Plate-fin heat exchanger

Abstract

The present disclosure relates to a plate-fin heat exchanger, comprising an upper cover plate, a lower cover plate, a side wall plate and a plurality of partition plates, the upper cover plate, the lower cover plate and the side wall plate jointly form a closed heat exchange cavity, the plurality of partition plates are arranged in the heat exchange cavity and are used for separating the heat exchange cavity into a plurality of first flow channels and second flow channels arranged alternately from top to bottom; the plate-fin heat exchanger is formed with first fluid inflow through holes, first fluid outflow through holes for flowing of a first fluid and second fluid inflow through holes, second fluid outflow through holes for flowing of a second fluid, each first flow channel is communicated with the first fluid inflow through holes and the first fluid outflow through holes, and each second flow channel is communicated with the second fluid inflow through holes and the second fluid outflow through holes. The above scheme can reduce the overall space occupied by the plate-fin heat exchanger, and can also improve the heat transfer area obtained by the unit volume core of the plate-fin heat exchanger, thereby achieving the purpose of improving the heat exchange efficiency of the plate-fin heat exchanger.

Description

Technical Field

[0001] This disclosure relates to the field of heat exchanger technology, and more specifically, to a plate-fin heat exchanger. Background Technology

[0002] Plate-fin heat exchangers, as compact, efficient, and energy-saving devices, are widely used in industries such as petroleum, chemical, and fertilizer. In related technologies, plate-fin heat exchangers are rectangular in shape, requiring a guide zone at the fluid inlet to ensure more uniform fluid distribution before entering the heat transfer area. However, the inclusion of this guide zone increases the space occupied by the plate-fin heat exchanger itself and reduces the heat transfer area per unit volume of the core, thus lowering the heat exchange efficiency. Summary of the Invention

[0003] The purpose of this disclosure is to provide a plate-fin heat exchanger to solve the technical problems existing in the related art.

[0004] To achieve the above objectives, this disclosure provides a plate-fin heat exchanger, including an upper cover plate, a lower cover plate, side panels, and multiple partitions. The upper cover plate, lower cover plate, and side panels together form a closed heat exchange cavity. The multiple partitions are disposed within the heat exchange cavity and are used to divide the heat exchange cavity into multiple first flow channels and second flow channels arranged alternately from top to bottom. The plate-fin heat exchanger has a first fluid inlet through hole and a first fluid outlet through hole for supplying a first fluid, and a second fluid inlet through hole and a second fluid outlet through hole for supplying a second fluid. Each first flow channel is connected to the first fluid inlet through hole and the first fluid outlet through hole, and each second flow channel is connected to the second fluid inlet through hole and the second fluid outlet through hole.

[0005] Optionally, the plate-fin heat exchanger further includes a plurality of first annular seals and a plurality of second annular seals, wherein the plurality of first annular seals are disposed in the first fluid inflow through hole and the first fluid outflow through hole to seal between the two partitions having the second flow channel formed thereon; Multiple second annular seals are provided within the second fluid inflow through-hole and the second fluid outflow through-hole to seal between the two partitions having the first flow channel.

[0006] Optionally, the first fluid inlet and the first fluid outlet are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger, and the second fluid inlet and the second fluid outlet are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger.

[0007] Optionally, the angle between the line connecting the vertical axis of the first fluid inflow through hole and the vertical center line and the line connecting the second fluid inflow through hole and the vertical center line is 30°~150°. The angle between the line connecting the vertical axis of the first fluid outflow through-hole and the vertical center line and the line connecting the second fluid outflow through-hole and the vertical center line is 30°~150°.

[0008] Optionally, the plate-fin heat exchanger further includes a first heat exchange fin and a second heat exchange fin. The first heat exchange fin is disposed in the first flow channel to divide the first flow channel into a plurality of first cooling grooves spaced apart along the radial direction of the plate-fin heat exchanger, and each first cooling groove extends along the circumferential direction of the partition plate. The second heat exchange fin is disposed in the second flow channel to divide the second flow channel into a plurality of second cooling grooves spaced apart along the radial direction of the plate-fin heat exchanger, and each second cooling groove extends along the circumferential direction of the partition.

[0009] Optionally, two adjacent first cooling tanks are interconnected, and two adjacent second cooling tanks are interconnected.

[0010] Optionally, each of the first heat exchange fins is provided with multiple sets of first through holes, and the multiple sets of first through holes are spaced apart along the circumferential direction of the plate-fin heat exchanger. Each of the second heat exchange fins is provided with multiple sets of second through holes, which are spaced apart along the circumferential direction of the plate-fin heat exchanger.

[0011] Optionally, the plate-fin heat exchanger further includes a first barrier and a second barrier. The first barrier is disposed in the first flow channel and located between the first fluid inlet through hole and the first fluid outlet through hole. The first barrier is used to change the flow path of the fluid in the first flow channel. The second barrier is disposed in the second flow channel and located between the second fluid inlet through hole and the second fluid outlet through hole. The second barrier is used to change the flow path of the fluid in the second flow channel.

