow heat exchange of the cold flow and the hot flow is achieved through the rear turbulent flow heat exchange area, and layered buffering output of the cold flow is achieved through the cold flow slow outlet area.

Description

Technical Field

[0001] The present invention relates to a heat exchanger based on uniform cooling and with multiple sections of turbulence and vortex, and in particular to a heat exchanger which realizes buffered stratified input of cold flow through a cold flow slow-in zone, realizes primary turbulence heat exchange of cold and hot flow through a front turbulence heat exchange zone, realizes primary vortex heat exchange of cold and hot flow through a front vortex heat exchange zone, realizes output of uniform temperature cold flow through a cold mixed temperature uniform zone, realizes secondary vortex heat exchange of cold and hot flow through a rear vortex heat exchange zone, realizes secondary turbulence heat exchange of cold and hot flow through a rear turbulence heat exchange zone, and realizes stratified buffered output of cold flow through a cold flow slow-out zone, and belongs to the technical research and development field of heat exchangers. Background Art

[0002] Heat exchangers are devices that transfer part of the heat of hot fluid to cold fluid. They play an important role in industrial production such as chemical, petroleum, power, and food. However, the heat exchangers currently used still have the following problems: First, the heat exchange efficiency is low, and the turbulent state of the cold and hot flows in the heat exchanger is poor. The cold and hot flows cannot fully and fully exchange heat, and can only exchange heat on the surface of the cold and hot flows. The internal heat flow needs to be cooled by the heat transfer of the outer low-temperature heat flow, which makes the heat exchange efficiency low; second, the heat exchange is unbalanced. The heat flow temperatures in different areas of the same radial section in the heat exchanger are different, resulting in different temperatures of the cold flow after participating in the heat exchange. Because the cold flow in the heat exchanger is continuously flowing and exchanging heat, in the subsequent heat exchange, cold flows of different temperatures will cause unbalanced subsequent heat exchange, that is, the cold flow with low temperature rise can exchange heat better, while the cold flow with high temperature rise cannot effectively exchange heat, resulting in unbalanced heat exchange of the entire heat exchanger and inability to achieve smooth heat exchange.

[0003] Therefore, in view of the common problems of low heat exchange efficiency and unbalanced heat exchange in the use of existing heat exchangers, a comprehensive consideration should be given to the working mode and structure of the heat exchanger to design a heat exchanger with high heat exchange efficiency and balanced heat exchange. Summary of the invention

[0004] Aiming at the common problems of low heat exchange efficiency and unbalanced heat exchange in the use of existing heat exchangers, the present invention provides a heat exchanger based on uniform cooling and multi-stage vortex, which can effectively solve the above problems.

[0005] The present invention is based on uniform cooling and multi-stage vortex heat exchanger adopts the following technical solutions: A soaking and multi-segmented disturbing and vortex heat exchanger, comprising a heat exchange cylinder, a cold flow slow-in area, a front disturbing heat exchange area, a front vortex heat exchange area, a cold mixing and temperature equalizing area, a rear vortex heat exchange area, a rear disturbing heat exchange area, and a cold flow slow-out area. Inside the heat exchange tube, there are successively arranged from left to right a cold flow slow-in area, a front disturbing heat exchange area, a front vortex heat exchange area, a cold mixing and temperature equalizing area, a rear vortex heat exchange area, a rear disturbing heat exchange area, and a cold flow slow-out area; a cold flow inlet, a hot flow outlet, a hot flow inlet, and a cold flow outlet are welded on the heat exchange cylinder. The cold flow inlet and the hot flow outlet are on one side, and the hot flow inlet and the cold flow outlet are on the other side. Inside the heat exchange cylinder, there are successively arranged from left to right a cold flow outer plate A, a cold flow inner plate A, a support disturbing plate A, a support disturbing plate B, a support disturbing plate C, a cold flow inner plate B, and a cold flow outer plate B; the cold flow slow-in area is located between the cold flow outer plate A and the cold flow inner plate A. Buffer plates are welded on the cold flow outer plate A and the cold flow inner plate A. The cold flow inlet is located above the cold flow slow-in area. There are three groups of square holes A, namely upper, middle, and lower, on the cold flow inner plate A; the front disturbing heat exchange area is located between the cold flow inner plate A and the support disturbing plate A. Round holes, square holes B, and square holes C are provided on the support disturbing plate A. The hot flow outlet is located above the front disturbing heat exchange area; the front vortex heat exchange area is located between the support disturbing plate A and the support disturbing plate B. A front cold flow box A and a front cold flow box B are provided in the front vortex heat exchange area. The front cold flow box A and the front cold flow box B are respectively successively provided with convex disturbing sections, flat transition sections, and concave disturbing sections. The length value of the transverse plate B is 2.5 times the length value of the transverse plate A; the cold mixing and temperature equalizing area is located in the middle of the heat exchange cylinder. A support disturbing plate B and a soaking cylinder are provided in the cold mixing and temperature equalizing area. Round holes and openings for installing the soaking cylinder are provided on the support disturbing plate B. The soaking cylinder is welded on the openings of the support disturbing plate B. A mixing disturbing plate with round holes is welded inside the soaking cylinder. Sealing plates with square holes D are welded at the front and rear ends of the soaking cylinder; the rear vortex heat exchange area is located between the support disturbing plate B and the support disturbing plate C. A rear cold flow box A and a rear cold flow box B are provided in the rear vortex heat exchange area. Round holes are provided on the support disturbing plate C. The rear cold flow box A and the rear cold flow box B are respectively successively provided with convex disturbing sections, flat transition sections, and concave disturbing sections; the rear disturbing heat exchange area is located between the support disturbing plate C and the cold flow inner plate B. Round holes, square holes B, and square holes C are also provided on the support disturbing plate C. The hot flow inlet is located below the rear disturbing heat exchange area; the cold flow slow-out area is located between the cold flow inner plate B and the cold flow outer plate B. Buffer plates are respectively welded on the cold flow outer plate B and the cold flow inner plate B. The cold flow outlet is located below the cold flow slow-out area.

