Three-dimensional countercurrent flow channel functional heat exchange module and heat exchanger

Abstract

This invention belongs to the field of heat exchanger technology, specifically relating to a three-dimensional anisotropic flow channel functional heat exchange module and heat exchanger. The heat exchange medium flow channel of this invention has a sequentially stacked structure of a first main flow channel, a first auxiliary flow channel, a second auxiliary flow channel, and a second main flow channel. The first main flow channel and the first auxiliary flow channel are interconnected to form an upper heat source cavity, and the second main flow channel and the second auxiliary flow channel are interconnected to form a lower heat source cavity. In the same heat source cavity, the flow area of ​​the main flow channel is larger than that of the auxiliary flow channel, and the main flow channel and the auxiliary flow channel intersect each other, so that the intersection points form interconnected connection points. Along the stacking direction of the flow channels, the second auxiliary flow channel is adjacent to the first main flow channel, and the second main flow channel is adjacent to the first auxiliary flow channel. There is a connecting port between the upper heat source cavity and the lower heat source cavity. This invention ensures the self-cleaning function of the icing area through the combined action of "mixed ice melting" and "heat exchange ice melting".

Description

Technical Field

[0001] This invention belongs to the field of heat exchanger technology, specifically relating to a three-dimensional anisotropic flow channel functional heat exchange module and heat exchanger. Background Technology

[0002] LNG-powered ships utilize a fuel gas supply system (FGSS) to pressurize LNG via pumps, vaporize it in a high-pressure vaporizer, and then transport it to the power system as fuel. The high-pressure vaporizer is a key component of the FGSS system. Because the vaporizer operates in harsh environments with high pressure (above 30 MPa) and low temperature (-162°C), traditional shell-and-tube heat exchangers are large and heavy, and are prone to thermal stress damage due to the 200°C temperature difference between the hot and cold fluids, limiting their application in LNG ships. Conventional brazed plate, plate-fin, and frame plate heat exchangers cannot be used under high pressure; currently, diffusion-welded heat exchangers are more commonly used.

[0003] Currently, for the application of high-pressure liquefied natural gas (LNG) vaporization sections in FGSS systems for dual-fuel powered ships, diffusion-welded microchannel heat exchangers still face two challenges: Firstly, the temperature of LNG, the working medium, is extremely low, around -162°C, while the freezing point of heat exchange media such as ethylene glycol aqueous solutions is typically around -40°C. Since the temperature of cryogenic LNG is far lower than the freezing point of ethylene glycol aqueous solutions, the ethylene glycol aqueous solution side is prone to icing in many vaporizers. Once the heat exchange channels on the ethylene glycol aqueous solution side partially freeze, it gradually blocks heat exchange and flow, accelerating the icing rate until the ethylene glycol aqueous solution channels within the vaporizer are completely frozen, causing vaporization failure and affecting the normal operation of the system. Simply increasing the channel diameter to avoid icing is limited by chemical etching, machining processes, and manufacturing economics, and the current etching depth is difficult to exceed 2mm, resulting in very limited practical effectiveness. On the other hand, after prolonged use, the inner walls of the microchannels containing the heat exchange medium accumulate a large amount of impurities, dirt, and oil, which can clog the channels. Furthermore, due to the interconnected nature of the channels in the diffusion-welded microchannel heat exchanger, this can lead to deterioration of heat exchange or even complete failure to exchange heat, causing system shutdown. Therefore, this issue urgently needs to be addressed. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings of the prior art and provide a three-dimensional anisotropic flow channel functional heat exchange module. As an internal heat exchange component of the heat exchanger, it can utilize the temperature difference effect generated by the distance difference between the main channels and auxiliary channels at the working medium flow channel and the heat exchange medium flow channel, as well as the heat exchange and fusion heat exchange effects between the main channels and auxiliary channels and even different layers of heat source cavities. Through the combined action of "mixed ice melting" and "heat exchange ice melting", it ensures the suppression of ice growth rate and the continuous ice melting function at the ice-covered points of the main channels and even auxiliary channels. Under the premise of not affecting the normal operation of the vaporizer, it can ensure the self-cleaning function of the ice-covered points.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] A three-dimensional anisotropic flow channel functional heat exchange module includes a heat exchange plate and flow channels within the heat exchange plate for the passage of working medium and heat exchange medium. The flow channels include a first working medium flow channel constituting a first cold source, a heat exchange medium flow channel constituting a heat source, and a second working medium flow channel constituting a second cold source. The heat exchange medium flow channels are arranged in a sequentially stacked structure of a first main flow channel, a first auxiliary flow channel, a second auxiliary flow channel, and a second main flow channel. The first main flow channel and the first auxiliary flow channel are interconnected to form an upper heat source cavity, and the second main flow channel and the second auxiliary flow channel are interconnected to form a lower heat source cavity. In the same heat source cavity, the flow area of ​​the main flow channel is larger than that of the auxiliary flow channel, and the main flow channel and the auxiliary flow channel intersect each other, such that the intersection point forms a connecting point. Along the stacking direction of the flow channels, the second auxiliary flow channel is adjacent to the first main flow channel, and the second main flow channel and the first auxiliary flow channel are adjacent to each other, and there is a connecting port between the upper heat source cavity and the lower heat source cavity.

