Heat exchanger with adjustable water outlet temperature and application thereof

Abstract

The invention discloses a heat exchanger with adjustable water outlet temperature and application thereof. The heat exchanger with the adjustable water outlet temperature comprises a first fluid channel piece and a second fluid channel piece, wherein the first fluid channel piece comprises a first heat exchange area, a pair of first inlets and outlets, a pair of first communication areas and a pair of first conduction areas; the second fluid channel piece comprises a second heat exchange area, a pair of second inlets and outlets, a pair of second through areas and a pair of second conduction areas; the third fluid channel piece comprises a third heat exchange area, a pair of third inlets and outlets, a pair of third through areas and a pair of third communicating areas; the area of the third heat exchange area is smaller than that of the first heat exchange area; the fluid channel pieces are arranged in a laminated mode in the O-Z direction, the first fluid channel piece is located between the second fluid channel piece and the third fluid channel piece, a first inlet and outlet communicates with the second communicating area and the third communicating area to form a first inlet and outlet cavity, and a second inlet and outlet communicates with the first communicating area and the third communicating area to form a second inlet and outlet cavity. The third inlet and outlet communicates with the first conduction area and the second conduction area to form a third inlet and outlet cavity.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration technology, and in particular to a heat exchanger with adjustable outlet water temperature and applications thereof, in particular to a metastable water preparation system and method. Background Art

[0002] Metastable water is a critical state of water, including supercooled water and superheated water. It is widely used in chemical, electric power, metallurgy and other industries.

[0003] Supercooled water refers to liquid water that remains below its freezing point (0°C) but remains unfrozen. The preparation of supercooled water is plagued by issues such as ice blockage and insufficient supercooling, which restrict its application.

[0004] Superheated water refers to water that remains liquid even when its temperature exceeds the boiling point (100°C). The preparation of superheated water also has problems such as insufficient superheat and unadjustable temperature.

[0005] Heat exchangers are core components for producing supercooled and superheated water. For example, plate heat exchangers are typically used to exchange water and antifreeze. If the temperature is too low, ice blockage is likely to occur; if the temperature is too high, it cannot meet demand, and the outlet water temperature cannot be controlled as needed.

[0006] In view of this, it is necessary to provide an improved heat exchanger with adjustable outlet water temperature and its application to solve the above technical problems. Summary of the Invention

[0007] The object of the present invention is to provide a heat exchanger with adjustable outlet water temperature, a metastable water preparation system and a preparation method having the same. By arranging a first fluid channel plate, a second fluid channel plate and a third fluid channel plate in the heat exchanger and rationally configuring their area ratio and arrangement, the preparation efficiency of supercooled water and superheated water is significantly improved, while the risk of ice blockage is reduced, thereby meeting the demand for flexible adjustment of the outlet water temperature.

[0008] In order to achieve the above-mentioned object of the invention, the present invention adopts the following technical solutions: A heat exchanger with adjustable outlet water temperature, comprising: a plurality of first fluid channel sheets, comprising a first heat exchange area, a pair of first inlet and outlet connected to the first heat exchange area, a pair of first communication areas separated from the first heat exchange area by a first dam, and a pair of first conduction areas; a plurality of second fluid channel sheets, comprising a second heat exchange area, a pair of second inlet and outlet connected to the second heat exchange area, a pair of second through-areas separated from the second heat exchange area by a second dam, and a pair of second conduction areas; a plurality of third fluid channel sheets, comprising a third heat exchange area, a pair of third inlet and outlet connected to the third heat exchange area, a pair of third through-areas separated from the third heat exchange area by a third dam, and a pair of A pair of third connecting areas; the area of ​​the third heat exchange area is smaller than that of the first heat exchange area; wherein, the first fluid channel sheet, the second fluid channel sheet and the third fluid channel sheet are stacked along the OZ direction, and the first fluid channel sheet is located between the second fluid channel sheet and the third fluid channel sheet; along the OZ direction, a pair of first inlets and outlets are respectively connected with a pair of second through-through areas and a pair of third through-through areas to form a first inlet and outlet cavity, a pair of second inlets and outlets are respectively connected with a pair of first connecting areas and a pair of third connecting areas to form a second inlet and outlet cavity, and a pair of third inlets and outlets are respectively connected with a pair of first conduction areas and a pair of second conduction areas to form a third inlet and outlet cavity.

[0009] In some embodiments, the area of ​​the second heat exchange zone is 90% to 110% of the area of ​​the first heat exchange zone, and the area of ​​the third heat exchange zone is 1 / 2 to 1 / 3 of the area of ​​the first heat exchange zone.

[0010] In some embodiments, a pair of the first inlets and outlets include a first inlet and a first outlet; the projection of the third heat exchange zone along the OZ direction on the first fluid channel plate is located within the first heat exchange zone, and the distance between the projection and the first inlet is less than the distance between the projection and the first outlet; or, the projection of the third heat exchange zone along the OZ direction on the first fluid channel plate is located within the first heat exchange zone, and the projection is located in the middle area of ​​the first heat exchange zone; or, the projection of the third heat exchange zone along the OZ direction on the first fluid channel plate is located within the first heat exchange zone, and the distance between the projection and the first outlet is less than the distance between the projection and the first inlet.

[0011] In some embodiments, a plurality of microstructures are provided in the first heat exchange zone, the second heat exchange zone, and the third heat exchange zone; and the arrangement density of the microstructures in the third heat exchange zone is greater than the arrangement density of the microstructures in the first heat exchange zone and the second heat exchange zone.

[0012] In some embodiments, the first heat exchange zone is recessed from the first surface to the second surface of the first fluid channel plate, a pair of the first inlet and outlet are respectively arranged on both sides of the first heat exchange zone along the OX direction, and the first inlet and outlet are connected to the first heat exchange zone through a first transition zone; a pair of the first connecting areas are respectively arranged on both sides of the first heat exchange zone along the OY direction, a pair of the first conduction areas are located on one side of the first heat exchange zone along the OX direction, and a pair of the first conduction areas are respectively arranged on both sides of the first inlet and outlet along the OY direction; the second heat exchange zone is recessed from the first surface to the second surface of the second fluid channel plate, a pair of the second inlet and outlet are respectively arranged on both sides of the second heat exchange zone along the OY direction, and the second inlet and outlet are connected to the second heat exchange zone through a first transition zone. The two transition zones are connected; a pair of the second through-through zones are respectively arranged on both sides of the second heat exchange zone along the OX direction, a pair of the second conduction zones are located on one side of the second heat exchange zone along the OX direction, and a pair of the second conduction zones are respectively arranged on both sides of the second through-through zone along the OY direction; the third heat exchange zone is recessed from the first surface to the second surface of the third fluid channel plate, a pair of the third through-through zones are respectively arranged on both sides of the third heat exchange zone along the OX direction, a pair of the third connecting zones are respectively arranged on both sides of the third heat exchange zone along the OY direction, a pair of the third inlets and outlets are located on one side of the third heat exchange zone along the OX direction, and a pair of the third inlets and outlets are respectively arranged on both sides of the third through-through zone along the OY direction, and the third inlet and outlet are connected to the third heat exchange zone through the third transition zone.

[0013] In some embodiments, the heat exchanger with adjustable outlet water temperature further includes at least one temperature sensor located on at least one of the first fluid channel sheets.

[0014] In some embodiments, at least one of the temperature sensors is located within the projection of the third heat exchange zone on the first fluid channel plate along the OZ direction, or at least one of the temperature sensors is located at the upstream inlet of the projection of the third heat exchange zone on the first fluid channel plate along the OZ direction.

[0015] In some embodiments, the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are stacked in sequence along the OZ direction with the second fluid channel sheet, the first fluid channel sheet, the third fluid channel sheet, and the first fluid channel sheet as repeating units; or, the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are stacked in sequence along the OZ direction with the second fluid channel sheet, the first fluid channel sheet, and the third fluid channel sheet as repeating units.

[0016] A metastable water preparation system includes a first refrigerant system for providing a first refrigerant, a second refrigerant system for providing a second refrigerant, a water system for providing water, a heat exchanger and a control system, wherein the heat exchanger is any one of the above-mentioned heat exchangers with adjustable water outlet temperature, a pair of the first inlet and outlet are connected to the water system to form a path for the water to flow, a pair of the second inlet and outlet are connected to the first refrigerant system to form a loop for the first refrigerant to flow, a pair of the third inlet and outlet are connected to the second refrigerant system to form a loop for the second refrigerant to flow, and the control system is communicatively connected to the first refrigerant system, the water system and the second refrigerant system.

[0017] In some embodiments, the temperature of the first coolant is lower than the freezing point of water, and the temperature of the second coolant is no higher than the temperature of the first coolant.

[0018] In some embodiments, the metastable water preparation system also includes a third refrigerant system that provides a third refrigerant, and the third refrigerant system is connected to a pair of the third inlets and outlets to form a circuit for the flow of the third refrigerant, and the temperature of the third refrigerant is higher than the freezing point of water.

[0019] In some embodiments, the temperature of the first coolant is lower than the freezing point of water, and the temperature of the second coolant is higher than the freezing point of water.

[0020] In some embodiments, the temperature of the first coolant is higher than the boiling point of water, and the temperature of the second coolant is not lower than the temperature of the first coolant.

[0021] A metastable water preparation method is implemented based on any one of the above-mentioned metastable water preparation systems, and the metastable water preparation method includes the following steps: starting a first refrigerant system and a water system, and obtaining the outlet water temperature after running for a predetermined time; judging whether the outlet water temperature after the heat exchanger reaches a preset temperature, and if so, the first refrigerant system and the water system maintain the current operating state; if not, starting the second refrigerant system to supply cooling or heating to the water.

[0022] In some embodiments, the heat or cold required to be provided to the water is calculated based on the difference between the outlet water temperature and the preset temperature, and the temperature and / or flow rate of the second refrigerant provided by the second refrigerant system is controlled based on the heat or cold.

[0023] In some embodiments, the temperature of the first refrigerant is lower than the freezing point of water, and whether ice blockage occurs is detected. If so, a third refrigerant system connected in parallel with the second refrigerant system to the third inlet and outlet chamber is started, and a third refrigerant with a temperature higher than the freezing point of water is input into the heat exchanger; wherein, detecting whether ice blockage occurs includes: detecting the outlet water flow rate of the heat exchanger, and if the outlet water flow rate is lower than the rated flow rate, it is determined that ice blockage occurs; and / or, detecting the outlet water volume of the heat exchanger per unit time, and if the outlet water volume is less than the rated water volume, it is determined that ice blockage occurs; and / or, detecting the outlet water temperature of the heat exchanger, and if the outlet water temperature is not less than 0°C, it is determined that ice blockage occurs.

