Heat exchanger with adjustable outlet water temperature and application thereof

Abstract

The application discloses a heat exchanger with adjustable outlet water temperature and application thereof. The heat exchanger with adjustable outlet water temperature comprises a first fluid passage sheet, a second fluid passage sheet and a third fluid passage sheet. The first fluid passage sheet comprises a first heat exchange area, a pair of first inlets and outlets, a pair of first communication areas and a pair of first conducting areas. The second fluid passage sheet comprises a second heat exchange area, a pair of second inlets and outlets, a pair of second through areas and a pair of second conducting areas. The third fluid passage sheet comprises a third heat exchange area, a pair of third inlets and outlets, a pair of third through areas and a pair of third communication areas. The area of the third heat exchange area is smaller than the area of the first heat exchange area. The fluid passage sheets are arranged in a stacking mode along an O-Z direction. The first inlets and outlets of the first fluid passage sheet are communicated with the second through areas and the third through areas of the second fluid passage sheet and the third fluid passage sheet to form a first inlet and outlet cavity. The second inlets and outlets are communicated with the first communication areas and the third communication areas to form a second inlet and outlet cavity. The third inlets and outlets are communicated with the first conducting areas and the second conducting areas to form a third inlet and outlet cavity.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration, in particular to a heat exchanger with adjustable outlet water temperature and application thereof, especially in a metastable water preparation system and method. BACKGROUND

[0002] Metastable water is a critical state of water, including supercooled water and superheated water, which has a wide range of applications in chemical industry, power industry, metallurgy industry and other industries.

[0003] Supercooled water refers to liquid water with a temperature below the freezing point (0℃) without freezing. The preparation of supercooled water has problems such as easy ice blocking and insufficient supercooling degree, which restricts the application of supercooled water.

[0004] Superheated water refers to water that remains in a liquid state when the water temperature exceeds the boiling point (100℃). The preparation of superheated water also has problems such as insufficient superheating degree and unadjustable temperature.

[0005] The heat exchanger is the core component for preparing supercooled water and superheated water. Taking the preparation of supercooled water as an example, a plate heat exchanger is usually used as the exchange place for water and non-freezing liquid. However, the temperature is too low, which easily causes ice blocking; and the temperature is too high, which cannot meet the demand; and the outlet water temperature cannot be controlled according to the needs.

[0006] Therefore, it is necessary to provide an improved heat exchanger with adjustable outlet water temperature and application thereof to solve the above technical problems. SUMMARY

[0007] The present application aims to provide a heat exchanger with adjustable outlet water temperature, a metastable water preparation system and method having the same. By arranging first fluid passage sheets, second fluid passage sheets and third fluid passage sheets in the heat exchanger and reasonably configuring the area ratio and arrangement mode thereof, the preparation efficiency of supercooled water and superheated water is significantly improved, the risk of ice blocking is reduced, and the demand for flexible and adjustable outlet water temperature is met.

[0008] To achieve the above-mentioned application purposes, the present application adopts the following technical solutions:

[0009] The application discloses a heat exchanger with adjustable outlet water temperature, comprising: a plurality of first fluid channel sheets, each of which comprises a first heat exchange area, a pair of first inlets and outlets in communication with the first heat exchange area, a pair of first communication areas spaced apart from the first heat exchange area by a first dam, and a pair of first through areas; a plurality of second fluid channel sheets, each of which comprises a second heat exchange area, a pair of second inlets and outlets in communication with the second heat exchange area, a pair of second through areas spaced apart from the second heat exchange area by a second dam, and a pair of second through areas; a plurality of third fluid channel sheets, each of which comprises a third heat exchange area, a pair of third inlets and outlets in communication with the third heat exchange area, a pair of third through areas spaced apart from the third heat exchange area by a third dam, and a pair of third communication areas; the area of the third heat exchange area is smaller than the area of the first heat exchange area; wherein the first fluid channel sheets, the second fluid channel sheets and the third fluid channel sheets are arranged in layers along the O-Z direction, and the first fluid channel sheets are located between the second fluid channel sheets and the third fluid channel sheets; along the O-Z direction, the pair of first inlets and outlets are in communication with the pair of second through areas and the pair of third through areas to form a first inlet and outlet cavity, the pair of second inlets and outlets are in communication with the pair of first communication areas and the pair of third communication areas to form a second inlet and outlet cavity, and the pair of third inlets and outlets are in communication with the pair of first through areas and the pair of second through areas to form a third inlet and outlet cavity.

[0010] In some embodiments, the area of the second heat exchange area is 90% to 110% of the area of the first heat exchange area, and the area of the third heat exchange area is 1 / 2 to 1 / 3 of the area of the first heat exchange area.

[0011] In some embodiments, the pair of first inlets and outlets comprises a first inlet and a first outlet; the projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the distance from the projection to the first inlet is smaller than the distance from the projection to the first outlet; or, the projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the projection is located in the middle region of the first heat exchange area; or, the projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the distance from the projection to the first outlet is smaller than the distance from the projection to the first inlet.

[0012] In some embodiments, a plurality of microstructures are arranged in the first heat exchange area, the second heat exchange area and the third heat exchange area; the arrangement density of the microstructures in the third heat exchange area is greater than the arrangement density of the microstructures in the first heat exchange area and the second heat exchange area.

[0013] In some embodiments, the first heat exchange region is recessed from the first surface to the second surface of the first fluid channel sheet, a pair of the first inlets and outlets are arranged on two sides of the first heat exchange region along the O-X direction, and the first inlets and outlets are in communication with the first heat exchange region through a first transition region; a pair of the first communication regions are arranged on two sides of the first heat exchange region along the O-Y direction, a pair of the first through regions are arranged on one side of the first heat exchange region along the O-X direction, and a pair of the first through regions are arranged on two sides of the first inlets and outlets along the O-Y direction; the second heat exchange region is recessed from the first surface to the second surface of the second fluid channel sheet, a pair of the second inlets and outlets are arranged on two sides of the second heat exchange region along the O-Y direction, and the second inlets and outlets are in communication with the second heat exchange region through a second transition region; a pair of the second through regions are arranged on two sides of the second heat exchange region along the O-X direction, a pair of the second through regions are arranged on one side of the second heat exchange region along the O-X direction, and a pair of the second through regions are arranged on two sides of the second through regions along the O-Y direction; the third heat exchange region is recessed from the first surface to the second surface of the third fluid channel sheet, a pair of the third through regions are arranged on two sides of the third heat exchange region along the O-X direction, a pair of the third communication regions are arranged on two sides of the third heat exchange region along the O-Y direction, and a pair of the third inlets and outlets are arranged on one side of the third heat exchange region along the O-X direction, and a pair of the third inlets and outlets are arranged on two sides of the third through regions along the O-Y direction, and the third inlets and outlets are in communication with the third heat exchange region through a third transition region.

[0014] In some embodiments, the heat exchanger with adjustable outlet water temperature further comprises at least one temperature sensor arranged on at least one of the first fluid channel sheets.

[0015] In some embodiments, the at least one temperature sensor is arranged within the projection of the third heat exchange region on the first fluid channel sheet along the O-Z direction, or the at least one temperature sensor is arranged at an upstream inlet of the projection of the third heat exchange region on the first fluid channel sheet along the O-Z direction.

[0016] In some embodiments, the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are arranged in a sequence of 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 along the O-Z direction, or the first fluid channel sheet, the second fluid channel sheet, and the third fluid channel sheet are arranged in a sequence of 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 along the O-Z direction.

[0017] A metastable water preparation system, comprising a first coolant system providing a first coolant, a second coolant system providing a second coolant, a water system providing water, a heat exchanger, and a control system, the heat exchanger being any one of the heat exchangers with adjustable outlet water temperature, a pair of first inlets and outlets connected with the water system to form a path for water flow, a pair of second inlets and outlets connected with the first coolant system to form a loop for the first coolant flow, a pair of third inlets and outlets connected with the second coolant system to form a loop for the second coolant flow, and the control system being communicatively connected with the first coolant system, the water system, and the second coolant system.

[0018] In some embodiments, the first coolant has a temperature lower than the freezing point of water, and the second coolant has a temperature not higher than the temperature of the first coolant.

[0019] In some embodiments, the metastable water preparation system further comprises a third coolant system providing a third coolant, the third coolant system being connected with the pair of third inlets and outlets to form a loop for the third coolant flow, and the third coolant having a temperature higher than the freezing point of water.

[0020] In some embodiments, the first coolant has a temperature lower than the freezing point of water, and the second coolant has a temperature higher than the freezing point of water.

[0021] In some embodiments, the first coolant has a temperature higher than the boiling point of water, and the second coolant has a temperature not lower than the temperature of the first coolant.

[0022] A metastable water preparation method based on any one of the metastable water preparation systems, the metastable water preparation method comprising the following steps: starting the first coolant system and the water system, obtaining the temperature of the outlet water after running for a predetermined time; determining whether the temperature of the outlet water after the heat exchanger reaches a preset temperature, if yes, maintaining the current running state of the first coolant system and the water system; if no, starting the second coolant system to provide cooling or heating for the water.

