Heat exchange unit and modular heat exchange device

Abstract

This invention belongs to the field of thermal management technology, specifically relating to heat exchange equipment, and particularly to a heat exchange unit and a modular heat exchange device. The heat exchange unit achieves an integrated coupling design of micro heat pipes and heat exchange plates. The heat exchange plates form periodically changing flow channels through specific bending, effectively balancing flow field distribution and flow resistance. Individual heat pipes are vertically and pluggably installed in the through-holes of the plates using an innovative mechanical fastening structure, facilitating disassembly and maintenance. The modular heat exchange device of this invention systematically couples the micro heat pipe array, modular plate structure, and optimized flow channel design, achieving comprehensive performance including high-efficiency heat transfer, compact structure, independent maintenance, controllable flow resistance and fouling, and flexible configuration. It solves the technical contradictions of traditional heat exchange equipment in terms of maintainability, compactness, flow resistance control, and anti-fouling performance, and is particularly suitable for heat exchange scenarios with stringent requirements for space, weight, and reliability, such as liquid cooling of electronic equipment and thermal management of new energy sources.

Description

Technical Field

[0001] This invention belongs to the field of thermal management technology, and relates to heat exchange equipment, particularly to a heat exchange unit and a modular heat exchange device. Background Technology

[0002] Traditional heat exchange equipment includes plate heat exchangers and heat pipe heat exchangers. Plate heat exchangers suffer from problems such as localized thermal stress concentration, easy blockage of flow channels, poor temperature uniformity, and the need for complete replacement once corrosion or damage occurs, resulting in high maintenance costs. Heat pipe heat exchangers, on the other hand, often use large heat pipes combined with fins or directly inserted into the housing, which results in disadvantages such as large size, loose structure, and difficulty in achieving miniaturization and high-density integration; moreover, the connection between the heat pipes and the housing is often inconvenient to disassemble, making it impossible to easily replace and repair individual heat pipes.

[0003] Existing heat exchange equipment cannot achieve a good balance between high-efficiency heat transfer, low flow resistance, and high anti-fouling performance, and lacks flexible modular expansion capabilities, making it unsuitable for thermal management scenarios with stringent requirements for space layout, volume control, and heat exchange efficiency. Therefore, there is an urgent need to propose a novel heat exchange technology to overcome the aforementioned shortcomings of existing technologies. Summary of the Invention

[0004] The purpose of this invention is to provide a novel heat exchange unit and modular heat exchange device to solve the technical problems of existing heat exchange equipment that cannot achieve a good balance between high-efficiency heat transfer, low flow resistance and high anti-fouling performance, and lack flexible modular expansion capabilities, thus failing to meet the compact requirements of special scenarios.

[0005] To achieve the above objectives, the present invention provides the following solution: On one hand, the present invention provides a heat exchange unit, including heat exchange plates and a heat pipe array, wherein: The heat exchange plates are provided with periodic concave and convex bending areas; The heat pipe array includes a plurality of heat pipe units protruding from the surface of the heat exchange plate. The heat pipe array is provided on at least one side of the heat exchange plate and is located in the periodic concave-convex bending region.

[0006] Preferably, any bending point of the heat exchange plate is an arc-shaped structure or a zigzag structure.

[0007] Preferably, each of the heat pipe units is a columnar heat pipe unit, and each of the columnar heat pipe units is perpendicular to the corresponding area surface of the heat exchange plate.

[0008] Preferably, the periodic concave-convex bending region is provided with an array of through holes that match the heat pipe array; the columnar heat pipe unit includes a columnar heat pipe body and radial fins disposed on the outer wall of the columnar heat pipe body; The columnar heat pipe body penetrates through the corresponding through hole and is connected and fixed to the heat exchange plate through the radial fins. The two ends of the columnar heat pipe body protrude from the two side surfaces of the heat exchange plate, so that the heat pipe array is formed on both sides of the heat exchange plate.

[0009] Preferably, the radial fins are annular fins, and the contact interface between the annular fins and the heat exchange plate is filled with thermally conductive silicone.

[0010] Preferably, the annular fins are fixed to the heat exchange plate by bolts.

[0011] Preferably, the columnar heat pipe body is a cylinder or a prism.

[0012] Preferably, the columnar heat pipe body and the radial fins are integrally formed.

[0013] Preferably, the length ratio of the columnar heat pipe body protruding from both sides of the heat exchange plate is 1:1 to 1:2.

[0014] Preferably, the outer periphery of the heat exchange plate is further provided with a periphery connecting part for series fixation with adjacent heat exchange plates.

[0015] On the other hand, the present invention proposes a modular heat exchange device, including multiple heat exchange units as described above, wherein the multiple heat exchange units are connected in series, and a flow channel for fluid flow and heat exchange is formed between the heat exchange plates of any two adjacent heat exchange units.

[0016] Preferably, all the heat exchange units have the same structure, and all the heat exchange units are arranged in a straight line or staggered.

[0017] Preferably, all of the heat exchange units have different structures, and the different heat exchange units are arranged alternately at intervals.

[0018] Preferably, the modular heat exchange device further includes a housing, on which a fluid inlet and a fluid outlet are provided, and a plurality of the heat exchange units are fixed inside the housing and located between the fluid inlet and the fluid outlet.

[0019] The present invention achieves the following technical effects compared to the prior art: The heat exchange unit of this invention achieves an integrated coupling design of micro heat pipes and heat exchange plates. The heat exchange plates form periodically changing flow channels through specific bending, which can effectively balance the flow field distribution and flow resistance. The flow channel design includes gradually widening and narrowing types as well as constant cross-section types, and the corresponding flow channel design can be adopted according to different scenarios and usage requirements.

[0020] The heat pipe unit is vertically and pluggably mounted in the plate through-hole via an innovative mechanical fastening structure. This structure uses a micro-bolt and nut assembly to engage with the annular fins integrally formed in the center of the heat pipe, and fills the contact interface with non-fluorine high thermal conductivity silicone, achieving mechanical fixation, efficient heat conduction, and reliable sealing.