[0024] A method for preparing supercooled water is implemented based on the above-mentioned metastable water preparation system, and the supercooled water preparation method includes the following steps: starting a first refrigerant system and a water system, wherein the temperature of the first refrigerant is lower than the freezing point of water; after running for a predetermined time, monitoring whether ice blockage occurs in the heat exchanger, and if so, starting a second refrigerant system to provide a second refrigerant with a temperature higher than the freezing point of water; if not, the first refrigerant system and the water system maintain the current operating state; wherein, detecting whether ice blockage occurs includes: detecting the outlet water flow rate of the heat exchanger, and if the outlet water flow rate is lower than the rated flow rate, it is determined that ice blockage occurs; and / or, detecting the outlet water volume of the heat exchanger per unit time, and if the outlet water volume is less than the rated water volume, it is determined that ice blockage occurs; and / or, detecting the outlet water temperature of the heat exchanger, and if the outlet water temperature is not less than 0°C, it is determined that ice blockage occurs.

[0025] Compared with the prior art, the beneficial effect of the present invention is that: by arranging the first fluid channel plate, the second fluid channel plate, and the third fluid channel plate in the heat exchanger and rationally configuring the area ratio and arrangement of their heat exchange areas, the present invention significantly improves the preparation efficiency of supercooled water and superheated water, while reducing the risk of ice blockage and meeting the demand for flexible and adjustable water outlet temperature. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 Schematic diagram of the structure of a heat exchanger with adjustable outlet water temperature in one embodiment of the present invention.

[0027] Figure 2 for Figure 1 Partial exploded view.

[0028] Figure 3 for Figure 1 Schematic diagram of the first fluid channel sheet in FIG.

[0029] Figure 4 for Figure 1 Schematic diagram of the second fluid channel sheet in FIG.

[0030] Figure 5 for Figure 1 Schematic diagram of the third fluid channel sheet in FIG.

[0031] Figure 6 Schematic diagram of the structure of the third fluid channel sheet in another embodiment of the present invention.

[0032] Figure 7 Schematic diagram of the structure of the third fluid channel sheet in another embodiment of the present invention.

[0033] Figure 8 Schematic diagram of the structure of the third fluid channel sheet in another embodiment of the present invention.

[0034] Figure 9 Schematic diagram of the structure of the third fluid channel sheet in another embodiment of the present invention.

[0035] Figure 10 This is a partial exploded view of a heat exchanger with adjustable outlet water temperature in another embodiment of the present invention.

[0036] Figure 11 FIG. 4 is a schematic diagram of a first fluid channel sheet according to another embodiment of the present invention.

[0037] Figure 12 FIG. 1 is a schematic diagram of a second fluid channel sheet in another embodiment of the present invention.

[0038] Figure 13 FIG. 1 is a schematic diagram of a third fluid channel sheet in another embodiment of the present invention.

[0039] Figure 14 for Figure 13 Cross-sectional view at AA, BB, and CC.

[0040] Figure 15 Schematic diagram of temperature change when preparing metastable water using the heat exchanger with adjustable outlet water temperature of the present invention.

[0041] Among them, the dotted lines in the figure are only for illustrating the boundaries of the areas, 100-heat exchanger with adjustable water outlet temperature, 1-first fluid channel plate, 11-first heat exchange zone, 12-first dam, 13-first inlet and outlet, 132-first inlet and outlet cavity, 14-first transition zone, 15-first connecting zone, 16-first conduction zone, 2-second fluid channel plate, 21-second heat exchange zone, 22-second dam, 23-second inlet and outlet, 232-second inlet and outlet cavity, 24-second transition zone, 25-second through-zone, 26-second conduction zone, 3-third fluid channel plate, 31-third heat exchange zone, 32-third dam, 33-third inlet and outlet, 332-third inlet and outlet cavity, 34-third transition zone, 35-fourth heat exchange zone, 36-fourth transition zone, 37-third through-zone, 38-third connecting zone, 4-microstructure. DETAILED DESCRIPTION

[0042] The present invention will be described in detail below with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments do not limit the present invention, and any structural, methodological, or functional changes made by those skilled in the art based on these embodiments are all within the scope of protection of the present invention.

[0043] In the various drawings of the present invention, for the sake of convenience, some sizes of structures or parts are exaggerated relative to other structures or parts, and thus, only the basic structure of the subject matter of the present invention is illustrated.

[0044] The terms "first," "second," and "third" in the present invention are used solely to distinguish features and do not limit the quantity or order of the fluid channel sheets. For example, the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 refer to three types of fluid channel sheets. Any "fluid channel sheet" not qualified as "first," "second," or "third" herein refers collectively to the three types of fluid channel sheets.

[0045] For the convenience of description, the plane where the fluid channel sheet is located (or the extension surface) is the O-XY plane, and the thickness direction of the fluid channel sheet is the OZ direction. A coordinate system O-XYZ is established, and the OX direction, OY direction and OZ direction are perpendicular to each other.

[0046] Please refer to Figures 1 to 14 As shown, the present invention provides a heat exchanger 100 with adjustable outlet water temperature, comprising a plurality of first fluid channel sheets 1, a plurality of second fluid channel sheets 2, and a plurality of third fluid channel sheets 3. The first fluid channel sheets 1, the second fluid channel sheets 2, and the third fluid channel sheets 3 all extend in the O-XY plane, and the thickness directions of the first fluid channel sheets 1, the second fluid channel sheets 2, and the third fluid channel sheets 3 are aligned with the OZ direction.

[0047] Each fluid channel sheet has a heat exchange area and a connecting structure that matches its function, and is used to construct the overall fluid channel layout of the heat exchanger.

[0048] Please refer to Figures 1 to 3 、 Figure 11 As shown, the first fluid channel plate 1 includes a first heat exchange area 11, a pair of first inlet and outlet ports 13 communicating with the first heat exchange area 11, a pair of first communication areas 15 separated from the first heat exchange area 11 by a first dam 12, and a pair of first conduction areas 16 separated from the first heat exchange area 11 by the first dam 12. The first fluid enters the first heat exchange area 11 through one of the first inlet and outlet ports 13 and exits the first heat exchange area 11 through the other first inlet and outlet 13. The first dam 12 surrounds the first heat exchange area 11 to prevent the first fluid from flowing out of the first heat exchange area 11.

[0049] Please refer to Figures 1 to 2 、 Figure 4 and Figure 12As shown, the second fluid channel sheet 2 includes a second heat exchange area 21, a pair of second inlet and outlet ports 23 communicating with the second heat exchange area 21, a pair of second through-hole regions 25 separated from the second heat exchange area 21 by a second dam 22, and a pair of second conduction regions 26 separated from the second heat exchange area 21 by the second dam 22. The second fluid enters the second heat exchange area 21 through one of the second inlet and outlet ports 23 and exits the second heat exchange area 21 through the other second inlet and outlet ports 23. The second dam 22 surrounds the second heat exchange area 21 to prevent the second fluid from flowing out of the second heat exchange area 21.

[0050] Please refer to Figures 1 to 2 、 Figures 5 to 9 and Figure 13 As shown, the third fluid channel plate 3 includes a third heat exchange area 31, a pair of third inlet and outlet ports 33 connected to the third heat exchange area 31 via a third transition area 34, a pair of third through-hole ports 37 separated from the third heat exchange area 31 by a third dam 32, and a pair of third communication ports 38 separated from the third heat exchange area 31 by the third dam 32. The third fluid enters the third heat exchange area 31 through one of the third inlet and outlet ports 33 and exits the third heat exchange area 31 through the other third inlet and outlet 33. The third dam 32 surrounds the third heat exchange area 31 to prevent the third fluid from flowing out of the third heat exchange area 31.

[0051] Please refer to Figures 1 to 14 As shown, a plurality of first fluid channel sheets 1, a plurality of second fluid channel sheets 2 and a plurality of third fluid channel sheets 3 are stacked along the OZ direction to form fluid channels between adjacent fluid channel sheets.

[0052] A first fluid channel is formed between the first heat exchange zone 11 of the first fluid channel sheet 1 and the adjacent fluid channel sheet. A pair of first inlets and outlets 13 are connected along the OZ direction to the pair of second through-holes 25 on the second fluid channel sheet 2 and the pair of third through-holes 37 on the third fluid channel sheet 3, forming a pair of first inlet and outlet cavities 132. The first fluid enters one of the first inlet and outlet cavities 132, then flows through the corresponding first inlet and outlet 13 into the first heat exchange zone 11. It then flows out through the other first inlet and outlet 13 and the first inlet and outlet cavity 132, exchanging heat with the fluid in the adjacent fluid channel in the first heat exchange zone 11.

[0053] A second fluid channel is formed between the second heat exchange zone 21 of the second fluid channel sheet 2 and the adjacent fluid channel sheet. A pair of second inlets and outlets 23 are connected along the OZ direction to the pair of first communication areas 15 on the first fluid channel sheet 1 and the pair of third communication areas 38 on the third fluid channel sheet 3, respectively, to form a pair of second inlet and outlet cavities 232. The second fluid enters one of the second inlet and outlet cavities 232, then flows through the corresponding second inlet and outlet 23 into the second heat exchange zone 21, then flows out through the other second inlet and outlet 23 and the second inlet and outlet cavity 232, exchanging heat with the fluid in the adjacent fluid channel in the second heat exchange zone 21.

[0054] A third fluid channel is formed between the third heat exchange region 31 of the third fluid channel sheet 3 and the adjacent fluid channel sheet. A pair of third inlets and outlets 33 are connected along the OZ direction to the pair of first conductive areas 16 on the first fluid channel sheet 1 and the pair of second conductive areas 26 on the second fluid channel sheet 2, forming third inlet and outlet cavities 332. The third fluid enters one of the third inlet and outlet cavities 332, flows through the corresponding third inlet and outlet 33, and then flows out of the third heat exchange region 31 through the other third inlet and outlet 33 and the third inlet and outlet cavity 332, exchanging heat with the fluid in the adjacent fluid channel in the third heat exchange region 31.

[0055] The first fluid channel sheet 1 is located between the second fluid channel sheet 2 and the third fluid channel sheet 3. Through the stacking arrangement and structural design of the above three fluid channel sheets, the first fluid can obtain cold or heat from the second and third fluids on both sides, thereby achieving efficient heat exchange.

[0056] It should be noted that the "through area", "connection area" and "conduction area" may penetrate the fluid channel sheet along the thickness direction, or may not penetrate the fluid channel sheet, but the sheet material in the corresponding area may be removed after the stacking to form the inlet and outlet cavities.

