Micro-channel plate-fin heat exchanger

Abstract

A micro-channel plate-fin heat exchanger, comprising a heat exchange unit (1). The heat exchange unit (1) is configured to form a path through which a hot fluid flows, so as to absorb the heat of the hot fluid, and to perform heat transfer by means of the flow of an external cold fluid so as to achieve heat exchange, thereby completing heat transfer and implementing temperature adjustment and control. Due to the improvement in a sealing structure, the present invention can improve the sealing performance of a traditional heat exchanger, and can meet a sealing effect even under a higher fluid pressure, thereby realizing stable heat exchange of the hot fluid, and thus ensuring the stability and reliability of a temperature control process. In addition, due to the use of an assembled structure, heat exchange units can be combined on the basis of actual needs, thereby improving the use flexibility of the heat exchange units, being adaptable to more use environments, and therefore meeting temperature adjustment and control requirements in different cases.

Description

A microchannel plate-fin heat exchanger Technical Field

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

[0002] Plate-fin heat exchangers and microchannel heat exchangers are widely used in industries such as petroleum, chemical, natural gas, pharmaceutical, air conditioning, and automotive, offering advantages such as compactness, lightweight design, and high heat transfer efficiency. However, the manufacturing process of plate-fin heat exchangers is complex, typically involving the stacking of multiple materials, including baffles, fins, guide vanes, hot fluid channel side seals, and cold fluid channel side seals, which are then brazed to form the heat exchange core. During brazing, technical defects such as incomplete welds, missing welds, and the brazing filler metal itself can occur at the connection between the baffles and fins, severely impacting the heat transfer efficiency of the plate-fin heat exchanger. Furthermore, the ability to achieve high-standard, high-density fins is limited by equipment processing capabilities.

[0003] Plate-fin heat exchangers also have many drawbacks in practical applications.

[0004] Among them, the manufacturing process of microchannel heat exchangers is relatively simpler than that of plate-fin heat exchangers. However, they also suffer from technical defects such as poor soldering thermal resistance, missing soldering thermal resistance, and the thermal resistance of the brazing filler metal itself at the connection between the flat tube and the fins. In addition, the center dimension of the two channels in the flat tube is generally more than 2mm. Even if it is reduced to less than 2mm, the cost is extremely high. Moreover, the width of the center dimension of the two fluid channels and the thickness of the fins are all determined by a mold for a flat tube product. Therefore, the product size has poor flexibility and is difficult to adapt to the needs of modern society.

[0005] In addition, the core of plate-fin heat exchangers is prone to scaling and clogging, and is difficult to clean. Scale and clogging seriously affect the heat exchange efficiency of plate-fin heat exchangers. Moreover, in the food and pharmaceutical industries, the internal channels of plate-fin heat exchangers are often blocked or difficult to clean, which leads to the infection and growth of bacteria in a large number of raw materials, resulting in the scrapping of raw materials and causing significant economic losses to enterprises.

[0006] In today's booming online sales platforms, the diverse needs of end customers have led to a variety of heat exchanger product sizes. In this context, the cost of flat tube molds increases product costs, thereby affecting the actual promotion and use of the product.

[0007] It is evident that current heat exchanger solutions still have room for improvement and require optimization to enhance heat exchange performance while maintaining greater compatibility for flexible use in various application scenarios. Therefore, a more reasonable technical solution is needed to address the problems existing in the current technology. Summary of the Invention

[0008] The present invention aims to provide a microchannel plate-fin heat exchanger, which improves the composition and structure of the heat exchanger, making the heat exchanger product simpler to manufacture, more flexible in size, and more efficient in heat exchange, thereby solving the technical defects of existing plate-fin and microchannel heat exchangers.