[0021] In the modular heat exchange device of this invention, each heat exchange unit is combined through modular integration, and the spacing between adjacent plates can be adjusted within the range of 8mm to 20mm. By optimizing the arrangement of adjacent plates (straight-line / staggered), a compact heat exchange module with reconfigurable characteristics is formed.

[0022] The modular heat exchange device of this invention systematically couples micro heat pipe arrays, modular plate structures, and optimized flow channel design, achieving comprehensive performance in terms of high-efficiency heat transfer, compact structure, independent maintenance, controllable flow resistance and fouling, and flexible configuration. It solves the technical contradictions of traditional heat exchange equipment in terms of maintainability, compactness, flow resistance control, and anti-fouling performance, and is particularly suitable for heat exchange scenarios with stringent requirements for space, weight, and reliability, such as liquid cooling of electronic equipment and thermal management of new energy. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a three-dimensional structural diagram of the heat exchange plate disclosed in Embodiment 1 of the present invention; Figure 2 This is a front view of the heat exchange plate disclosed in Embodiment 1 of the present invention; Figure 3 This is a side view of the heat exchange plate disclosed in Embodiment 1 of the present invention; Figure 4 This is a three-dimensional structural schematic diagram of the heat exchange unit disclosed in Embodiment 2 of the present invention; Figure 5 This is a front view of the heat exchange unit disclosed in Embodiment 2 of the present invention; Figure 6 This is a schematic diagram of the side cross-sectional structure of the heat exchange unit disclosed in Embodiment 2 of the present invention; Figure 7 This is a three-dimensional structural diagram of the heat exchange plate disclosed in Embodiment 3 of the present invention; Figure 8 This is a front view of the heat exchange plate disclosed in Embodiment 3 of the present invention; Figure 9 This is a side view of the heat exchange plate disclosed in Embodiment 3 of the present invention; Figure 10 This is a schematic diagram of the installation of a heat pipe unit disclosed in an embodiment of the present invention; Figure 11 This is a front view of the installation structure of the heat pipe unit disclosed in an embodiment of the present invention; Figure 12 This is a top view of the installation structure of the heat pipe unit disclosed in an embodiment of the present invention; Figure 13 This is a schematic diagram of the modular heat exchange device disclosed in Embodiment 4 of the present invention; Figure 14 This is a schematic diagram of the sequential arrangement of heat exchange units in the modular heat exchange device disclosed in Embodiment 4 of the present invention; Figure 15 This is a schematic diagram of the staggered arrangement structure of the heat exchange units in the modular heat exchange device disclosed in Embodiment 4 of the present invention; Figure 16 This is a schematic diagram of the sequential arrangement of heat exchange units in the modular heat exchange device disclosed in Embodiment 5 of the present invention; Figure 17 This is a schematic diagram of the staggered arrangement structure of the heat exchange units in the modular heat exchange device disclosed in Embodiment 5 of the present invention; Figure 18 This is a cloud map comparing the outlet temperature field of the flow channel in the modular heat exchanger of the present invention with that of a traditional flat plate array. Figure 19 This is a pressure comparison cloud diagram of the flow channel in the modular heat exchanger of the present invention and a traditional flat plate array system; Figure 20 This is a comparison diagram of the flow field structure of the modular heat exchange device of the present invention and that of the traditional flat plate array (the left side is the flow field of the flow channel of the present invention, and the right side is the flow field of the traditional flat plate array).

[0025] In the figure, the reference numerals are: 100 - heat exchange unit; 200 - modular heat exchange device; 1-Heat exchange plate; 11-Periodic concave-convex bending area; 111-Bending position; 12-Fluid corner hole; 2-Heat pipe array; 21-Heat pipe unit; 211-Columnar heat pipe body; 212-Radial fins; 3- Bolts; 4- Thermally conductive silicone; 5-Nuts; 6-Edge connection; 61-Flange; 7-Fixing screw; 8-Flow channel. Detailed Implementation

[0026] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0027] One of the objectives of this invention is to provide a novel heat exchange unit to address the technical problems of existing heat exchange equipment that cannot achieve a good balance between high-efficiency heat transfer, low flow resistance and high anti-fouling performance, and lacks flexible modular expansion capabilities, thus failing to meet the compact requirements of special scenarios.

[0028] Another objective of this invention is to provide a modular heat exchange device comprising the aforementioned heat exchange unit, in order to solve the technical problem that existing heat exchange equipment cannot achieve a good balance between high-efficiency heat transfer, low flow resistance and high anti-fouling performance, and lacks flexible modular expansion capability, thus failing to meet the compactness requirements of special scenarios.

[0029] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0030] Example 1 like Figures 1-3 As shown, this embodiment provides a heat exchange unit 100, which includes a heat exchange plate 1 and a heat pipe array 2. The heat exchange plate 1 has periodically irregularly shaped bending regions 11. The heat pipe array 2 includes a plurality of heat pipe units 21 protruding from the surface of the heat exchange plate 1. The heat exchange plate 1 may have the aforementioned heat pipe array 2 on only one side or on both sides. Regardless of whether it is on one side or both sides, it is preferable that the heat pipe array 2 is distributed in the periodically irregularly shaped bending regions 11, so as to achieve efficient heat exchange by integrating the point distribution of the plurality of heat pipe units 21 with the gradually expanding and contracting configuration of the periodically irregularly shaped bending regions 11. Each heat pipe unit 21 is preferably detachably connected to the heat exchange plate 1, so as to facilitate flexible and independent replacement of the heat pipe unit 21.