[0012] Optionally, both the first barrier and the second barrier include a top plate and two oppositely arranged side plates. The top plate is connected between the two side plates. The side of the top plate facing away from the side plates is connected to one of the two adjacent partitions. The side of the side plate facing away from the top plate is connected to the other of the two adjacent partitions. Each of the side plates is provided with a plurality of through holes extending along its own thickness direction, and the plurality of through holes are spaced apart along the length direction of the side plate.

[0013] Optionally, the connecting holes on the two side plates are staggered.

[0014] Through the above technical solution, during the operation of the plate-fin heat exchanger, the first fluid can flow from the first fluid inflow through hole into the first flow channel in the heat exchange chamber and flow out through the first fluid outflow through hole. At the same time, the second fluid can flow from the second fluid inflow through hole into the second flow channel in the heat exchange chamber and flow out through the second fluid outflow through hole. In this way, the first fluid flowing in the first flow channel can exchange heat with the second fluid flowing in the second flow channel through the partition located between the two, thereby realizing the heat exchange between the first fluid and the second fluid.

[0015] Furthermore, since the first fluid inlet through-hole, the first fluid outlet through-hole, the second fluid inlet through-hole, and the second fluid outlet through-hole are all located inside the plate-fin heat exchanger, and the first fluid inlet through-hole, the first fluid outlet through-hole, and the second fluid inlet through-hole can guide the flow of the first fluid as it enters the first flow channel, and the second fluid outlet and the second fluid inlet can guide the flow of the second fluid as it enters the second flow channel, there is no need to install additional flow guiding components outside the heat exchange chamber. This reduces the overall space occupied by the plate-fin heat exchanger, making it easier to assemble and arrange. At the same time, it can also increase the heat transfer area per unit volume of the plate-fin heat exchanger core, thereby improving the heat exchange efficiency of the plate-fin heat exchanger.

[0016] Other features and advantages of this disclosure will be described in detail in the following detailed description section. Attached Figure Description

[0017] The accompanying drawings are provided to further illustrate the present disclosure and form part of the specification. They are used together with the following detailed description to explain the present disclosure, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a cross-sectional view of a plate-fin heat exchanger provided in an exemplary embodiment of this disclosure; wherein the cutting point is located within the space where the first flow channel is located; Figure 2 yes Figure 1 A schematic diagram of the cross-sectional structure at point AA; Figure 3 This is a cross-sectional view of a plate-fin heat exchanger provided in an exemplary embodiment of this disclosure; wherein the cutting point is located within the space where the second flow channel is located; Figure 4 This is a cross-sectional view of a plate-fin heat exchanger provided in an exemplary embodiment of this disclosure; Figure 5This is a partial cross-sectional view of a plate-fin heat exchanger provided in an exemplary embodiment of this disclosure; Figure 6 This is a perspective view of a first or second barrier member of a plate-fin heat exchanger provided in an exemplary embodiment of this disclosure. Figure 7 This is a perspective view of a first or second barrier member of a plate-fin heat exchanger provided in another exemplary embodiment of this disclosure.

[0018] Explanation of reference numerals in the attached figures 1-Plate-fin heat exchanger; 10-Upper cover plate; 20-Lower cover plate; 30-Side plate; 40-Baffle plate; 41-First flow channel; 410-First cooling tank; 42-Second flow channel; 420-Second cooling tank; 50-First fluid inlet through hole; 51-First fluid outlet through hole; 52-Second fluid inlet through hole; 53-Second fluid outlet through hole; 54-First annular seal; 55-Second annular seal; 61-First heat exchange fin; 610-First through hole; 62-Second heat exchange fin; 620-Second through hole; 70-First barrier; 80-Second barrier; 81-Top plate; 82-Side plate; 83-Bottom plate; 820-Connecting hole; 90-Bratter layer; 100-Liquid supply end. Detailed Implementation

[0019] The specific embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit this disclosure.

[0020] In this disclosure, unless otherwise stated, directional terms such as "up," "down," "left," and "right" are used to indicate orientation or positional relationships only for the convenience of describing this disclosure and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or a specific orientation structure and operation, and therefore should not be construed as a limitation of this disclosure. The terms "inner" and "outer" refer to the inner and outer contours of the corresponding structures.

[0021] Additionally, it should be noted that the terms used, such as "first" and "second," are used to distinguish one element from another and do not indicate sequence or importance. Furthermore, in the description referring to the accompanying drawings, the same reference numerals in different drawings denote the same element.

[0022] In the description of this disclosure, it should also be noted that, unless otherwise expressly specified and limited, the terms "set up," "connect," "link," and "install" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this disclosure according to the specific circumstances.

[0023] like Figures 1 to 7 As shown, this disclosure provides a plate-fin heat exchanger 1, including an upper cover plate 10, a lower cover plate 20, a side plate 30, and a plurality of partitions 40. The upper cover plate 10, the lower cover plate 20, and the side plate 30 together form a closed heat exchange cavity. The plurality of partitions 40 are disposed in the heat exchange cavity and are used to divide the heat exchange cavity into a plurality of first flow channels 41 and second flow channels 42 arranged alternately from top to bottom. The plate-fin heat exchanger 1 has a first fluid inlet through hole 50 and a first fluid outlet through hole 51 for supplying a first fluid, and a second fluid inlet through hole 52 and a second fluid outlet through hole 53 for supplying a second fluid. Each first flow channel 41 is connected to the first fluid inlet through hole 50 and the first fluid outlet through hole 51, and each second flow channel 42 is connected to the second fluid inlet through hole 52 and the second fluid outlet through hole 53.