[0007] Preferably, in a top-view projection, the second auxiliary channel is located within the projection range of the first main channel, and the second main channel is located within the projection range of the first auxiliary channel.

[0008] Preferably, the bottom end of the first auxiliary flow channel and the top end of the second auxiliary flow channel intersect each other along the stacking direction of the flow channels, and the intersection forms the confluence port.

[0009] Preferably, the upper heat source cavity and the lower heat source cavity are formed by three heat exchange plates; a grooved first main flow channel is provided on the lower surface of the first heat exchange plate, a grooved first auxiliary flow channel is provided on the upper surface of the second heat exchange plate, a grooved second auxiliary flow channel is provided on the lower surface of the second heat exchange plate, and a grooved second main flow channel is provided on the upper surface of the third heat exchange plate; the corresponding main flow channel and auxiliary flow channel are slotted together at the connection point to form the corresponding heat source cavity; an upper heat exchange plate with a first working medium flow channel is arranged above the first heat exchange plate, and a lower heat exchange plate with a second working medium flow channel is arranged below the third heat exchange plate.

[0010] Preferably, the upper heat source cavity and the lower heat source cavity are formed by three heat exchange plates. The lower surface of the first heat exchange plate is etched with a grooved first main flow channel, the upper surface of the second heat exchange plate is etched with a grooved first auxiliary flow channel, the lower surface of the second heat exchange plate is etched with a grooved second auxiliary flow channel, and the upper surface of the third heat exchange plate is etched with a grooved second main flow channel. The corresponding main flow channel and auxiliary flow channel are slotted together at the connection point to form the corresponding heat source cavity. A side heat exchange plate that has both a low-pressure LNG flow channel and a high-pressure LNG flow channel is also arranged above or below the first heat exchange plate.

[0011] Preferably, each auxiliary flow channel is formed by combining two or more independent flow channels side by side; each independent flow channel is independently connected to the corresponding main flow channel of the same heat source cavity at the connection point.

[0012] Preferably, each main channel and each auxiliary channel has a V-shaped, W-shaped, or wavy shape. In the same heat source cavity, the openings of the main channels and auxiliary channels that cooperate with each other are opposite to each other, so that the openings of the main channels and auxiliary channels are matched to form a closed loop structure, and the connection point is set at the matching point of the closed loop structure. The turning point of the V-shaped or W-shaped main channels and auxiliary channels, or the peak or trough of the wavy main channels and auxiliary channels, are the inflection points of each channel. The main channels and auxiliary channels that cooperate with each other in the same heat source cavity form a row of channel units. The adjacent inflection points of the current row of channel units are connected to the next row of channel units in the same heat source cavity.

[0013] Preferably, the angle formed between each main flow channel and auxiliary flow channel and the length direction of each heat exchange plate is in the range of (0°, 15°).