[0006] The heat exchange cylinder is of a cylindrical structure; the cold flow outer plate A and the cold flow inner plate A are respectively welded on the inner wall of the heat exchange cylinder. The cold flow outer plate A is of a circular structure. Three buffer plates are respectively welded at equal intervals from top to bottom on the cold flow outer plate A and the cold flow inner plate A. The buffer plates on the cold flow outer plate A and the buffer plates on the cold flow inner plate A are arranged staggeredly. The width value of the buffer plate is 2 / 3 of the width value of the cold flow slow-in area.

[0007] The support plate A is welded on the inner wall of the heat exchange tube, and the circular holes and square holes B and square holes C on the support plate A are arranged alternately. The square hole B is located in the middle of the support plate A. The square holes B in the middle of the support plate A are divided into two layers, upper and lower, and three holes are arranged at equal intervals in each layer. The number of circular holes on the support plate A is 23; the upper and lower parts of the support plate A are respectively provided with two layers of square holes C, and the number of holes in each layer is 1; the square holes B and the square holes C are of the same height, and the length of the square hole C is 2.5 times the length of the square hole B; part of the front cold flow box A and the front cold flow box B are provided between the cold flow inner plate A and the support plate A, and the front cold flow box A passes through and is welded to the support plate A. The front cold flow box B passes through and is welded to the square hole C of the support and spoiler plate A and the square hole A of the cold flow inner plate A respectively; the number of circular holes on the support and spoiler plate C is 37, and the cold flow outer plate B and the cold flow inner plate B have the same structural dimensions as the cold flow outer plate A and the cold flow inner plate A respectively; the front cold flow box B is welded by the upper and lower spoiler plates B, the left and right horizontal plates B and the front and rear longitudinal plates, and the front cold flow box A is welded by the upper and lower spoiler plates A, the left and right horizontal plates A and the front and rear longitudinal plates respectively, and a rectangular hole is provided in the middle of the horizontal plate A and the horizontal plate B, and a square tube is welded in the middle of the horizontal plate A and the horizontal plate B respectively.

[0008] The front cold flow box A and the front cold flow box B are of equal length and height, the rear cold flow box A and the rear cold flow box B are of equal length and height, the convex section is convex upward, the flat section is horizontal, the concave section is concave downward, and the longitudinal sections of the convex section and the concave section are equilateral triangles respectively; the square tubes are respectively located in the middle of the transverse plate A and the transverse plate B; two equally spaced front cold flow boxes B are respectively provided at the upper and lower parts of the heat exchange tube, and three groups of upper and lower equally spaced front cold flow boxes A are provided in the middle part of the heat exchange tube, and support plates are respectively provided between adjacent front cold flow boxes A and front cold flow boxes B.

[0009] The number of square holes D on the sealing plate is 2 and they are arranged symmetrically up and down. The square tubes of the front cold flow box A, the front cold flow box B and the rear cold flow box A, the rear cold flow box B are respectively welded on the square holes D and are the same as the uniform cooling cylinder; the uniform cooling cylinder is a cylindrical structure, and the turbulence plate in the uniform cooling cylinder is a semicircular structure. There are 4 turbulence plates in the uniform cooling cylinder and 2 of them are arranged symmetrically up and down in a group. The height of the turbulence plate is 3 / 4 of the radius of the uniform cooling cylinder; 7 rows of circular holes are arranged at equal intervals from top to bottom on the support disturbance plate B, and the circular holes on the support disturbance plate B are staggered with the uniform cooling cylinder.

[0010] The present invention realizes buffered and layered input of cold flow through the cold flow slow-in zone, that is, the cold flow entering through the cold flow inlet is buffered and layered through the buffer plate of the cold flow slow-in zone. Specifically, when the cold flow enters, the buffer plate prevents the cold flow from flowing in in large quantities and impacting and damaging the heat exchanger, and the cold flow is blocked, pressurized and changed in direction. The pressurized and changed-direction cold flow is convenient for pressurized input to the front cold flow box A and the front cold flow box B.

[0011] In the present invention, the buffer plates of the cold flow outer plate A and the cold flow inner plate A are arranged in an alternating manner. Through this design, it is convenient to make the cold flow partitioned and layered and flow forward to the front cold flow box A and the front cold flow box B. Under the alternating arrangement, the turbulence of the cold flow can also be realized, and heat exchange is carried out with the turbulence on the other side of the cold flow inner plate A.

[0012] In the present invention, the width value of the buffer plate is 2 / 3 of the width value of the cold flow slow-in area. Through this design, the change of the cold flow direction is realized.