[0024] Through the above technical solution, during the operation of the plate-fin heat exchanger 1, the first fluid can flow from the first fluid inflow through hole 50 into the first flow channel 41 in the heat exchange chamber and flow out through the first fluid outflow through hole 51. At the same time, the second fluid can flow from the second fluid inflow through hole 52 into the second flow channel 42 in the heat exchange chamber and flow out through the second fluid outflow through hole 53. In this way, the first fluid flowing in the first flow channel 41 can exchange heat with the second fluid flowing in the second flow channel 42 through the partition 40 located between them, thereby realizing the heat exchange between the first fluid and the second fluid.

[0025] Furthermore, since the first fluid inflow through-hole 50, the first fluid outflow through-hole 51, the second fluid inflow through-hole 52, and the second fluid outflow through-hole 53 are all located inside the plate-fin heat exchanger 1, and the first fluid inflow through-hole 50, the first fluid outflow through-hole 51, and the second fluid inflow through-hole 52 can guide the flow of the first fluid as it enters the first flow channel 41, and the second fluid outflow and the second fluid inflow can guide the flow of the second fluid as it enters the second flow channel 42, there is no need to install additional flow guiding components outside the heat exchange chamber. This reduces the overall space occupied by the plate-fin heat exchanger 1, making it easier to assemble and arrange the plate-fin heat exchanger 1. At the same time, it can also increase the heat transfer area obtained per unit volume of the core of the plate-fin heat exchanger 1, thereby improving the heat exchange efficiency of the plate-fin heat exchanger 1.

[0026] It should be noted that one of the first fluid and the second fluid is a hot fluid, and the other of the first fluid and the second fluid is a cold fluid. That is, there is a certain temperature difference between the first fluid and the second fluid to facilitate heat exchange between them.

[0027] Optionally, such as Figure 2 , Figure 5 As shown, the plate-fin heat exchanger 1 also includes a plurality of first annular seals 54 and a plurality of second annular seals 55. The plurality of first annular seals 54 are disposed in the first fluid inflow through hole 50 and the first fluid outflow through hole 51 to seal between the two partitions 40 having the second flow channel 42. The plurality of second annular seals 55 are disposed in the second fluid inflow through hole 52 and the second fluid outflow through hole 53 to seal between the two partitions 40 having the first flow channel 41. In the above scheme, on the one hand, the first annular seal 54 and the second annular seal 55 set between the two partitions 40 can provide certain support and reinforcement for the partitions 40, thereby improving the overall structural strength and pressure bearing capacity of the plate-fin heat exchanger 1. On the other hand, the first annular seal 54 and the second annular seal 55 set between the two partitions 40 can also increase the contact area with the upper and lower partitions 40, and make it easier to weld with the upper and lower partitions 40 by brazing, thereby improving the fixing strength and sealing performance between the two, and preventing fluid leakage from the connection between the two.

[0028] Similarly, regarding the aforementioned side panel 30, in one exemplary embodiment provided in this disclosure, the side panel 30 can be formed as a cylindrical structure with the same height as the heat exchange cavity, that is, the side panel 30 can directly wrap around the outer periphery of the partition 40 to form a closed heat exchange cavity together with the upper cover plate 10 and the lower cover plate 20. Alternatively, in another exemplary embodiment provided in this disclosure, such as... Figure 5 As shown, the side panel 30 may include multiple outer annular seals, each of which seals between the outer ends of two adjacent partitions 40, thus also providing a sealing effect for the two adjacent partitions 40.

[0029] In one exemplary embodiment provided in this disclosure, the upper and lower ends of the first annular seal 54 can be connected to the two partitions 40 located above and below it by means of welding, hot melting, brazing, etc. Similarly, the upper and lower ends of the second annular seal 55 can be connected to the two partitions 40 located above and below it by means of welding, hot melting, brazing, etc., so that the first annular seal 54, the second annular seal 55 and the partitions 40 located on the upper and lower sides together form the first flow channel 41 or the second flow channel 42.

[0030] To facilitate welding between the first annular seal 54 and the partition 40 located above and below it, such as Figure 2 As shown, this disclosure also includes a brazing layer 90 disposed on the partition 40. Under high temperature, the brazing layer 90 can become molten, thereby achieving welding with the first annular seal 54 and the second annular seal 55.