[0009] To achieve the above objectives, the plate-fin heat exchanger disclosed in this invention can adopt the following solution:

[0010] A microchannel plate-fin heat exchanger mainly consists of a heat exchange unit and independent baffles or flat plate fins forming the heat exchange core. The heat exchange unit is obtained by secondary cutting and grooving of a one-piece molded single-sided heat exchange fin or plate. The one-piece molded single-sided heat exchange fin has cold fluid channels, cold fluid channel side seals, a base plate, and cold fluid channel fins. The heat exchange unit is formed by secondary processing of the base plate through cutting and grooving. The heat exchange unit is composed of baffles, hot fluid channel fins, cold fluid channel fins, hot fluid channels, cold fluid channels, hot fluid channel side seals, and cold fluid channel side seals, all made of the same material. The main technical... The technical features are: the baffle, hot fluid channel fins, and cold fluid channel fins are made of the same material as a whole. The hot or cold fluid channel fins are parallel to each other and perpendicular to both sides of the baffle. The hot and cold fluid channel fins are intersected, with a minimum angle between 30° and 90°. To create a turbulence pattern in the hot and cold fluid channels, the secondary-processed hot and cold fluid channel fins can be bent so that the fin feet of the hot or cold fluid channel fins are parallel to each other, and the hot or cold fluid channel fins are inclined to both sides of the baffle. The series combination also forms a fluid guiding channel on the cold fluid side seal. For high-end, custom-sized products, the channels on both sides of the baffle can be directly cut and grooved from sheet metal, but this results in significant material waste and is only suitable for high-end, custom-sized products.

[0011] The microchannel plate-fin heat exchanger provided in this application has the following positive technical effects:

[0012] 1. Product manufacturing is simplified. As we can see from the utility model content, the heat exchange core of a microchannel plate-fin heat exchanger is composed of a heat exchange unit and independent baffles or flat fins. The heat exchange unit is a whole of the same material, which greatly reduces the product assembly steps and the manufacturing and processing costs of fins, hot and cold channels side seals, and fin forming equipment costs.

[0013] 2. More flexible and mobile product dimensions: The dimensions of the heat exchanger equipment's y-axis, x-axis, hot fluid channel, and fin thickness can be freely and flexibly adjusted according to customer needs. It is known that the length of the one-piece molded single-sided fin heat sink can fully meet the needs of various product dimensions along the y-axis. Since the width of the single-sided fin heat sink is limited by the one-piece molding equipment, when the dimension in the x-axis direction is larger than the limitation of the existing one-piece molding equipment, we can adopt a butt joint method in the x-axis direction. Since the cross-section of the hot fluid channel is usually relatively small, we can assume that the hot fluid is under static pressure and calculate the cross-sectional area pressure value of the hot fluid channel according to the cross-sectional area pressure formula, that is, calculate the axial tensile force in the direction of the hot fluid channel. Adding the contact area of ​​the hot fluid side seal and the fin height as the sealing surface, and with the support of independent baffles or flat fins, there is no need to worry about the axial pressure resistance in the direction of the hot fluid channel. As for the size of the hot fluid channel and the thickness of the fins, we can meet the size requirements of different products by changing the cutting and grooving tools. Through practical testing, I have found that the center size of the two hot fluid channels can easily reach 1mm or even lower by using the cutting and grooving process. Moreover, the equipment cost and equipment operating cost of this solution are very low. In air conditioning applications, it can significantly reduce the amount of refrigerant used. Of course, in special fields, EDM or etching technology can be used to achieve a smaller channel cross-sectional area, but the manufacturing cost will increase significantly.

[0014] 3. The product's heat exchange efficiency is significantly improved, mainly due to the fact that the baffle and the fins of the hot and cold channels are made of the same material, and the arrangement of the hot and cold channels and fins. As mentioned above, the baffle and the fins of the hot and cold fluid channels are made of the same material. This means that the problems of poor welding, missing welding, and the thermal resistance of the brazing filler metal itself at the connection between the baffle and the fins or the microchannel flat tube and the fins in the above-mentioned plate-fin heat exchanger will no longer exist. However, in implementing this utility model, I found that, compared with each other, when the cross-sectional area of ​​the hot and cold fluid channels, the surface area of ​​the fins, and the number of hot and cold channels are all the same, solving some of the poor welding, missing welding, and the thermal resistance of the brazing filler metal itself is better than solving all of the aforementioned technical defects. The heat exchange performance will be even better (this will be explained in detail in the accompanying drawings). Regarding the hot and cold channels and fin arrangement, I believe that the smaller the heat exchange efficiency of plate-fin heat exchangers and microchannel heat exchangers, and the smaller the surface area difference of the fins on both sides of the baffle, the better the heat exchange effect. However, the fin processing size of plate-fin heat exchangers and the flat tube processing size of microchannel heat exchangers are limited by the equipment, making it impossible to achieve standard microchannels and standard fin arrangements. Through practical implementation, this utility model can easily achieve a center size of about 1mm for the two hot fluid channels. In addition, the fins of the hot and cold channels and the baffle are made of the same material, thereby greatly improving the heat exchange efficiency. Therefore, this application can better adapt to the heat exchange needs of special environments.