[0023] In some embodiments, the amount of heat or cold required to be provided to the water is calculated according to the difference between the temperature of the outlet water and the preset temperature, and the temperature and / or flow rate of the second coolant provided by the second coolant system is controlled based on the amount of heat or cold.

[0024] In some embodiments, the temperature of the first refrigerant is lower than the freezing point of water. If ice blockage occurs, a third refrigerant system, connected in parallel with the second refrigerant system to the third inlet / outlet chamber, is activated to introduce a third refrigerant with a temperature higher than the freezing point of water into the heat exchanger. The detection of ice blockage includes: detecting the outlet water flow rate of the heat exchanger; if the outlet water flow rate is lower than the rated flow rate, ice blockage is determined to have occurred; 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, ice blockage is determined to have occurred; and / or, detecting the outlet water temperature of the heat exchanger; if the outlet water temperature is not less than 0°C, ice blockage is determined to have occurred.

[0025] A method for preparing supercooled water, based on the aforementioned metastable water preparation system, 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; 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 their current operating state; wherein, 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 has occurred; 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 has occurred; and / or, detecting the outlet water temperature of the heat exchanger; if the outlet water temperature is not less than 0°C, it is determined that ice blockage has occurred.

[0026] Compared with the prior art, the beneficial effects of the present invention are as follows: by setting a first fluid channel plate, a second fluid channel plate, and a third fluid channel plate in the heat exchanger, and rationally configuring the area ratio and arrangement of their heat exchange zones, the present invention significantly improves the preparation efficiency of supercooled water and superheated water, while reducing the risk of ice blockage and meeting the need for flexible and adjustable outlet water temperature. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the structure of a heat exchanger with adjustable outlet water temperature according to one embodiment of the present invention.

[0028] Figure 2 for Figure 1 Partially exploded diagram.

[0029] Figure 3 for Figure 1 A schematic diagram of the first fluid channel plate in the image.

[0030] Figure 4 for Figure 1 A schematic diagram of the second fluid channel plate in the diagram.

[0031] Figure 5 for Figure 1 A schematic diagram of the third fluid channel plate in the diagram.

[0032] Figure 6 Structure diagram of the third fluid passage sheet in another embodiment of the present application.

[0033] Figure 7 Structure diagram of the third fluid passage sheet in another embodiment of the present application.

[0034] Figure 8 Structure diagram of the third fluid passage sheet in another embodiment of the present application.

[0035] Figure 9 Structure diagram of the third fluid passage sheet in another embodiment of the present application.

[0036] Figure 10 Partial exploded view of the heat exchanger with adjustable outlet water temperature in another embodiment of the present application.

[0037] Figure 11 Structure diagram of the first fluid passage sheet in another embodiment of the present application.

[0038] Figure 12 Structure diagram of the second fluid passage sheet in another embodiment of the present application.

[0039] Figure 13 Structure diagram of the third fluid passage sheet in another embodiment of the present application.

[0040] Figure 14 Structure diagram of the third fluid passage sheet in another embodiment of the present application. Figure 13 Cross-sectional view at A-A, B-B, C-C in FIG.

[0041] Figure 15 Temperature variation diagram for preparing metastable water by using the heat exchanger with adjustable outlet water temperature in the present application.

[0042] In the figure, the dotted line is only for showing the boundary of the area, 100 - heat exchanger with adjustable outlet water temperature, 1 - first fluid passage sheet, 11 - first heat exchange area, 12 - first dam, 13 - first inlet and outlet, 132 - first inlet and outlet cavity, 14 - first transition area, 15 - first communication area, 16 - first conduction area, 2 - second fluid passage sheet, 21 - second heat exchange area, 22 - second dam, 23 - second inlet and outlet, 232 - second inlet and outlet cavity, 24 - second transition area, 25 - second through area, 26 - second conduction area, 3 - third fluid passage sheet, 31 - third heat exchange area, 32 - third dam, 33 - third inlet and outlet, 332 - third inlet and outlet cavity, 34 - third transition area, 35 - fourth heat exchange area, 36 - fourth transition area, 37 - third through area, 38 - third communication area, 4 - microstructure. DETAILED DESCRIPTION

[0043] The application will be described in detail below with reference to the specific embodiments shown in the drawings. However, these embodiments do not limit the application, and the structural, method, or functional changes made by those of ordinary skill in the art based on these embodiments are included in the protection scope of the application.

[0044] In various diagrams of the application, the sizes of some structures or parts are exaggerated relative to other structures or parts for ease of illustration, and thus only serve to illustrate the basic structure of the subject matter of the application.

[0045] The first, second, third, and the like descriptions of the application are only for distinguishing features and do not have the limitation of quantity and order. Taking the fluid channel sheet as an example, the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 refer to three kinds of fluid channel sheets. The "fluid channel sheet" without the "first, second, third" limitation in the text means the general term of the three kinds of fluid channel sheets.

[0046] For ease of description, the plane (or called extension plane) where the fluid channel sheet is located is the O-XY plane, and the thickness direction of the fluid channel sheet is the O-Z direction. The coordinate system O-XYZ is established, and the O-X direction, the O-Y direction, and the O-Z direction are perpendicular to each other.

[0047] Please refer to Figures 1 to 14 The application provides a heat exchanger 100 with adjustable outlet water temperature, which includes 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 sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 all extend in the O-XY plane, and the thickness direction of the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 is consistent with the O-Z direction.

[0048] Each kind of fluid channel sheet has a heat exchange area and a communication structure matched with its function, which is used to build the overall fluid channel layout of the heat exchanger.

[0049] Please refer to Figures 1 to 3 、 Figure 11 The first fluid channel sheet 1 includes a first heat exchange area 11, a pair of first inlet and outlet ports 13 in communication with the first heat exchange area 11, a pair of first communication areas 15 spaced apart from the first heat exchange area 11 by a first dam 12, and a pair of first conduction areas 16 spaced apart 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 flows out of the first heat exchange area 11 through the other first inlet and outlet port 13. The first dam 12 is arranged around the first heat exchange area 11 to prevent the first fluid from flowing out of the first heat exchange area 11.

[0050] Please refer to Figures 1 to 2 、 Figure 4 and Figure 12As shown, the second fluid passage sheet 2 comprises a second heat exchange region 21, a pair of second inlets and outlets 23 communicating with the second heat exchange region 21, a pair of second through regions 25 spaced apart from the second heat exchange region 21 by a second dam 22, and a pair of second communication regions 26 spaced apart from the second heat exchange region 21 by the second dam 22. The second fluid enters the second heat exchange region 21 from one of the second inlets and outlets 23, and flows out of the second heat exchange region 21 from the other of the second inlets and outlets 23. The second dam 22 is arranged around the second heat exchange region 21 to prevent the second fluid from flowing out of the second heat exchange region 21.

[0051] As shown in Figures 1 to 2 , Figures 5 to 9 and Figure 13 As shown, the third fluid passage sheet 3 comprises a third heat exchange region 31, a pair of third inlets and outlets 33 communicating with the third heat exchange region 31 through a third transition region 34, a pair of third through regions 37 spaced apart from the third heat exchange region 31 by a third dam 32, and a pair of third communication regions 38 spaced apart from the third heat exchange region 31 by the third dam 32. The third fluid enters the third heat exchange region 31 from one of the third inlets and outlets 33, and flows out of the third heat exchange region 31 from the other of the third inlets and outlets 33. The third dam 32 is arranged around the third heat exchange region 31 to prevent the third fluid from flowing out of the third heat exchange region 31.

[0052] As shown in Figures 1 to 14 As shown, the first fluid passage sheet 1, the second fluid passage sheet 2, and the third fluid passage sheet 3 are arranged in layers along the O-Z direction, and a fluid passage is formed between adjacent fluid passage sheets.

[0053] The first heat exchange region 11 of the first fluid passage sheet 1 and the adjacent fluid passage sheet form a first fluid passage. A pair of first inlets and outlets 13 respectively communicate with a pair of second through regions 25 on the second fluid passage sheet 2 and a pair of third through regions 37 on the third fluid passage sheet 3 in the O-Z direction to form a pair of first inlet and outlet cavities 132. The first fluid enters one of the first inlet and outlet cavities 132, then flows into the first heat exchange region 11 from the corresponding first inlet and outlet 13, then flows out through the other first inlet and outlet 13 and the first inlet and outlet cavity 132, and exchanges heat with the fluid in the first heat exchange region 11 and the adjacent fluid passage.

[0054] The second fluid passage piece 2 forms a second fluid passage between the second heat exchange area 21 and the adjacent fluid passage piece, and a pair of second inlets and outlets 23 correspondingly communicate with the pair of first communication areas 15 on the first fluid passage piece 1 and the pair of third communication areas 38 on the third fluid passage piece 3 along the O-Z direction 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 into the second heat exchange area 21 through the corresponding second inlet and outlet 23, and then flows out through the other second inlet and outlet 23 and the second inlet and outlet cavity 232, and exchanges heat with the fluid in the second heat exchange area 21 and the adjacent fluid passage.