[0013] In the present invention, the primary turbulence heat exchange between the hot and cold flows is realized through the front turbulence heat exchange area, that is, the hot flow is subjected to primary turbulence heat exchange through some of the front cold flow box A and the front cold flow box B in the front turbulence heat exchange area. Specifically, the front cold flow box A and the front cold flow box B change the flow direction of the hot flow in the front turbulence heat exchange area, playing a role in disturbing the flow, so that the hot flow exchanges heat with the cold flow in the cold flow box A and the front cold flow box B under the turbulent state.

[0014] In the present invention, the round holes on the support baffle plate A and the square holes B and C are arranged in an alternating manner. Through this design, the hot flow flows respectively above and below the front cold flow box A and the front cold flow box B, realizing all-round cold and hot flow exchange and improving the heat exchange efficiency.

[0015] In the present invention, the number of round holes on the support baffle plate C is set to 37, and the number of round holes on the support baffle plate A is 23. Through this design, the hot flow can quickly enter the rear turbulence heat exchange area through the support baffle plate C, and due to the design of fewer round holes at the support baffle plate A, the hot flow slowly flows forward to the front turbulence heat exchange area, extending the residence time of the hot flow in the front vortex heat exchange area for sufficient heat exchange.

[0016] In the present invention, the primary vortex heat exchange between the hot and cold flows is realized through the front vortex heat exchange area, that is, the front cold flow box A and the front cold flow box B in the front vortex heat exchange area cause the hot flow flowing through them and the internal cold flow to generate vortices respectively. By using the generated series of vortices, the heat exchange between the cold and hot flows is accelerated, and the heat exchange efficiency is improved. Taking the front cold flow box A as an example, when the cold flow flows to the convex disturbance section, since the convex disturbance section bulges upward and changes the flow channel, it prompts the cold flow to change the flow direction accordingly, and vortices are generated before and after the raised end of the internal flow channel, increasing the turbulent motion of the cold flow and enabling more cold flow to participate in the heat exchange with the hot flow; while the hot flow outside the front cold flow box A generates vortices before and after the convex disturbance section when flowing through it, 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 disturbance section, the heat exchange efficiency is improved through the generated vortices; and a flat transition section is provided between the convex disturbance section and the concave disturbance section, enabling the cold and hot flows to have a smooth transition section between the two vortices, that is, it can utilize this transition section to fully exchange heat between the cold and hot flows 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.

[0017] The present invention is respectively provided with a convex disturbance section, a flat transition section and a concave disturbance section on the front cold flow box A and the front cold flow box B in sequence. Through this design, vortices are respectively generated in the cold and hot flows. The present invention positions the square tube at the center of the transverse plate A and the transverse plate B respectively. Through this design, the cold flow quickly fills the front cold flow box A and the front cold flow box B through the square tube.

[0018] The present invention sets the longitudinal sections of the convex disturbance section and the concave disturbance section as equilateral triangles respectively. Through this design, it is not only convenient for processing and manufacturing, but also can generate equal vortices before and after the convex disturbance section and the concave disturbance section respectively, ensuring the balance of vortex heat transfer.

[0019] The present invention sets the length value of the transverse plate B to 2.5 times the length value of the transverse plate A. Through this design, it is convenient to place the front cold flow box B with a large cross-section on the upper and lower parts of the heat exchange cylinder, and place multiple front cold flow boxes A with a small cross-section in the middle of the heat exchange cylinder, realizing a reasonable layout within the limited space of the heat exchange cylinder.

[0020] The present invention is respectively provided with support plates between adjacent front cold flow boxes A and front cold flow boxes B. Through this design, it can not only improve the stiffness of the front cold flow box A and the front cold flow box B, but also play a role in disturbing the hot flow through the support plates, enabling the hot flow to participate in heat transfer in a turbulent state.

[0021] The present invention realizes the output of a uniform-temperature cold flow through the cold mixing and temperature equalizing zone, that is, the cold flow of adjacent front cold flow boxes A or front cold flow boxes B is collected by the equalizing cylinder in the cold mixing and temperature equalizing zone. Under the action of the mixing disturbance plate, the cold flow entering the equalizing cylinder is fully mixed and heat exchanged, and the cold flow is output to the rear cold flow box A or the rear cold flow box B in a uniform-temperature state, ensuring the uniformity and stability of the heat transfer of the subsequent hot flow by the rear cold flow box A or the rear cold flow box B.

[0022] The present invention is provided with a mixing disturbance plate with round holes in the equalizing cylinder. Through this design, the mixing and disturbing effect on the cold flow is realized, that is, the mixing disturbance plate plays a role in blocking and disturbing the hot flow passing through it, and plays a role in mixing and impacting the disturbed cold flow through the round holes on it, thereby accelerating the heat exchange between the cold flows so that the cold flow is output in a uniform-temperature state.

[0023] The present invention is provided with an equalizing cylinder in the center of the heat exchange cylinder. Through this design, the non-uniform-temperature cold flow after heat exchange in the first half of the heat exchange cylinder is collected, and the non-uniform-temperature cold flow is fully heat exchanged in the equalizing cylinder to reach a uniform-temperature state.

[0024] The present invention realizes the secondary vortex heat exchange of the cold and hot flows through the rear vortex heat exchange zone, that is, the rear cold flow box A and the rear cold flow box B in the rear vortex heat exchange zone respectively generate vortices for the hot flow passing through them and the cold flow flowing through them, and the generated vortices are used to make the cold and hot flows fully heat exchanged, improving the heat exchange efficiency.