[0014] Preferably, an upper arc groove is etched on the surface of the upper heat exchange plate, and the upper arc groove cavity cooperates with the adjacent heat exchange plate to form a first working medium flow channel; a lower arc groove is etched on the lower heat exchange plate, and the lower arc groove cavity cooperates with the adjacent heat exchange plate to form a second working medium flow channel; the groove openings of the upper arc groove and the lower arc groove face each other or are away from each other.

[0015] Preferably, the heat exchanger uses the aforementioned three-dimensional countercurrent flow channel functional heat exchange module, characterized in that: it includes a tube box and a core located inside the tube box, the core being formed by two or more sets of three-dimensional countercurrent flow channel functional heat exchange modules stacked sequentially along the flow channel stacking direction.

[0016] Preferably, the lower heat exchange plate of the current three-dimensional countercurrent flow channel functional heat exchange module and the upper heat exchange plate of the next three-dimensional countercurrent flow channel functional heat exchange module share the same plate body.

[0017] The beneficial effects of this invention are as follows:

[0018] 1) Through the above scheme, the present invention relies on the special design concept of "main and auxiliary flow separation and temperature difference de-icing". It relies on the main flow channel close to the cold source and the auxiliary flow channel relatively far away from the cold source to cooperate with each other. When in use, the dual cold source naturally makes each main flow channel form a specific stacked state of the first main flow channel, the first auxiliary flow channel, the second auxiliary flow channel and the second main flow channel.

[0019] Taking ethylene glycol aqueous solution and cryogenic LNG as examples: Due to the difference in flow area between the main flow channel and the auxiliary flow channel, during normal operation, the ethylene glycol aqueous solution mainly flows along the main flow channel, facilitating heat exchange with the cryogenic LNG in the adjacent working medium flow channel. When severe icing occurs, it mostly happens in the main flow channel; because the auxiliary flow channel is relatively farther from the working medium flow channel and has a relatively higher temperature, it is less prone to icing. At this time, as ice blocks the flow, the flow rate in the main flow channel decreases, and the flow rate in the auxiliary flow channel gradually exceeds that of the main flow channel. At this point, more ethylene glycol aqueous solution begins to enter the relatively unobstructed auxiliary flow channel. When the flow rate in the auxiliary flow channel is greater than that in the main flow channel, the auxiliary flow channel actually surpasses the main flow channel, thus forming a substitute flow channel for the main flow channel, achieving the purpose of continuous flow and heat exchange of the ethylene glycol aqueous solution.

[0020] When the auxiliary flow channel operates as a substitute flow channel, a portion of the ethylene glycol aqueous solution still flows into the main flow channel, continuously flushing the ice-covered areas and achieving a "mixing and melting" effect. Meanwhile, the remaining ethylene glycol aqueous solution entering the auxiliary flow channel, due to its proximity to the corresponding main flow channel, achieves indirect heat exchange with the main flow channel, thus serving a "heat exchange and melting" function. Throughout this process, the equipment can still operate without shutting down.

[0021] Furthermore, a connection point exists between the upper and lower heat source cavities. This connection can be a separate connecting channel or formed by the upper and lower heat source cavities being close together to create a junction. The arrangement of this connection point allows for both contact and indirect heat exchange of the heat transfer medium, i.e., the ethylene glycol aqueous solution, between the upper and lower heat source cavities, and even between the two channels within the same heat source cavity. This further maintains the flowability of the ethylene glycol aqueous solution at the freezing point, enhances the effect of inhibiting the ice growth rate, and thus ensures the adaptability of the flow rate and temperature range control of the ethylene glycol aqueous solution.

[0022] In summary, when localized icing occurs, this invention utilizes the ethylene glycol aqueous solution as the heat exchange medium. Through cross-flow contact heat exchange and indirect heat exchange at the front and rear sides of the specific icing location, and cleverly leverages the "heat difference" generated by the different distances between the main flow channel and the auxiliary flow channel and the cold source, it effectively enhances the "ice-melting effect" and fully ensures the permeability of the ethylene glycol aqueous solution. The combined effect of "mixed ice melting" and "heat exchange ice melting" enables continuous ice melting at the icing points in the main flow channel and even the auxiliary flow channel; and ensures the self-cleaning function of the icing points without affecting the normal operation of the vaporizer.