[0055] The third fluid passage piece 3 forms a third fluid passage between the third heat exchange area 31 and the adjacent fluid passage piece, and a pair of third inlets and outlets 33 correspondingly communicate with the pair of first communication areas 16 on the first fluid passage piece 1 and the pair of second communication areas 26 on the second fluid passage piece 2 along the O-Z direction to form a pair of third inlet and outlet cavities 332. The third fluid enters one of the third inlet and outlet cavities 332, then flows into the third heat exchange area 31 through the corresponding third inlet and outlet 33, and then flows out through the other third inlet and outlet 33 and the third inlet and outlet cavity 332, and exchanges heat with the fluid in the third heat exchange area 31 and the adjacent fluid passage.

[0056] The first fluid passage piece 1 is located between the second fluid passage piece 2 and the third fluid passage piece 3, and through the stacking arrangement and structural design of the three fluid passage pieces, the first fluid can obtain cold or heat from the second fluid and the third fluid on both sides, thereby realizing efficient heat exchange.

[0057] It should be noted that the "through area", "communication area" and "communication area" can pass through the fluid passage piece along the thickness direction, or can not pass through the fluid passage piece, but remove the sheet material of the corresponding area to form the inlet and outlet cavity after the stacking.

[0058] When stacking, the heat exchange areas of all fluid passage pieces are located on the same side of the corresponding fluid passage piece along the O-Z direction and are aligned along the O-Z direction, so that heat exchange is realized between the fluids flowing through the heat exchange areas.

[0059] In an embodiment of the present application, the design of the inlet and outlet and the through area position of each fluid passage piece is as follows.

[0060] The first fluid passage sheet 1 is designed as follows: the first fluid passage sheet 1 comprises a first surface and a second surface arranged oppositely along a thickness direction, the first heat exchange area 11 is recessed from the first surface to the side where the second surface is located (or is recessed to form), or the first dam 12 is protruded from the first surface to the direction away from the second surface. The first inlet and outlet 13 communicates with the first heat exchange area 11 through the first transition area 14, the first fluid flows through the first transition area 14 and the first heat exchange area 11, the first dam 12 is located at the first surface and surrounds the first heat exchange area 11 and the first transition area 14, preventing the first fluid from flowing out of the first heat exchange area 11 and the first transition area 14.

[0061] The first heat exchange area 11 is located in the middle, a pair of first inlets and outlets 13 are arranged on both sides of the first heat exchange area 11 along the O-X direction, a pair of first communication areas 15 are arranged on both sides of the first heat exchange area 11 along the O-Y direction, a pair of first conduction areas 16 are located on one side of the first heat exchange area 11 along the O-X direction, and a pair of first conduction areas 16 are arranged on both sides of the first inlet and outlet 13 along the O-Y direction. A pair of first inlets and outlets 13 are arranged on both sides of the first heat exchange area 11 along the O-X direction, so that water can be uniformly distributed and flow through the first fluid passage.

[0062] The second fluid passage sheet 2 is designed as follows: the second fluid passage sheet 2 comprises a first surface and a second surface arranged oppositely along a thickness direction, the second heat exchange area 21 is recessed from the first surface to the side where the second surface is located (or is recessed to form), or the second dam 22 is protruded from the first surface to the direction away from the second surface. The second fluid flows through the second transition area 24 and the second heat exchange area 21, the second dam 22 is located at the first surface and surrounds the second heat exchange area 21 and the second transition area 24, preventing the second fluid from flowing out of the second heat exchange area 21 and the second transition area 24.

[0063] The second heat exchange area 21 is located in the middle, a pair of second inlets and outlets 23 are arranged on both sides of the second heat exchange area 21 along the O-Y direction, a pair of second through areas 25 are arranged on both sides of the second heat exchange area 21 along the O-X direction, a pair of second conduction areas 26 are located on one side of the second heat exchange area 21 along the O-X direction, and a pair of second conduction areas 26 are arranged on both sides of the second through area 25 along the O-Y direction. The second fluid passage sheet 2 is obtained by rotating the first fluid passage sheet 1 by 90° around the center, and the first coolant flows through the second heat exchange area 21 along the O-Y direction, forming a straight flow with water.

[0064] The third fluid channel sheet 3 is designed as follows: the third fluid channel sheet 3 comprises a first surface and a second surface arranged opposite in the thickness direction, and the third heat exchange area 31 is recessed from the first surface to the side where the second surface is located (or is recessed to form), or the third dam 32 is protrudingly arranged from the first surface to the direction away from the second surface. The third fluid flows through the third transition area 34 and the third heat exchange area 31, and the third dam 32 is located at the first surface and surrounds the third heat exchange area 31 and the third transition area 34 to prevent the third fluid from flowing out of the third heat exchange area 31 and the third transition area 34.

[0065] The third heat exchange area 31 is located in a local area in the middle, a pair of third through areas 37 are arranged on both sides of the third heat exchange area 31 along the O-X direction, a pair of third communication areas 38 are arranged on both sides of the third heat exchange area 31 along the O-Y direction, and a pair of third inlets and outlets 33 are located on one side of the third heat exchange area 31 along the O-X direction, and the pair of third inlets and outlets 33 are arranged on both sides of the third through area 37 along the O-Y direction.

[0066] The structure design optimizes the flow paths of each fluid channel by reasonably distributing the positions of the inlets and outlets, through areas, communication areas, and conducting areas on the fluid channel sheet, achieving efficient heat exchange between fluids. The positions of the inlets and outlets, through areas, and communication areas ensure the connectivity of each fluid between the channel sheets, avoiding the cross-flow of fluids inside the heat exchanger.

[0067] Through the above arrangement, each heat exchange area can form an independent fluid circuit with the corresponding inlet and outlet, through area, communication area, and conducting area, effectively reducing the fluid flow resistance in the heat exchanger and optimizing the heat transfer path of the fluid. In addition, this design also enhances the modularity of the heat exchanger, facilitating production and maintenance.

[0068] In this embodiment, the reasonable arrangement of the inlets and outlets, through areas, communication areas, and conducting areas ensures the compactness and efficiency of the heat exchanger structure, while further improving the working performance and applicability of the heat exchanger, especially in the working condition of efficiently preparing supercooled water or superheated water, which has a significant advantage.

[0069] The first fluid, the second fluid, and the third fluid can be any fluid. In this application, the first fluid is the fluid to be heated or cooled, and the second fluid and the third fluid provide cold or heat for the first fluid.

[0070] In one embodiment of the application, 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 refrigerants, and the second fluid channel sheet 2 and the third fluid channel sheet 3 are respectively designed for the flow of the first refrigerant and the second refrigerant.

[0071] In an embodiment of the present application, the first fluid passage sheet 1, the second fluid passage sheet 2 and the third fluid passage sheet 3 are sequentially stacked in the O-Z direction in a specific repeating unit. Specifically, the arrangement of these fluid passage sheets includes but is not limited to the following two.

[0072] In an embodiment, as shown in FIG. 1, the second fluid passage sheet 2, the first fluid passage sheet 1 and the third fluid passage sheet 3 are sequentially stacked in the O-Z direction as a repeating unit. The second coolant compensates for the cold or heat on one side and the first coolant compensates for the cold or heat on the other side, both of which can improve the degree of supercooling or superheating of water. Figure 2

[0073] In another embodiment, as shown in FIG. 2, the second fluid passage sheet 2, the first fluid passage sheet 1, the third fluid passage sheet 3 and the first fluid passage sheet 1 are sequentially stacked in the O-Z direction as a repeating unit. The first coolant is on both sides of the water, the second coolant is on both sides of the water, and the first coolant and the second coolant directly provide cold or heat to the water, which has high heat exchange efficiency. Figure 10 The above-mentioned stacking design of the passage sheet aims to achieve efficient heat transfer between fluids through a modular structural arrangement, and to achieve rapid and stable temperature regulation.

[0074] Through this structured stacking design, the heat exchanger of the present application not only realizes modular production and assembly, reduces manufacturing cost, but also improves the flexibility and stability of system operation. This arrangement is suitable for various industrial application scenarios for preparing high supercooling water or high superheating water, further broadening the application range of the heat exchanger, and significantly improving its performance and reliability.

[0075] On the basis of the above design, as shown in FIG. 3, the area of the third heat exchange area 31 is smaller than the area of the first heat exchange area 11, and the first fluid is partially compensated, which can further regulate the outlet water temperature to meet the diversified application requirements.

[0076] Figures 2 to 14 In an embodiment of the present application, the area of the second heat exchange area 21 is 90% to 110%, preferably 97% to 107%, preferably 95% to 105%, preferably 93% to 103%, preferably the same as the area of the first heat exchange area 11. The area of the third heat exchange area 31 is 1 / 2 to 1 / 3 of the area of the first heat exchange area 11. The design of the area ratio is mainly based on the function and role of each fluid passage in the heat exchange process to optimize the heat exchange efficiency and fluid flow performance.

[0077] In an embodiment of the present application, the area of the second heat exchange area 21 is 90% to 110%, preferably 97% to 107%, preferably 95% to 105%, preferably 93% to 103%, preferably the same as the area of the first heat exchange area 11. The area of the third heat exchange area 31 is 1 / 2 to 1 / 3 of the area of the first heat exchange area 11. The design of the area ratio is mainly based on the function and role of each fluid passage in the heat exchange process to optimize the heat exchange efficiency and fluid flow performance.