[0057] When stacking, the heat exchange areas of all fluid channel sheets are located on the same side of the corresponding fluid channel sheets along the OZ direction and are aligned along the OZ direction, so that heat exchange is achieved between the fluids flowing through the heat exchange areas.

[0058] In one embodiment of the present invention, the positions of the inlet and outlet and the through-region of each fluid channel sheet are designed as follows.

[0059] The first fluid channel sheet 1 is designed as follows: it includes a first surface and a second surface disposed opposite each other along the thickness direction. A first heat exchange region 11 is recessed (or concavely formed) from the first surface toward the second surface, and a first dam 12 protrudes from the first surface away from the second surface. A first inlet and outlet 13 communicates with the first heat exchange region 11 via a first transition region 14. The first fluid flows through the first transition region 14 and the first heat exchange region 11. The first dam 12 is located on the first surface and surrounds the first heat exchange region 11 and the first transition region 14, preventing the first fluid from flowing out of the first heat exchange region 11 and the first transition region 14.

[0060] The first heat exchange zone 11 is located in the center. A pair of first inlets and outlets 13 are provided on either side of the first heat exchange zone 11 along the OX direction. A pair of first communication areas 15 are provided on either side of the first heat exchange zone 11 along the OY direction. A pair of first conduction areas 16 are located on one side of the first heat exchange zone 11 along the OX direction, and the pair of first conduction areas 16 are provided on either side of the first inlet and outlet 13 along the OY direction. The pair of first inlets and outlets 13 are provided on either side of the first heat exchange zone 11 along the OX direction to ensure that water is evenly distributed and flows through the first fluid channel.

[0061] The second fluid channel sheet 2 is designed as follows: it includes a first surface and a second surface disposed opposite each other along its thickness. A second heat exchange region 21 is recessed (or concavely formed) from the first surface toward the second surface, and a second dam 22 protrudes from the first surface away from the second surface. The second fluid flows through the second transition region 24 and the second heat exchange region 21. The second dam 22 is located on the first surface and surrounds the second heat exchange region 21 and the second transition region 24, preventing the second fluid from flowing out of the second heat exchange region 21 and the second transition region 24.

[0062] The second heat exchange zone 21 is located in the center. A pair of second inlets and outlets 23 are located on either side of the second heat exchange zone 21 along the OY direction. A pair of second through-holes 25 are located on either side of the second heat exchange zone 21 along the OX direction. A pair of second conduction zones 26 are located on one side of the second heat exchange zone 21 along the OX direction, and a pair of second conduction zones 26 are located on either side of the second through-hole 25 along the OY direction. The second fluid channel sheet 2 is formed by rotating the first fluid channel sheet 1 90° around its center. The first refrigerant flows through the second heat exchange zone 21 along the OY direction, forming a direct current flow with the water.

[0063] The third fluid channel sheet 3 is designed as follows: it includes a first surface and a second surface arranged opposite each other along its thickness. A third heat exchange region 31 is recessed (or concavely formed) from the first surface toward the second surface, and a third dam 32 protrudes from the first surface away from the second surface. The third fluid flows through the third transition region 34 and the third heat exchange region 31. The third dam 32 is located on the first surface and surrounds the third heat exchange region 31 and the third transition region 34, preventing the third fluid from flowing out of the third heat exchange region 31 and the third transition region 34.

[0064] The third heat exchange zone 31 is located in a local area in the middle, a pair of third through-zones 37 are respectively arranged on both sides of the third heat exchange zone 31 along the OX direction, a pair of third connecting zones 38 are respectively arranged on both sides of the third heat exchange zone 31 along the OY direction, a pair of third inlets and outlets 33 are located on one side of the third heat exchange zone 31 along the OX direction, and a pair of third inlets and outlets 33 are respectively arranged on both sides of the third through-zone 37 along the OY direction.

[0065] This structural design optimizes the flow paths of each fluid channel by rationally distributing the inlet and outlet, through-hole area, connection area, and conduction area on the fluid channel sheet, achieving efficient heat exchange between the fluids. The placement of the inlet and outlet, through-hole area, and connection area ensures the connectivity of each fluid between the channel sheets, preventing cross-flow and mixing of the fluids within the heat exchanger.

[0066] Through this arrangement, each heat exchange zone forms an independent fluid circuit with its corresponding inlet and outlet, through-hole, connection, and conduction zones, effectively reducing fluid flow resistance within the heat exchanger and optimizing the fluid's heat transfer path. Furthermore, this design enhances the heat exchanger's modularity, facilitating production and maintenance.

[0067] In this embodiment, the compactness and efficiency of the heat exchanger structure are ensured by the reasonable arrangement of the inlet and outlet, through-area, connecting area, and conduction area, while further improving the working performance and applicability of the heat exchanger, especially in working conditions requiring efficient preparation of supercooled water or superheated water, which has significant advantages.

[0068] The first fluid, the second fluid and the third fluid can be any one of the fluids. In the present invention, the first fluid is the fluid to be heated or cooled, and the second fluid and the third fluid provide cooling or heating for the first fluid.

[0069] In one embodiment of the invention, the first fluid is water, and the first fluid channel sheet 1 is designed for the flow of water; the second fluid and the third fluid are coolants, and the second fluid channel sheet 2 and the third fluid channel sheet 3 are designed for the flow of the first coolant and the second coolant, respectively.

[0070] In one embodiment of the present invention, the first fluid channel sheet 1, the second fluid channel sheet 2 and the third fluid channel sheet 3 are stacked in a specific repeating unit along the OZ direction. Specifically, the arrangement of these fluid channel sheets includes but is not limited to the following two methods.

[0071] In one embodiment, if Figure 2 As shown, the second fluid channel sheet 2, the first fluid channel sheet 1, and the third fluid channel sheet 3 are stacked sequentially along the OZ direction as a repeating unit. The second refrigerant compensates for the water's cooling or heating while also compensating for the first refrigerant's cooling or heating, both increasing the water's subcooling or superheating.

[0072] In another embodiment, if Figure 10 As shown, the second fluid channel sheet 2, the first fluid channel sheet 1, the third fluid channel sheet 3, and the first fluid channel sheet 1 are stacked sequentially along the OZ direction as a repeating unit. Water is placed on both sides of the first coolant, and water is placed on both sides of the second coolant. Both the first and second coolants directly provide cooling or heating to the water, resulting in high heat exchange efficiency.

[0073] The stacking design of the above-mentioned channel sheets is intended to achieve efficient heat transfer between fluids through a modular structural arrangement, and to achieve fast and stable temperature control.

[0074] Through this structured, laminated design, the heat exchanger of this invention not only achieves modular production and assembly, reducing manufacturing costs, but also improves the flexibility and stability of system operation. This arrangement is suitable for a variety of industrial applications such as preparing highly subcooled or superheated water, further broadening the heat exchanger's scope of application and significantly improving its performance and reliability.

[0075] Based on the above design, Figures 2 to 14 As shown, the area of ​​the third heat exchange zone 31 is smaller than that of the first heat exchange zone 11, and local compensation is performed on the first fluid, which can further regulate the outlet water temperature to meet diverse application requirements.

[0076] In one embodiment of the present invention, the area of ​​the second heat exchange zone 21 is 90% to 110% of the area of ​​the first heat exchange zone 11, preferably 97% to 107%, preferably 95% to 105%, preferably 93% to 103%, and preferably the same. The area of ​​the third heat exchange zone 31 is 1 / 2 to 1 / 3 of the area of ​​the first heat exchange zone 11. This area ratio is designed primarily based on the function and role of each fluid channel in the heat exchange process to optimize heat exchange efficiency and fluid flow performance.

[0077] The area of ​​the second heat exchange zone 21 is similar to that of the first heat exchange zone 11 (90% to 110%), ensuring uniform and efficient heat exchange between the first and second fluid channels. This area ratio matching effectively reduces pressure differentials and avoids fluid flow imbalances caused by large area differences, thereby improving system stability.

[0078] The third heat exchange zone 31 is smaller, measuring only 1 / 2 to 1 / 3 the area of ​​the first heat exchange zone 11. This design allows for more precise temperature control within a localized area. This smaller area allows heat exchange to be concentrated in a specific region, avoiding ice blockage or temperature fluctuations that could occur if the entire flow path participates in heat exchange. Specifically, this area ratio allows for more effective control of the water's subcooling when producing subcooled water; and when producing superheated water, it allows for enhanced localized heating to achieve a higher superheating effect.

[0079] By rationally designing the areas of the second and third heat exchange zones 21 and 31, the present invention maintains the heat exchanger's high efficiency while further optimizing system safety and flexibility, meeting the requirements for supercooled or superheated water production in various industrial scenarios. This area-matching design also reduces manufacturing complexity and costs while ensuring the long-term, stable operation of the fluid system.

[0080] The positional relationship between the third heat exchange zone 31 and the first heat exchange zone 11 is very important. In one embodiment of the present invention, the pair of first inlet and outlet ports 13 includes a first inlet and a first outlet. The third heat exchange zone 31 forms a projection on the first fluid channel sheet 1 along the OZ direction. The projection position can be one of the following three situations.

[0081] The first case, such as Figure 5 、 Figure 6 、 Figure 13 As shown, this projection is located within the first heat exchange zone 11 and is closer to the first outlet than to the first inlet. The projection of the third heat exchange zone 31 is located closer to the first outlet, enabling the water temperature to be further lowered or raised as it exits the heat exchanger, thereby ensuring that the outlet water temperature reaches the target value. This arrangement is particularly suitable for operating conditions requiring high subcooling or superheating, and its proximity to the outlet significantly reduces the residence time of low- or high-temperature fluids within the heat exchanger, thereby reducing the risk of ice blockage or heat loss.

[0082] The second case, such as Figure 7 As shown, the projection is located within the first heat exchange zone 11, and in the middle of the first heat exchange zone 11. Its function is to provide temperature compensation for the water flow in the middle section. When the water flows through the first half of the first fluid channel, its temperature has already dropped significantly. The cooling compensation in the middle section can further regulate the temperature, thereby achieving more precise supercooling or superheating effects.

[0083] In the third case, please refer to Figure 8 As shown, this projection is located within the first heat exchange zone 11 and is closer to the first inlet than to the first outlet. The projection of the third heat exchange zone 31 is located closer to the first inlet. By enhancing local heat exchange at the inlet of the first fluid channel, the temperature of the incoming water flow can be rapidly reduced, thereby improving the efficiency of the entire heat exchanger. This arrangement is suitable for fluids with relatively high initial temperatures and can significantly increase the cooling rate.