[0023] 2) To maximize the "heat exchange and ice melting" effect, the optimized scheme of this invention can be used, namely, the second auxiliary flow channel is located within the projection range of the first main flow channel, and the second main flow channel is located within the projection range of the first auxiliary flow channel. At this time, the second auxiliary flow channel is closest to the first main flow channel while being relatively farthest from the cold source, thereby achieving a rapid heat exchange and ice melting effect on the first main flow channel; the same principle applies to the second main flow channel and the first auxiliary flow channel.

[0024] 3) As a further preferred embodiment of the present invention, the confluence port of the present invention is formed by two auxiliary channels approaching each other and converging at the connection point. At this time, when the first auxiliary channel and the second auxiliary channel approach each other and converge, a variable thickness rotary shear surface similar to an "S" shape is formed at the intersection line of the two, so that the ethylene glycol aqueous solution at this point can be further rotary sheared when flowing, further enhancing the contact mixing heat exchange effect; at the same time, the ethylene glycol aqueous solution can rely on its own convergence, mixing and diversion to further enhance the flowability and ensure anti-icing blockage and fouling blockage performance.

[0025] 4) The above-described flow channel structure, combined with multiple rows of flow channel units, offers the following advantages: Firstly, the main and auxiliary flow channels within the same row of flow channel units can always redistribute flow at inflection points, ensuring the permeability of the ethylene glycol aqueous solution. Secondly, flow can be redistributed between adjacent rows of flow channel units. The ethylene glycol aqueous solution can also further enhance its permeability and ensure resistance to icing and fouling blockages through its own convergence, mixing, and diversion.

[0026] 5) The auxiliary flow channel employs a multi-channel parallel arrangement or a single channel with baffles. Another reason is to reduce the overall depth of the auxiliary flow channel, facilitating etching. Furthermore, the main flow channel and auxiliary flow channel are respectively opened at the two heat exchange plates, and then they are joined together to form corresponding heat source chambers. This not only increases the flow area of ​​the heat source chamber for ethylene glycol aqueous solution, a medium prone to freezing or fouling, but also allows the heat source chamber to exceed the 2mm etching depth limitation of conventional diffusion plate heat exchangers. Combined with a three-dimensional network formed by interconnected single or even multiple heat source chambers, the ethylene glycol aqueous solution can achieve continuous and intermittent combined flow patterns within a three-dimensional continuous and variable space, ensuring uniform heat exchange efficiency in each channel and further reducing the risk of freezing.

[0027] 6) The range of the angles formed between each main and auxiliary flow channel and the length direction of each heat exchange plate is limited. However, overall, along the length direction of the heat exchange plate, when the main and auxiliary flow channels of the same row of flow channel units extend outward from the base point, they are still far apart from each other in the direction of extension. They then approach each other at the farthest point and finally converge at a certain inflection point, repeating this process. This design, combined with the confluence port, facilitates the formation of a three-dimensional network and makes processing easier. Attached Figure Description

[0028] Figure 1 and Figure 2 This is a cross-sectional view of the connection point of two installation methods in one embodiment of the heat exchanger.

[0029] Figure 3 This is a flow channel arrangement diagram of the functional heat exchange module of the present invention;

[0030] Figure 4 for Figure 3 The front view;

[0031] Figure 5 for Figure 3 Top view of the structure shown;

[0032] Figure 6 This is a schematic diagram of another embodiment of the heat exchanger.