[0031] Optionally, such as Figure 1 , Figure 3 as well as Figure 4 As shown, the first fluid inlet through hole 50 and the first fluid outlet through hole 51 are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger 1, and the second fluid inlet through hole 52 and the second fluid outlet through hole 53 are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger 1. Since the first fluid inlet hole 50 and the first fluid outlet hole 51 are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger 1, and the second fluid inlet hole 52 and the second fluid outlet hole 53 are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger 1, this ensures that the distance between the first fluid inlet hole 50 and the vertical center line of the plate-fin heat exchanger 1 is equal to the distance between the first fluid outlet hole 51 and the vertical center line of the plate-fin heat exchanger 1. Similarly, the distance between the second fluid inlet hole 52 and the vertical center line of the plate-fin heat exchanger 1 is also equal to the distance between the second fluid outlet hole 53 and the vertical center line of the plate-fin heat exchanger 1. This results in a more balanced flow of the first fluid inlet hole 50, the first fluid outlet hole 51, the second fluid inlet hole 52, and the second fluid outlet hole 53.

[0032] It should be noted that, in order to increase the flow path of the first fluid from the first fluid inlet through hole 50 to the first fluid outlet through hole 51, and the flow path of the second fluid from the second fluid inlet through hole 52 to the second fluid outlet through hole 53, the flow paths of the first fluid inlet through hole 50, the first fluid outlet through hole 51, the second fluid inlet through hole 52, and the second fluid outlet through hole 53 can be arranged as close as possible to the side plate 30. That is, the distance between the flow paths of the first fluid inlet through hole 50 and the first fluid outlet through hole 51, and the distance between the flow paths of the second fluid inlet through hole 52 and the second fluid outlet through hole 53 can be increased as much as possible. This increases the residence time of the first fluid in the first flow channel 41 and the residence time of the second fluid in the second flow channel 42, and reduces or avoids the flow dead zones of the first flow channel 41 and the second flow channel 42 near the side plate 30, further improving the utilization rate of the first flow channel 41 and the second flow channel 42 and improving the heat exchange efficiency.

[0033] In one exemplary embodiment provided in this disclosure, the distance between the first fluid inflow through-hole 50 and the side plate 30 is 0.5 to 1 times the diameter of the first fluid inflow through-hole 50 itself; the distance between the first fluid outflow through-hole 51 and the side plate 30 is 0.5 to 1 times the diameter of the first fluid outflow through-hole 51 itself; the distance between the second fluid inflow through-hole 52 and the side plate 30 is 0.5 to 1 times the diameter of the second fluid inflow through-hole 52 itself; and the distance between the second fluid outflow through-hole 53 and the side plate 30 is 0.5 to 1 times the diameter of the second fluid outflow through-hole 53 itself. Within this range, the arrangement of the through-holes can both prevent the first fluid and the second fluid from being too close to the side plate 30 during flow and reduce the dead zone of the first fluid in the first flow channel 41 and the second fluid in the second flow channel 42, further increasing the heat exchange area between the first flow channel 41 and the second flow channel 42 and improving the heat exchange effect.

[0034] It should be noted that the inner diameters of the first fluid inlet through-hole 50, the first fluid outlet through-hole 51, the second fluid inlet through-hole 52, and the second fluid outlet through-hole 53 can be the same or different, depending on the specific heat exchange condition. For embodiments where the inner diameters of the first fluid inlet through-hole 50, the first fluid outlet through-hole 51, the second fluid inlet through-hole 52, and the second fluid outlet through-hole 53 are the same, the centers of the first fluid inlet through-hole 50, the first fluid outlet through-hole 51, the second fluid inlet through-hole 52, and the second fluid outlet through-hole 53 all fall on the same circle, meaning that the distances between the first fluid inlet through-hole 50, the first fluid outlet through-hole 51, the second fluid inlet through-hole 52, and the second fluid outlet through-hole 53 and the vertical centerline of the plate-fin heat exchanger 1 are equal.

[0035] In one embodiment provided by this supply, the angle between the line connecting the vertical axis and the vertical center line of the first fluid inflow through-hole 50 and the line connecting the second fluid inflow through-hole 52 and the vertical center line is 30° to 150°; the angle between the line connecting the vertical axis and the vertical center line of the first fluid outflow through-hole 51 and the line connecting the second fluid outflow through-hole 53 and the vertical center line is 30° to 150°. Within this angle range, interference or interference between the first fluid inflow through-hole 50 and the second fluid inflow through-hole 52 can be avoided, as can interference or interference between the first fluid outflow through-hole 51 and the second fluid outflow through-hole 53.

[0036] In one exemplary embodiment provided in this disclosure, such as Figure 1 , Figure 3 as well as Figure 5As shown, the angle between the line connecting the vertical axis and the vertical center line of the first fluid inflow through-hole 50 and the line connecting the second fluid inflow through-hole 52 and the vertical center line can be 90°, and the angle between the line connecting the vertical axis and the vertical center line of the first fluid outflow through-hole 51 and the line connecting the second fluid outflow through-hole 53 and the vertical center line can also be 90°. In this way, after the first fluid enters the first flow channel 41 through the first fluid inlet through hole 50, it will split into two streams and converge into the first fluid outlet through hole 51, and then flow out from the first fluid outlet through hole 51. The angle between the line connecting the vertical axis and the vertical center line of the first fluid inlet through hole 50 and the line connecting the second fluid inlet through hole 52 and the vertical center line can be 90°. That is to say, the first fluid inlet through hole 50 and the first fluid outlet through hole 51 are symmetrically arranged about the center of the heat exchange chamber. In this way, the first fluid can flow through the same length regardless of which direction it flows into the first fluid outlet through hole 51. That is to say, the residence time of all the first fluid in the first flow channel 41 is also the same, thereby ensuring that the heat exchange of the first fluid at different positions is more uniform, reducing the temperature difference and improving the temperature consistency of the fluid flowing out of the first fluid outlet through hole 51. The principle of the second fluid inflow through-hole 52 and the second fluid outflow through-hole 53 is the same as that of the first fluid inflow through-hole 50 and the first fluid outflow through-hole 51, and will not be described in detail here.