[0078] ​​The area of the second heat exchange zone 21 is similar to that of the first heat exchange zone 11 (90%-110%), which ensures that uniform and efficient heat exchange can be achieved between the first fluid channel and the second fluid channel. This area ratio matching can effectively reduce the pressure difference and avoid fluid flow imbalance caused by excessive area difference, thereby improving the stability of system operation.

[0079] The area of the third heat exchange zone 31 is smaller, only 1 / 2 to 1 / 3 of the area of the first heat exchange zone 11. The design is to achieve more precise temperature regulation in a local area. Smaller area can concentrate heat exchange in a specific area, avoiding the problem of ice blockage or temperature fluctuation caused by full-flow heat exchange. Specifically, in the preparation of subcooled water, this area ratio can more effectively control the subcooling degree of water flow; in the preparation of superheated water, it can achieve higher superheating effect by locally strengthening the temperature.

[0080] Through the reasonable design of the areas of the second heat exchange zone 21 and the third heat exchange zone 31, the present application further optimizes the safety and flexibility of the system while maintaining the efficiency of the heat exchanger, meeting the needs of subcooling or superheating water preparation in different industrial scenarios. This area matching design can also reduce manufacturing difficulty and cost, while ensuring long-term stable operation of the fluid system.

[0081] The positional relationship between the third heat exchange zone 31 and the first heat exchange zone 11 is very important. In an embodiment of the present application, a pair of first inlets and outlets 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 O-Z direction, and the projection position is one of the following three cases.

[0082] The first case, as shown in Figure 5 , Figure 6 , Figure 13 , the projection is located in the first heat exchange zone 11, and the distance from the first outlet is less than the distance from the first inlet. The projection position of the third heat exchange zone 31 is close to the first outlet, which can further reduce the temperature or increase the temperature when the water is about to flow out of the heat exchanger, thereby ensuring that the temperature of the outlet water flow reaches the target value. This arrangement is particularly suitable for working conditions that require high subcooling or high superheating, and its proximity to the outlet can significantly reduce the residence time of low-temperature or high-temperature fluid in the heat exchanger, thereby reducing the risk of ice blockage or heat loss.

[0083] The second case, as shown in Figure 7 , the projection is located in the first heat exchange zone 11, and the projection is located in the middle region of the first heat exchange zone 11; its role is to provide temperature compensation for the middle section of the water flow. When the water flow passes through the first half of the first fluid channel, its temperature has been significantly reduced, and the cold compensation in the middle region can further regulate the temperature, thereby achieving more precise subcooling or superheating effect.

[0084] In the third case, please refer to Figure 8 The projection is located in the first heat exchange zone 11, and the distance from the first inlet is less than the distance from the first outlet. The projection position of the third heat exchange zone 31 is close to the first inlet, and by strengthening the local heat exchange at the first fluid passage inlet, the temperature of the entering water flow can be quickly reduced, thereby improving the efficiency of the entire heat exchanger. This arrangement is suitable for fluids with high initial temperature and can significantly improve the cooling speed.

[0085] Through the flexible design of the above three projection positions, the present application realizes the optimized distribution of local heat exchange of the third fluid passage, and can adjust the working mode and effect of the heat exchanger according to actual needs. The local arrangement position of the third heat exchange zone 31 can be flexibly selected, which significantly improves the applicability and flexibility of the heat exchanger, and at the same time can maintain high efficiency and stable performance in different application scenarios.

[0086] In addition, based on the embodiment shown in Figures 5 to 7 , Figure 13 , as shown in Figure 9 , the third fluid passage sheet 3 further comprises a fourth heat exchange zone 35 and a pair of fourth inlets and outlets in communication with the fourth heat exchange zone 35 through a fourth transition zone 36. The fourth heat exchange zone 35 and the fourth transition zone 36 are provided with microstructures 4.

[0087] The structure, position, etc. of the third heat exchange zone 31 can be as shown in Figures 5 to 7 , Figure 13 . The third heat exchange zone 31 and the fourth heat exchange zone 35 are arranged along the O-X direction, and heat the water flow from different positions in the direction of the water flow. The pair of fourth inlets and outlets are located on the other side of the third heat exchange zone 31 along the O-X direction, i.e. the fourth inlets and outlets and the third inlets and outlets 33 are respectively located at both ends along the O-X direction, and the pair of fourth inlets and outlets are respectively arranged on both sides of the third through zone 37 along the O-Y direction. Based on this, the first fluid passage sheet 1 and the second fluid passage sheet 2 are respectively provided with fourth through zones corresponding to the fourth inlets and outlets to form fourth inlet and outlet cavities for inputting the fourth fluid into the fourth heat exchange zone 35.

[0088] Based on the third fluid passage sheet 3 shown in Figure 9 , after stacking, one of the third heat exchange zone 31 and the fourth heat exchange zone 35 is close to the first inlet, and the other is close to the first outlet. The third fluid and the fourth fluid can be provided at the same time or at different times as needed; and the temperature of the third fluid and the fourth fluid can be adjusted as needed.

[0089] For example, in the case of sub-cooled 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 below the freezing point, which increases the cooling rate of the water flow and reduces the temperature of the water flow; the temperature of the third fluid is below the freezing point, which further reduces the temperature of the sub-cooled water. In another embodiment, the temperature of the fourth fluid is below the freezing point, which increases the cooling rate of the water flow and reduces the temperature of the water flow; the temperature of the third fluid is above the freezing point, which provides the third fluid to thaw ice when ice blockage occurs.

[0090] 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 above the boiling point, which increases the heating rate of the water flow and increases the temperature; the temperature of the third fluid is above the boiling point, which further increases the temperature of the superheated water.

[0091] Based on any of the above designs, in one embodiment of the present application, 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 concave from the first surface in the thickness direction, forming a structure similar to a "river channel" with the surrounding dam, and the fluid flows in the heat exchange zone.

[0092] A plurality of microstructures 4 are arranged in the heat exchange zone of each of the three fluid channel sheets. The microstructures 4 are used to enhance the heat exchange capacity in the fluid channel, and at the same time, in combination with the adjacent fluid channel sheet, to form support and improve pressure resistance.

[0093] The microstructures 4 are mainly formed by forming protrusions in the heat exchange zone. The height of the microstructures 4 is consistent with the dam, and can be combined with the adjacent fluid channel sheet. These microstructures 4 significantly improve the heat exchange efficiency by disturbing the boundary layer of the fluid and increasing the contact area between the fluid and the channel wall.

[0094] In one embodiment, the microstructures protrude from the heat exchange zone to the side where the first surface is located. When a sheet material with good heat conductivity such as stainless steel is used to form the fluid channel sheet, a patterned etching process is usually used to form the heat exchange zone, that is, the part of the heat exchange zone where no structure is arranged is etched and removed from the first surface, and the part that is not etched constitutes the dam and the microstructures 4.

[0095] In the heat exchange zone of the third fluid channel sheet 3, the density of the microstructures 4 is greater than the density of the microstructures 4 in the heat exchange zones of the first fluid channel sheet 1 and the second fluid channel sheet 2. The density of the microstructures 4 in the first fluid channel sheet 1 and the second fluid channel sheet 2 is relatively low, which is designed to provide basic heat exchange capacity while reducing flow resistance and ensuring the smoothness of the water and the first coolant flow. The density of the microstructures 4 in the third fluid channel sheet 3 is higher, which is used to strengthen the local heat exchange effect and accurately control the temperature of the water in the first fluid channel.

[0096] The design of high-density arrangement of the microstructure 4 in the third fluid channel sheet 3 can more effectively utilize the cold or heat of the second cold carrier, and quickly realize local cooling or heating. This design not only improves the response speed of the heat exchanger, but also can accurately control the outlet water temperature, especially in the preparation of subcooled water, the local area is concentrated with cold supplement, which reduces the flow distance of the subcooled water and significantly reduces the probability of ice blockage.

[0097] By reasonably distributing the density of the microstructure 4 in each fluid channel sheet, the application realizes the balance between the heat exchange efficiency and the fluid flow performance of each channel, and further improves the overall heat exchange capacity of the system through the enhanced heat exchange capacity of the third fluid channel sheet 3, to meet the requirements of temperature regulation accuracy and efficiency under different working conditions. This design not only optimizes the performance, but also maintains the compactness of the structure and the feasibility of manufacturing.

[0098] In addition, the area between the heat exchange area and the inlet and outlet of each fluid channel sheet is referred to as the transition area, which corresponds to the dam of the adjacent fluid channel sheet along the O-Z direction. The transition area is also provided with microstructure 4, and the microstructure 4 of the transition area is larger than that of the heat exchange area to improve the bonding force of the transition area and ensure the pressure resistance at the inlet and outlet. Specifically, in the first fluid channel sheet 1, the first heat exchange area 11 and the first inlet and outlet 13 are connected through the first transition area 14, and the first transition area 14 is provided with microstructure 4, and the microstructure 4 of the first transition area 14 is larger than that of the first heat exchange area 11. In the second fluid channel sheet 2, the second heat exchange area 21 and the second inlet and outlet 23 are connected through the second transition area 24, and the second transition area 24 is provided with microstructure 4, and the microstructure 4 of the second transition area 24 is larger than that of the second heat exchange area 21. In the third fluid channel sheet 3, the third heat exchange area 31 and the third inlet and outlet 33 are connected through the third transition area 34, and the third transition area 34 is provided with microstructure 4, and the microstructure 4 of the third transition area 34 is larger than that of the third heat exchange area 31.