[0031] In some feasible embodiments, preferably, any bending position 111 of the heat exchange plate 1 is an arc-shaped or zigzag-shaped structure. The heat exchange plate 1 is a one-piece molded plate, and its overall outline includes, but is not limited to, polygonal, circular, or elliptical shapes. Figure 1 and Figure 2 As shown, the overall outline of the heat exchange plate 1 is rectangular. The periodic concave-convex bending region 11 in the middle is formed by the reciprocating bending of the heat exchange plate 1. The two ends of the periodic concave-convex bending region 11 remain as flat plates, on which fluid corner holes 12 can be formed. Figure 1 and Figure 2 As shown, a fluid corner hole 12 is formed at each of the four corners of the heat exchange plate 1 to allow the fluid to be exchanged to flow. The shape of the fluid corner hole 12 includes, but is not limited to, circles, polygons, etc.

[0032] In some feasible implementations, heat pipe arrays 2 are preferably provided on both sides of the heat exchange plate 1 to ensure the heat exchange efficiency of the heat exchange unit 100. The heat pipe arrays 2 on both sides can be installed on both sides of the heat exchange plate 1 respectively, or the heat pipe arrays 2 on both sides can be integrated into one piece by installing each heat pipe unit 21 through the heat exchange plate 1.

[0033] like Figures 1-3 The diagram shows a heat pipe unit 21 penetrating the heat exchange plate 1, thus forming a heat pipe array 2 on both sides of the heat exchange plate 1. Specifically, each heat pipe unit 21 is a columnar heat pipe unit, and each columnar heat pipe unit is arranged at an angle to the corresponding mounting area surface of the heat exchange plate 1. The angle can be acute or right angle. Figure 3 As shown, in order to maximize the surface area of ​​the portion of the heat pipe unit 21 that protrudes from the surface of the heat exchange plate 1, it is preferable that any heat pipe unit 21 is perpendicular to the surface of the corresponding installation area of ​​the heat exchange plate 1, thereby ensuring better heat exchange effect of the heat pipe array 2 on each side of the heat exchange plate 1.

[0034] In some feasible implementations, the cylindrical heat pipe unit can be either a cylinder or a prism. Specifically, the prism can be a triangular prism, a square prism, or a pentagonal prism, etc. Figures 1-3 The diagram shown is a schematic of a structure in which each columnar heat pipe unit adopts a cylindrical shape.

[0035] In some feasible implementations, the dimensions of each columnar heat pipe unit can be: an outer wall diameter of 5mm to 9mm, an axial length of 17mm to 24mm, and an effective heat exchange length (i.e., the sum of the portions extending to both sides of the heat exchange plate 1) of 15mm to 20mm. Specifically, the outer wall diameter of the columnar heat pipe unit is 8mm.

[0036] In some feasible implementations, the periodically concave and convex bending region 11 is provided with an array of through holes for installing the heat pipe array 2. The form of the through hole array matches (i.e. is exactly the same) the layout of the heat pipe array 2. The through holes correspond one-to-one with the columnar heat pipe units and are fitted with gaps.

[0037] Some feasible implementation methods, such as Figure 3 , Figures 10-12As shown, the columnar heat pipe unit includes a columnar heat pipe body 211 and radial fins 212 disposed on the outer wall of the columnar heat pipe body 211. The columnar heat pipe body 211 is cylindrical, and the radial fins 212 are integrally formed with the columnar heat pipe body 211 and extend outward along the radial direction of the columnar heat pipe body 211. After the columnar heat pipe unit penetrates the corresponding through hole from one side of the heat exchange plate 1 to the other side of the heat exchange plate 1, it contacts one side of the heat exchange plate 1 (opposite to the aforementioned "other side") through the radial fins 212. The radial fins 212 limit the depth of the columnar heat pipe unit penetrating the through hole, thereby achieving the positioning of the columnar heat pipe unit on the heat exchange plate 1. The radial fins 212 and the heat exchange plate 1 are preferably connected by mechanical fasteners that are easy to disassemble and assemble. The mechanical fasteners include, but are not limited to, bolt pairs. The bolt pairs include bolts 3 and nuts 5 that are adapted to bolts 3. Bolt 3 passes through the radial fins 212 and the heat exchange plate 1 in sequence and is then tightened with nut 5, thus fixing and sealing the radial fins 212 and the heat exchange plate 1. To improve connection reliability, it is preferable that each columnar heat pipe unit is fixed by multiple circumferentially distributed bolt pairs, as shown in the reference. Figures 10-12 This is a schematic diagram of the structure in which each columnar heat pipe unit is fixed by four circumferentially distributed bolt pairs. After the columnar heat pipe unit is fixed to the heat exchange plate 1 by radial fins 212, both ends of the columnar heat pipe body 211 protrude from the two side surfaces of the heat exchange plate 1, thereby forming a heat pipe array 2 on both sides of the heat exchange plate 1.

[0038] Since the corresponding heat pipes on both sides of the heat exchange plate 1 share a single columnar heat pipe, and combined with the periodic distribution of the bending positions 111 in the periodic concave-convex bending region 11, the heat pipe arrays 2 on both sides of the heat exchange plate 1 are staggered, rather than completely symmetrical.

[0039] The columnar heat pipe unit is installed in the through hole of heat exchange plate 1 in a pluggable manner, which facilitates disassembly and maintenance.

[0040] In some feasible implementations, the radial fins 212 can be radial fin protrusions, in which case multiple radial fins 212 can be arranged at intervals around the outer wall of the columnar heat pipe body 211. Alternatively, the radial fins 212 can also be continuous, integral annular fins, such as... Figures 10-12 The diagram shown illustrates a one-piece annular fin with a circular ring structure. In practical applications, a one-piece annular fin can also employ a polygonal ring structure.