[0084] Through the flexible design of the three projected positions described above, the present invention achieves optimized distribution of local heat exchange within the third fluid channel, enabling adjustment of the heat exchanger's operating mode and effectiveness based on actual needs. The flexible placement of the third heat exchange zone 31 significantly improves the heat exchanger's applicability and flexibility, while maintaining efficient and stable performance across diverse application scenarios.

[0085] In addition, Figures 5 to 7 、 Figure 13 Based on the embodiment shown, Figure 9 As shown, the third fluid channel sheet 3 further includes a fourth heat exchange region 35 and a pair of fourth inlets and outlets connected to the fourth heat exchange region 35 via a fourth transition region 36. Microstructures 4 are provided in the fourth heat exchange region 35 and the fourth transition region 36.

[0086] The structure and position of the third heat exchange zone 31 can be as follows Figures 5 to 7 、 Figure 13 As shown. The third and fourth heat exchange zones 31 and 35 are arranged along the OX direction, heating the water from different locations along the direction of the water flow. A pair of fourth inlets and outlets are located on the other side of the third heat exchange zone 31 along the OX direction. That is, the fourth inlet and outlet 33 are located at opposite ends of the third heat exchange zone 31 along the OX direction, and a pair of fourth inlets and outlets are provided on either side of the third through-hole zone 37 along the OY direction. Therefore, corresponding fourth through-hole zones are provided on both the first and second fluid channel sheets 1 and 2, forming a fourth inlet and outlet cavity with the fourth inlet and outlet for supplying the fourth fluid to the fourth heat exchange zone 35.

[0087] based on Figure 9 In the third fluid channel sheet 3 shown, after lamination, one of the third heat exchange zone 31 and the fourth heat exchange zone 35 is located near the first inlet, while the other is located near the first outlet. The third fluid and the fourth fluid can be supplied either or both as needed, and their temperatures can be adjusted as needed.

[0088] Taking the generation of supercooled water as an example, the third heat exchange zone 31 is located at the first outlet, and the fourth heat exchange zone 35 is located at the first inlet. In one embodiment, the temperature of the fourth fluid is below the freezing point, increasing the cooling rate of the water flow and reducing the water temperature; the temperature of the third fluid is below the freezing point, further reducing the temperature of the supercooled water. In another embodiment, the temperature of the fourth fluid is below the freezing point, increasing the cooling rate of the water flow and reducing the water temperature; the temperature of the third fluid is above the freezing point, providing the third fluid for melting ice in the event of ice blockage.

[0089] For example, in the case of superheated water, the third heat exchange zone 31 is located at the first outlet, and the fourth heat exchange zone 35 is located at the first inlet. In one embodiment, the temperature of the fourth fluid is higher than the boiling point, increasing the rate of temperature increase and the temperature of the water flow; the temperature of the third fluid is higher than the boiling point, further increasing the temperature of the superheated water.

[0090] Based on any of the above designs, in one embodiment of the present invention, in the first fluid channel sheet 1, the second fluid channel sheet 2 and the third fluid channel sheet 3, the heat exchange zone is recessed from the first surface along the thickness direction, forming a structure similar to a "river channel" with the surrounding dam, and the fluid flows in the heat exchange zone.

[0091] The heat exchange areas of the three types of fluid channel sheets are all provided with a number of microstructures 4. The microstructures 4 are used to enhance the heat exchange capacity of the fluid channels and, at the same time, form support with adjacent fluid channel sheets to improve pressure resistance.

[0092] The microstructures 4 are formed by forming protrusions within the heat exchange zone. These protrusions are aligned with the height of the dam and can be integrated with adjacent fluid channel sheets. These microstructures 4 significantly improve heat exchange efficiency by disturbing the fluid boundary layer and increasing the contact area between the fluid and the channel wall.

[0093] In one embodiment, the microstructures protrude from the heat exchange region toward the first surface. When forming the fluid channel sheet using a sheet material with good thermal conductivity, such as stainless steel, the heat exchange region is typically formed using a patterned etching process. Specifically, the unstructured portion of the heat exchange region is etched away from the first surface, leaving the unetched portion forming the dam and microstructure 4.

[0094] The density of microstructures 4 within the heat exchange area of ​​the third fluid channel sheet 3 is greater than that of the first and second fluid channel sheets 1 and 2. The lower density of microstructures 4 within the first and second fluid channel sheets 1 and 2 provides basic heat exchange capacity while reducing flow resistance and ensuring smooth circulation of water and the first refrigerant. The higher density of microstructures 4 within the third fluid channel sheet 3 enhances local heat exchange and precisely controls the water temperature within the first fluid channels.

[0095] The high-density arrangement of microstructures 4 within the third fluid channel sheet 3 more effectively utilizes the cooling or heating capacity of the second coolant, rapidly achieving localized cooling or heating. This design not only improves the heat exchanger's response speed but also enables precise control of the outlet water temperature. This is particularly true during supercooled water production, as it allows for concentrated cooling in localized areas, reduces the distance the supercooled water flows, and significantly reduces the likelihood of ice blockage.

[0096] By rationally distributing the density of microstructures 4 within each fluid channel sheet, the present invention achieves a balance between the heat exchange efficiency of each channel and the fluid flow properties. Furthermore, the enhanced heat exchange capacity of the third fluid channel sheet 3 further enhances the overall heat exchange capacity of the system, meeting the requirements for temperature control accuracy and efficiency under various operating conditions. This design optimizes performance while maintaining structural compactness and manufacturability.

[0097] In addition, the area between the heat exchange zone and the inlet and outlet of each fluid channel sheet is called the transition zone. The transition zone corresponds to the dam of the adjacent fluid channel sheet along the OZ direction. Microstructures 4 are also provided in the transition zone, and these are larger than those in the heat exchange zone. This improves the bonding strength of the transition zone and ensures pressure resistance at the inlet and outlet. Specifically, in the first fluid channel sheet 1, the first heat exchange zone 11 and the first inlet and outlet 13 are connected via a first transition zone 14. Microstructures 4 are provided in the first transition zone 14, and these are larger than those in the first heat exchange zone 11. In the second fluid channel sheet 2, the second heat exchange zone 21 and the second inlet and outlet 23 are connected via a second transition zone 24. Microstructures 4 are provided in the second transition zone 24, and these are larger than those in the second heat exchange zone 21. In the third fluid channel sheet 3 , the third heat exchange zone 31 and the third inlet and outlet 33 are connected through the third transition zone 34 . A microstructure 4 is provided in the third transition zone 34 . The microstructure 4 of the third transition zone 34 is larger than that of the third heat exchange zone 31 .

[0098] In addition, such as Figures 11 to 14 As shown, each fluid channel sheet has a first guide surface 6 at the edge of the transition zone facing the inlet and outlet (or the inlet and outlet edges). This first guide surface 6 is located on the side of the fluid channel sheet where the heat exchange area is located, guiding water into the transition zone. Each fluid channel sheet has a second guide surface 6' at the edge of the dam facing the through-zone or conduction zone. This second guide surface 6' is located on the side without the heat exchange area, guiding fluid into the corresponding fluid channel. The provision of the first and second guide surfaces 6' reduces resistance to fluid entering the fluid channel.

[0099] It should be noted that Figures 1 to 10 The fluid channel sheet may also be provided with a first guide surface 6 and a second guide surface 6' at corresponding positions.

[0100] In one embodiment of the present invention, the heat exchanger 100 with adjustable outlet water temperature further includes at least one temperature sensor located on at least one first fluid channel sheet 1. This temperature sensor is used to monitor the temperature of the fluid within the first fluid channel sheet 1 in real time, ensuring that the heat exchanger can accurately control the outlet water temperature to meet the requirements of different operating conditions.

[0101] The temperature sensor installed on the first fluid channel plate 1 directly senses the dynamic changes in the water temperature. This temperature data accurately reflects the heat exchange efficiency within the first fluid channel. Based on this data, the control system can adjust the flow rate and temperature of the coolant in the second and third fluid channels in real time to achieve more precise heat exchange control.

[0102] The temperature sensor is preferably placed in a key heat exchange area of ​​the first fluid channel plate 1, such as near the water inlet, mid-zone, or outlet. Temperature monitoring at the inlet reflects the initial state of the incoming water flow, monitoring in the mid-zone captures local heat exchange effects, and monitoring at the outlet directly determines whether the final outlet water temperature meets the target. This arrangement not only accurately monitors water temperature fluctuations but also effectively prevents ice blockage and overheating caused by temperature anomalies.

[0103] By incorporating a temperature sensor on the first fluid channel plate 1, the heat exchanger of this invention implements intelligent temperature monitoring and control, significantly improving system operational safety and temperature control accuracy. This design is suitable for industrial applications with strict temperature requirements, such as supercooled or superheated water production in the chemical, power, and metallurgical sectors, effectively meeting the requirements for efficient, safe, and stable operation.

[0104] In one embodiment of the present invention, at least one temperature sensor is located within the projection of the third heat exchange zone 31 along the OZ direction onto the first fluid channel sheet 1, or at least one temperature sensor is located at the upstream entrance of the projection of the third heat exchange zone 31 along the OZ direction onto the first fluid channel sheet 1. By monitoring the temperature of these specific areas, the present invention achieves precise control of key heat exchange locations.

[0105] When the temperature sensor is located within the projection of the third heat exchange zone 31, its primary function is to monitor the temperature changes of the water flow in this local heat exchange area in real time. This location is where local heat exchange occurs between the third fluid channel and the first fluid channel. By acquiring temperature data in this area, it is possible to directly assess whether the third fluid is needed to compensate for the water temperature and also to evaluate the third fluid's effectiveness in regulating the water temperature within the first fluid channel. This arrangement is crucial for optimizing local heat exchange efficiency and ensuring stable water temperature within the first fluid channel.

[0106] When the temperature sensor is located at the upstream inlet of the projection of the third heat exchange zone 31, its function is to pre-detect the water temperature before it enters the local heat exchange area. By monitoring the temperature at the upstream inlet, it can promptly identify trends in water temperature changes, predict heat exchange requirements, and dynamically adjust the flow rate or temperature of the refrigerant in the third fluid channel, thereby optimizing overall heat exchange capacity.

[0107] This temperature sensor arrangement not only provides accurate temperature data for the system but also effectively reduces the risk of ice blockage when producing subcooled water and enhances the warming effect when producing superheated water. By monitoring temperature at specific locations, this invention further enhances the intelligence and operational efficiency of the heat exchanger, meeting the demands of efficient and stable industrial applications. This arrangement is suitable for scenarios requiring highly precise temperature control and provides important technical support for optimizing heat exchanger performance.