[0015] The microchannel plate-fin heat exchanger disclosed herein achieves simpler product manufacturing, more flexible product size, and higher heat exchange efficiency through optimized product structure and processing technology. It also demonstrates the outstanding substantive features and significant progress of a microchannel plate-fin heat exchanger, and the positive effects are obvious.

[0016] The above discloses one microchannel plate-fin heat exchanger structure described in this application. This application also discloses another microchannel plate-fin heat exchanger structure.

[0017] A microchannel plate-fin heat exchanger includes a pressure-bearing block, a sealing gasket, and heat exchange units. At least two heat exchange units are overlapped to form a heat exchange fluid channel between adjacent heat exchange cores. A sealing gasket is disposed between adjacent heat exchange units. Pressure-bearing blocks are disposed at both ends of the overlapped heat exchange units. A partition is disposed on each heat exchange unit, and heat-conducting fins higher than the partition plane are disposed on at least one of the two planes of the partition.

[0018] In some designs, the pressure blocks are fastened together by pressure bolts, and the components can be separated by removing the pressure bolts to achieve detachability.

[0019] Furthermore, in this invention, during the process of splicing and overlapping heat exchanger units, adjacent heat exchanger units can be isolated by means of isolation to ensure sealing. This can be achieved through various schemes, and its structure is not limited to a single one. Here, we optimize and propose one feasible option: an independent partition is provided between two adjacent heat exchanger units, and a heat exchange fluid channel is formed between the independent partition and the heat exchanger unit, and a sealing gasket is provided between the independent partition and the heat exchanger unit.

[0020] Furthermore, in this invention, to facilitate the fixing of the heat exchanger, corresponding hanging structures can be provided for fixation. The adopted scheme is not limited to one specific method. Here, we optimize and propose one feasible option: continuous or intermittent support grooves are provided on any surface of the heat exchanger. When adopting the above scheme, the support grooves can be tapered grooves and fixedly set at the top of the heat exchange body to achieve the hanging setup. In other feasible solutions, various structures can also be used, which will not be elaborated here.

[0021] Furthermore, in some solutions, to better stack the heat exchange units to adjust the heat exchange capacity and maintain the tightness of the fit between adjacent heat exchange units, the mating surfaces can be optimized. One feasible option is proposed here: a gap adjustment block is provided between two adjacent heat exchange units or between a heat exchange unit and a pressure-bearing block. When adopting the above solution, the gap adjustment block can be constructed as a thin sheet.

[0022] Furthermore, the heat exchange baffle is used to conduct heat from the hot fluid outwards. To improve heat exchange efficiency, the structure of the heat exchange baffle can be optimized. One feasible option is proposed here: the upper plane of the heat exchange baffle is located inside the hot fluid channel, and the upper plane forms an array of several internal heat-conducting fins. When adopting the above scheme, the internal heat-conducting fins can be continuously or intermittently arranged, with the aim of guiding the hot fluid to flow within the hot fluid channel and improving heat exchange efficiency.

[0023] Furthermore, the extension direction of the internal heat-conducting fins is not uniquely limited. Here, we propose one feasible option: the internal heat-conducting fins are continuously arranged along the extension direction of the heat fluid channel, dividing the heat fluid channel into several fluid grooves. When adopting the above scheme, the internal heat-conducting fins are elongated strip structures, extending from one end of the heat fluid channel to the other.