[0041] In some feasible implementations, to ensure the sealing at the insertion point between the columnar heat pipe body 211 and the heat exchange plate 1, thermally conductive silicone 4 can be filled at the contact interface between the radial fins 212 and the heat exchange plate 1. The thermally conductive silicone 4 is an annular gasket that is pressed between the radial fins 212 and the heat exchange plate 1 when the bolts are tightened to secure the columnar heat pipe unit. Simultaneously, the thermally conductive silicone 4 has good thermal conductivity and will not affect the overall heat exchange performance of the heat exchange unit 100. It should be noted that the thermally conductive silicone 4 is tightly fitted onto the outside of the columnar heat pipe body 211. After being pressed, the thermally conductive silicone 4 effectively seals the gap between the through hole on the heat exchange plate 1 and the columnar heat pipe body 211, as well as the gap between the thermally conductive silicone 4 and the columnar heat pipe body 211, achieving a good sealing effect.

[0042] Thermally conductive silicone 4 can preferably be a non-fluorine high thermally conductive silicone.

[0043] Thermally conductive silicone 4 can be located on the inner ring of each bolt pair, in which case bolt 3 will not penetrate the thermally conductive silicone 4. Alternatively, thermally conductive silicone 4 can also cover the penetration point of bolt 3, in which case bolt 3 will penetrate the thermally conductive silicone 4 during installation.

[0044] The specifications of bolt 3 can be flexibly adjusted according to different sizes of heat pipe units 21. The available bolts 3 include, but are not limited to, miniature bolts of M1.2, M1.4, or M1.6. Generally, the larger the outer diameter of the heat pipe unit 21 and the larger the radial length of the radial fins 212, the larger the available bolt specifications 3, and vice versa.

[0045] In some feasible implementations, to ensure the reliability of each bolt pair, it is preferable to also include a washer in the bolt pair, such as... Figures 10-12 As shown, the gasket is located on the side of the radial fin 212 away from the heat exchange plate 1. The bolt 3 passes through the gasket, the radial fin 212 and the heat exchange plate 1 in sequence and is then tightened with the nut 5. The head of the bolt 3 presses the gasket tightly.

[0046] In some feasible implementations, the length ratio of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 is 1:1 to 1:2. When the length ratio of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 is 1:1, it indicates that the lengths of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 are the same; when the length ratio of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 is not 1:1, it indicates that the lengths of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 are different. When the lengths of the two sides of the columnar heat pipe body 211 protruding from the heat exchange plate 1 are different, it is preferable that the length of the side located in the cold fluid is shorter than the length of the side located in the hot fluid, for example, the ratio of the length of the side in the cold fluid to the length of the side in the hot fluid is 1:2.

[0047] In some feasible implementations, preferably, any bending point 111 of the heat exchange plate 1 is a zigzag structure, and the zigzag structure is an isosceles trapezoid. (See reference) Figure 1 and Figure 3 Each bend 111 has its apex a vertical section parallel to the straight ends of the heat exchange plate 1. This vertical section is flanked by symmetrical sloping sections. The vertical section and the sloping sections together constitute a bend 111. The structure of each bend 111 is identical, except that every two adjacent bends 111 bulge towards both sides of the heat exchange plate 1, forming a periodic convex-concave arrangement. Rows of columnar heat pipe units are installed on the sloping sections on both sides of each bend 111. (See details...) Figure 1 and Figure 3 .

[0048] In some feasible implementations, the width of the heat exchange plate 1 in the heat exchange unit 100 is preferably 150 mm, and the length is between 200 mm and 300 mm. The total number of heat pipe units 21 installed on the heat exchange plate 1 is unlimited and is determined according to actual needs. (Refer to...) Figure 1 This is a schematic diagram of the installation of 78 heat pipe units 21.

[0049] In some feasible implementations, at each bending position 111, the angle between the inclined segment and the vertical segment is α. α can also be called the expansion angle or contraction angle of the periodic concave-convex bending region 11, and α is preferably 15°~35°. (Reference) Figure 3 The supplementary angle of α is the bending angle at each bending position 111.

[0050] To improve heat exchange efficiency, it is preferable that the heat pipe units 21 on the two inclined sections at each bend 111 are staggered in the width direction of the heat exchange plate 1 (i.e., the row direction of the heat pipe units 21), such as... Figure 1 As shown, seven heat pipe units 21 are installed on one side of the inclined section at each bend position 111, and six heat pipe units 21 are installed on the other side of the inclined section.

[0051] The heat exchange unit 100 can be assembled individually in the shell or multiple units can be connected in series to form a heat exchanger core.

[0052] In the heat exchanger core, the plate spacing between two adjacent heat exchange plates 1 is adjustable within the range of 8mm to 20mm. The operating temperature of the heat exchanger core does not exceed 100 degrees Celsius and is suitable for gas-liquid, liquid-liquid, or coal-water slurry heat exchange scenarios.

[0053] Example 2 like Figures 4-6As shown, this embodiment proposes a heat exchange unit 100, which, based on embodiment 1, also has a perimeter connection part 6 on the outer periphery of the heat exchange plate 1 for series fixation with adjacent heat exchange plates 1.

[0054] refer to Figure 4 Preferably, the edge connecting part 6 is integrally formed with the heat exchange plate 1. The edge connecting part 6 is a closed ring and perpendicular to the heat exchange plate 1. The edge connecting part 6 extends symmetrically to both sides of the heat exchange plate 1 to form the enclosure sidewall of the heat exchange plate 1. In order to facilitate the connection between adjacent heat exchange units 100 through the edge connecting part 6, it is preferable that both ends of the edge connecting part 6 are also provided with flanges 61, which are parallel to the flat plate sections at both ends of the heat exchange plate 1. Adjacent heat exchange units 100 can be seamlessly connected through the flanges 61, and then the fixing screws 7 can be inserted through the flanges 61 of the two heat exchange units 100 to realize the series fixation of adjacent heat exchange units 100.

[0055] refer to Figure 4 Preferably, multiple mounting holes are provided on the flange 61 along its circumference. After the flanges 61 of the two heat exchange units 100 are connected, the mounting holes are aligned one by one, and the fixing screw 7 can be passed through the mounting holes to achieve fixation.