[0108] Based on any of the above designs, the dimensions of the fluid channel sheet are described. The fluid channel sheet is generally square, with an outer dimension L1 in the OX or OY directions no greater than 50 mm, for example, 20 mm to 40 mm. This shortens the fluid flow distance within the heat exchanger, reducing risks such as ice blockage. In one embodiment, the dimension L2 of the heat exchange zone in the fluid flow direction is 30 mm ± 5 mm. This allows for greater fluid agitation over a shorter distance, improving heat exchange efficiency and capacity.

[0109] The fluid channel sheet is made of a sheet material such as stainless steel, approximately 0.2 mm thick. The thickness (in the OZ direction) of the dam and microstructures is consistent with that of the stainless steel sheet. The thickness (in the OZ direction) of the heat exchange zone where the microstructures are not located is 40%-60% of the thickness of the stainless steel sheet, preferably 50% ± 5%, and in one embodiment, 0.1 mm ± 0.02 mm. Adjacent fluids exchange heat through the thin partition wall, resulting in high heat exchange efficiency and excellent heat transfer capacity.

[0110] In one embodiment, the heat exchange zone is formed by etching from the first surface to the second surface using processes such as photoetching and chemical etching, and the height of the dam and microstructure protruding upward from the heat exchange zone is the difference between the thickness of the sheet and the thickness of the heat exchange zone.

[0111] Based on the design of the fluid channel sheet described above, the structure and method of the compact heat exchanger are briefly described.

[0112] A 2mm-5mm thick plate is used as the end plate in the OZ direction. The first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 are stacked between the two end plates in the order of the above-mentioned repeating units, and then all the sheets are combined into a whole using an atomic diffusion bonding process.

[0113] In some embodiments, Figures 11 to 13 As shown, positioning holes 7 are provided on the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3. By passing positioning pins through the positioning holes 7, the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 can be aligned in the OZ direction.

[0114] It should be noted that the positioning pins can be fixed to one of the end plates, and the first fluid channel sheet 1, second fluid channel sheet 2, and third fluid channel sheet 3 can be stacked on this end plate, and then another end plate with corresponding positioning holes can be placed on top of the fluid channel sheets. Alternatively, positioning holes can be provided on both end plates, and the end plates and all fluid channel sheets can be positioned using positioning pins.

[0115] Figures 1 to 10 The fluid channel sheet in the device can also be provided with positioning holes, which are arranged at the edge. Of course, when the positioning holes are not provided, positioning can also be achieved with the help of a positioning tool.

[0116] The atomic diffusion bonding process may adopt existing technology, and may be, but is not limited to, using a vacuum furnace for atomic diffusion bonding.

[0117] End plates are welded on the side of the first inlet and outlet cavity 132, a pair of second inlet and outlet cavities 232, and a pair of third inlet and outlet cavities 332 away from the heat exchange area, and inlet and outlet holes connected to the inlet and outlet cavities are opened on any end plate connected to the inlet and outlet cavities; and then pipes are assembled at the inlet and outlet holes to facilitate connection with the external fluid system.

[0118] The present invention also provides another heat exchanger 100 with adjustable outlet water temperature, comprising a heat exchange core, a pair of first inlet and outlet cavities 132 , a pair of second inlet and outlet cavities 232 , and a pair of third inlet and outlet cavities 332 .

[0119] The heat exchange core includes a plurality of first fluid channels, a plurality of second fluid channels, and a plurality of third fluid channels arranged along the OZ direction. In this embodiment, the heat exchange core is an integrated structure, consistent with the structure formed by combining the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3.

[0120] This integrated structure can be formed by, but is not limited to, 3D printing technology.

[0121] The first fluid channel is designed for water circulation. A pair of first inlet and outlet cavities 132 are connected to the plurality of first fluid channels for water to flow in and out. The structure of the first fluid channel is consistent with the first transition zone 14 and the first heat exchange zone 11 of the first fluid channel sheet 1 described above.

[0122] Specifically, the first fluid channel includes a first channel portion connected to the first inlet and outlet cavities 132 and a first heat exchange portion located between the pair of first channel portions. The first channel portion is configured consistent with the first transition zone 14 , and the first heat exchange portion is configured consistent with the first heat exchange zone 11 .

[0123] The second fluid channels are designed for the circulation of a second coolant. A pair of second inlet and outlet cavities 232 communicate with the plurality of second fluid channels, allowing the first coolant to enter and exit. The structure of the second fluid channels is consistent with the second transition region 24 and second heat exchange region 21 of the second fluid channel plate 2 described above.

[0124] Specifically, the second fluid channel includes a second channel portion connected to the second inlet and outlet chambers 232 and a second heat exchange portion located between the second channel portions. The second channel portion is configured consistent with the second transition zone 24 , and the second heat exchange portion is configured consistent with the second heat exchange zone 21 .

[0125] The third fluid channels are designed for the circulation of a second coolant. A pair of third inlet and outlet cavities 332 communicate with the plurality of third fluid channels, allowing for the entry and exit of the second coolant. The structure of the third fluid channels is identical to that of the third transition region 34 and third heat exchange region 31 of the third fluid channel plate 3 described above and will not be further described here.

[0126] Specifically, the third fluid channel includes a third channel portion connected to the third inlet and outlet chambers 332 and a third heat exchange portion located between the pair of third channel portions. The third channel portion is configured in the same manner as the third transition zone 34 , and the third heat exchange portion is configured in the same manner as the third heat exchange zone 31 .

[0127] Through this partitioned design, the heat exchanger can achieve efficient heat exchange between fluids and adjust the outlet water temperature as needed to meet the needs of different industrial applications.

[0128] The first fluid channel is sandwiched between the second fluid channel and the third fluid channel. Through this double-sided heat exchange structure, the first fluid channel can efficiently absorb cold or heat from both sides, thereby quickly cooling or heating, and improving the preparation efficiency of supercooled water or superheated water.

[0129] The third heat exchange channel, with a smaller area than the first, is designed to locally compensate for the temperature of the water in the first fluid channel, rather than allowing the entire channel to participate in heat exchange. This design not only avoids ice blockage caused by an excessively long supercooled water flow path, but also allows for flexible adjustment of the outlet water temperature by properly controlling the layout of the third fluid channel.

[0130] The above structure and function ensure that the heat exchanger can efficiently prepare supercooled water or superheated water, while providing flexibility in regulating the outlet water temperature.

[0131] Specifically, the area of ​​the channel portion is much smaller than that of the heat exchange portion, and the heat exchange within the channel portion is limited. "The area of ​​the third heat exchange channel is smaller than that of the first heat exchange channel" mainly means that the area of ​​the third heat exchange portion is smaller than that of the first heat exchange portion.

[0132] In one embodiment of the present invention, the area of ​​the second heat exchange section is 90% to 110% of the area of ​​the first heat exchange section, and the area of ​​the third heat exchange section is 1 / 2 to 1 / 3 of the area of ​​the first heat exchange section. This area ratio is designed to optimize heat exchange efficiency and pressure balance between the fluids.

[0133] The area of ​​the second heat exchange section is close to or slightly different from that of the first heat exchange section. This matching relationship ensures that the first fluid channel can efficiently absorb cold air from the second fluid channel without reducing heat exchange efficiency or increasing pressure loss due to a large area difference. This area ratio also helps avoid imbalances in fluid flow rates, thereby improving the overall performance of the heat exchanger.

[0134] The third heat exchange section is smaller, measuring only 1 / 2 to 1 / 3 the area of ​​the first. Its design prioritizes localized compensatory heat exchange within the third fluid channel, rather than full-channel heat exchange. This limited area effectively controls fluid flow and heat exchange within the third fluid channel, preventing ice blockage caused by overcooling during supercooled water production while ensuring stable localized warming during superheated water production.

[0135] By optimizing the above area ratios, the heat exchanger of the present invention significantly reduces the risk of ice blockage while maintaining efficient heat exchange, improving system reliability and stability. This area ratio is particularly suitable for applications such as producing supercooled or superheated water, and can be adjusted to meet the specific requirements of different industrial conditions.

[0136] In one embodiment of the present invention, the first inlet and outlet chambers 132 include a first inlet chamber and a first outlet chamber, and the projection position of the third fluid channel on the first fluid channel along the OZ direction has one of the following three situations: first, the projection is located in the first fluid channel, and the distance from the first inlet chamber is less than the distance from the first outlet chamber; second, the projection is located in the middle area of ​​the first fluid channel; third, the projection is located in the first fluid channel, and the distance from the first outlet chamber is less than the distance from the first inlet chamber.

[0137] In the above design, the location selection of the third fluid channel is of great significance for optimizing the heat exchange effect. When the projection of the third fluid channel is located on the side close to the first inlet chamber, its function is mainly to provide cooling for the water in the initial stage of entering the heat exchanger, quickly reduce the temperature of the water, and thus improve the efficiency of preparing cooling water. When the projection of the third fluid channel is located in the middle area of ​​the first fluid channel, it is possible to supplement cold or heat when the water flows through the middle area, and further adjust the outlet water temperature. In the third case, that is, the projection of the third fluid channel is located near the first outlet chamber, it is possible to enhance heat exchange when the water is about to flow out of the heat exchanger, further reduce the water temperature in the supercooling zone, or increase the outlet temperature when preparing superheated water.

[0138] Preferably, the third fluid channel is as close to the first outlet chamber as possible. This arrangement ensures that low- and high-temperature water have a short flow path within the heat exchanger, thereby reducing temperature fluctuations and the risk of ice blockage caused by long-distance flow. Furthermore, this structural design significantly improves subcooling when producing subcooled water and enhances superheating when producing superheated water.

[0139] By flexibly selecting the three positions mentioned above, the third fluid channel can optimize the heat exchanger's performance according to actual needs, ensuring that the outlet water temperature meets the diverse requirements of industrial applications while further reducing the probability of ice blockage or heat loss. This design significantly improves the heat exchanger's applicability and efficiency.

[0140] The heat exchanger 100 with adjustable outlet water temperature according to an embodiment of the present invention further includes at least one temperature sensor located within at least one first fluid channel. This temperature sensor is configured to monitor the temperature of the fluid within the first fluid channel in real time, providing the system with accurate temperature data for effective regulation of the outlet water temperature.

[0141] The advantage of placing a temperature sensor in the first fluid channel is that the first fluid channel is the water flow channel, and its temperature directly reflects the heat exchange efficiency and outlet water temperature of the heat exchanger. By embedding the temperature sensor in the first fluid channel, real-time water temperature changes can be detected, allowing for the timely detection of temperature anomalies, such as excessively low temperatures in the undercooling area, which may cause ice blockage, or temperatures in the overheating area that do not meet the target.