[0024] Furthermore, when the heat exchange baffle is equipped with external heat-conducting fins, it can be configured in various ways. Here, we optimize and propose a feasible option: the lower plane of the heat exchange baffle is located within the cold fluid channel, and the lower plane forms an array of several external heat-conducting fins. When using the above scheme, the external heat-conducting fins can be continuously or intermittently arranged, with the aim of guiding gas through to achieve heat exchange, so that the heat conducted by the hot fluid to the heat exchange baffle is removed.

[0025] Furthermore, the specific structure of the external heat-conducting fins can take various forms and is not limited to one. Here, we optimize and propose one feasible option: the external heat-conducting fins are continuously arranged along the extension direction of the cold fluid channel, dividing the cold fluid channel into several fluid gaps. When adopting the above scheme, the fluid gaps formed by the external heat-conducting fins can better guide the airflow, thereby improving the heat exchange effect and helping the heat on the heat exchange baffle to be transferred away more quickly.

[0026] This invention discloses a microchannel plate-fin heat exchanger with the following advantages: All components of the microchannel plate-fin heat exchanger, including the pressure block, sealing gasket, independent partition, and heat exchange unit, can be disassembled. Disassembly allows for thorough cleaning and disinfection of every nook and cranny of the internal and external heat exchange fluid channels, ensuring cleanliness and stable heat exchange efficiency. In case of malfunction, any component of the plate-fin heat exchanger can be replaced, significantly reducing equipment replacement costs and achieving cost reduction and efficiency improvement. In corrosive environments, targeted anti-corrosion treatments, such as anodizing, nickel plating, and spraying, can be applied to the heat exchange fluid channels to expand the application range of the plate-fin heat exchanger. These advantages sufficiently demonstrate the outstanding substantive features and significant progress of this plate-fin heat exchanger, and its positive effects are evident. Attached Figure Description

[0027] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 is a schematic diagram of the single-channel combined series mode of the heat exchanger in Example 1 and a partial unfolded diagram.

[0029] Figure 2 is a schematic diagram of the heat exchanger in the dual-channel combination parallel mode and a partial unfolded diagram in Example 1.

[0030] Figure 3 is a schematic diagram of the unfolded part of the heat exchanger with the inner and outer heat-conducting fins facing each other in Example 2.

[0031] Figure 4 is a partial schematic diagram of the heat exchanger's inner and outer heat-conducting fins arranged in the same direction in Example 2.

[0032] In the above attached figures, the meanings of each label are as follows:

[0033] 1. Heat exchanger unit; 2. Baffle plate; 3. Fins; 301. Inner heat-conducting fins; 302. Outer heat-conducting fins; 4. Flat plate fins; 5. Side seal of hot fluid channel; 6. Side seal of cold fluid channel; 7. Fluid guide channel; 8. Cover plate; 9. Base plate; 10. Guide cover plate; 11. Manifold; 12. Diverter box; 13. Hot fluid inlet; 14. Hot fluid outlet; 15. Cold fluid inlet; 16. Cold fluid outlet; 17. Hot fluid channel; 18. Cold fluid channel; 19. Independent baffle plate; 20. Heat exchanger unit docking point; 21. Pressure-bearing block; 22. Sealing gasket; 23. Pressure-bearing bolt; 24. Gap adjustment block; 25. Support slide groove; 26. Heat exchanger baffle plate; 27. Sealing surface. Embodiments of the present invention

[0034] The following description, in conjunction with the accompanying drawings and specific embodiments, further illustrates this embodiment.

[0035] In view of the shortcomings of existing heat exchangers, such as poor heat exchange effect, limited heat exchange pressure, easy leakage, and limited application scenarios, the following embodiments are optimized and overcome the defects of existing technologies.

[0036] Example 1

[0037] This embodiment provides a microchannel plate-fin heat exchanger.