[0037] Optionally, such as Figure 2 As shown, the plate-fin heat exchanger 1 may further include a first heat exchange fin 61 and a second heat exchange fin 62. The first heat exchange fin 61 is disposed in the first flow channel 41 to divide the first flow channel 41 into a plurality of first cooling grooves 410 spaced apart along the radial direction of the plate-fin heat exchanger 1, and each first cooling groove 410 extends along the circumferential direction of the partition plate 40. The second heat exchange fin 62 is disposed in the second flow channel 42 to divide the second flow channel 42 into a plurality of second cooling grooves 420 spaced apart along the radial direction of the plate-fin heat exchanger 1, and each second cooling groove 420 extends along the circumferential direction of the partition plate 40. The arrangement of the first heat exchange fin 61 and the second heat exchange fin 62 can divide the first flow channel 41 and the second flow channel 42 into multiple spaced first cooling tanks 410 and second cooling tanks 420, which further refines the flow of fluid in the first flow channel 41 and the second flow channel 42, and can increase the contact area between the fluid and the first heat exchange fin 61 and the second heat exchange fin 62, thereby improving the heat exchange effect of the fluid.

[0038] In addition, the arrangement of the first heat exchange fin 61 and the second heat exchange fin 62 can also support and strengthen the partition 40 from below, thereby improving the strength and stability of the partition 40 and thus improving the overall pressure bearing capacity of the plate-fin heat exchanger 1.

[0039] This disclosure does not limit the specific structure of the first heat exchange fin 61 and the second heat exchange fin 62 described above. For example, in an exemplary embodiment provided in this disclosure, such as... Figure 2 As shown, the first heat exchange fin 61 can be formed by bending a plate. Multiple upward-opening first upper grooves and multiple downward-opening first lower grooves are formed on the first heat exchange fin 61. Both the first upper and lower grooves extend along the circumferential direction of the first flow channel 41. Along the radial direction of the plate-fin heat exchanger 1, the first upper and lower grooves are arranged alternately in sequence. Each first upper groove and the partition plate 40 above it together form a first cooling groove 410, and each first lower groove and the partition plate 40 below it together form a first cooling groove 410. 10; The second heat exchange fin 62 is formed by bending a plate. The second heat exchange fin 62 has a plurality of upward-opening second upper grooves and a plurality of downward-opening second lower grooves. The second upper grooves and the second lower grooves extend along the circumferential direction of the second flow channel 42 and along the radial direction of the plate-fin heat exchanger 1. The second upper grooves and the second lower grooves are arranged alternately in sequence. Each second upper groove and the partition plate 40 above it together form a second cooling groove 420. Each second lower groove and the partition plate 40 below it together form a second cooling groove 420. Thus, each first upper groove and the partition 40 above it, and each first lower groove and the partition 40 above it can respectively form an independently arranged first cooling tank 410. Similarly, each second upper groove and the partition 40 above it, and each second lower groove and the partition 40 above it can respectively form an independently arranged second cooling tank 420. Furthermore, since the first flow channel 41 containing a higher temperature fluid and the second flow channel 42 containing a lower temperature fluid are alternately arranged in the vertical direction, the bottom of the first upper groove... The wall of the first upper groove is in contact with the partition 40 located below it. The higher temperature fluid in the first upper groove can exchange heat with the partition 40 located below it through the bottom wall of the first upper groove, thereby achieving heat exchange with the lower temperature fluid in the second flow channel 42 located below the partition 40. The top wall of the first lower groove is in contact with the partition 40 located above it. The higher temperature fluid in the first lower groove can exchange heat with the partition 40 located above it through the top wall of the first lower groove, thereby achieving heat exchange with the lower temperature fluid in the second flow channel 42 located above the partition 40.

[0040] Similarly, for the second upper groove and the second lower groove, the bottom wall of the second upper groove is in contact with the partition 40 located below it. The lower temperature fluid in the second upper groove can exchange heat with the partition 40 located below it through the bottom wall of the second upper groove, thereby achieving heat exchange with the high temperature fluid in the first flow channel 41 located below the partition 40. The top wall of the second lower groove is in contact with the partition 40 located above it. The lower temperature fluid in the second lower groove can exchange heat with the partition 40 located above it through the top wall of the second lower groove, thereby achieving heat exchange with the high temperature fluid in the first flow channel 41 located above the partition 40.