[0056] The fixing screw 7 includes, but is not limited to, bolts. After the bolt passes through the mounting hole, it is tightened with the matching nut to complete the series fixing and sealing of adjacent heat exchange units 100. At this time, the perimeter connection part 6 of the two heat exchange units 100 together constitutes the sealing enclosure of the two heat exchange plates 1.

[0057] Example 3 like Figures 7-9 As shown, this embodiment proposes a heat exchange unit 100, which differs from embodiments 1 and 2 in that: at any bending position 111 of the heat exchange plate 1, the included angle α between the inclined section and the vertical section is 90°. (Reference) Figure 9 The supplementary angle of α, that is, the bending angle of each bending position 111 is 90°.

[0058] The remaining structure of the heat exchange unit 100 in this embodiment is the same as that in embodiments 1 and 2, and will not be described again here.

[0059] Example 4 like Figure 13 As shown, this embodiment proposes a modular heat exchange device 200, which includes multiple heat exchange units 100 as disclosed in Embodiment 2. The multiple heat exchange units 100 are arranged in sequence, and adjacent heat exchange units 100 are seamlessly connected through flanges 61. The series fixation of adjacent heat exchange units 100 can be achieved by using fixing screws 7 passing through the flanges 61 of two adjacent heat exchange units 100.

[0060] In the modular heat exchanger 200, a flow channel 8 for fluid circulation and heat exchange is formed between the heat exchange plates 1 of any two adjacent heat exchange units 100. Since each perimeter connection 6 extends a certain length to both sides of the heat exchange plate 1, after multiple heat exchange units 100 are sequentially connected and fixed in series, the perimeter connection 6 of each heat exchange unit 100 is sequentially sealed and joined to form the side wall shell of the entire modular heat exchanger 200. By sealing the two ends of the side wall shell with end plates, a closed modular heat exchanger 200 can be formed. Fluid inlets and fluid outlets can be provided on the end plates to communicate with the interior of the device.

[0061] In some feasible implementations, the heat exchange units 100 in the modular heat exchange device 200 can be of the same specification or different specifications. When the heat exchange units 100 are of the same specification, for example, all of them are heat exchange units 100 of Embodiment 2, and all heat exchange units 100 can be configured according to... Figure 13 The arrangement shown can also be done in the following order: Figure 15 The arrangement is staggered as shown.

[0062] like Figure 14 As shown, when the heat exchange units 100 are arranged in a row, the flow channel 8 structure between any two adjacent heat exchange plates 1 of the heat exchange units 100 is exactly the same. Figure 14 The diagram shows a modular heat exchange device 200 consisting of six heat exchange units 100 connected in series, with five identical flow channels 8 forming the device. The heat pipe units 21 in each heat exchange unit 100 are arranged in a straight line.

[0063] like Figure 15 As shown, when the heat exchange units 100 are arranged in a staggered manner, the heat exchange plates 1 of any two adjacent heat exchange units 100 are arranged symmetrically, resulting in the flow channels 8 formed between the heat exchange plates 1 being gradually expanding and contracting periodic flow channels. Furthermore, the expansion and contraction positions of each adjacent flow channel 8 are staggered. Simultaneously, the heat pipe units 21 in each heat exchange unit 100 are arranged in a staggered manner. This design is more conducive to improving the heat exchange effect.

[0064] The aforementioned modular heat exchange device 200 is essentially a modular high-efficiency heat exchange device with an integrated micro heat pipe array. It is generally composed of 6 heat exchange units 100 connected in series. Its operating temperature is no higher than 100 degrees Celsius. It is suitable for gas-liquid, liquid-liquid, or water-coal slurry heat exchange scenarios. It is particularly suitable for advanced thermal management scenarios such as slurry and ionic liquid heat exchange, liquid cooling of electronic equipment, thermal management of new energy vehicles, and aerospace environmental control systems, where there are strict requirements for spatial layout, volume control, and heat exchange efficiency.

[0065] Example 5 This embodiment proposes a modular heat exchange device 200, which differs from Embodiment 4 only in that the heat exchange plates 1 of the heat exchange unit 100 adopt the structure of Embodiment 3.

[0066] like Figure 16 As shown, when the heat exchange units 100 are arranged in a row, the flow channel 8 structure between any two adjacent heat exchange plates 1 of the heat exchange units 100 is exactly the same. Figure 16 The diagram shows a modular heat exchange device 200 consisting of six heat exchange units 100 connected in series, with five identical flow channels 8 forming the device. The heat pipe units 21 in each heat exchange unit 100 are arranged in a straight line.

[0067] like Figure 17 As shown, when the heat exchange units 100 are arranged in a staggered manner, the heat exchange plates 1 of any two adjacent heat exchange units 100 are arranged symmetrically, resulting in the flow channels 8 formed between the heat exchange plates 1 being gradually expanding and contracting periodic flow channels. Furthermore, the expansion and contraction positions of each adjacent flow channel 8 are staggered. Simultaneously, the heat pipe units 21 in each heat exchange unit 100 are arranged in a staggered manner. This design is more conducive to improving the heat exchange effect.

[0068] The aforementioned modular heat exchange device 200 is essentially a modular high-efficiency heat exchange device with an integrated micro heat pipe array. It is generally composed of 6 heat exchange units 100 connected in series. Its operating temperature is no higher than 100 degrees Celsius. It is suitable for gas-liquid, liquid-liquid, or water-coal slurry heat exchange scenarios. It is particularly suitable for advanced thermal management scenarios such as slurry and ionic liquid heat exchange, liquid cooling of electronic equipment, thermal management of new energy vehicles, and aerospace environmental control systems, where there are strict requirements for spatial layout, volume control, and heat exchange efficiency.

[0069] Example 6 This embodiment proposes a modular heat exchange device 200, which differs from embodiments 4 and 5 in that the heat exchange units 100 in the modular heat exchange device 200 adopt two specifications: one heat exchange unit 100 uses the heat exchange plates 1 of embodiment 1, and the other heat exchange unit 100 uses the heat exchange plates 1 of embodiment 3. In this case, the two specifications of heat exchange units 100 are preferably arranged in a staggered manner, and each adjacent heat exchange unit 100 can be arranged in a straight line or in a staggered manner.