[0038] Figure 1 shows a single-channel combined series configuration and partial unfolded view of a microchannel plate-fin heat exchanger. As shown in Figure 1, the heat exchange unit 1 is a single-sided finned heat sink that has been cut and slotted through secondary processing to form a baffle 2, fins 3, hot fluid channel 17, hot fluid channel side seal 5, and fluid guide channel 7. The baffle 2, the fins 3 of the hot and cold channels, the hot fluid channel side seal 5, and the cold fluid channel side seal 6 on the heat exchange unit 1 are all made of the same material. The fins 3 of the hot and cold channels are perpendicular to the baffle 2. Fluid guide channels 7 are provided on the side seal 6 of the cold fluid channel and on the independent baffle 19 of the heat exchange unit 1. Several heat exchange units 1 and independent baffles 19 are stacked in sequence, with the openings of the hot and cold channels of the heat exchange unit 1 and the adjacent heat exchange unit 1 facing the same direction, until the design requirements are met. Finally, a cover plate 8, a bottom plate 9, and two guide cover plates 10 on both sides are added and brazed to form a complete microchannel plate-fin heat exchanger.

[0039] Specifically, the openings of the cold fluid channels and hot fluid channels of the heat exchange unit and the adjacent heat exchange unit are oriented in the same direction, and an independent partition is provided between the two heat exchange units.

[0040] Example 2

[0041] This embodiment provides a microchannel plate-fin heat exchanger.

[0042] Figure 2 is a schematic diagram of a dual-channel parallel configuration and partial unfolding of a microchannel plate-fin heat exchanger. As shown in Figure 2, the heat exchange unit 1 in the figure is the same as the heat exchange unit 1 in Figure 1, and will not be described again here. Several heat exchange units 1 and flat plate fins 4 are stacked sequentially, with the openings of the hot and cold channels of heat exchange unit 1 and adjacent heat exchange units 1 facing opposite directions, until the design requirements are met. Finally, a cover plate 8, a bottom plate 9, a manifold box 11, and a distribution box 12 are added, and a complete microchannel plate-fin heat exchanger is formed by brazing. If the pressure, the height of the hot and cold channel fins 3, and other operating conditions allow, the flat plate fins 4 can be eliminated. The contact points of the hot fluid channel side seals 5 and the cold fluid channel side seals 6 of the upper and lower heat exchange units 1 can be directly laser welded or argon arc welded, which can reduce the investment in brazing equipment and space, adapt to customers with smaller order volumes, and greatly increase the flexibility and mobility of product production. When the size in the x-axis direction is greater than the limitation of the one-piece molding equipment, the product size limitation in the x-axis direction can be increased by the butt joint method of heat exchange units 1, forming the heat exchange unit butt joint point 20, which is also suitable for the implementation scheme in Figure 1. Preferably, a mating interface is formed at the docking point of the heat exchange units, allowing the heat fluid channels of the two docked heat exchange units 1 to connect and form a longer channel, thereby forming a series structure. Lengthening the heat fluid channel improves the heat exchange effect. This allows for adaptation to more application scenarios and meets various heat exchange requirements.

[0043] Specifically, the openings of the cold fluid channel and hot fluid channel of the heat exchange unit and the adjacent heat exchange unit face opposite directions, and a flat plate fin is provided between the two heat exchange units.

[0044] Alternatively, the openings of the cold fluid channels and hot fluid channels of the heat exchange unit and the adjacent heat exchange unit are oriented in opposite directions, the hot fluid channels between the two heat exchange units are connected and joined together, and the cold fluid channels between the two heat exchange units are connected and joined together.

[0045] The heat exchange principle is shown in Figure 1. The hot fluid enters the hot fluid channel 17 directly through the hot fluid inlet 13 and flows through the hot fluid channel 17 of the first heat exchange unit 1. After reaching the end of the heat exchange unit 1, it enters the fluid guide channel 7 and then enters the second heat exchange unit 1. This cycle continues until the hot fluid exits from the hot fluid outlet 14. The hot fluid is in close contact with the fins 3 of the hot fluid channel 17. The fins 3 transfer most of the heat to the baffle 2. Because the fins 3 and the baffle 2 are made of the same material, there is no thermal resistance from poor soldering, missing soldering, or the solder itself. Therefore, the fins 3 transfer most of the heat to the baffle 2, which then transfers the heat to the cold fluid channel 18. On the fins 3 of the hot fluid channel 17, heat is finally released to the cold fluid by the fins 3 of the cold fluid channel 18. Only a small portion of the heat is transferred to the independent partition 19 through the fins 3 of the hot fluid channel 17. This is because there are thermal resistances such as poor soldering, missing soldering, and the thermal resistance of the solder itself at the contact points between the independent partition 19 and the fins 3 on both sides. Finally, a small portion of the heat is transferred to the fins 3 of the cold fluid channel 18 by the independent partition 19. The fins 3 of the cold fluid channel 18 release a small portion of the heat to the cold fluid. The cold fluid enters the cold fluid channel 18 through the cold fluid inlet 15, carrying away the heat released by the fins 3 of the cold fluid channel 18 and discharging it from the cold fluid outlet 15, thus realizing the heat exchange process.