[0041] This disclosure does not limit the specific shape of the first heat exchange fin 61 and the second heat exchange fin 62. For example, the cross-section of the first heat exchange fin 61 and the cross-section of the second heat exchange fin 62 can be formed as a regular polygon, or the cross-section of the first heat exchange fin 61 and the cross-section of the second heat exchange fin 62 can also be formed as a circle.

[0042] To further enhance the freedom of the first fluid within the first flow channel 41 and the second fluid within the second flow channel 42, optionally, two adjacent first cooling tanks 410 are interconnected, and two adjacent second cooling tanks 420 are interconnected. That is, the first fluid can enter from one first cooling tank 410 into other adjacent first cooling tanks 410, and the fluid in multiple first cooling tanks 410 can flow freely. Similarly, the fluid in multiple second cooling tanks 420 can flow freely, thereby enhancing the turbulence of the fluids and improving the heat exchange effect.

[0043] Optionally, such as Figure 2 As shown, each first heat exchange fin 61 is provided with multiple sets of first through holes 610, which are spaced apart along the circumferential direction of the plate-fin heat exchanger 1; each second heat exchange fin 62 is provided with multiple sets of second through holes 620, which are spaced apart along the circumferential direction of the plate-fin heat exchanger 1. The arrangement of the first through holes 610 and the second through holes 620 causes radial mixing of the fluid while it flows circumferentially, enhancing the turbulence of the fluid and further improving the heat transfer efficiency.

[0044] Furthermore, each group of first through holes 610 may include multiple first through holes 610 spaced apart in the vertical direction; each group of second through holes 620 includes multiple second through holes 620 spaced apart in the vertical direction. The multiple first through holes 610 can further increase the flow rate of the first fluid between two adjacent first cooling tanks 410, and the multiple second through holes 620 can further increase the flow rate of the second fluid between two adjacent second cooling tanks 420. This facilitates the mixing of the first fluid in different first cooling tanks 410 and the mixing of the second fluid in different second cooling tanks 420, resulting in a more balanced temperature of the first and second fluids in different first cooling tanks 410 and second cooling tanks 420, and reducing temperature differences.

[0045] In the embodiment where the cross-section of the first heat exchange fin 61 can be formed as a regular polygon, the first fluid flows into the heat exchange fin in three ways: the first path is when the overflow direction of the first fluid is consistent with the extension direction of the first heat exchange fin 61, it can directly flow into the first cooling tank 410 formed by the first heat exchange fin 61 and the partition plate 40 or the lower cover plate 20; the second path is when the overflow direction of the first fluid is perpendicular to the extension direction of the first heat exchange fin 61, it can only enter the first cooling tank 410 through the first through hole 610 on the surface of the first heat exchange fin 61; the third path is when the overflow direction of the first fluid is at a certain angle to the extension direction of the first heat exchange fin 61, then part of the first fluid directly enters the first cooling tank 410, and another part of the first fluid enters the adjacent first cooling channel through the first through hole 610. In the above process, since the surface of the first heat exchange fin 61 has a first through hole 610, when the first fluid and the second fluid on the other side of the first cooling tank 410 transfer heat through the partition 40, the first fluid will undergo transverse mixing with a direction different from the extension direction of the first cooling tank 410 during the flow process, thereby enhancing the turbulence effect and improving the heat transfer efficiency. Similarly, the same applies to the embodiment where the cross-section of the second heat exchange fin 62 can be formed as a regular polygon, which will not be described in this disclosure.

[0046] Because adjacent first cooling tanks 410 and adjacent second cooling tanks 420 are interconnected, taking the first fluid as an example, in multiple flow channels, a shorter path often means that the fluid needs to overcome less friction and other resistance, so the fluid tends to choose such a path. Thus, during the process of the first fluid flowing from the first fluid inlet through-hole 50 through the first cooling tank 410 and out of the first fluid outlet through-hole 51, the first fluid will sequentially pass through multiple first through-holes 610 formed on multiple first heat exchange fins 61 in the radial direction, flowing directly from the first fluid inlet through-hole 50 into the first fluid outlet through-hole 51 via the shortest path. On the one hand, this reduces the flow time of the first fluid in the first cooling tank 410; on the other hand, the first fluid only flows through part of the path, thus reducing the heat exchange area between the first fluid and the baffle 40 and the first heat exchange fins 61, thereby reducing the heat exchange effect. Based on this, in an exemplary embodiment provided in this disclosure, such as... Figure 1 , Figure 3 as well as Figure 4 As shown, the plate-fin heat exchanger 1 may further include a first barrier 70 and a second barrier 80. The first barrier 70 is disposed in the first flow channel 41 and located between the first fluid inlet through hole 50 and the first fluid outlet through hole 51. The first barrier 70 is used to change the flow path of the fluid in the first flow channel 41. The second barrier 80 is disposed in the second flow channel 42 and located between the second fluid inlet through hole 52 and the second fluid outlet through hole 53. The second barrier 80 is used to change the flow path of the fluid in the second flow channel 42.