[0142] Furthermore, the temperature sensors provide fundamental data support for the linkage between the heat exchanger and the control system. Combined with the sensor data, the control system dynamically adjusts the temperature and flow rate of the fluids in the second and third fluid channels, achieving precise heat exchange control and ensuring that the outlet water temperature meets the target.

[0143] By incorporating these temperature sensors, the present invention not only significantly improves the control accuracy of the outlet water temperature, but also effectively enhances the safety and stability of system operation, preventing operational failures caused by ice blockage or overheating. This design is particularly suitable for industrial scenarios with strict temperature control requirements. The use of temperature sensors enhances the system's intelligence and provides reliable technical support for optimizing heat exchanger performance.

[0144] In one embodiment of the present invention, at least one temperature sensor is located within the projection of the third fluid channel onto the first fluid channel along the OZ direction, or at the upstream entrance of the projection of the third fluid channel onto the first fluid channel along the OZ direction. This design provides the system with more targeted temperature control data by accurately monitoring the temperature in key areas.

[0145] When a temperature sensor is placed within the projection of the third fluid channel onto the first fluid channel, it can monitor the temperature changes of the water flow in this area in real time. This location is often a key area for local heat exchange in the third fluid channel, and its temperature data directly reflects the local cooling or heating effect. By monitoring the temperature in this area, the system can promptly adjust the temperature or flow rate of the coolant or hot fluid in the third fluid channel, thereby optimizing heat exchange efficiency and ensuring stable and controllable water outlet temperature.

[0146] When the temperature sensor is located at the upstream inlet of the third fluid channel's projection on the first fluid channel, it functions to proactively detect the water's temperature before it enters the critical heat exchange area. By monitoring the temperature at the upstream inlet, the system can predict subsequent heat exchange requirements and adjust the heat exchanger's operating parameters to meet target temperatures. This arrangement is crucial for preventing runaway temperatures in overcooled or overheated areas, particularly during supercooled water preparation. It allows for timely identification of potential ice blockages and the implementation of appropriate measures.

[0147] The arrangement of these temperature sensors enables the heat exchanger of this invention to possess more precise temperature sensing capabilities, further enhancing the system's automated control capabilities. By monitoring the temperature in key areas or upstream inlets, heat exchange can be optimized while mitigating the risk of failures caused by ice blockage or temperature fluctuations. This design has significant practical value in industrial production, particularly in scenarios requiring stringent overcooling or overheating requirements.

[0148] In one embodiment of the present invention, the first fluid channel, the second fluid channel, and the third fluid channel are arranged in a specific repeating unit along the OZ direction. Specifically, the fluid channel arrangement includes the following two methods: first, the second fluid channel, the first fluid channel, the third fluid channel, and the first fluid channel are arranged as a repeating unit along the OZ direction; second, the second fluid channel, the first fluid channel, and the third fluid channel are arranged as a repeating unit along the OZ direction.

[0149] This repeating unit arrangement is designed to optimize the heat exchanger's structure and performance. By alternating the first fluid channel with the second and third fluid channels, the efficiency of cooling or heating the water within the first fluid channel is effectively improved. Specifically, the second fluid channel provides a base for cooling or heating the first fluid channel through heat exchange over a larger area, while the third fluid channel further regulates the outlet water temperature through localized compensatory heat exchange. This dual-channel alternating heat exchange design significantly improves overall heat exchange efficiency.

[0150] The repeating unit arrangement also offers the advantages of structural simplification and modularity. By repeatedly stacking specific units, not only can the manufacturing and assembly process be simplified, but the number of repeating units can also be flexibly adjusted to accommodate varying heat transfer requirements. For example, when preparing water with a higher degree of supercooling, the number of repeating units can be increased to enhance the overall cooling effect; whereas, to minimize the risk of ice blockage, the number of repeating units can be reduced to optimize the fluid flow path.

[0151] The present invention utilizes this repeating unit design to create a compact, highly efficient, and adaptable heat exchanger that can meet the needs of a variety of industrial applications. This arrangement, in particular, further enhances the reliability and flexibility of the system during the production of supercooled and superheated water.

[0152] The heat exchanger 100 with adjustable outlet water temperature of the present invention can be used to prepare metastable water such as supercooled water and superheated water. Based on this, the present invention also provides a metastable water preparation system and preparation method.

[0153] In one embodiment of the present invention, a metastable water preparation system is also provided, comprising a first refrigerant system for providing a first refrigerant, a second refrigerant system for providing a second refrigerant, a water system for providing water, a heat exchanger and a control system.

[0154] A pair of first inlets and outlets 13 are connected to the water system to form a water supply path, a pair of second inlets and outlets 23 are connected to the first brine system to form a circuit for the first brine, and a pair of third inlets and outlets 33 are connected to the second brine system to form a circuit for the second brine. A control system is communicatively connected to the first brine system, the water system, and the second brine system to control the start, stop, or flow of the water, the first brine, and the second brine.

[0155] The first brine system includes a first temperature control device and a first pump capable of providing a first brine. The second brine system includes a second temperature control device and a second pump capable of providing a second brine. The third brine system includes a third temperature control device and a third pump capable of providing a third brine. The heat exchanger is any of the above-described heat exchangers 100 with adjustable outlet water temperature.

[0156] In one embodiment, the first coolant system provides a first coolant at a temperature lower than the freezing point of water to reduce the temperature of the water. The second coolant system provides a second coolant at a specific temperature according to demand. The water temperature can be further reduced by providing a second coolant at a lower temperature than the first coolant in the second coolant system to obtain supercooled water at an even lower temperature, such as Figure 15 As shown in (a). Or the second coolant system increases the water temperature under certain circumstances. For example, when ice blockage occurs, a second coolant with a temperature higher than the freezing point of water is provided to provide heat to the water to relieve the ice blockage, such as Figure 15 As shown in (b).

[0157] The heat exchanger's three-channel design allows the water flow to receive cooling or heating simultaneously from both sides, achieving rapid and uniform heat exchange. The primary refrigerant system provides basic cooling, with its flow rate and temperature dynamically adjusted by the control system based on real-time feedback from the outlet water temperature. The secondary refrigerant system provides local precision control, with its temperature and flow rate flexibly adjusted based on actual needs.

[0158] The control system communicates with temperature sensors within the heat exchangers to obtain real-time water temperature data and dynamically controls the operating parameters of the primary and secondary refrigerant systems based on preset temperature targets. This design precisely controls outlet water temperature while effectively preventing ice blockage in undercooled areas and energy waste in overheated areas.

[0159] Preferably, when preparing supercooled water, the second coolant provides cooling to water at 0°C or below. When preparing superheated water, the second coolant provides heat to water at 100°C or above.

[0160] The system design in this embodiment achieves efficient and stable operation of the metastable water preparation system, meeting the stringent water temperature control requirements of industrial applications. This system is particularly suitable for water preparation scenarios requiring high degrees of subcooling or superheating, significantly improving water temperature control accuracy and system reliability.

[0161] In one embodiment of the present invention, Figure 15 As shown in (a), the temperature of the first brine is lower than the freezing point of water, and the temperature of the second brine provided by the second brine system is not higher than the temperature of the first brine provided by the first brine system, so as to generate supercooled water with a lower temperature.

[0162] In this embodiment, the first brine system delivers a first brine below the freezing point of water (0°C) into the heat exchanger via the second inlet and outlet chambers 232, exchanging heat with the water in the water system. The first brine, at its lower temperature, rapidly lowers the water temperature, bringing it close to or even to a supercooled state. The second brine system delivers a second brine at an even lower temperature into the heat exchanger via the third inlet and outlet chambers 332, further cooling the water flow and generating even lower supercooled water.

[0163] The design of this invention ensures that the water flow within the heat exchanger quickly and evenly reaches the target temperature range through the synergistic effect of the first and second brine systems. The first brine provides the base cooling capacity, while the second brine further precisely controls the water temperature, surpassing the cooling limits of traditional heat exchangers. By incorporating brine at different temperatures into the two brine systems, the heat exchanger can flexibly adapt to diverse industrial needs.

[0164] The control system communicates with temperature sensors to monitor the real-time temperature of the water flowing through the heat exchanger and dynamically adjusts the temperature and flow rate of the primary and secondary coolants. Keeping the secondary coolant temperature within a specified range ensures that the entire system effectively avoids heat backflow and temperature fluctuations, thereby improving heat exchange efficiency.

[0165] Through this embodiment, the metastable water production system of the present invention can generate supercooled water at relatively low temperatures, meeting the demand for deeply supercooled water in the chemical and power industries. It also significantly reduces the risk of ice blockage and improves the stability and reliability of system operation. This design not only meets the needs of industrial applications, but also improves the system's temperature control accuracy and energy efficiency.

[0166] In one embodiment of the present invention, Figure 15 As shown in (b), the temperature of the first coolant is lower than the freezing point of water, and the temperature of the second coolant provided by the second coolant system is higher than the freezing point of water, which is used to melt ice when ice blockage occurs.

[0167] In this embodiment, the first brine system delivers a first brine at a temperature below the freezing point of water (0°C) to the heat exchanger via the second inlet and outlet chambers 232, lowering the water temperature to produce supercooled water. However, if ice blockage occurs in the subcooled region of the water flow due to excessively low temperatures, the second brine system supplies a second brine at a temperature above the freezing point of water via the third inlet and outlet chambers 332, which is then delivered to the heat exchanger to resolve the ice blockage.

[0168] The secondary coolant transfers heat through the third fluid channel to the first fluid channel, gradually melting the frozen ice and restoring normal water flow. This design leverages the flexibility of the secondary coolant, enabling rapid intervention based on temperature monitoring during system operation to resolve system disruptions caused by ice blockage.

[0169] The control system monitors the water flow rate and flow rate at the heat exchanger outlet to determine if ice blockage has occurred. For example, if the water flow rate or water output per unit time falls below a preset value, the system identifies ice blockage and automatically activates the secondary refrigerant system. The control system dynamically adjusts the temperature and flow rate of the secondary refrigerant to ensure rapid and efficient defrosting while minimizing disruption to overall system operation.

[0170] Through this embodiment, the metastable water preparation system of the present invention can promptly defrost ice when ice blockage occurs, significantly improving the reliability and continuity of system operation. This design is suitable for applications requiring deeply subcooled water flows and provides a simple and efficient technical solution to the common ice blockage problem in industry.