[0046] The heat exchange principle is shown in Figure 2, which differs from Figure 1. The flow channel pattern can be either series or parallel. In Figure 2, the independent baffle 19 is replaced with flat plate fins 4. The flat plate fins 4 have a three-stage heat transfer function and increase the overall strength of the heat exchanger. The hot fluid enters the distribution box 12 through the hot fluid inlet 13. After entering the distribution box 12, the hot fluid enters several hot fluid channels 17, making close contact with the fins 3 of the hot fluid channels 17 and absorbing heat from the hot fluid. This heat is then transferred to the baffle 2, and the baffle 2 then transfers the heat to the cold fluid channel 1. The fins 3 of the cold fluid channel 18 release heat to the cold fluid. The hot fluid enters the manifold 11 after passing through several hot fluid channels 17. Finally, the hot fluid is discharged from the hot fluid outlet 14. The cold fluid enters the cold fluid channel 18 through the cold fluid inlet 15, carrying away the heat released by the fins 3 of the cold fluid channel 18, and is discharged from the cold fluid outlet 16, thus realizing the heat exchange process. Of course, the flat plate fins 4 of the hot and cold fluid channels will also absorb or release some heat. The heat exchange principle is obvious and does not need to be described in detail here.

[0047] It is easy to see from the heat exchange performance of the combination of Figures 1 and 2 that Figure 1 only solves some of the thermal resistance issues such as poor welding, missing welding, and brazing itself at the connection between the baffle 2 and the fin 3. The aforementioned technical defects will no longer exist when the combination of Figure 2 is used. Logically speaking, solving all of the aforementioned technical defects is better than solving some of them. However, the superior heat exchange performance of the combination mode of this application is the opposite. We can assume that the cross-sectional area of ​​the hot and cold channels, the thickness of the fin 3, the length, width, and height of the heat exchange unit 1, and the number of hot and cold channels are the same in Figures 1 and 2. No matter how small the cross-sectional area of ​​the hot and cold channels in Figure 2 becomes, the combination mode of Figure 1 will have an additional heat transfer path of the independent baffle 19. Therefore, from the perspective of heat exchange performance, the combination mode of Figure 1 is far superior to the combination mode of Figure 2, while the combination mode of Figure 2 is more flexible than that of Figure 1.

[0048] The fins in Figures 1 and 2 can be further processed, such as openings or holes in the fins 3 of the hot and cold channels, or bending them with the fin peaks of the fins 3 of the hot and cold channels as the point of force to create a certain turbulence function.

[0049] Example 3

[0050] The above embodiments 1 and 2 provide a microchannel plate-fin radiator scheme and disclose the specific structure. This embodiment provides another structure of a microchannel plate-fin radiator.

[0051] As shown in Figure 3, the heat exchange unit 1 is formed by machining, welding and other processes, including inner heat-conducting fins 301, outer heat-conducting fins 302, hot fluid channel 17, cold fluid channel 18 and heat exchange baffle 26. The heat exchange baffle 26 is located between the inner heat-conducting fins 301 and the outer heat-conducting fins 302. The function of the heat exchange baffle 26 is to transfer heat from one side to the other and to separate the hot and cold fluids.