[0025] The present invention realizes the secondary turbulent heat exchange between the hot and cold flows through the rear turbulent heat exchange area, that is, the partial rear cold flow boxes A and B in the rear turbulent heat exchange area perform secondary turbulent heat exchange on the hot flow.

[0026] The present invention realizes the stratified buffering output of the cold flow through the cold flow slow-out area, that is, the buffer plate in the cold flow slow-out area performs stratified buffering output on the cold flow flowing towards the cold flow outlet.

[0027] The beneficial effects of the present invention are as follows: the cold flow is buffered and stratified input through the cold flow slow-in area, the primary turbulent heat exchange between the hot and cold flows is realized through the front turbulent heat exchange area, the primary vortex heat exchange between the hot and cold flows is realized through the front vortex heat exchange area, the output of a uniformly temperature-controlled cold flow is realized through the cold mixing and temperature equalizing area, the secondary vortex heat exchange between the hot and cold flows is realized through the rear vortex heat exchange area, the secondary turbulent heat exchange between the hot and cold flows is realized through the rear turbulent heat exchange area, and the stratified buffering output of the cold flow is realized through the cold flow slow-out area. Brief Description of the Drawings

[0028] Figure 1 It is the overall front view structural schematic diagram of the present invention.

[0029] Figure 2 It is the layout schematic diagram of the buffer plate on the cold flow outer plate A of the present invention.

[0030] Figure 3 It is the structural schematic diagram of the cold flow inner plate A of the present invention.

[0031] Figure 4 It is the partial structural schematic diagram of the cold flow slow-in area and the front turbulent heat exchange area of the present invention.

[0032] Figure 5 It is the structural schematic diagram of the support baffle A of the present invention.

[0033] Figure 6 It is the layout schematic diagram of the temperature equalizing cylinder on the support baffle B of the present invention.

[0034] Figure 7 It is the partial structural schematic diagram of the front cold flow box B of the present invention.

[0035] Figure 8 It is the structural schematic diagram of the front cold flow box B of the present invention.

[0036] Figure 9 It is the structural schematic diagram of the front cold flow box A of the present invention.

[0037] Figure 10 It is the partial structural schematic diagram of the cold mixing and temperature equalizing area of the present invention.

[0038] Figure 11 It is the structural schematic diagram of the sealing plate of the present invention.

[0039] Figure 12It is a schematic structural diagram of the post-cooling flow box B of the present invention.

[0040] Figure 13 It is a schematic structural diagram of the post-cooling flow box A of the present invention.

[0041] Figure 14 It is a schematic structural diagram of the support baffle C of the present invention.

[0042] Among them: 1. Cold flow outlet, 2. Inner cold flow plate B, 3. Support baffle C, 4. Heat exchange cylinder, 5. Support baffle B, 6. Front cold flow box A, 7. Front cold flow box B, 8. Heat flow outlet, 9. Outer cold flow plate A, 10. Cold flow inlet, 11. Buffer plate, 12. Support baffle A, 13. Support plate, 14. Equalizing cylinder, 15. Mixing baffle, 16. Post-cooling flow box A, 17. Post-cooling flow box B, 18. Heat flow inlet, 19. Square hole A, 20. Round hole, 21. Square hole B, 22. Square hole C, 23. Convex baffle section, 24. Flat section, 25. Concave baffle section, 26. Square pipe, 27. Horizontal plate B, 28. Turbulence baffle B, 29. Vertical plate, 30. Sealing plate, 31. Square hole D, 32. Horizontal plate A, 33. Turbulence baffle A, 34. Inner cold flow plate A, 35. Outer cold flow plate B. Detailed implementation manner

[0043] As Figure 1 shown, a kind of equalizing and multi-section disturbing and vortex type heat exchanger includes a heat exchange cylinder 4, a cold flow slow-in area, a front disturbing heat exchange area, a front vortex heat exchange area, a cold mixing and equalizing temperature area, a rear vortex heat exchange area, a rear disturbing heat exchange area, and a cold flow slow-out area. The cold flow slow-in area, the front disturbing heat exchange area, the front vortex heat exchange area, the cold mixing and equalizing temperature area, the rear vortex heat exchange area, the rear disturbing heat exchange area, and the cold flow slow-out area are arranged in sequence from left to right inside the heat exchange tube; the cold flow inlet 10, the heat flow outlet 8, the heat flow inlet 18, and the cold flow outlet 1 are welded on the heat exchange cylinder 4. The cold flow inlet 10 and the heat flow outlet 8 are on one side, and the heat flow inlet 18 and the cold flow outlet 1 are on the other side. The cold flow outer plate A 9, the cold flow inner plate A 34, the support baffle A 33, the support baffle B 5, the support baffle C 3, the cold flow inner plate B 2, and the cold flow outer plate B 35 are arranged in sequence from left to right inside the heat exchange cylinder 4.

[0044] Combined with Figure 2 , Figure 3 and Figure 4 shown, the cold flow slow-in area is located between the cold flow outer plate A 9 and the cold flow inner plate A 34. The buffer plate 11 is welded on the cold flow outer plate A 9 and the cold flow inner plate A 34. The cold flow inlet 10 is located above the cold flow slow-in area. There are three groups of square holes A 19 on the cold flow inner plate A 34, namely upper, middle, and lower.

[0045] The cold flow outer plate A9 and the cold flow inner plate A34 are respectively welded on the inner wall of the heat exchange tube 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, and the width of the buffer plate 11 is 2 / 3 of the width of the cold flow slow-in zone.