[0171] In one embodiment of the present invention, the metastable water preparation system further includes a third brine system communicatively connected to the control system. The third brine system is connected in parallel with the second brine system and includes a third temperature control device and a third pump for providing the third brine. The third brine system is connected to the pair of third inlets and outlets 33 to form a circuit for the flow of the third brine. The temperature of the third brine provided by the third brine system is higher than the freezing point of water, thereby relieving ice blockages.

[0172] In this embodiment, the first refrigerant system inputs a first refrigerant at a temperature below the freezing point of water (0°C) through the second inlet and outlet chambers 232 for cooling. The second refrigerant system further compensates for the water's temperature drop through the third inlet and outlet chambers 332. However, to address potential ice blockage, a third refrigerant system is added in parallel with the second refrigerant system. When ice blockage occurs, the second refrigerant system is shut down and the third refrigerant system is activated. The third refrigerant, which is provided by the second refrigerant system and has a temperature above the freezing point of water, transfers heat to the ice-blocked area within the first fluid channel through the third fluid channel.

[0173] This design allows for either the secondary or tertiary coolant system to operate selectively. By introducing a suitably low-temperature fluid into the tertiary fluid channel, the temperature of the supercooled water is lowered. By introducing a suitably hot fluid into the tertiary fluid channel, frozen water in the ice-blocked area can be quickly melted, while preventing overheating or heat exchange failure in other areas due to high temperatures.

[0174] The control system monitors parameters such as the heat exchanger's water flow rate and flow rate to determine whether ice blockage has occurred. For example, if the heat exchanger's outlet flow rate falls below the rated value, or the water output per unit time falls below a preset value, the system identifies ice blockage and automatically switches to the third refrigerant system. The control system dynamically adjusts the temperature and flow rate of the third refrigerant to ensure a fast and efficient defrosting process.

[0175] By incorporating a parallel third coolant system, the metastable water preparation system of the present invention can flexibly respond to ice blockage and quickly resume normal operation. This design significantly improves system reliability while reducing downtime and maintenance costs caused by ice blockage, making it particularly suitable for industrial applications requiring deeply subcooled water flows.

[0176] In one embodiment of the present invention, Figure 15 As shown in (c), the temperature of the first refrigerant is higher than the boiling point of water, and the temperature of the second refrigerant provided by the second refrigerant system is not lower than the temperature of the first refrigerant provided by the first refrigerant system, so as to generate water with a higher degree of superheat.

[0177] In this embodiment, the first brine system inputs a first brine at a temperature above the boiling point of water (100°C) through the second inlet and outlet chambers 232 to raise the water temperature. This heat is transferred to the water flow through the first fluid channel of the heat exchanger, rapidly raising the water temperature to near or above the boiling point. The second brine system provides a second brine at a temperature no lower than that of the first brine through the third inlet and outlet chambers 332 to further compensate for the heat, ensuring that the water temperature exceeds the boiling point and generating highly superheated water.

[0178] In this invention, the heat compensation function of the second refrigerant system effectively prevents the water from experiencing temperature drops or vaporization due to long-distance flow within the heat exchanger. Furthermore, by ensuring that the temperature of the second refrigerant is no less than that of the first refrigerant, the system ensures heat exchange efficiency while avoiding temperature fluctuations within the first fluid channel and ensuring temperature stability of the water flow.

[0179] The control system monitors the real-time temperature of the water flowing through the heat exchanger through communication with temperature sensors, dynamically adjusting the temperature and flow rate of the primary and secondary coolants as needed. The secondary coolant is particularly useful in scenarios requiring high-precision temperature control. For example, when preparing superheated water, it can achieve a higher superheat by compensating for the temperature rise, meeting the high-temperature water requirements of specific industrial sectors.

[0180] Through this embodiment, the metastable water production system of the present invention can generate highly superheated water, meeting the high-temperature water flow requirements of scientific research, chemical engineering, and other fields, while significantly improving the accuracy and reliability of the system's temperature control. This design not only broadens the system's application range but also further enhances its stability and operational efficiency.

[0181] The present invention also provides a method for preparing metastable water, comprising the following steps: starting a first refrigerant system and a water system, and obtaining the outlet water temperature after passing through a heat exchanger after running for a predetermined time; judging whether the outlet water temperature reaches a preset temperature, and if so, the first refrigerant system and the water system maintain the current operating state; if not, starting a second refrigerant system to additionally cool or heat the water to achieve target temperature control.

[0182] In this embodiment, the first coolant system inputs a first coolant through the second inlet and outlet chambers 232. Depending on actual needs, the temperature of the first coolant can be below the freezing point of water to cool the water, or above the boiling point of water to heat the water. The water system inputs water through the first inlet and outlet chambers 132, exchanging heat with the first coolant to bring the water temperature close to a preset value.

[0183] The system uses a temperature sensor to monitor the water temperature at the heat exchanger outlet in real time and feeds this data back to the control system for evaluation. When the water temperature reaches the preset target, the system maintains the current operating parameters. If the water temperature does not reach the target, the control system activates the secondary refrigerant system, injecting a secondary refrigerant through the third inlet and outlet chambers 332 to further cool or heat the water.

[0184] The secondary refrigerant system selects the appropriate temperature and flow rate based on the needs, working in conjunction with the primary refrigerant system to compensate for any insufficient heat exchange within the primary fluid channel, ensuring the outlet water temperature precisely reaches the target value. The control system dynamically adjusts the operating parameters of the secondary refrigerant to dynamically regulate the water temperature, ensuring the efficiency and stability of the entire heat exchange process.

[0185] Through this embodiment, the metastable water production method of the present invention can quickly determine and adjust water temperature, meeting the stringent temperature control requirements of industrial production. This method is not only suitable for producing subcooled water, but can also be flexibly applied to the production of superheated water, significantly improving the system's operating efficiency and temperature control accuracy while reducing energy consumption and failure rates.

[0186] In one embodiment of the present invention, the following steps are also included: calculating the heat or cold required to be provided to the water based on the difference between the water outlet temperature and the preset temperature, and controlling the temperature and / or flow rate of the second refrigerant provided by the second refrigerant system based on the heat or cold.

[0187] In this embodiment, the system activates the first brine system and the water system, bringing the water flow close to the target temperature through heat exchange through the heat exchanger. The control system uses a temperature sensor to monitor the water temperature at the heat exchanger outlet in real time, comparing the current outlet temperature with a preset temperature to generate temperature differential data. Based on this temperature differential, the control system calculates the required heat or cooling compensation and dynamically adjusts the operating parameters of the second brine system.

[0188] When the current water temperature is detected to be below the preset target, the system activates the secondary coolant system, supplying coolant at a lower temperature through the third inlet and outlet chambers 332 for additional cooling. Conversely, when preparing superheated water, if the water temperature falls below the target, the secondary coolant system provides a higher temperature coolant to compensate for the temperature increase. The flow rate and temperature of the secondary coolant are precisely adjusted based on the demand values ​​calculated by the control system to achieve efficient temperature compensation.

[0189] This approach, combining temperature monitoring with heat calculation, not only optimizes the efficiency of the secondary coolant but also significantly improves the overall temperature control accuracy of the system. Dynamically adjusting the coolant's temperature and flow rate allows the outlet water temperature to reach the preset target value in the shortest possible time, while avoiding energy waste caused by over-adjustment.

[0190] Through this embodiment, the metastable water production method of the present invention can meet the demand for highly precise temperature control and is particularly suitable for industrial scenarios with strict requirements for supercooled or superheated water. This method improves heat exchange efficiency while reducing system operating costs, providing a highly efficient and reliable solution for temperature control.

[0191] In one embodiment of the present invention, the method for preparing metastable water also includes the following steps: the temperature of the first refrigerant is lower than the freezing point of water, and whether ice blockage occurs is detected. If ice blockage occurs, the third refrigerant system connected in parallel with the second refrigerant system to the third inlet and outlet chambers 332 is started, and the third refrigerant with a temperature higher than the freezing point of water is input into the heat exchanger.

[0192] Among them, detecting whether ice blockage occurs includes: detecting the outlet water flow rate of the heat exchanger, if the outlet water flow rate is lower than the rated flow rate, it is determined that ice blockage occurs; and / or detecting the outlet water volume of the heat exchanger per unit time, if the outlet water volume is less than the rated water volume, it is determined that ice blockage occurs; and / or, detecting the outlet water temperature of the heat exchanger, when the outlet water temperature is not less than 0°C, it is determined that ice blockage occurs.

[0193] In this embodiment, the first refrigerant system inputs a first refrigerant below the freezing point of water through the second inlet and outlet chambers 232 to cool the water and produce supercooled water. During operation, the system monitors the water flow in real time using temperature sensors, flow meters, and flow rate sensors. If the water flow rate out of the heat exchanger or the water output per unit time is detected to be below a preset value, the control system determines that ice blockage has occurred.

[0194] When ice blockage occurs, the second refrigerant system is shut down and a third refrigerant system, connected in parallel with the second, is automatically activated. A third refrigerant with a temperature above the freezing point of water is fed into the heat exchanger through the third inlet and outlet chambers 332. The third refrigerant transfers heat to the ice-blocked area through the third fluid channel, gradually melting the frozen water and restoring normal water flow.

[0195] During the operation of the third brine system, the control system dynamically adjusts its temperature and flow rate to ensure rapid ice melting while avoiding overheating of the water flowing in other areas. Once ice melting is complete, the control system shuts down the third brine system and resumes normal operation of the first and second brine systems to continue producing supercooled water.

[0196] Through the above-mentioned method, the present invention can quickly respond and resolve ice blockage when it occurs, significantly improving the reliability and stability of the metastable water preparation system. This design is particularly suitable for industrial applications under deep supercooling conditions. While meeting high supercooling requirements, it also solves the problem of operational interruptions caused by ice blockage, providing technical support for the continuous operation of the system.

[0197] The present invention also provides a method for preparing supercooled water, comprising the following steps: starting a first refrigerant system and a water system, wherein the temperature of the first refrigerant is lower than the freezing point of water; after running for a predetermined time, monitoring whether ice blockage occurs in the heat exchanger, and if ice blockage occurs, starting a second refrigerant system to provide a second refrigerant with a temperature higher than the freezing point of water; if ice blockage does not occur, the first refrigerant system and the water system maintain the current operating state.

[0198] The method for detecting whether ice blockage occurs is as described above and will not be repeated here.

[0199] In this embodiment, the first refrigerant system inputs a first refrigerant below the freezing point of water (0°C) through the second inlet and outlet chambers 232 to cool the water and produce supercooled water. The water system inputs water through the first inlet and outlet chambers 132, exchanging heat with the first refrigerant system to reduce the water temperature to the target subcooling temperature. During operation, the system monitors the water output status of the heat exchanger in real time using temperature sensors, flow rate sensors, and flow meters.