[0052] In this embodiment, the inner heat-conducting fins 301 and 302 are plate-shaped heat-conducting fins. Columnar heat-conducting fins, perforated heat-conducting fins, etc., are also consistent with this embodiment. The function of the inner heat-conducting fins 301 is to transfer most of the heat from the hot fluid in the heat-absorbing fluid channel 17 to the heat exchange baffle 26. A small portion of the heat is directly absorbed by the heat exchange baffle 26, which then transfers the heat to the outer heat-conducting fins 302. The outer heat-conducting fins 302 release most of the heat to the cold fluid, while a small portion is directly released by the heat exchange baffle 26 to the cold fluid. In some less demanding applications, such as intercoolers, the inner heat-conducting fins 301 can be omitted, and the heat fluid channel 17 can be formed by the thickness of the sealing gasket 22 or by adding other fillers. When the heat fluid passes through, the heat exchange baffle 26 directly absorbs the heat and transfers it to the outer heat-conducting fins 302, which then release the heat to the cold fluid. Of course, the hot and cold fluid channels can be interchanged in actual implementation, and the heat exchange process is reversed.

[0053] Several heat exchanger units 1 are overlapped, and corresponding sealing gaskets 22 are placed between the heat exchanger units 1. After the number of layers reaches the required setting, pressure blocks 21 are placed at the two ends of the overlapped heat exchanger units 1, and pressure bolts 23 are inserted to the opposite pressure blocks 21. Bolt fixing points are set on the pressure blocks 21 at both ends of the overlapped heat exchanger units 1, and the pressure bolts 23 are tightened so that the sealing surface 27 on the heat exchanger unit 1 is in close contact with the sealing gasket 22. The function of the sealing gasket 22 is to fill the micro gaps between the sealing surfaces, establish a stable sealing contact, and prevent the heat exchange fluid from leaking between the two sealing surfaces 27, so as to achieve the purpose of sealing and bearing pressure. In this way, the plate fin heat exchanger is formed as a whole. In the actual operation of the plate fin heat exchanger, the pressure of the hot fluid channel 17 and the rebound force of the sealing gasket 22 directly act on the pressure bolts 23 and the pressure blocks 21. Hot fluid enters each hot fluid channel 17 through hot fluid inlet 13 and then flows out from hot fluid outlet 14. Cold fluid enters cold fluid channel 12 through the corresponding inlet, and after heat exchange, flows out from the corresponding outlet.

[0054] Finally, install the bracket slide 25. The bracket slide 25 can be installed on any surface of the microchannel plate-fin heat exchanger. The bracket slide 25 can be continuous or intermittent. When installing a clamp plate-fin heat exchanger at the user end, the bracket fixing parts can slide freely in the slide. With the addition of angle steel and slotted holes on two sides, a three-dimensional bracket that can be freely adjusted along the y-axis, x-axis, and z-axis is formed. This solves the problem of damage to the fixing end or the fixed end when the bracket bolt holes do not align during the installation of the heat exchanger at the user end.

[0055] In this embodiment of the invention, the threaded rod of the pressure-bearing bolt 23 is hidden inside the heat exchange unit 1. To reduce material usage, the threaded rod of the pressure-bearing bolt 23 can be exposed, but from an aesthetic point of view, it is not as aesthetically pleasing as the concealed arrangement in this embodiment. If the inlet and outlet of the hot and cold fluids are large enough, the pressure-bearing bolt 23 can be completely hidden within the inlet and outlet of the hot and cold fluids. The positions of the inlet and outlet of the hot and cold fluids can be adjusted arbitrarily at the front and rear of the end of the heat exchange unit 1 or on the pressure block 21.

[0056] As shown in Figure 3, the inner and outer heat-conducting fins of two adjacent heat exchanger units 1 are arranged to overlap in opposite directions. As shown in Figure 4, the inner and outer heat-conducting fins of two adjacent heat exchanger units 1 are arranged to overlap in the same direction. It is only necessary to add an independent partition 19 and a corresponding sealing gasket 22 between adjacent heat exchanger units 1. The heat exchange fluid flow, heat exchange process, specific implementation method and the positive effects produced are basically the same as those in Figure 3. The functions of the independent partition 19 and the heat exchange partition 26 are basically the same, except that the independent partition 19 does not have inner and outer heat-conducting fins on its two surfaces.

[0057] In Figures 3 and 4, gap adjustment blocks 24 are provided between two adjacent heat exchanger units 1 or between heat exchanger unit 1 and pressure block 21. The function of gap adjustment blocks 24 is to adjust the sealing gap and stabilize the external heat conduction fins 302 on both sides. If the required requirements can be met, gap adjustment blocks 24 can be omitted.