[0033] The actual correspondence between the reference numerals and component names in this invention is as follows:

[0034] 10a - First working medium flow channel; 10b - Heat exchange medium flow channel; 10c - Second working medium flow channel;

[0035] 11a - First main flow channel; 11b - First auxiliary flow channel; 12a - Second auxiliary flow channel; 12b - Second main flow channel;

[0036] 13-Connecting port; 14-Upper heat exchange plate; 15-First heat exchange plate; 16-Second heat exchange plate;

[0037] 17-Third heat exchange plate; 18-Lower heat exchange plate. Detailed Implementation

[0038] For ease of understanding, this section combines... Figures 1-6 The specific structure and operation of the present invention are further described below:

[0039] To facilitate the explanation of the actual working process of the present invention, in the following description, the working medium is cryogenic LNG and the heat exchange medium is ethylene glycol aqueous solution; of course, in actual operation, the working medium and the heat exchange medium can be selected according to the site conditions.

[0040] Therefore, the specific structure of the present invention is as follows. Figures 1-5 As shown; it includes a tube box and a core located within the tube box. The tube box includes an upper end plate and a lower end plate, and the core is located between the two end plates. The core includes one or more three-dimensional counter-current flow channel functional heat exchange modules. Each functional heat exchange module has a built-in first working medium flow channel 10a, a second working medium flow channel 10c, and a heat exchange medium flow channel 10b, as shown. Figure 1 As shown. The first working medium flow channel 10a and the second working medium flow channel 10c constitute a cold source, while the heat exchange medium flow channel 10b constitutes a heat source, as shown. Figure 1 As shown.

[0041] The low-pressure LNG flow channel 10a and the high-pressure LNG flow channel 10c can be referenced. Figure 6 The heat exchanger type shown allows both cold sources to be arranged on the same side of the heat source. In this case, a side heat exchange plate with both low-pressure LNG and high-pressure LNG flow channels can be arranged above or below the first heat exchange plate. Alternatively, it can be arranged as follows... Figure 1 and Figure 2 The arrangement shown is on both sides of the heat source to achieve heat exchange.

[0042] For ease of description, here we will assume that the low-pressure LNG flow channel 10a and the high-pressure LNG flow channel 10c are located on both sides of the heat source, that is, as shown below. Figure 1 and Figure 2 The implementation methods shown are described below:

[0043] Furthermore, the three-dimensional anisotropic flow channel functional heat exchange module is composed of multiple plates of different functional types stacked in a specific order, including at least an upper heat exchange plate 14, a first heat exchange plate 15, a second heat exchange plate 16, a third heat exchange plate 17, and a lower heat exchange plate 18. In actual arrangement, the heat exchange plates are stacked on top of each other, thereby forming channel-shaped flow channel cavities from the corresponding etched groove-shaped flow channels. The combination method between the functional heat exchange modules... Figure 1 and Figure 2The structure shown is a reference example; in actual operation, it can be set as appropriate according to the situation.

[0044] The upper heat exchange plate 14 and the lower heat exchange plate 18 can be arranged as a straight channel, a corrugated structure, or a sawtooth structure along the flow direction. A straight channel results in relatively low flow resistance, while a corrugated or sawtooth structure provides better heat exchange.

[0045] The main flow channel and auxiliary flow channel formed by the cooperation of the first heat exchange plate 15, the second heat exchange plate 16 and the third heat exchange plate 17, Figure 1 and Figure 2 This is also shown in the diagram. In actual design, the bottom dimension of each main channel, i.e., a single large trench, is the sum of the top dimensions of each auxiliary channel, i.e., multiple small trenches, and the dimensions of the solid connecting section in the middle. Furthermore, each trench is a wavy or sawtooth structure formed by bending along the length of the heat exchange plate; Figure 3 and Figure 6 As can be seen, on the same cross section, the flow directions of each main channel intersect, and the flow directions of each auxiliary channel also intersect. Adjacent main channels and auxiliary channels also form an intersecting structure. At the same time, by utilizing the confluence port 13, a three-dimensional grid-like flow channel structure is formed.

[0046] Specifically, when the main flow channel and the auxiliary flow channel combine to form the corresponding heat source cavity, such as Figures 3-5 As shown, the upper heat source cavity is formed by the combination of the first main flow channel 11a as a large trench and the first auxiliary flow channel 11b as parallel independent small trenches; the lower heat source cavity is formed by the second auxiliary flow channel 12a as parallel small independent trenches and the second main flow channel 12b as a large trench; and in the projection direction or the top view, the first auxiliary flow channel 11b is located directly above the second main flow channel 12b and arranged close to each other, while the first main flow channel 11a is located directly above the second auxiliary flow channel 12a and arranged close to each other, thus forming the above-mentioned cross structure.