[0200] When the heat exchanger's outlet water flow rate or water output per unit time is detected to be below a preset value, the control system determines ice blockage has occurred and automatically activates the secondary coolant system. A secondary coolant, at a temperature above the freezing point of water, is fed through the third inlet and outlet chambers 332. This secondary coolant transfers heat to the ice-blocked area, gradually melting the frozen water and restoring normal system operation. The control system dynamically adjusts the temperature and flow rate of the secondary coolant to ensure rapid ice melting while preventing overheating in other areas.

[0201] When no ice blockage is detected, the system maintains the current operating status of the first refrigerant system and the water system and continues to prepare supercooled water, thereby reducing energy consumption and improving operating efficiency.

[0202] Through this method, the present invention can flexibly address ice blockage during the supercooled water preparation process, ensuring stable system operation under high supercooling conditions. This design offers significant advantages in avoiding system downtime and improving operational reliability and continuity, making it particularly suitable for industrial scenarios with stringent requirements for temperature control accuracy and system reliability.

[0203] It should be understood that although this specification is described in terms of implementation methods, not every implementation method contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each implementation method can also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0204] The series of detailed descriptions listed above are only specific descriptions of feasible implementation methods of the present invention. They are not intended to limit the scope of protection of the present invention. Any equivalent implementation methods or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A heat exchanger with adjustable water outlet temperature, characterized in that: include: a plurality of first fluid channel sheets, comprising a first heat exchange area, a pair of first inlets and outlets communicating with the first heat exchange area, a pair of first communication areas separated from the first heat exchange area by a first dam, and a pair of first conduction areas; a plurality of second fluid channel sheets, comprising a second heat exchange region, a pair of second inlets and outlets communicating with the second heat exchange region, a pair of second through-regions separated from the second heat exchange region by a second dam, and a pair of second conduction regions; a plurality of third fluid channel sheets, comprising a third heat exchange region, a pair of third inlets and outlets communicating with the third heat exchange region, a pair of third through-regions separated from the third heat exchange region by a third dam, and a pair of third communicating regions; the area of ​​the third heat exchange region is smaller than that of the first heat exchange region; Among them, the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are stacked along the OZ direction, and the first fluid channel sheet is located between the second fluid channel sheet and the third fluid channel sheet; along the OZ direction, a pair of first inlets and outlets are respectively connected with a pair of second through-through areas and a pair of third through-through areas to form a first inlet and outlet cavity, a pair of second inlets and outlets are respectively connected with a pair of first connecting areas and a pair of third connecting areas to form a second inlet and outlet cavity, and a pair of third inlets and outlets are respectively connected with a pair of first conductive areas and a pair of second conductive areas to form a third inlet and outlet cavity.

2. The heat exchanger with adjustable outlet water temperature according to claim 1, characterized in that: The area of ​​the second heat exchange zone is 90% to 110% of the area of ​​the first heat exchange zone, and the area of ​​the third heat exchange zone is 1 / 2 to 1 / 3 of the area of ​​the first heat exchange zone.

3. The heat exchanger with adjustable outlet water temperature according to claim 2, characterized in that: The first inlet and outlet include a first inlet and a first outlet; The projection of the third heat exchange zone along the OZ direction on the first fluid channel sheet is located within the first heat exchange zone, and the distance between the projection and the first inlet is shorter than the distance between the projection and the first outlet; Alternatively, a projection of the third heat exchange zone along the OZ direction on the first fluid channel sheet is located within the first heat exchange zone, and the projection is located in a middle area of ​​the first heat exchange zone; Alternatively, the projection of the third heat exchange zone along the OZ direction on the first fluid channel plate is located within the first heat exchange zone, and the distance between the projection and the first outlet is shorter than the distance between the projection and the first inlet.

4. The heat exchanger with adjustable outlet water temperature according to claim 1, characterized in that: A plurality of microstructures are provided in the first heat exchange zone, the second heat exchange zone and the third heat exchange zone; the arrangement density of the microstructures in the third heat exchange zone is greater than the arrangement density of the microstructures in the first heat exchange zone and the second heat exchange zone.

5. The heat exchanger with adjustable outlet water temperature according to claim 1, characterized in that: The first heat exchange zone is recessed from the first surface to the second surface of the first fluid channel sheet, a pair of first inlets and outlets are respectively arranged on both sides of the first heat exchange zone along the OX direction, and the first inlets and outlets are connected to the first heat exchange zone through a first transition zone; a pair of first connecting areas are respectively arranged on both sides of the first heat exchange zone along the OY direction, a pair of first conducting areas are located on one side of the first heat exchange zone along the OX direction, and a pair of first conducting areas are respectively arranged on both sides of the first inlet and outlet along the OY direction; The second heat exchange zone is recessed from the first surface to the second surface of the second fluid channel sheet, a pair of second inlets and outlets are respectively arranged on both sides of the second heat exchange zone along the OY direction, and the second inlets and outlets are connected to the second heat exchange zone through a second transition zone; a pair of second through-passing zones are respectively arranged on both sides of the second heat exchange zone along the OX direction, a pair of second conduction zones are located on one side of the second heat exchange zone along the OX direction, and a pair of second conduction zones are respectively arranged on both sides of the second through-passing zone along the OY direction; The third heat exchange zone is recessed from the first surface to the second surface of the third fluid channel plate, a pair of third through-zones are respectively arranged on both sides of the third heat exchange zone along the OX direction, a pair of third connecting zones are respectively arranged on both sides of the third heat exchange zone along the OY direction, a pair of third inlets and outlets are located on one side of the third heat exchange zone along the OX direction, and a pair of third inlets and outlets are respectively arranged on both sides of the third through-zone along the OY direction, and the third inlets and outlets are connected to the third heat exchange zone through a third transition zone.

6. The heat exchanger with adjustable outlet water temperature according to claim 1, characterized in that: The heat exchanger with adjustable outlet water temperature further includes at least one temperature sensor located on at least one of the first fluid channel sheets.

7. The heat exchanger with adjustable outlet water temperature according to claim 6, characterized in that: At least one of the temperature sensors is located within the projection of the third heat exchange zone along the OZ direction on the first fluid channel sheet. Alternatively, at least one of the temperature sensors is located at an upstream inlet of a projection of the third heat exchange zone along the OZ direction on the first fluid channel sheet.

8. The heat exchanger with adjustable outlet water temperature according to any one of claims 1 to 7, characterized in that: The first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are stacked in sequence along the OZ direction, with the second fluid channel sheet, the first fluid channel sheet, the third fluid channel sheet, and the first fluid channel sheet as a repeating unit; Alternatively, the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are stacked in sequence along the OZ direction, with the second fluid channel sheet, the first fluid channel sheet, and the third fluid channel sheet serving as a repeating unit.

9. A metastable water preparation system, comprising a first brine system for providing a first brine, a second brine system for providing a second brine, a water system for providing water, a heat exchanger, and a control system, characterized in that: The heat exchanger is a heat exchanger with adjustable water outlet temperature as described in any one of claims 1 to 8, a pair of the first inlet and outlet are connected to the water system to form a path for the water to flow, a pair of the second inlet and outlet are connected to the first refrigerant system to form a circuit for the first refrigerant to flow, a pair of the third inlet and outlet are connected to the second refrigerant system to form a circuit for the second refrigerant to flow, and the control system is communicatively connected to the first refrigerant system, the water system, and the second refrigerant system.

10. The metastable water preparation system according to claim 9, characterized in that: The temperature of the first brine is lower than the freezing point of water, and the temperature of the second brine is not higher than that of the first brine.

11. The metastable water preparation system according to claim 10, characterized in that: The metastable water preparation system also includes a third coolant system that provides a third coolant. The third coolant system is connected to a pair of the third inlets and outlets to form a circuit for the flow of the third coolant. The temperature of the third coolant is higher than the freezing point of water.

12. The metastable water preparation system according to claim 9, characterized in that: The temperature of the first coolant is lower than the freezing point of water, and the temperature of the second coolant is higher than the freezing point of water.

13. The metastable water preparation system according to claim 9, characterized in that: The temperature of the first brine is higher than the boiling point of water, and the temperature of the second brine is not lower than the temperature of the first brine.

14. A method for preparing metastable water, implemented based on the metastable water preparation system according to any one of claims 9 to 13, characterized in that: The metastable water preparation method comprises the following steps: Start the first refrigerant system and water system, and after running for a predetermined time, obtain the outlet water temperature; Determine whether the outlet water temperature after the heat exchanger reaches the preset temperature. If so, the first refrigerant system and the water system maintain the current operating state; if not, start the second refrigerant system to provide cooling or heating for the water.

15. The method for preparing metastable water according to claim 14, characterized in that: According to the difference between the outlet water temperature and the preset temperature, the heat or cold amount required to be provided to the water is calculated, and the temperature and / or flow rate of the second refrigerant provided by the second refrigerant system is controlled based on the heat or cold amount.

16. The method for preparing metastable water according to claim 14, wherein: The temperature of the first refrigerant is lower than the freezing point of water, and ice blockage is detected. If so, a third refrigerant system connected in parallel with the second refrigerant system to the third inlet and outlet chamber is started to input the third refrigerant with a temperature higher than the freezing point of water into the heat exchanger; Detection of ice blockage includes: Check the outlet water flow rate of the heat exchanger. If the outlet water flow rate is lower than the rated flow rate, it is determined that ice blockage has occurred; and / or detecting the water output of the heat exchanger per unit time, and if the water output is less than the rated water output, ice blockage is determined to have occurred; And / or, the outlet water temperature of the heat exchanger is detected, and when the outlet water temperature is not less than 0° C., it is determined that ice blockage has occurred.

17. A method for preparing supercooled water, implemented based on the metastable water preparation system according to claim 9, characterized in that: The steps include: Start the first coolant system and the water system, and the temperature of the first coolant is lower than the freezing point of water; After running for a predetermined time, monitor whether the heat exchanger is blocked by ice. If so, start the second coolant system to provide a second coolant with a temperature higher than the freezing point of water; if not, the first coolant system and the water system maintain their current operating status; The detection of whether ice blockage occurs includes: detecting the outlet flow rate of the heat exchanger, and determining that ice blockage occurs if the outlet flow rate is lower than the rated flow rate; and / or detecting the water output of the heat exchanger per unit time, and if the water output is less than the rated water output, ice blockage is determined to have occurred; And / or, the outlet water temperature of the heat exchanger is detected, and when the outlet water temperature is not less than 0° C., it is determined that ice blockage has occurred.

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