[0058] The above are the embodiments listed in this example; however, this example is not limited to the optional embodiments described above; those skilled in the art can arbitrarily combine the above methods to obtain other various embodiments; anyone can derive other various forms of embodiments under the guidance of this example. The above specific embodiments should not be construed as limiting the scope of protection of this example; the scope of protection of this example should be determined by the claims.

Claims

1. A microchannel plate-fin heat exchanger, comprising a heat exchange unit (1), characterized in that: The heat exchange unit (1) is a single-sided heat sink or plate that is integrally formed and then cut and slotted. The heat exchange unit (1) is composed of a partition (2), a hot fluid channel (17) fin (3), and a cold fluid channel (18) fin (3) made of the same material. The feet of the hot fluid channel (17) fin (3) or the feet of the cold fluid channel (18) fin (3) are parallel to each other. The hot fluid channel (17) fin (3) or the cold fluid channel (18) fin (3) is perpendicular or inclined to both sides of the partition (2). The feet of the hot fluid channel (17) fin (3) and the feet of the cold fluid channel (18) fin (3) are intersected. The minimum angle formed by the intersection is between 30° and 90°.

2. The microchannel plate-fin heat exchanger according to claim 1, characterized in that: The openings of the hot and cold channels of the heat exchange unit (1) and the adjacent heat exchange unit (1) are aligned, and an independent partition (19) is provided between the two heat exchange units (1).

3. The microchannel plate-fin heat exchanger according to claim 1, characterized in that: The openings of the hot and cold channels of the heat exchange unit (1) and the adjacent heat exchange unit (1) are opposite in orientation, and a flat plate fin (4) is provided between the two heat exchange units (1).

4. The microchannel plate-fin heat exchanger according to claim 1, characterized in that: The openings of the hot and cold channels of the heat exchange unit (1) and the adjacent heat exchange unit (1) are opposite in orientation, and no flat plate fins (4) are provided between the two heat exchange units (1).

5. The microchannel plate-fin heat exchanger according to claim 1, characterized in that: The heat exchange unit (1) has a heat exchange unit docking point (20) in the X-axis direction.

6. The microchannel plate-fin heat exchanger according to claim 1, characterized in that: The partition (2), the hot fluid channel (17) fin (3), the cold fluid channel (18) fin (3), the hot fluid channel side seal (5), and the cold fluid channel side seal (6) are all made of the same material.

7. The microchannel plate fin heat exchanger of claim 6, wherein: Fluid guiding channels (7) are provided on the hot fluid channel side seal (5) or cold fluid channel side seal (6) and the independent partition (19).

8. A microchannel plate-fin heat exchanger, comprising a pressure block (21), a sealing gasket (22), and a heat exchange unit (1), characterized in that: At least two heat exchange units (1) are overlapped to form a heat exchange fluid channel (17) between two adjacent heat exchange cores. A sealing gasket (22) is provided between two adjacent heat exchange units (1). A pressure block (21) is provided at both ends after the at least two heat exchange units (1) are overlapped. A partition (2) is provided on the heat exchange unit (1). A heat-conducting fin higher than the plane of the partition (2) is provided on at least one of the two planes of the partition (2).

9. The microchannel plate-fin heat exchanger according to claim 8, characterized in that: An independent partition (19) is provided between two adjacent heat exchange units (1), and a heat exchange fluid channel (17) is formed between the independent partition (19) and the heat exchange unit (1), and a sealing gasket (22) is provided between the independent partition (19) and the heat exchange unit (1).

10. The microchannel plate-fin heat exchanger according to claim 8 or 9, characterized in that: The heat exchanger has continuous or intermittent support grooves (25) on any surface.

11. The microchannel plate-fin heat exchanger according to claim 8 or 9, characterized in that: A gap adjustment block (24) is provided between two adjacent heat exchange units (1) or between a heat exchange unit (1) and a pressure block (21).

12. The microchannel plate-fin heat exchanger according to claim 8 or 9, characterized in that: The pressure blocks (21) are fastened together by pressure bolts (23). The components can be separated by removing the pressure bolts (23) to achieve detachability.

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