[0070] The aforementioned modular heat exchange device 200 is essentially a modular high-efficiency heat exchange device with an integrated micro heat pipe array. It is generally composed of 6 heat exchange units 100 connected in series. Its operating temperature is no higher than 100 degrees Celsius. It is suitable for gas-liquid, liquid-liquid, or water-coal slurry heat exchange scenarios. It is particularly suitable for advanced thermal management scenarios such as slurry and ionic liquid heat exchange, liquid cooling of electronic equipment, thermal management of new energy vehicles, and aerospace environmental control systems, where there are strict requirements for spatial layout, volume control, and heat exchange efficiency.

[0071] Example 7 This embodiment proposes a modular heat exchange device 200, which differs from embodiments 4, 5, and 6 in that it also includes a dedicated outer shell, within which the entire series structure of heat exchange units with sidewalls is fixed. The outer shell has a fluid inlet and a fluid outlet, and multiple heat exchange units 100 are located between the fluid inlet and the fluid outlet.

[0072] In summary, the heat exchange unit 100 of this invention achieves an integrated coupling design of micro heat pipes and heat exchange plates. The heat exchange plates form periodically changing flow channels through specific bending, which can effectively balance the flow field distribution and flow resistance, forming a flow drag-reducing array-type thermal superconducting modular heat exchange device. The flow channel design includes gradually widening and narrowing types (α is an acute angle) and constant cross-section types (α is a right angle), and the corresponding flow channel design can be adopted according to different scenarios and usage requirements.

[0073] The heat pipe unit employs a micro heat pipe structure with an outer diameter of 8mm and a length of 15-20mm. It is vertically and pluggably installed in the plate through-hole through a novel mechanical fastening structure. This structure uses a micro bolt and nut assembly to mate with the annular fins integrally formed in the middle of the heat pipe, and fills the contact interface with non-fluorine high thermal conductivity silicone, thus achieving mechanical fixation, efficient heat conduction, and reliable sealing.

[0074] In the modular heat exchanger 200, each heat exchange unit is combined through modular integration, and the spacing between adjacent plates can be adjusted within the range of 8mm to 20mm. By optimizing the arrangement of adjacent plates (straight-ahead / staggered), a compact heat exchange module with reconfigurable characteristics is formed.

[0075] The Modular Heat Exchanger 200 systematically couples micro heat pipe arrays, modular plate structures, and optimized flow channel design, achieving comprehensive performance in terms of high-efficiency heat transfer, compact structure, independent maintenance, controllable flow resistance and fouling, and flexible configuration. It solves the technical contradictions of traditional heat exchange equipment in terms of maintainability, compactness, flow resistance control, and anti-fouling performance, and is particularly suitable for heat exchange scenarios with stringent requirements for space, weight, and reliability, such as liquid cooling of electronic equipment and thermal management of new energy.

[0076] Compared with the prior art, the advantages of the present invention are as follows: (i) Modular maintenance capability, extremely low total lifecycle cost: This invention enables the independent installation and replacement of individual micro heat pipes through a detachable mechanical connection structure. When an individual heat pipe is damaged due to corrosion, wear, or accidental failure, it is not necessary to scrap the entire plate or heat exchanger core; only the faulty unit needs to be replaced. This completely solves the industry pain points of traditional brazed plate heat exchangers where partial damage results in complete scrapping, and the difficulty of maintaining large heat pipe heat exchangers, greatly reducing equipment maintenance costs, downtime, and total life cycle costs.

[0077] (ii) Overall heat transfer and fluid mixing performance: This invention achieves deep optimization of the heat transfer and flow process through the synergistic design of "periodicly widening and narrowing flow channels" and "micro heat pipe arrays arranged in parallel / staggered rows". Enhanced heat transfer: The periodic flow channel effectively disrupts the fluid boundary layer, while the heat pipe array greatly enhances the local heat transfer intensity through phase change heat transfer. The coupling of the two produces a synergistic effect of "1+1>2".

[0078] Promotes mixing: The gradually widening and narrowing flow channel structure, combined with the turbulence effect of the heat pipe array, greatly enhances the lateral and radial mixing capabilities of the fluid within the flow channel, ensuring the uniformity of the temperature field, thereby improving the overall heat exchange efficiency and reducing the thermal resistance.

[0079] (iii) Compact and lightweight: Due to the extremely high phase change heat transfer efficiency of micro heat pipes, this invention can achieve a huge heat exchange load in a very small volume. To achieve the same heat exchange capacity, the volume of this invention is only about 1 / 23 of that of a traditional plate heat exchanger and about 1 / 33 of that of a traditional shell-and-tube heat exchanger. This order-of-magnitude advantage makes it irreplaceable in applications with stringent space and weight requirements.

[0080] (iv) Low flow resistance and high anti-fouling properties: This invention creatively combines a "periodically varying gradually widening and narrowing flow channel" with a "large adjustable plate spacing," producing a synergistic effect. This design not only achieves low flow resistance while maintaining high-efficiency heat exchange, but more importantly, through the physical guidance of the flow channel and the spacious flow area, it fundamentally inhibits scale formation, significantly reducing maintenance frequency and cleaning costs.

[0081] (v) High reliability and design flexibility: The heat pipe units are mechanically connected, avoiding welding thermal stress; the non-fluorinated thermally conductive silicone is stable at 100℃ and has strong compatibility; the detachable structure facilitates regular inspection and preventive maintenance. Furthermore, by adjusting the plate spacing, the number of heat pipes, and the flow channel angle, it can flexibly adapt to different heat loads and various heat exchange scenarios such as gas-liquid and liquid-liquid exchanges.