[0046] The present invention realizes buffered and layered input of cold flow through the cold flow slow-in zone, that is, the cold flow entering through the cold flow inlet 10 is buffered and layered through the buffer plate 11 in the cold flow slow-in zone. Specifically, when the cold flow enters, the buffer plate 11 prevents the cold flow from flowing in in large quantities and impacting and damaging the heat exchanger, and the cold flow is blocked, pressurized and changed in direction. The pressurized and changed-direction cold flow is convenient for pressurized input to the front cold flow box A6 and the front cold flow box B7.

[0047] 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 to the front cold flow box A6 and the front cold flow box B7 in a partitioned and layered manner. In addition, under the staggered arrangement, the cold flow turbulence can be achieved to exchange heat with the turbulence on the other side of the cold flow inner plate A34.

[0048] The width of the buffer plate 11 of the present invention is 2 / 3 of the width of the cold flow slow-in zone, and the change of the cold flow direction is achieved through this design.

[0049] Combination Figure 5 As shown, the front spoiler heat exchange zone is located between the cold flow inner plate A34 and the support spoiler plate A12, and the support spoiler plate A12 is provided with a circular hole 20, a square hole B21 and a square hole C22. The hot flow outlet 8 is located above the front spoiler heat exchange zone, and the number of the circular holes 20 on the support spoiler plate A12 is 23.

[0050] The support plate A12 is welded on the inner wall of the heat exchange tube 4. The circular holes 20 and the square holes B21 and C22 on the support plate A12 are arranged alternately. The square hole B21 is located in the middle of the support plate A12. The square holes B21 in the middle of the support plate A12 are divided into two layers, upper and lower, and three holes are arranged at equal intervals in each layer. The upper and lower parts of the support plate A12 are respectively provided with two layers of square holes C22, and the number of holes in each layer is one. The square holes B21 and C22 are of the same height. The length of hole C22 is 2.5 times the length of square hole B21; part of the front cold flow box A6 and the front cold flow box B7 are provided between the cold flow inner plate A34 and the support plate A12, and the front cold flow box A6 passes through and is welded to the square hole B21 of the support plate A12 and the square hole A19 of the cold flow inner plate A34, and the front cold flow box B7 passes through and is welded to the square hole C22 of the support plate A12 and the square hole A19 of the cold flow inner plate A34.

[0051] The present invention realizes the primary turbulent heat exchange between the hot and cold flows through the front turbulent heat exchange area, that is, the primary turbulent heat exchange of the hot flow is carried out by means of some of the front cold flow boxes A6 and front cold flow boxes B7 in the front turbulent heat exchange area. Specifically, the front cold flow boxes A6 and front cold flow boxes B7 change the flow direction of the hot flow in the front turbulent heat exchange area, playing a role in disturbing the flow, so that the hot flow exchanges heat with the cold flow in the cold flow box A and the front cold flow box B7 under turbulent conditions.

[0052] The present invention arranges the round holes 20, square holes B21 and square holes C22 on the support baffle A12 in a staggered manner. Through this design, the hot flow flows respectively above and below the front cold flow box A6 and the front cold flow box B7, realizing the all-round exchange of cold and hot flows and improving the heat exchange efficiency.

[0053] The present invention sets the number of round holes 20 on the support baffle C3 to 37 and the number of round holes 20 on the support baffle A12 to 23. Through this design, the hot flow can quickly enter the rear turbulent heat exchange area through the support baffle C3, and due to the design of fewer round holes 20 at the support baffle A12, the hot flow slowly flows to the front turbulent heat exchange area, prolonging the residence time of the hot flow in the front vortex heat exchange area for sufficient heat exchange.

[0054] Combined Figure 6 、 Figure 7 、 Figure 8 and Figure 9 As shown, the front vortex heat exchange area is located between the support baffle A12 and the support baffle B5. The front cold flow boxes A6 and front cold flow boxes B7 are arranged in the front vortex heat exchange area. The front cold flow boxes A6 and front cold flow boxes B7 are of equal length and equal height. The convex disturbance sections 23, flat transition sections 24 and concave disturbance sections 25 are successively arranged on the front cold flow boxes A6 and front cold flow boxes B7 respectively. The front cold flow box B7 is formed by welding the upper and lower two turbulent flow plates B28, the left and right two transverse plates B27 and the front and rear two longitudinal plates 29. The front cold flow box A6 is respectively formed by welding the upper and lower two turbulent flow plates A33, the left and right two transverse plates A32 and the front and rear two longitudinal plates 29. Rectangular holes are provided in the centers of the transverse plate A32 and the transverse plate B27, and square tubes 26 are respectively welded in the centers of the transverse plate A32 and the transverse plate B27; the length value of the transverse plate B27 is 2.5 times the length value of the transverse plate A32.

[0055] The convex disturbance section 23 protrudes upward, the flat transition section 24 is horizontal, the concave disturbance section 25 is recessed downward, and the longitudinal sections of the convex disturbance section 23 and the concave disturbance section 25 are respectively equilateral triangles; the square tubes 26 are respectively located in the centers of the transverse plate A32 and the transverse plate B27; 2 front cold flow boxes B7 with equal spacing are respectively provided at the upper and lower parts of the heat exchange cylinder 4, and 3 groups of front cold flow boxes A6 with equal upper and lower spacing are provided in the middle of the heat exchange cylinder 4. Support plates 13 are respectively arranged between the adjacent front cold flow boxes A6 and front cold flow boxes B7.