[0047] Meanwhile, the lengths of each single-channel segment of the first main flow channel 11a at the bottom of the first heat exchange plate 15 and each single-channel segment of the first auxiliary flow channel 11b at the top of the second heat exchange plate 16 are all the same, and their deviations from the central axis are also exactly the same. This makes the upper heat source cavity formed after the overall trench assembly present as follows: Figure 5 The diagram shows a regularly distributed diamond-shaped mesh flow channel structure. The lower heat source cavity formed by the second heat exchange plate 16 and the third heat exchange plate 17 is similar.

[0048] Based on the above structure, such as Figure 3As shown, the etched grooves on the upper and lower surfaces of the second heat exchange plate 16 are brought closer together until the first auxiliary flow channel 11b and the second auxiliary flow channel 12a intersect in spatial height. This intersection, also known as the intersection line in the cavity, forms an "S"-shaped variable thickness rotary cut surface, i.e., the confluence port 13. When the ethylene glycol aqueous solution from the first heat exchange plate 15, the second heat exchange plate 16, and the third heat exchange plate 17 undergoes indirect heat exchange within their respective tortuous lengths, the ethylene glycol aqueous solution will be further rotary-cut at the "S"-shaped variable thickness rotary cut surface, further enhancing the contact-type mixing heat exchange effect.

[0049] For ease of understanding, the actual workflow of this invention is further described below:

[0050] In practical use, this invention can be divided into two situations based on the flow state of the heat exchange medium inside the core, i.e., the ethylene glycol aqueous solution, during use: a conventional heat exchange condition where the channels are not blocked by ice or dirt, and a heat exchange condition where the channels are partially blocked by ice or dirt. These are described below:

[0051] 1) Conventional heat exchange conditions where there is no ice buildup or dirt clogging the channels:

[0052] At this time, the grooves in the upper heat exchange plate 14 and the lower heat exchange plate 18, together with the corresponding first heat exchange plate 15 or third heat exchange plate 17, form two working medium flow channels of the cold source respectively; the first heat exchange plate 15, the second heat exchange plate 16 and the third heat exchange plate 17 are paired with each other to form the corresponding upper heat source cavity and lower heat source cavity, and the upper heat source cavity and the lower heat source cavity are connected to each other by the confluence port 13, and finally form the heat exchange medium flow channel 10b.

[0053] The upper and lower heat source cavities have a wave-shaped or sawtooth-shaped flow structure, allowing the main and auxiliary flow channels within the same heat source cavity to connect at the connection point and confluence port 13, ensuring that the ethylene glycol aqueous solution can flow freely within all flow channel units of both heat source cavities. At the core inlet, refer to... Figure 3As shown, the cross-sectional area of ​​the first main flow channel 11a accounts for more than 60% of the total cross-sectional area of ​​the upper heat source cavity. Thus, most of the ethylene glycol aqueous solution enters the first main flow channel 11a, forming the main flow channel; a small amount of ethylene glycol aqueous solution enters the first auxiliary flow channel 11b, forming an auxiliary flow channel. At this time, because the first main flow channel 11a is closer to the upper first cold source, it can fully perform indirect heat exchange, and the temperature of the ethylene glycol aqueous solution in the first main flow channel 11a is also lower. Correspondingly, the first auxiliary flow channel 11b is farther from the upper first cold source than the first main flow channel 11a, and performs insufficient indirect heat exchange; therefore, the temperature of the ethylene glycol aqueous solution in the first auxiliary flow channel 11b is relatively higher. The second main flow channel 12b and the second auxiliary flow channel 12a are similar. The ethylene glycol aqueous solution in each flow channel will converge and exchange heat at each connection point and confluence port 13, then redistribute the flow rate, and then repeat the convergence and heat exchange process until it finally flows out of the core.