[0099] In addition, as shown in Figures 11 to 14 , the edge of the transition area of each fluid channel sheet towards the inlet and outlet (or the edge of the inlet and outlet) is provided with a first guide surface 6, and the first guide surface 6 is located on the side surface of the fluid channel sheet where the heat exchange area is arranged, which guides the water into the transition area. The edge of the dam of each fluid channel sheet towards the through area or the through area is provided with a second guide surface 6', and the second guide surface 6' is located on the side surface which is not provided with the heat exchange area, which guides the fluid into the corresponding fluid channel. By arranging the first guide surface 6 and the second guide surface 6', the resistance of the fluid entering the fluid channel can be reduced.

[0100] It should be noted that Figures 1 to 10 the fluid channel sheet in may also be provided with a first guide surface 6 and a second guide surface 6' at the corresponding position.

[0101] In an embodiment of the present application, the heat exchanger 100 with adjustable outlet water temperature further comprises at least one temperature sensor located on the at least one first fluid passage sheet 1. The temperature sensor is used to monitor the temperature of the fluid in the first fluid passage sheet 1 in real time, to ensure that the heat exchanger can accurately regulate the outlet water temperature to meet the needs of different working conditions.

[0102] The purpose of arranging the temperature sensor on the first fluid passage sheet 1 is to directly perceive the dynamic changes of the water flow temperature, and these temperature data can truly reflect the heat exchange effect in the first fluid passage. Based on these data, the control system can adjust the flow rate and temperature of the cold carrier in the second fluid passage and the third fluid passage in real time to achieve more accurate heat exchange control.

[0103] The temperature sensor is preferably arranged at a key heat exchange area of the first fluid passage sheet 1, such as a position close to the water inlet, the middle area or the outlet. Temperature monitoring at the inlet can reflect the initial state of the incoming water flow, monitoring at the middle area can capture the local heat exchange effect, and monitoring at the outlet can directly judge whether the final outlet water temperature meets the expected target. This arrangement not only accurately monitors the water temperature change, but also effectively prevents ice blockage or overheating caused by temperature abnormalities.

[0104] By arranging the temperature sensor on the first fluid passage sheet 1, the heat exchanger of the present application realizes intelligent temperature monitoring and control function, significantly improving the operation safety and temperature control accuracy of the system. This design is suitable for industrial scenes with strict temperature requirements, such as preparation of subcooled water or superheated water in chemical, power and metallurgical fields, effectively meeting the needs of efficient, safe and stable operation.

[0105] In an embodiment of the present application, the at least one temperature sensor is located within the projection of the third heat exchange area 31 on the first fluid passage sheet 1 along the O-Z direction, or the at least one temperature sensor is located at an upstream inlet of the projection of the third heat exchange area 31 on the first fluid passage sheet 1 along the O-Z direction. By monitoring the temperature of these specific areas, the present application realizes accurate control of the key heat exchange position.

[0106] When the temperature sensor is located within the projection of the third heat exchange area 31, its main function is to monitor the temperature change of the water flow in this local heat exchange area in real time. This position is the area where local heat exchange occurs between the third fluid passage and the first fluid passage. By obtaining the temperature data of this area, it can directly evaluate whether the third fluid needs to compensate for the temperature of the water, or evaluate the regulation effect of the third fluid on the water temperature in the first fluid passage. This arrangement plays an important role in optimizing the local heat exchange efficiency and ensuring the stability of the water temperature in the first fluid passage.

[0107] When the temperature sensor is located at the upstream inlet of the third heat exchange zone 31, its function is to sense the water temperature state in advance before entering the local heat exchange area. By monitoring the temperature at the upstream inlet, the trend of water temperature change can be detected in time, the heat exchange demand can be predicted, and the flow rate or temperature of the cold carrier in the third fluid channel can be dynamically adjusted, thereby optimizing the overall heat exchange capacity.

[0108] The arrangement of the above-mentioned temperature sensor not only provides accurate temperature data for the system, but also effectively reduces the risk of ice blocking when preparing supercooled water, or enhances the warming effect when preparing superheated water. By monitoring the temperature at a specific location, the intelligent level and operating efficiency of the heat exchanger are further improved, which can meet the needs of efficient and stable industrial applications. This arrangement is suitable for scenarios that require highly precise temperature control, providing important technical support for optimizing the performance of the heat exchanger.

[0109] On the basis of any of the above designs, the size of the fluid channel sheet is described. The fluid channel sheet is generally square in shape, with an outer contour size L1 in the O-X or O-Y direction not greater than 50 mm, for example, 20-40 mm. The flow distance of the fluid in the heat exchanger is short, which can reduce the risk of ice blocking, etc. In an embodiment, the size L2 of the heat exchange zone in the fluid flow direction is 30 mm±5 mm, and the fluid is disturbed violently in a short distance, improving the heat exchange efficiency and heat exchange capacity.

[0110] The fluid channel sheet is made of sheet material such as stainless steel sheet with a thickness of about 0.2 mm. The thickness (size in the O-Z direction) at the location of the dam and the microstructure is consistent with the thickness of the stainless steel sheet, and the thickness (size in the O-Z direction) at the location in the heat exchange zone where no microstructure is provided 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 are separated by thin walls for heat exchange, with high heat exchange efficiency and good heat exchange capacity.

[0111] In an embodiment, the heat exchange zone is etched from the first surface to the second surface using photolithography, chemical etching, etc., and the height of the dam and the microstructure protruding upward from the heat exchange zone is the difference between the thickness of the sheet material and the thickness of the heat exchange zone.

[0112] Based on the design of the above fluid channel sheet, the structure and method of the compact heat exchanger are briefly described.

[0113] A 2-5 mm thick plate is used as the end plate in the O-Z direction, and the first fluid channel sheet 1, the second fluid channel sheet 2, and the third fluid channel sheet 3 are sequentially arranged between the two end plates, and then all the sheet materials are combined into one whole by using atomic diffusion bonding process.

[0114] In some embodiments, asFigures 11 to 13 As shown, the first fluid passage sheet 1, the second fluid passage sheet 2 and the third fluid passage sheet 3 are provided with positioning holes 7 correspondingly. By means of the positioning pin passing through the positioning hole 7, the first fluid passage sheet 1, the second fluid passage sheet 2 and the third fluid passage sheet 3 can be aligned in the O-Z direction.

[0115] It should be noted that the positioning pin can be fixed to one of the end plates, and the first fluid passage sheet 1, the second fluid passage sheet 2 and the third fluid passage sheet 3 are stacked on the end plate, and the other end plate provided with the positioning hole is covered on the fluid passage sheet. The positioning holes can also be provided on both end plates, and the end plates and all fluid passage sheets are positioned by the positioning pin.

[0116] Figures 1 to 10 The fluid passage sheet in the above embodiment can also be provided with the positioning hole, and the positioning hole is arranged at the edge. Of course, when the positioning hole is not arranged, the positioning can also be realized by means of the positioning tool.

[0117] The atomic diffusion bonding process can adopt the existing technology, and can but not limited to adopt the vacuum furnace for atomic diffusion bonding.

[0118] The end plate is welded on the side of the first inlet and outlet cavity 132, the pair of second inlet and outlet cavities 232 and the pair of third inlet and outlet cavities 332 away from the heat exchange area, and the inlet and outlet holes are arranged on the end plate in communication with the inlet and outlet cavities; and the pipe is assembled at the inlet and outlet holes, so as to be connected with the external fluid system.

[0119] The application also provides another heat exchanger 100 with adjustable outlet water temperature, which comprises 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.

[0120] The heat exchange core comprises a plurality of first fluid passages, a plurality of second fluid passages and a plurality of third fluid passages arranged in the O-Z direction. In this embodiment, the heat exchange core is an integrated structure, which is consistent with the structure of the whole combined with the first fluid passage sheet 1, the second fluid passage sheet 2 and the third fluid passage sheet 3.

[0121] The integrated structure can but not limited to be formed by using the 3D printing technology.

[0122] The first fluid passage is designed for water flow, and the pair of first inlet and outlet cavities 132 are in communication with the plurality of first fluid passages for water inlet and outlet. The structure of the first fluid passage is consistent with the structure of the first transition zone 14 and the first heat exchange zone 11 of the first fluid passage sheet 1.

[0123] Specifically, the first fluid channel includes a first channel portion connected with the first inlet and outlet cavity 132, and a first heat exchange portion located between the pair of first channel portions. The first channel portion is arranged in accordance with the first transition zone 14, and the first heat exchange portion is arranged in accordance with the first heat exchange zone 11.

[0124] The second fluid channel is designed for the flow of the second coolant, and a pair of second inlet and outlet cavities 232 are in communication with a plurality of second fluid channels for the inlet and outlet of the first coolant. The structure of the second fluid channel is consistent with the structure of the second transition zone 24 and the second heat exchange zone 21 of the second fluid channel sheet 2 described above.

[0125] Specifically, the second fluid channel includes a second channel portion connected with the second inlet and outlet cavity 232, and a second heat exchange portion located between the pair of second channel portions. The second channel portion is arranged in accordance with the second transition zone 24, and the second heat exchange portion is arranged in accordance with the second heat exchange zone 21.