[0082] The following is a comparative demonstration of the technical effects of using the modular heat exchanger 200 of Example 4 for liquid-liquid heat exchange: The modular heat exchanger 200 consists of multiple identical heat exchange units 100 connected in series via flanges 61. Each heat exchange unit 100 includes a rectangular heat exchange plate 1 with planar dimensions of 250mm × 150mm. A triangular staggered array of through-holes is formed on the heat exchange plate 1, housing 78 individual copper-water heat pipes with an outer diameter of 8mm and an effective heat exchange length of 16mm. The evaporation section to condensation section of each heat pipe is in a 1:1 ratio, and the individual heat pipes are vertically and detachably fixed to the heat exchange plate 1 via integrally formed annular fins and M1.4 micro-bolt and nut assemblies. All metal contact interfaces are filled with non-fluorinated high thermal conductivity silicone.

[0083] The heat exchange plate 1 has integrally formed perimeter connecting portions 6 perpendicular to the plate, thus forming a shallow disc-shaped structure on both sides of the heat exchange plate 1. Fluid corner holes 12 are provided at the four corners of the heat exchange plate 1. This design is exactly the same as that of a conventional plate heat exchanger, laying the foundation for the organization of flow channels. A series of fastening through holes for mounting bolts are provided on the edge flange 61 of the perimeter connecting portion 6.

[0084] The heat exchange plate 1 is formed by stamping into periodically widening and narrowing flow channels with an α angle of 25 degrees. This flow channel effectively disrupts the fluid boundary layer and promotes turbulence. The heat pipe unit adopts... Figure 14 The staggered arrangement shown, in conjunction with the gradually widening and narrowing flow channels, jointly achieves efficient fluid mixing and enhanced heat transfer.

[0085] During assembly, the six heat exchange units 100 are stacked in alignment. Sealing gaskets with specific opening and closing patterns at the fluid corner holes 12 are placed between adjacent units, creating efficient diagonal flow channels within the assembled heat exchange device. Subsequently, bolts passing through the fastening through-holes are used for compression sealing, forming a rigid heat exchange device. Finally, end caps with fluid inlets and outlets are sealed at both ends of the heat exchange device, completing the assembly of the entire device.

[0086] The plate spacing between connected heat exchange units 100 is set at 14 mm. This relatively large spacing effectively reduces flow resistance and inhibits fouling while ensuring compactness. This embodiment fully demonstrates the modularity, maintainability, high compactness, and enhanced heat transfer capabilities of the present invention. A single heat exchange unit 100 can be replaced as a whole in the event of large-area damage, while a damaged single heat pipe can be replaced individually, achieving dual modular maintenance.

[0087] Comparative Example 1: Traditional Plate Heat Exchanger (without heat pipes and optimized flow channels) This comparative example uses a rectangular heat exchange plate with dimensions similar to the aforementioned embodiment, approximately 250mm × 150mm in planar projection. The plate is a flat or conventionally shallowly corrugated metal plate, lacking an array of through-holes for mounting micro heat pipes. The basic module is characterized by an annular shell sidewall integrally formed around the heat exchange plate, perpendicular to the plate, thus forming a shallow disc-shaped structure. Fluid corner holes are provided at the four corners of the heat exchange plate, and a series of fastening through-holes for mounting bolts are provided on the edge flange of the annular shell sidewall. The module is assembled in the same way as in the embodiments of the present invention: multiple basic modules are sequentially aligned and stacked, sealed with gaskets and bolt flange assemblies, and end caps with connecting pipes are sealed at both ends of the core, thus forming a complete heat exchanger core. The equivalent width of the flow channel is the same as the average width of the flow channel in the embodiments of the present invention, which is 14mm.

[0088] Comparative Example 2: Commercial Brazed Plate Heat Exchanger This comparative example uses a standard commercial brazed plate heat exchanger, model BR0.5 series. This heat exchanger consists of dozens of 316L stainless steel plates pressed into a herringbone corrugated pattern at specific angles (e.g., 45° or 60°), stacked together. The plates are permanently sealed together by copper or nickel brazing filler around the perimeter, forming a non-removable integral core. Fluid is distributed through corner holes at the plate corners, forming a complex mesh-like flow channel to enhance turbulence.

[0089] Comparative Example 3: Traditional Shell-and-Tube Heat Exchanger This comparative example uses a fixed tubesheet shell-and-tube heat exchanger commonly used in industrial applications, model BEM 300-150-2-1.0. This heat exchanger consists of a cylindrical carbon steel shell, a tube bundle composed of multiple heat exchange tubes, and multiple baffles to change the flow direction of the shell-side fluid. Heat exchange occurs between the tube-side and shell-side fluids through the tube walls.

[0090] Comparative experiments and effect verification To comprehensively and quantitatively verify the significant advantages of this invention over traditional technologies in terms of overall thermal performance and equipment compactness, the following two sets of comparative analyses are conducted. The first set focuses on the flow and heat transfer performance of the core heat transfer unit, while the second set provides a macroscopic comparison from the perspectives of overall size and integration.

[0091] I. Implementation Example and Performance Verification of Comparative Example 1 (Traditional Flat Panel Array) This section uses CFD simulation to compare the thermal performance of the flow channel of this invention with that of Comparative Example 1 (traditional flat panel array) under the same benchmark.

[0092] 1. Comparative Analysis of Heat Exchange Efficiency like Figure 18The outlet temperature field comparison contour map results shown are under the same inlet temperature conditions: The average outlet temperature of Comparative Example 1 (traditional flat panel array) is 309.21 K.

[0093] The average outlet temperature of the embodiment of the present invention (periodic widening and narrowing flow channel) is 331.59 K.

[0094] Conclusion: The outlet temperature of the flow channel of the present invention is 22.38 K higher, and the heat exchange efficiency is improved by 7.2%, which proves the enhancing effect of the periodic flow channel design on heat exchange efficiency.

[0095] 2. Comparative Analysis of Flow Resistance like Figure 19 The system pressure comparison contour plots shown below, under the same flow rate conditions: The required inlet pressure for Comparative Example 1 (traditional flat panel array) is 147.05 Pa.