[0056] The present invention realizes the primary vortex heat exchange of cold and hot fluids through the front vortex heat exchange area, that is, through the front cold fluid box A6 and the front cold fluid box B7 in the front vortex heat exchange area, the hot fluid flowing through them and the internal cold fluid respectively generate vortices. By using the generated series of vortices, the heat exchange between the cold and hot fluids is accelerated, and the heat exchange efficiency is improved. Taking the front cold fluid box A6 as an example, when the cold fluid flows to the convex disturbance section 23, since the convex disturbance section 23 bulges upward and changes the flow channel, it prompts the cold fluid to change its flow direction accordingly, and vortices are generated before and after the raised end of the internal flow channel, increasing the turbulent motion of the cold fluid and enabling more cold fluid to participate in the heat exchange with the hot fluid; while the hot fluid outside the front cold fluid box A6 also generates vortices before and after the convex disturbance section 23 when flowing through it, prompting more hot fluid to participate in the heat exchange with the cold fluid; similarly, when the cold and hot fluids flow through the concave disturbance section 25, the heat exchange efficiency is improved through the generated vortices; and a flat transition section 24 is provided between the convex disturbance section 23 and the concave disturbance section 25, enabling the cold and hot fluids to have a smooth transition section between the two vortices, that is, it can make the cold and hot fluids fully exchange heat under the action of the vortices by using this transition section, and can also prevent the direct interaction between the two vortices, so as to avoid reducing the heat exchange efficiency and generating vortex collision noise.

[0057] The present invention is respectively provided with a convex disturbance section 23, a flat transition section 24 and a concave disturbance section 25 on the front cold fluid box A6 and the front cold fluid box B7 in sequence, and through this design, the cold and hot fluids respectively generate vortices. The present invention places the square pipe 26 in the middle of the transverse plate A32 and the transverse plate B27 respectively. Through this design, the cold fluid fills the front cold fluid box A6 and the front cold fluid box B7 quickly through the square pipe 26.

[0058] The present invention sets the longitudinal sections of the convex disturbance section 23 and the concave disturbance section 25 as equilateral triangles respectively. Through this design, it is not only convenient for processing and manufacturing, but also can generate equal vortices before and after the convex disturbance section 23 and the concave disturbance section 25 respectively, ensuring the balance of vortex heat exchange.

[0059] The present invention sets the length value of the transverse plate B27 to 2.5 times the length value of the transverse plate A32. Through this design, it is convenient to place the front cold fluid box B7 with a large cross-section at the upper and lower parts of the heat exchange cylinder 4, and place multiple front cold fluid boxes A6 with a small cross-section in the middle of the heat exchange cylinder 4, realizing a reasonable layout within the limited space of the heat exchange cylinder 4.

[0060] The present invention is respectively provided with support plates 13 between adjacent front cold fluid boxes A6 and front cold fluid boxes B7. Through this design, it can not only improve the stiffness of the front cold fluid box A6 and the front cold fluid box B7, but also play a role in disturbing the hot fluid through the support plates 13, enabling the hot fluid to participate in the heat exchange in a turbulent state.

[0061] Combined with Figure 10 and Figure 11As shown in the figure, the cold mixing and temperature equalizing zone is located in the center of the heat exchange cylinder 4. Inside the cold mixing and temperature equalizing zone, there are support baffles B5 and a temperature equalizing cylinder 14. The support baffle B5 is provided with round holes 20 and openings for installing the temperature equalizing cylinder 14. The temperature equalizing cylinder 14 is welded to the openings of the support baffle B5. Inside the temperature equalizing cylinder 14, there is a mixing baffle 15 with round holes 20 welded inside. At the front and rear ends of the temperature equalizing cylinder 14, there are sealing plates 30 with square holes D31 opened.

[0062] The number of square holes D31 on the sealing plate 30 is 2, and they are symmetrically arranged up and down. The square pipes 26 of the front cold flow box A6, front cold flow box B7, rear cold flow box A16, and rear cold flow box B17 are respectively welded to the square holes D31 and are the same as the temperature equalizing cylinder 14. The temperature equalizing cylinder 14 is of a cylindrical structure. The mixing baffle 15 inside the temperature equalizing cylinder 14 is of a semi-circular structure. There are 4 mixing baffles 15 inside the temperature equalizing cylinder 14, and 2 are in a group and symmetrically arranged up and down. The height value of the mixing baffle 15 is 3 / 4 of the radius value of the temperature equalizing cylinder 14. The support baffle B5 is provided with 7 rows of round holes 20 at equal intervals from top to bottom. The round holes 20 on the support baffle B5 are arranged staggeredly with the temperature equalizing cylinder 14.

[0063] The present invention realizes the output of temperature-equalized cold flow through the cold mixing and temperature equalizing zone, that is, the cold flow from the adjacent front cold flow box A6 or front cold flow box B7 is collected by the temperature equalizing cylinder 14 in the cold mixing and temperature equalizing zone. Under the action of the mixing baffle 15, the cold flow entering the temperature equalizing 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 temperature-equalized state, ensuring the uniformity and stability of the heat exchange of the subsequent hot flow by the rear cold flow box A16 or rear cold flow box B17.