[0126] The third fluid channel is designed for the flow of the second coolant, and a pair of third inlet and outlet cavities 332 are in communication with a plurality of third fluid channels for the inlet and outlet of the second coolant. The structure of the third fluid channel is consistent with the structure of the third transition zone 34 and the third heat exchange zone 31 of the third fluid channel sheet 3 described above, which will not be repeated here.

[0127] Specifically, the third fluid channel includes a third channel portion connected with the third inlet and outlet cavity 332, and a third heat exchange portion located between the pair of third channel portions. The third channel portion is arranged in accordance with the third transition zone 34, and the third heat exchange portion is arranged in accordance with the third heat exchange zone 31.

[0128] Through this zoning 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.

[0129] 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 rapidly cooling or heating, and improving the preparation efficiency of subcooled water or superheated water.

[0130] The area of the third heat exchange channel is smaller than that of the first heat exchange channel, and its design aims to locally compensate the temperature of the water in the first fluid channel, rather than involving all the flow channels in heat exchange. This design not only avoids the problem of ice blockage caused by the long flow path of subcooled water, but also allows flexible adjustment of the outlet water temperature by reasonable control of the layout of the third fluid channel.

[0131] The above structure and function ensure that the heat exchanger can efficiently prepare subcooled water or superheated water, while providing flexibility in adjusting the outlet water temperature.

[0132] Specifically, the area of the passage portion is much smaller than that of the heat exchange portion, and the heat exchange within the passage portion is limited. The "area of the third heat exchange passage is smaller than that of the first heat exchange passage" mainly refers to the area of the third heat exchange portion is smaller than that of the first heat exchange portion.

[0133] In an embodiment of the present application, the area of the second heat exchange portion is 90% to 110% of the area of the first heat exchange portion, and the area of the third heat exchange portion is 1 / 2 to 1 / 3 of the area of the first heat exchange portion. The design of this area ratio aims to optimize the heat exchange efficiency and pressure balance between fluids.

[0134] The area of the second heat exchange portion is close to or slightly deviates from the area of the first heat exchange portion. Through such a matching relationship, it is ensured that the first fluid passage can efficiently absorb cold energy from the second fluid passage without causing a decrease in heat exchange efficiency or an increase in pressure loss due to a large area difference. At the same time, this area ratio helps to avoid imbalance of fluid flow rate, thereby improving the overall performance of the heat exchanger.

[0135] The area of the third heat exchange portion is relatively small, only 1 / 2 to 1 / 3 of the area of the first heat exchange portion. Its design is based on the local compensation heat exchange function of the third fluid passage, rather than full-flow heat exchange. This area limitation can effectively control the fluid flow and heat exchange of the third fluid passage, avoid the ice block phenomenon caused by excessive cooling during the preparation of supercooled water, and at the same time ensure that stable local warming effect can be provided during the preparation of superheated water.

[0136] Through the above-mentioned optimization design of the area ratio, the heat exchanger of the present application significantly reduces the risk of ice block while maintaining high-efficiency heat exchange, thereby improving the reliability and stability of system operation. This area relationship is particularly suitable for application scenarios of preparing supercooled water or superheated water, and can be appropriately adjusted according to actual needs to meet specific requirements under different industrial conditions.

[0137] In an embodiment of the present application, the first inlet and outlet cavities 132 include a first inlet cavity and a first outlet cavity, and the projection position of the third fluid passage on the first fluid passage along the O-Z direction has one of the following three cases: one, the projection is located within the first fluid passage, and the distance from the first inlet cavity is smaller than the distance from the first outlet cavity; two, the projection is located in the middle region of the first fluid passage; three, the projection is located within the first fluid passage, and the distance from the first outlet cavity is smaller than the distance from the first inlet cavity.

[0138] The position of the third fluid channel is important for optimizing the heat exchange effect. When the projection of the third fluid channel is located near the first inlet cavity, its function is mainly to provide cooling for the water in the initial stage of entering the heat exchanger, quickly reducing the temperature of the water, thereby improving the efficiency of preparing cooling water. When the projection of the third fluid channel is located in the middle region of the first fluid channel, it can supplement the cold or heat when the water flows through the middle region, further adjusting the outlet water temperature. In the third case, the projection of the third fluid channel is located near the first outlet cavity, which can strengthen the heat exchange when the water is about to flow out of the heat exchanger, further reducing the water temperature in the supercooling region, or increasing the outlet temperature when preparing superheated water.

[0139] Preferably, the third fluid channel is closer to the first outlet cavity. This arrangement can ensure that the flow path of low-temperature or high-temperature water in the heat exchanger is shorter, thereby reducing the temperature change and the risk of ice blockage caused by long-distance flow. In addition, in the preparation of super-cooled water, this structural design can significantly improve the supercooling degree, while in the preparation of superheated water, it can enhance the superheating effect.

[0140] By flexible selection of the above three positions, the third fluid channel can optimize the performance of the heat exchanger according to the actual needs, ensure that the outlet water temperature meets the diversified requirements of industrial applications, and further reduce the probability of ice blockage or heat loss. This design significantly improves the applicability and efficiency of the heat exchanger.

[0141] The outlet water temperature adjustable heat exchanger 100 according to the embodiment of the present application further comprises at least one temperature sensor located in at least one first fluid channel. The temperature sensor is used to monitor the temperature of the fluid in the first fluid channel in real time, providing accurate temperature data for the system to effectively regulate the outlet water temperature.

[0142] The advantage of placing the temperature sensor in the first fluid channel is that the first fluid channel is the flow channel of the water, and its temperature directly reflects the heat exchange effect of the heat exchanger and the state of the outlet water temperature. By embedding the temperature sensor inside the first fluid channel, the temperature change of the water flow can be collected in real time, so that temperature abnormalities can be found in time, such as ice blockage caused by too low temperature in the supercooling region, or the temperature in the superheating region not reaching the expected target.

[0143] In addition, the setting of the temperature sensor provides basic data support for the linkage of the heat exchanger and the control system. Combined with sensor data, the control system can dynamically adjust the temperature and flow rate of the fluid in the second fluid channel and the third fluid channel, realizing accurate heat exchange control, thereby ensuring that the outlet water temperature meets the target requirements.

[0144] Through the arrangement of the temperature sensor, the application can not only significantly improve the control accuracy of the outlet water temperature, but also effectively improve the safety and stability of the system operation, avoiding operation 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 intelligent level of the system, providing reliable technical support for optimizing the performance of heat exchangers.

[0145] In an embodiment of the application, at least one temperature sensor is located within the projection of the third fluid channel on the first fluid channel along the O-Z direction, or at the upstream inlet of the projection of the third fluid channel on the first fluid channel along the O-Z direction. This design provides more targeted temperature regulation data for the system through precise monitoring of the temperature in the key area.

[0146] When the temperature sensor is arranged within the projection of the third fluid channel on the first fluid channel, it can monitor the temperature changes of the water flow in this area in real time. This position is usually the key area for local heat exchange of the third fluid channel, and its temperature data can directly reflect the effect of local cooling or heating. By monitoring the temperature in this area, the system can timely adjust the temperature or flow rate of the refrigerant or hot fluid in the third fluid channel, thereby optimizing the heat exchange efficiency and ensuring stable and controllable outlet water temperature.

[0147] When the temperature sensor is located at the upstream inlet of the projection of the third fluid channel on the first fluid channel, its function is to sense the temperature state of the water flow before it enters the key heat exchange area. By monitoring the temperature at the upstream inlet, the system can predict the subsequent heat exchange requirements and adjust the operating parameters of the heat exchanger to meet the target temperature requirements. This arrangement is of great significance in preventing temperature runaway in supercooling or overheating areas, especially when preparing supercooling water, potential ice blockage risks can be detected in time and appropriate measures can be taken.

[0148] The arrangement of the above-mentioned temperature sensor enables the heat exchanger of the application to have more accurate temperature sensing capability, providing a guarantee for further improving the automation control level of the system. By monitoring the temperature in the key area or the upstream inlet, the heat exchange effect can be better optimized, and the risk of failure caused by ice blockage or temperature fluctuations can be reduced. This design has significant practical value in industrial production, especially in scenarios with strict requirements for supercooling or overheating conditions.

[0149] In an embodiment of the application, the first fluid channel, the second fluid channel and the third fluid channel are arranged along the O-Z direction in a specific repeating unit. Specifically, the arrangement of the fluid channels includes the following two types: one is that the second fluid channel, the first fluid channel, the third fluid channel and the first fluid channel are arranged along the O-Z direction as a repeating unit; the other is that the second fluid channel, the first fluid channel and the third fluid channel are arranged along the O-Z direction as a repeating unit.

[0150] The arrangement of the repeating units is designed to optimize the structure and performance of the heat exchanger. By alternating the contact of the first fluid channel with the second fluid channel and the third fluid channel, the cooling or heating efficiency of the water in the first fluid channel can be effectively improved. Specifically, the second fluid channel provides basic cooling or heating for the first fluid channel through a larger area, and the third fluid channel further regulates the outlet water temperature through local compensation heat exchange. This design of double-channel alternating heat exchange significantly improves the overall heat exchange efficiency.