[0054] 2) Conventional heat exchange conditions where channels are blocked by ice or dirt:

[0055] When severe icing occurs, the icing sites are mostly located in the main flow channels where the ethylene glycol aqueous solution has a relatively lower temperature, namely the first main flow channel 11a and the second main flow channel 12b. In this case, once the main flow channels are partially blocked, the ethylene glycol aqueous solution cannot easily pass through, and naturally begins to use the auxiliary flow channels as the main flow channels. At this time, some of the ethylene glycol aqueous solution will still flow into the main flow channels, continuously flushing the icing sites, achieving a "mixing and melting" effect; while the other part of the ethylene glycol aqueous solution entering the auxiliary flow channels, because it is close to the corresponding main flow channels and the liquid temperature in the auxiliary flow channels is relatively higher, achieves indirect heat exchange with the corresponding main flow channels, playing a "heat exchange and melting" role. The combined effect of "mixing and melting" and "heat exchange and melting" enables continuous melting of the icing sites in the main flow channels, ensuring the self-cleaning function of the icing sites without affecting the normal operation of the vaporizer.

[0056] Of course, when ice forms in one of the small channels in the auxiliary channel, the presence of other small channels and the connecting points at each inflection point allows the ice in that small channel to melt entirely through the impact of the liquid and heat exchange between the walls. This is one of the reasons why the auxiliary channel adopts a multi-channel parallel flow channel structure. Furthermore, the "S"-shaped variable-thickness rotary shear surface of this invention further enhances the rotary shearing phenomenon of the ethylene glycol aqueous solution and further strengthens the contact-type mixing heat exchange function, which will not be elaborated further here.

[0057] It is now understood that the design concept of this invention is to treat all heat exchange plates as a whole, increase the hydraulic diameter by etching grooves and then joining them together, and when local icing occurs, the heat exchange medium exchanges heat through cross-flow contact heat exchange and indirect heat exchange at the front and rear sides of the specific icing position, and cleverly utilizes the "heat difference" generated by the different distances between the main flow channel and the auxiliary flow channel and the cold source, which effectively enhances the "ice melting effect" and fully ensures the flowability of the heat exchange medium.

[0058] Of course, if the flow channel is blocked by internal fouling generated during the heat exchange process or reaction process, the above design of the present invention can also prevent the flow channel from being completely blocked and unable to flow. That is, due to the existence of the three-dimensional flow system of the present invention, the blockage point only exists in a small area of ​​the large system. In particular, the corresponding main flow channel and auxiliary flow channel in this area can automatically switch with each other, so the flowability can still be guaranteed to ensure the continuous and reliable operation of the equipment.

[0059] Through the above design, the present invention can minimize the adverse effects of ice blockage or dirt blockage, and ensure the stable operation of the heat exchanger and system.

[0060] Of course, those skilled in the art will recognize that the present invention is not limited to the details of the exemplary embodiments described above, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0061] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0062] The technologies, shapes, and structures not described in detail in this invention are all known technologies.

Claims

1. A three-dimensional anisotropic flow channel type functional heat exchange module, comprising a heat exchange plate and flow channels located within the heat exchange plate for the passage of the working medium and the heat exchange medium; characterized in that: The flow channels include a first working medium flow channel (10a) constituting a first cold source, a heat exchange medium flow channel (10b) constituting a heat source, and a second working medium flow channel (10c) constituting a second cold source; the heat exchange medium flow channel (10b) is a sequentially stacked structure of a first main flow channel (11a), a first auxiliary flow channel (11b), a second auxiliary flow channel (12a), and a second main flow channel (12b), and the first main flow channel (11a) and the first auxiliary flow channel (11b) are interconnected to form an upper heat source cavity, and the second main flow channel (10c) is... 2b) The second auxiliary channel (12a) is connected to each other to form the lower heat source cavity; in the same heat source cavity, the flow area of ​​the main channel is larger than that of the auxiliary channel, and the main channel and the auxiliary channel intersect each other so that the intersection point forms a connection point that is connected to each other; along the stacking direction of the channels, the second auxiliary channel (12a) is adjacent to the first main channel (11a), the second main channel (12b) and the first auxiliary channel (11b) are adjacent to each other, and there is a connecting port (13) between the upper heat source cavity and the lower heat source cavity. In the top-view projection, the second auxiliary channel (12a) is located within the projection range of the first main channel (11a), and the second main channel (12b) is located within the projection range of the first auxiliary channel (11b). The bottom end of the first auxiliary channel (11b) and the top end of the second auxiliary channel (12a) intersect each other along the stacking direction of the channels, and the intersection forms the confluence (13).

2. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 1, characterized in that: The upper heat source cavity and the lower heat source cavity are formed by three heat exchange plates. The lower surface of the first heat exchange plate (15) is provided with a grooved first main flow channel (11a), the upper surface of the second heat exchange plate (16) is provided with a grooved first auxiliary flow channel (11b), the lower surface of the second heat exchange plate (16) is provided with a grooved second auxiliary flow channel (12a), and the upper surface of the third heat exchange plate (17) is provided with a grooved second main flow channel (12b). The corresponding main flow channel and auxiliary flow channel are slotted together at the connection point to form the corresponding heat source cavity. Above the first heat exchange plate (15), an upper heat exchange plate (14) with a first working medium flow channel (10a) is arranged, and below the third heat exchange plate (17), a lower heat exchange plate (18) with a second working medium flow channel (10c) is arranged.

3. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 1, characterized in that: The upper heat source cavity and the lower heat source cavity are formed by three heat exchange plates. The lower surface of the first heat exchange plate (15) is etched with a grooved first main flow channel (11a), the upper surface of the second heat exchange plate (16) is etched with a grooved first auxiliary flow channel (11b), the lower surface of the second heat exchange plate (16) is etched with a grooved second auxiliary flow channel (12a), and the upper surface of the third heat exchange plate (17) is etched with a grooved second main flow channel (12b). The corresponding main flow channel and auxiliary flow channel are slotted together at the connection point to form the corresponding heat source cavity. A side heat exchange plate with a first working medium flow channel (10a) and a second working medium flow channel (10c) is also arranged above or below the first heat exchange plate (15).

4. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 2 or 3, characterized in that: Each auxiliary flow channel is formed by two or more independent flow channels arranged side by side; each independent flow channel is independently connected to the corresponding main flow channel of the same heat source cavity at the connection point.

5. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 2 or 3, characterized in that: Each main channel and each auxiliary channel has a V-shaped, W-shaped, or wavy shape. In the same heat source cavity, the openings of the main channels and auxiliary channels that cooperate with each other are opposite to each other, so that the openings of the main channels and auxiliary channels are matched to form a closed loop structure, and the connection point is set at the matching point of the closed loop structure. The turning point of the V-shaped or W-shaped main channels and auxiliary channels, or the peak or trough of the wavy main channels and auxiliary channels, are the inflection points of each channel. The main channels and auxiliary channels that cooperate with each other in the same heat source cavity form a row of channel units. The adjacent inflection points of the current row of channel units are connected to the next row of channel units in the same heat source cavity.

6. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 5, characterized in that: The angle between each main flow channel and auxiliary flow channel and the length direction of each heat exchange plate ranges from 0° to 15°.

7. The three-dimensional anisotropic flow channel functional heat exchange module according to claim 2, characterized in that: The upper heat exchange plate (14) has an upper arc groove etched on its surface. The upper arc groove cavity cooperates with the adjacent heat exchange plate to form a first working medium flow channel (10a). The lower heat exchange plate (18) has a lower arc groove etched on its surface. The lower arc groove cavity cooperates with the adjacent heat exchange plate to form a second working medium flow channel (10c). The openings of the upper and lower arc grooves face each other or are away from each other.

8. A heat exchanger that uses the three-dimensional countercurrent flow channel functional heat exchange module as described in claim 2 or 3, characterized in that: It includes a tube box and a core located inside the tube box. The core is formed by stacking two or more sets of three-dimensional counter-current flow channel functional heat exchange modules sequentially along the flow channel stacking direction.

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