[0064] The present invention is provided with a mixing baffle 15 with round holes 20 inside the temperature equalizing cylinder 14. Through this design, the mixing and turbulence effect on the cold flow is realized, that is, the mixing baffle 15 plays a role in blocking and disturbing the flowing hot flow, and the round holes 20 on it play a role in mixing and impacting the cold flow after the disturbance, thereby accelerating the heat exchange between the cold flows and enabling the cold flow to be output in a temperature-equalized state.

[0065] The present invention is provided with a temperature equalizing cylinder 14 in the center of the heat exchange cylinder 4. Through this design, the non-isothermal cold flow after heat exchange in the first half of the heat exchange cylinder 4 is collected, and the non-isothermal cold flow is fully heat exchanged inside the temperature equalizing cylinder 14 to reach a temperature-equalized state.

[0066] Combined Figure 12 、 Figure 13 and Figure 14 As shown in the figure, the rear vortex heat exchange zone is between the support baffle B5 and the support baffle C3. Inside the rear vortex heat exchange zone, there are a rear cold flow box A16 and a rear cold flow box B17. The support baffle C3 is provided with round holes 20. The rear cold flow box A16 and the rear cold flow box B17 are of the same length and height. The rear cold flow box A16 and the rear cold flow box B17 are respectively provided with a convex disturbance section 23, a flat transition section 24, and a concave disturbance section 25 in sequence.

[0067] The present invention realizes the secondary vortex heat exchange of cold and hot fluids through the rear vortex heat exchange area, that is, the rear cold fluid box A16 and the rear cold fluid box B17 in the rear vortex heat exchange area generate vortices for the hot fluid flowing through them and the cold fluid flowing through them respectively, and the generated vortices are used to make the cold and hot fluids fully exchange heat, thereby improving the heat exchange efficiency.

[0068] The rear turbulent flow heat exchange area is located between the support turbulent plates C3 and between the cold fluid inner plates B2. The support turbulent plates C3 are also provided with round holes 20, square holes B21 and square holes C22. The hot fluid inlet 18 is located below the rear turbulent flow heat exchange area, and the number of round holes 20 on the support turbulent plates C3 is 37.

[0069] The present invention realizes the secondary turbulent flow heat exchange of cold and hot fluids through the rear turbulent flow heat exchange area, that is, the partial rear cold fluid boxes A16 and rear cold fluid boxes B17 in the rear turbulent flow heat exchange area perform secondary turbulent flow heat exchange on the hot fluid.

[0070] The cold fluid slow outlet area is located between the cold fluid inner plates B2 and between the cold fluid outer plates B. The cold fluid outer plate B35 and the cold fluid inner plate B have the same structural dimensions as the cold fluid outer plate A9 and the cold fluid inner plate A34 respectively. Buffer plates 11 are welded on the cold fluid outer plate B35 and the cold fluid inner plate B respectively. The cold fluid outlet 1 is located below the cold fluid slow outlet area.

[0071] The present invention realizes the stratified buffering output of the cold fluid through the cold fluid slow outlet area, that is, the buffer plates 11 in the cold fluid slow outlet area perform stratified buffering output on the cold fluid flowing towards the cold fluid outlet 1.

[0072] The assembly process of the entire heat exchanger is as follows: (1) Weld the mixing turbulent plate 15 inside the uniform cooling cylinder 14, and weld the sealing plates 30 at both ends of the uniform cooling cylinder 14; (2) Weld the cold fluid inlet 10, the hot fluid outlet 8, the hot fluid inlet 18 and the cold fluid outlet 1 on the side walls at both ends of the heat exchange cylinder 4 respectively, and weld the support turbulent plate B5 on the inner wall in the middle of the heat exchange cylinder 4; (3) Weld the uniform cooling cylinder 14 in the openings of the support turbulent plate B5; (4) Weld the front cold fluid box A6, the front cold fluid box B7, the rear cold fluid box A16 and the rear cold fluid box B17 welded with the support plates 13 on the uniform cooling cylinder 14; (5) Sleeve-weld the support turbulent plate A12 on the front cold fluid box A6 and the front cold fluid box B7, and sleeve-weld the support turbulent plate C3 on the rear cold fluid box A16 and the rear cold fluid box B17; (6) Sleeve-weld the cold fluid inner plate A34 welded with the buffer plate 11 on the front cold fluid box A6 and the front cold fluid box B7, and sleeve-weld the cold fluid inner plate B2 welded with the buffer plate 11 on the rear cold fluid box A16 and the rear cold fluid box B17; (7) Weld the cold fluid outer plate A9 and the cold fluid outer plate B35 welded with the buffer plate 11 on the outermost ends of the heat exchange cylinder 4 respectively.