[0151] The arrangement of the repeating units also has the advantages of structural simplification and modularity. By repeating and stacking specific units, not only can the production process be simplified during manufacturing and assembly, but the number of repeating units can also be flexibly adjusted to meet different heat exchange needs. For example, when preparing water with higher supercooling degree, the number of repeating units can be increased to enhance the overall cooling effect; while in scenarios where the risk of ice blockage needs to be reduced, the number of repeating units can be reduced to optimize the fluid flow path.

[0152] The design of the repeating units described above makes the heat exchanger have the characteristics of compact structure, high performance and strong adaptability, which can meet the needs of various application scenarios in industry. Especially in the preparation process of supercooled water and superheated water, this arrangement further improves the reliability and flexibility of the system.

[0153] The outlet water temperature adjustable heat exchanger 100 of the present application can be used to prepare supercooled water, superheated water and other metastable water. Based on this, the present application also provides a metastable water preparation system and a preparation method.

[0154] In an embodiment of the present application, a metastable water preparation system is also involved, which includes a first coolant system providing a first coolant, a second coolant system providing a second coolant, a water system providing water, a heat exchanger, and a control system.

[0155] A pair of first inlets and outlets 13 are connected with the water system to form a water flow path, a pair of second inlets and outlets 23 are connected with the first coolant system to form a first coolant flow loop, and a pair of third inlets and outlets 33 are connected with the second coolant system to form a second coolant flow loop. The control system is in communication connection with the first coolant system, the water system and the second coolant system to control the start-stop or flow of water, first coolant and second coolant.

[0156] Among them, the first coolant system includes a first temperature control device capable of providing a first coolant and a first pump. The second coolant system includes a second temperature control device capable of providing a second coolant and a second pump. The third coolant system includes a third temperature control device capable of providing a third coolant and a third pump. The heat exchanger is any one of the outlet water temperature adjustable heat exchanger 100 described above.

[0157] In one embodiment, the first coolant system provides a first coolant with a temperature below the freezing point of water to reduce the temperature of the water. The second coolant system then provides a second coolant with a specific temperature according to the demand. The temperature of the water can be further reduced, i.e. the second coolant system provides a second coolant with a temperature lower than the first coolant, to obtain subcooled water with a lower temperature, as shown in (a) of Figure 15 . Or the second coolant system increases the temperature of the water in specific situations. For example, when ice blockage occurs, the second coolant with a temperature higher than the freezing point of water is provided to supply heat to the water to remove the ice blockage, as shown in (b) of Figure 15 .

[0158] The three-channel design of the heat exchanger enables the water flow to receive cold or heat from both sides at the same time, achieving fast and uniform heat exchange. The first coolant system is responsible for providing basic cooling, and its flow rate and temperature are dynamically adjusted by the control system according to real-time feedback of the outlet water temperature. The second coolant system then undertakes the role of local precise control, and its temperature and flow rate can be flexibly adjusted according to actual demand.

[0159] The control system obtains real-time temperature data of the water flow by communicating with the temperature sensors inside the heat exchanger, and dynamically controls the operating parameters of the first coolant system and the second coolant system according to the preset temperature target. This design can accurately control the outlet water temperature, while effectively avoiding ice blockage in the supercooled region or energy waste in the superheated region.

[0160] Preferably, in the preparation of subcooled water, the second coolant provides cold to the water at 0°C and below. In the preparation of superheated water, the second coolant provides heat to the water at 100°C and above.

[0161] Through the system design in this embodiment, the metastable water preparation system realizes efficient and stable operation, meeting the strict requirements of water temperature control in industrial applications. This system is particularly suitable for the preparation of water with high subcooling or high superheating, significantly improving the accuracy of water temperature control and the reliability of the system.

[0162] In one embodiment of the present application, as shown in (a) of Figure 15 , the temperature of the first coolant is below the freezing point of water, and the temperature of the second coolant provided by the second coolant system is not higher than the temperature of the first coolant provided by the first coolant system, to generate subcooled water with a lower temperature.

[0163] In this embodiment, the first coolant system inputs the first coolant below the freezing point of water (0°C) into the heat exchanger through the second inlet and outlet cavity 232, and exchanges heat with the water flow of the water system. The first coolant rapidly reduces the temperature of the water by a lower temperature, making it close to or reach the supercooled state. The second coolant system inputs the second coolant with a lower temperature into the heat exchanger through the third inlet and outlet cavity 332 to perform supplementary cooling treatment on the water flow, thereby generating supercooled water with a lower temperature.

[0164] The design of the present application ensures that the water flow can quickly and uniformly reach the target temperature range in the heat exchanger through the synergistic effect of the first coolant system and the second coolant system. The first coolant provides basic cooling capacity, and the second coolant further precisely controls the water temperature, breaking through the cooling limit of traditional heat exchangers. By introducing coolants with different temperatures in the two coolant systems, the heat exchanger can flexibly adapt to different industrial demands.

[0165] The control system monitors the real-time temperature data of the water flow in the heat exchanger through communication with the temperature sensor, and dynamically adjusts the temperature and flow rate of the first coolant and the second coolant. The temperature of the second coolant is not higher than the limit, which ensures that the entire system can effectively avoid heat backflow and temperature fluctuations, thereby improving the heat exchange efficiency.

[0166] Through this embodiment, the metastable water preparation system of the present application can generate supercooled water with a lower temperature, meet the demand for deep supercooled water in the fields of chemical industry, power and the like, and significantly reduce the risk of ice blockage, thereby improving the stability and reliability of system operation. This design meets the demand for industrial application while improving the temperature control accuracy and energy efficiency of the system.

[0167] In an embodiment of the present application, as shown in (b) of the above (a), 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 thaw ice when ice blockage occurs. Figure 15

[0168] In this embodiment, the first coolant system inputs the first coolant below the freezing point of water (0°C) into the heat exchanger through the second inlet and outlet cavity 232, which is used to reduce the temperature of the water to prepare supercooled water. However, when ice blockage occurs in the supercooled region of the water flow due to excessively low temperature, the second coolant system provides the second coolant with a temperature higher than the freezing point of water through the third inlet and outlet cavity 332, which is input into the heat exchanger to resolve the ice blockage.

[0169] The second coolant transfers heat to the first fluid channel through the third fluid channel, so that the frozen ice gradually melts and the normal channel of the water flow is restored. This design fully utilizes the flexibility of the second coolant, which can quickly intervene according to the temperature monitoring condition during system operation to resolve the system interruption problem caused by ice blockage. ​

[0170] The control system determines whether ice blockage occurs by monitoring the water flow rate and flow change at the outlet of the heat exchanger. For example, when the water flow rate or the water output per unit time is lower than a preset value, the system determines that ice blockage occurs and automatically starts the second refrigerant system. The temperature and flow rate of the second refrigerant are dynamically adjusted by the control system to ensure that the ice melting process is fast and efficient, while avoiding excessive disturbance to the overall operation of the system.

[0171] Through this embodiment, the metastable water preparation system of the present application can timely melt ice when ice blockage occurs, significantly improving the reliability and continuity of system operation. This design is suitable for water flow application scenarios that require deep supercooling, and provides a simple and efficient technical solution to the common ice blockage problem in industry.

[0172] In an embodiment of the present application, the metastable water preparation system further comprises a third refrigerant system in communication connection with the control system, the third refrigerant system being connected in parallel with the second refrigerant system, the third refrigerant system comprising a third temperature control device for providing third refrigerant and a third pump. The third refrigerant system is connected to a pair of third inlets and outlets 33 to form a loop for the flow of third refrigerant, and the third refrigerant provided by the third refrigerant system has a temperature higher than the freezing point of water, which is used to remove ice blockage.

[0173] In this embodiment, the first refrigerant system inputs first refrigerant below the freezing point of water (0°C) through the second inlet and outlet cavity 232 for cooling, and the second refrigerant system further cools and compensates the water through the third inlet and outlet cavity 332. However, in order to deal with the possible ice blockage problem, the system is additionally provided with a third refrigerant system connected in parallel with the second refrigerant system. When ice blockage occurs, the second refrigerant system is closed and the third refrigerant system is started, which provides third refrigerant with a temperature higher than the freezing point of water, and transfers heat to the ice blockage area in the first fluid channel through the third fluid channel.

[0174] This design allows the second refrigerant system and the third refrigerant system to work alternately. By introducing a low-temperature fluid with a suitable temperature into the third fluid channel, the temperature of the supercooled water is reduced; by introducing a hot fluid with a suitable temperature into the third fluid channel, the frozen water in the ice blockage area can be quickly melted, while avoiding overheating or heat exchange failure in other areas due to high temperature.

[0175] The control system determines whether ice blockage occurs by monitoring the water flow rate, flow and other parameters of the heat exchanger. For example, when the water flow rate of the heat exchanger is lower than the rated value or the water output per unit time is lower than a preset value, the system determines that ice blockage occurs and automatically switches to the third refrigerant system. The temperature and flow rate of the third refrigerant are dynamically adjusted by the control system to ensure that the ice melting process is fast and efficient.

[0176] By introducing a third parallel refrigerant system, the metastable water preparation system of the present application can flexibly cope with ice blockage and quickly restore normal operation. This design significantly improves the reliability of the system, while reducing downtime and maintenance costs caused by ice blockage, and is particularly suitable for industrial application scenarios that require deep supercooled water flow.