[0047] By setting the first barrier 70 and the second barrier 80, during the flow of the first fluid and the second fluid, the first barrier 70 can block and isolate the first fluid, and the second barrier 80 can block and isolate the second fluid. This causes the first fluid to bypass the first barrier 70 before flowing out of the first fluid outlet through hole 51, and the second fluid to bypass the second barrier 80 before flowing out of the second fluid outlet through hole 53. In this way, on the one hand, the flow path of the first fluid and the second fluid is extended, and the flow dead zone is reduced. On the other hand, the residence time of the first fluid in the first cooling tank 410 and the residence time of the second fluid in the second cooling tank 420 are increased, which significantly improves the heat exchange effect between the first fluid and the second fluid.

[0048] Optionally, such as Figure 6As shown, both the first barrier 70 and the second barrier 80 may include a top plate 81 and two oppositely arranged side plates 82. The top plate 81 is connected between the two side plates 82. The side of the top plate 81 facing away from the side plate 82 is connected to one of the two adjacent partitions 40. The side plate 82 facing away from the top plate 81 is connected to the other of the two adjacent partitions 40. Each side plate 82 is provided with a plurality of through holes 820 extending along its own thickness direction. The plurality of through holes 820 are spaced apart along the length direction of the side plate 82. Thus, for the first fluid, during its flow from the first fluid inlet through hole 50 to the first fluid outlet through hole 51, it first flows into the interior of the first barrier 70 through the connecting hole 820 on one side plate 82. After entering the interior of the first barrier 70, the first fluid is redistributed and eventually flows out of the interior of the first barrier 70 in three parts. The first part of the first fluid and the second part of the first fluid flow out from the two ends of the two side plates 82 respectively, and the third part of the first fluid flows into the first cooling tank 410 near the first fluid outlet through hole 51 through the connecting hole 820 on the other side plate 82. On the one hand, this increases the residence time of the first fluid in the first cooling tank 410. On the other hand, the arrangement of the first barrier 70 can also prevent the first fluid from flowing along the shortest flow path between the first fluid inlet through hole 50 and the first fluid outlet through hole 51, so that the first fluid and the second fluid have a larger flow area and base area, which makes it easier for the first fluid and the second fluid to exchange heat evenly and further improve the heat exchange effect.

[0049] Furthermore, to ensure a more uniform flow rate of the first and second fluids exiting from both ends of the side plate 82, the centerline of the first barrier 70 along its length is collinear with the line connecting the first fluid inlet hole 50 and the first fluid outlet hole 51. That is, the first barrier 70 is perpendicular to the line connecting the first fluid inlet hole 50 and the first fluid outlet hole 51, and the first fluid inlet hole 50 and the first fluid outlet hole 51 are symmetrically arranged with respect to the first barrier 70. Similarly, the centerline of the second barrier 80 along its length is collinear with the line connecting the second fluid inlet hole 52 and the second fluid outlet hole 53. That is, the first barrier 70 is perpendicular to the line connecting the second fluid inlet hole 52 and the second fluid outlet hole 53, and the second fluid inlet hole 52 and the second fluid outlet hole 53 are symmetrically arranged with respect to the second barrier 80.

[0050] Or, such as Figure 7As shown, the first barrier 70 and the second barrier 80 may both include a base plate 83. The base plate 83 is disposed opposite to the top plate 81 and connected between the two side plates 82, so that the top plate 81, the base plate 83, and the side plates 82 together form a tubular structure with a U-shaped cross section. This can further improve the strength of the first barrier 70 and the second barrier 80, prevent the first barrier 70 and the second barrier 80 from deforming, and also provide stable support for the partition plate 40, thereby improving the overall pressure bearing capacity of the plate-fin heat exchanger 1.

[0051] In one embodiment provided in this disclosure, the lengths of the first barrier 70 and the second barrier 80 are not less than 1.5 times the inner diameters of the first fluid inflow through hole 50 and the second fluid inflow through hole 52, and the widths and wall thicknesses of the first barrier 70 and the second barrier 80 are not less than the widths and wall thicknesses of the first heat exchange fins 61 and the second heat exchange fins 62.

[0052] Furthermore, when the first fluid and the second fluid flow out from both ends of the two side plates 82, they will mix with the first fluid and the second fluid that originally flowed normally from the edge of the side plates 82, thereby disrupting the normal flow of the first fluid and the second fluid, making the flow of the first fluid and the second fluid more chaotic and disordered, thereby enhancing the turbulence effect of the first fluid and the second fluid and achieving the purpose of improving heat transfer efficiency.

[0053] Optionally, the connecting holes 820 on the two side plates 82 are staggered. Thus, when the first fluid flows from one first cooling tank 410 through one connecting hole 820 to another first cooling tank 410 via the other connecting hole 820, the staggered arrangement of the two connecting holes 820 on the two first heat exchange fins 61 increases the flow path of the first fluid, thereby increasing the flow time of the first fluid in the radial mixing process and improving heat transfer efficiency. Furthermore, the increased flow path of the first fluid in the above process further disrupts the flow of the first fluid within the first cooling tank 410, enhancing the turbulent state of the first fluid. Similarly, the flow state of the second fluid within two adjacent second cooling tanks 420 is also similar, and will not be described in detail in this disclosure.