Claims

1. A heat exchanger based on uniform cooling and multi-stage turbulence and vortex, comprising a heat exchange tube, a cold flow slow entry zone, a front turbulence heat exchange zone, a front vortex heat exchange zone, a cold mixing temperature uniformity zone, a rear vortex heat exchange zone, a rear turbulence heat exchange zone, and a cold flow slow exit zone. The heat exchange tube is provided with a cold flow slow entry zone, a front turbulence heat exchange zone, a front vortex heat exchange zone, a cold mixing temperature uniformity zone, a rear vortex heat exchange zone, a rear turbulence heat exchange zone, and a cold flow slow exit zone from left to right in sequence; it is characterized in that: 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 the hot flow outlet are located on one side, and the hot flow inlet and the cold flow outlet are located on the other side. From left to right, the heat exchange cylinder is provided with a cold flow outer plate A, a cold flow inner plate A, a support plate A, a support plate B, a support plate C, a cold flow inner plate B, and a cold flow outer plate B; the cold flow slow-in zone is located between the cold flow outer plate A and the cold flow inner plate A, and a buffer plate is welded on the cold flow outer plate A and the cold flow inner plate A. The cold flow inlet is located at the cold flow outer plate A and the cold flow inner plate A. Above the slow-entry zone, the cold flow inner plate A is provided with three groups of square holes A, namely, upper, middle and lower. The front spoiler heat exchange zone is located between the cold flow inner plate A and the support spoiler plate A. The support spoiler plate A is provided with a circular hole, a square hole B and a square hole C. The hot flow outlet is located above the front spoiler heat exchange zone. The front vortex heat exchange zone is located between the support spoiler plate A and the support spoiler plate B. The front vortex heat exchange zone is provided with a front cold flow box A and a front cold flow box B. The front cold flow box A and the front cold flow box B are provided with a convex spoiler section, a flat section and a concave spoiler section respectively. The length of the horizontal plate B is The value is 2.5 times the length of the horizontal plate A; the cold mixing uniform temperature zone is located in the middle of the heat exchange cylinder, and a support plate B and a uniform cooling cylinder are arranged in the cold mixing uniform temperature zone. The support plate B is provided with a circular hole and an opening for installing the uniform cooling cylinder. The uniform cooling cylinder is welded to the opening of the support plate B. A mixing plate with a circular hole is welded in the uniform cooling cylinder. A sealing plate with a square hole D is welded at the front and rear ends of the uniform cooling cylinder; the rear vortex heat exchange zone is between the support plate B and the support plate C, and a rear cold flow box A and a rear cold flow box are arranged in the rear vortex heat exchange zone. Box B, a circular hole is provided on the support and disturbance plate C, and a convex disturbance section, a flat section and a concave disturbance section are respectively provided on the rear cold flow box A and the rear cold flow box B in sequence; the rear spoiler heat exchange zone is located between the support and disturbance plates C and the cold flow inner plate B, and a circular hole, a square hole B and a square hole C are also provided on the support and disturbance plate C, and the hot flow inlet is located below the rear spoiler heat exchange zone; the cold flow slow-out zone is located between the cold flow inner plate B and the cold flow outer plate B, and buffer plates are respectively welded on the cold flow outer plate B and the cold flow inner plate B, and the cold flow outlet is located below the cold flow slow-out zone.

2. A heat exchanger based on uniform cooling and multi-stage vortex heat exchanger according to claim 1, characterized in that: The heat exchange cylinder is a cylindrical structure; the cold flow outer plate A and the cold flow inner plate A are respectively welded on the inner wall of the heat exchange cylinder, the cold flow outer plate A is a circular structure, and 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 buffer plates of the cold flow inner plate A are arranged alternately, and the width of the buffer plates is 2 / 3 of the width of the cold flow slow-in zone.

3. The heat exchanger based on uniform cooling and multi-stage vortex heat exchanger according to claim 1, characterized in that: The support plate A is welded on the inner wall of the heat exchange tube, and the circular holes and square holes B and square holes C on the support plate A are arranged alternately. The square hole B is located in the middle of the support plate A. The square holes B in the middle of the support plate A are divided into two layers, upper and lower, and three holes are arranged at equal intervals in each layer. The number of circular holes on the support plate A is 23; the upper and lower parts of the support plate A are respectively provided with two layers of square holes C, and the number of holes in each layer is 1; the square holes B and the square holes C are of the same height, and the length of the square hole C is 2.5 times the length of the square hole B; part of the front cold flow box A and the front cold flow box B are provided between the cold flow inner plate A and the support plate A, and the front cold flow box A passes through and is welded to the support plate A. The front cold flow box B passes through and is welded to the square hole C of the support and spoiler plate A and the square hole A of the cold flow inner plate A respectively; the number of circular holes on the support and spoiler plate C is 37, and the cold flow outer plate B and the cold flow inner plate B have the same structural dimensions as the cold flow outer plate A and the cold flow inner plate A respectively; the front cold flow box B is welded by the upper and lower spoiler plates B, the left and right horizontal plates B and the front and rear longitudinal plates, and the front cold flow box A is welded by the upper and lower spoiler plates A, the left and right horizontal plates A and the front and rear longitudinal plates respectively, and a rectangular hole is provided in the middle of the horizontal plate A and the horizontal plate B, and a square tube is welded in the middle of the horizontal plate A and the horizontal plate B respectively.

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

5. The heat exchanger based on uniform cooling and multi-stage vortex heat exchanger according to claim 1, characterized in that: The number of square holes D on the sealing plate is 2 and they are arranged symmetrically up and down. The square tubes of the front cold flow box A, the front cold flow box B and the rear cold flow box A, the rear cold flow box B are respectively welded on the square holes D and are the same as the uniform cooling cylinder; the uniform cooling cylinder is a cylindrical structure, and the turbulence plate in the uniform cooling cylinder is a semicircular structure. There are 4 turbulence plates in the uniform cooling cylinder and 2 of them are arranged symmetrically up and down in a group. The height of the turbulence plate is 3 / 4 of the radius of the uniform cooling cylinder; 7 rows of circular holes are arranged at equal intervals from top to bottom on the support disturbance plate B, and the circular holes on the support disturbance plate B are staggered with the uniform cooling cylinder.

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