[0096] The required inlet pressure for the embodiment of this invention (periodic widening and narrowing flow channel) is 129.34 Pa.

[0097] Conclusion: The flow resistance of the flow channel of the present invention is reduced by 17.71 Pa and the pressure drop is reduced by 12%, which verifies the advantages of the design in reducing the energy consumption of the conveying process.

[0098] 3. Flow field structure and mechanism analysis like Figure 20 As shown, the streamlines in the flow channel of Comparative Example 1 are straight, and a distinct velocity boundary layer exists. In contrast, the flow channel of this invention generates an ordered secondary flow structure. This flow pattern enhances the radial mixing and heat transfer of the fluid, and reduces the shear resistance between the flow core and the wall through a "lubrication" effect. This explains, mechanistically, why it can simultaneously improve heat transfer efficiency and reduce flow resistance.

[0099] Our group's verification summary: Comparative data confirms that by simply introducing a periodically widening and narrowing flow channel design, a 7.2% increase in heat transfer and a 12% reduction in flow resistance can be achieved on the basis of the original structure, highlighting the independent innovative value of this design.

[0100] II. Implementation Examples and Comparative Examples 2 and 3 (Commercial Conventional Heat Exchangers) Compactness Verification From an engineering application perspective, this section compares the significant differences in space occupation between the device of this invention and traditional commercial heat exchangers when achieving the same heat exchange capacity (approximately 83.6 kW).

[0101] 1. Comparison objects and operating conditions: Embodiment of the present invention: a modular heat exchange device with flow drag reduction array type heat pipe, with an average plate spacing of 14mm.

[0102] Comparative Example 2: Commercial BR0.5 type brazed plate heat exchanger.

[0103] Comparative Example 3: BEM 300-150-2-1.0 shell-and-tube heat exchanger.

[0104] All three satisfy the same operating conditions and heat load for water-to-water heat exchange (hot side 60℃→40℃, cold side 20℃→40℃).

[0105] 2. Comparison of structural dimensions and volume: The table below clearly shows the physical space occupied by the three devices when achieving the same functionality:

[0106] Conclusion: Data shows that, while outputting the same heat exchange capacity, the volume of the device of this invention is only about 1 / 23 of that of a traditional plate heat exchanger and about 1 / 33 of that of a traditional shell-and-tube heat exchanger. This order-of-magnitude difference stems from the design concept of this invention, which deeply integrates micro heat pipe phase change heat transfer with efficient and compact flow channels, achieving a revolutionary improvement in heat exchange density and providing a disruptive solution for advanced application scenarios with limited space.

[0107] It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and to facilitate understanding. They are not intended to limit the scope of the invention and therefore have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and purpose of the invention, should still fall within the scope of the technical content disclosed herein. Furthermore, the terms "upper," "lower," "left," "right," "middle," and "one" used in this specification are merely for clarity and not intended to limit the scope of the invention. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of the invention's implementation.

[0108] Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this invention. Furthermore, those skilled in the art will recognize that, based on the ideas of this invention, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this invention.

Claims

1. A heat exchange unit, characterized in that, It includes heat exchange plates (1) and a heat pipe array (2), wherein: The heat exchange plate (1) is provided with periodic concave and convex bending areas (11). The heat pipe array (2) includes a plurality of heat pipe units (21) protruding from the surface of the heat exchange plate (1), the heat pipe array (2) is provided on at least one side of the heat exchange plate (1), and the heat pipe array (2) is located in the periodic concave-convex bending region (11).

2. The heat exchange unit according to claim 1, characterized in that, Any bending position (111) of the heat exchange plate (1) is an arc-shaped structure or a zigzag structure.

3. The heat exchange unit according to claim 2, characterized in that, Each of the heat pipe units (21) is a columnar heat pipe unit, and each of the columnar heat pipe units is perpendicular to the corresponding area surface of the heat exchange plate (1).

4. The heat exchange unit according to claim 3, characterized in that, The periodic concave-convex bending region (11) is provided with an array of through holes that match the heat pipe array (2); the columnar heat pipe unit includes a columnar heat pipe body (211) and radial fins (212) disposed on the outer wall of the columnar heat pipe body (211). The columnar heat pipe unit penetrates through the corresponding through hole and is connected and fixed to the heat exchange plate (1) through the radial fins (212). The two ends of the columnar heat pipe body (211) protrude from the two sides of the heat exchange plate (1) respectively, so that the heat pipe array (2) is formed on both sides of the heat exchange plate (1).

5. The heat exchange unit according to claim 4, characterized in that, The radial fins (212) are annular fins, and the contact interface between the annular fins and the heat exchange plate (1) is filled with thermally conductive silicone (4).

6. The heat exchange unit according to claim 4, characterized in that, The length ratio of the columnar heat pipe body (211) protruding from both sides of the heat exchange plate (1) is 1:1 to 1:

2.

7. The heat exchange unit according to any one of claims 1-6, characterized in that, The outer periphery of the heat exchange plate (1) is also provided with a periphery connection part (6) for connecting and fixing with the adjacent heat exchange plate (1) in series.

8. A modular heat exchanger, characterized in that, It includes a plurality of heat exchange units (100) as described in any one of claims 1 to 7, wherein the plurality of heat exchange units (100) are connected in series, and a flow channel (8) for fluid flow and heat exchange is formed between the heat exchange plates (1) of any two adjacent heat exchange units (100).

9. The modular heat exchanger according to claim 8, characterized in that, All of the heat exchange units (100) have the same structure, and all of the heat exchange units (100) are arranged in a straight line or staggered. Alternatively, all of the heat exchange units (100) may have different structures and may be arranged in an alternating pattern.

10. The modular heat exchanger according to claim 8 or 9, characterized in that, It also includes a housing with a fluid inlet and a fluid outlet, and a plurality of the heat exchange units (100) are fixed inside the housing and located between the fluid inlet and the fluid outlet.

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