[0054] In addition, such as Figure 5 As shown, a liquid supply end 100 is also provided on the lower cover plate 20, which is connected to the first fluid inflow through hole 50, the first fluid outflow through hole 51, the second fluid inflow through hole 52 and the second fluid outflow through hole 53. The liquid supply end 100 is used to supply the inflow and outflow of the first fluid and the second fluid.

[0055] The preferred embodiments of this disclosure have been described in detail above with reference to the accompanying drawings. However, this disclosure is not limited to the specific details of the above embodiments. Within the scope of the technical concept of this disclosure, various simple modifications can be made to the technical solutions of this disclosure, and these simple modifications all fall within the protection scope of this disclosure. It should also be noted that the various specific technical features described in the above embodiments can be combined in any suitable manner without contradiction. To avoid unnecessary repetition, this disclosure will not further describe the various possible combinations.

[0056] Furthermore, various different embodiments of this disclosure can be combined in any way, as long as they do not violate the spirit of this disclosure, they should also be regarded as the content disclosed in this disclosure.

Claims

1. A plate-fin heat exchanger, characterized in that, It includes an upper cover plate, a lower cover plate, side panels, and multiple partitions. The upper cover plate, lower cover plate, and side panels together form a closed heat exchange cavity. The multiple partitions are disposed in the heat exchange cavity and are used to divide the heat exchange cavity into multiple first flow channels and second flow channels arranged alternately from top to bottom. The plate-fin heat exchanger has a first fluid inlet through hole and a first fluid outlet through hole for supplying a first fluid, and a second fluid inlet through hole and a second fluid outlet through hole for supplying a second fluid. Each first flow channel is connected to the first fluid inlet through hole and the first fluid outlet through hole, and each second flow channel is connected to the second fluid inlet through hole and the second fluid outlet through hole.

2. The plate-fin heat exchanger according to claim 1, characterized in that, The plate-fin heat exchanger further includes a plurality of first annular seals and a plurality of second annular seals. The plurality of first annular seals are used to be disposed in the first fluid inflow through hole and the first fluid outflow through hole to seal between the two partitions forming the second flow channel. Multiple second annular seals are provided within the second fluid inflow through-hole and the second fluid outflow through-hole to seal between the two partitions having the first flow channel.

3. The plate-fin heat exchanger according to claim 1, characterized in that, The first fluid inlet and the first fluid outlet are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger, and the second fluid inlet and the second fluid outlet are symmetrically arranged on both sides of the vertical center line of the plate-fin heat exchanger.

4. The plate-fin heat exchanger according to claim 3, characterized in that, The angle between the line connecting the vertical axis of the first fluid inflow through hole and the vertical center line and the line connecting the second fluid inflow through hole and the vertical center line is 30°~150°; The angle between the line connecting the vertical axis of the first fluid outflow through-hole and the vertical center line and the line connecting the second fluid outflow through-hole and the vertical center line is 30°~150°.

5. The plate-fin heat exchanger according to any one of claims 1-4, characterized in that, The plate-fin heat exchanger further includes a first heat exchange fin and a second heat exchange fin. The first heat exchange fin is disposed in the first flow channel to divide the first flow channel into a plurality of first cooling grooves spaced apart along the radial direction of the plate-fin heat exchanger, and each first cooling groove extends along the circumferential direction of the partition plate. The second heat exchange fin is disposed in the second flow channel to divide the second flow channel into a plurality of second cooling grooves spaced apart along the radial direction of the plate-fin heat exchanger, and each second cooling groove extends along the circumferential direction of the partition.

6. The plate-fin heat exchanger according to claim 5, characterized in that, The two adjacent first cooling tanks are interconnected, and the two adjacent second cooling tanks are interconnected.

7. The plate-fin heat exchanger according to claim 6, characterized in that, Each of the first heat exchange fins is provided with multiple sets of first through holes, and the multiple sets of first through holes are spaced apart along the circumferential direction of the plate-fin heat exchanger. Each of the second heat exchange fins is provided with multiple sets of second through holes, which are spaced apart along the circumferential direction of the plate-fin heat exchanger.

8. The plate-fin heat exchanger according to any one of claims 1-4, characterized in that, The plate-fin heat exchanger further includes a first barrier and a second barrier. The first barrier is disposed in the first flow channel and located between the first fluid inlet through hole and the first fluid outlet through hole. The first barrier is used to change the flow path of the fluid in the first flow channel. The second barrier is disposed in the second flow channel and located between the second fluid inlet through hole and the second fluid outlet through hole. The second barrier is used to change the flow path of the fluid in the second flow channel.

9. The plate-fin heat exchanger according to claim 8, characterized in that, Both the first barrier and the second barrier include a top plate and two oppositely arranged side plates. The top plate is connected between the two side plates. The side of the top plate facing away from the side plates is connected to one of the two adjacent partitions. The side of the side plate facing away from the top plate is connected to the other of the two adjacent partitions. Each of the side plates is provided with a plurality of through holes extending along its own thickness direction, and the plurality of through holes are spaced apart along the length direction of the side plate.

10. The plate-fin heat exchanger according to claim 9, characterized in that, The connecting holes on the two side plates are staggered.

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