[0177] In an embodiment of the present application, as shown in (c) of Figure 15 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, for generating water with higher superheat.

[0178] In this embodiment, the first refrigerant system inputs the first refrigerant with a temperature higher than the boiling point of water (100℃) through the second inlet and outlet cavity 232, for warming up the water. The heat is transferred to the water flow through the first fluid passage of the heat exchanger, so that the temperature of the water rapidly rises to near or above the boiling point. The second refrigerant system provides the second refrigerant with a temperature not lower than the temperature of the first refrigerant through the third inlet and outlet cavity 332, for further compensating the heat to ensure that the water temperature can exceed the boiling point and generate water with higher superheat.

[0179] In the present application, the heat compensation function of the second refrigerant system can effectively prevent the problem of temperature drop or vaporization of the water flow in the heat exchanger due to long distance flow. At the same time, by limiting the temperature of the second refrigerant to be not lower than the temperature of the first refrigerant, the system ensures the heat exchange efficiency of the heat exchanger, while avoiding temperature fluctuations in the first fluid passage, and ensures the temperature stability of the water flow.

[0180] The control system monitors the real-time temperature data of the water flow in the heat exchanger through communication with the temperature sensor, and dynamically adjusts the temperature and flow rate of the first refrigerant and the second refrigerant as needed. The role of the second refrigerant is particularly suitable for scenarios that require high precision temperature control, such as in the preparation of superheated water, by compensating for the temperature rise to achieve higher superheat, to meet the demand for high temperature water in specific industrial fields.

[0181] Through this embodiment, the metastable water preparation system of the present application can generate water with higher superheat, meet the requirements of scientific research, chemical industry and other fields for high temperature water flow, and significantly improve the precision and reliability of the system temperature control. This design not only broadens the application range of the system, but also further improves its stability and operating efficiency.

[0182] The application also provides a method for preparing metastable water, comprising the following steps: starting a first cold carrier system and a water system, obtaining the water temperature after the heat exchanger after running for a predetermined time; judging whether the water temperature reaches a preset temperature, if yes, the first cold carrier system and the water system remain in the current running state; if no, starting a second cold carrier system to supplement the cooling or heating of the water to achieve target temperature control.

[0183] In the embodiment, the first cold carrier system inputs the first cold carrier through the second inlet and outlet cavity 232, and the temperature of the first cold carrier can be lower than the freezing point of water to cool the water or higher than the boiling point of water to heat the water according to actual needs. The water system inputs the water flow through the first inlet and outlet cavity 132 to exchange heat with the first cold carrier, so that the temperature of the water flow approaches the preset value.

[0184] The system monitors the water temperature at the outlet of the heat exchanger in real time through a temperature sensor, and feeds back the temperature data to the control system for judgment. When the water temperature reaches the preset temperature target, the system remains in the current running parameters; if the water temperature does not reach the target value, the control system starts the second cold carrier system to input the second cold carrier through the third inlet and outlet cavity 332 to further cool or heat the water flow.

[0185] The second cold carrier system works cooperatively with the first cold carrier system to compensate for the insufficient heat exchange of the water flow in the first fluid channel according to the needs of selecting appropriate temperature and flow rate, so as to ensure that the outlet water temperature accurately reaches the target value. The control system adjusts the running parameters of the second cold carrier to realize dynamic adjustment of the water temperature, and ensures the efficiency and stability of the whole heat exchange process.

[0186] Through the embodiment, the method for preparing metastable water can quickly judge and adjust the water temperature, and meets the strict requirements of temperature control in industrial production. The method is not only suitable for preparing supercooled water, but also can be flexibly applied to the preparation of superheated water, significantly improves the running efficiency and temperature control precision of the system, and reduces the energy consumption and failure rate.

[0187] In an embodiment of the application, the following steps are further included: calculating the heat or cold required to be provided to the water according to the difference between the outlet water temperature and the preset temperature, and controlling the temperature and / or flow rate of the second cold carrier provided by the second cold carrier system based on the heat or cold.

[0188] In the embodiment, the system starts the first cold carrier system and the water system, and the water flow approaches the target temperature through the heat exchange of the heat exchanger. The control system monitors the water temperature at the outlet of the heat exchanger in real time through a temperature sensor, compares the current outlet water temperature with the preset temperature, and obtains the temperature difference data. Based on the temperature difference, the control system calculates the heat or cold required to be compensated, and dynamically adjusts the running parameters of the second cold carrier.

[0189] When the current water temperature is detected to be lower than the preset target, the system starts the second coolant system to input a lower-temperature coolant through the third inlet and outlet cavity 332 for supplementary cooling. Conversely, when preparing superheated water, the second coolant system provides a higher-temperature coolant for temperature compensation when the water temperature is lower than the target temperature. The flow rate and temperature of the second coolant are accurately adjusted according to the demand value calculated by the control system to achieve efficient temperature compensation.

[0190] This method combines temperature monitoring and heat calculation, not only optimizing the use efficiency of the second coolant, but also significantly improving the overall temperature control accuracy of the system. Dynamically adjusting the temperature and flow rate of the coolant can adjust the outlet water temperature to the preset target value in the shortest possible time, while avoiding energy waste caused by excessive adjustment.

[0191] Through this embodiment, the metastable water preparation method of the application can meet the demand for highly accurate temperature control, and is particularly suitable for industrial scenarios with strict requirements for supercooled water or superheated water. This method not only improves the heat exchange efficiency, but also reduces the system operating cost, providing an efficient and reliable solution for temperature control.

[0192] In an embodiment of the application, the metastable water preparation method further comprises the following steps: the temperature of the first coolant is lower than the freezing point of water, and it is detected whether ice blocking occurs, if ice blocking occurs, a third coolant system connected in parallel with the second coolant system to the third inlet and outlet cavity 332 is started, and a third coolant with a temperature higher than the freezing point of water is input into the heat exchanger.

[0193] Among them, detecting whether ice blocking 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 blocking occurs; and / or detecting the outlet water amount of the heat exchanger per unit time, if the outlet water amount is less than the rated water amount, it is determined that ice blocking occurs; and / or, detecting the temperature of the outlet water of the heat exchanger, if the temperature of the outlet water is not less than 0℃, it is determined that ice blocking occurs.

[0194] In this embodiment, the first coolant system inputs the first coolant with a temperature lower than the freezing point of water through the second inlet and outlet cavity 232 to cool the water and prepare supercooled water. During operation, the system monitors the water flow state in real time through the temperature sensor, flow meter and flow rate sensor. If the outlet water flow rate of the heat exchanger or the outlet water amount per unit time is detected to be lower than the preset value, the control system determines that ice blocking occurs.

[0195] When ice blocking occurs, the second coolant system is closed, the third coolant system connected in parallel with the second coolant system is automatically started, and the third coolant with a temperature higher than the freezing point of water is input into the heat exchanger through the third inlet and outlet cavity 332. The third coolant transfers heat to the ice blocking area through the third fluid channel, so that the frozen water gradually melts and the normal flow of the water is restored.

[0196] During the third refrigerant system operation, the control system dynamically adjusts the temperature and flow rate of the third refrigerant to ensure quick ice melting while avoiding overheating effects on water flow in other areas. After ice melting is completed, the control system shuts down the third refrigerant system, restores normal operation of the first refrigerant system and the second refrigerant system, and continues to prepare subcooled water.

[0197] Through the above method, the application can quickly respond and solve the problem when ice blocking occurs, significantly improving the reliability and stability of the metastable water preparation system. This design is particularly suitable for industrial application scenarios under deep subcooling conditions, meeting the requirement of high subcooling degree while solving the problem of operation interruption caused by ice blocking, providing technical support for continuous operation of the system.

[0198] The application also provides a subcooled water preparation method, including the following steps: starting the first refrigerant system and the 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 blocking occurs in the heat exchanger, if ice blocking occurs, starting the second refrigerant system to provide the second refrigerant with a temperature higher than the freezing point of water; if ice blocking does not occur, the first refrigerant system and the water system remain in the current operating state.

[0199] Wherein, the way to detect whether ice blocking occurs is as described above, which will not be repeated here.

[0200] In this embodiment, the first refrigerant system inputs the first refrigerant with a temperature lower than the freezing point of water (0℃) through the second inlet and outlet cavity 232, which is used to cool the water and prepare subcooled water. The water system inputs water flow through the first inlet and outlet cavity 132, which exchanges heat with the first refrigerant system to reduce the water temperature to the target subcooling temperature. The system monitors the outlet water state of the heat exchanger in real time through the temperature sensor, flow rate sensor and flow meter during operation.

[0201] When the outlet water flow rate or the outlet water volume per unit time is detected to be lower than the preset value, the control system determines that ice blocking occurs, and automatically starts the second refrigerant system. The second refrigerant inputs the second refrigerant with a temperature higher than the freezing point of water through the third inlet and outlet cavity 332, which transfers heat to the ice blocking area to gradually melt the frozen water flow and restore the normal operation of the system. The temperature and flow rate of the second refrigerant are dynamically adjusted by the control system to ensure quick ice melting while avoiding overheating effects in other areas.

[0202] In the case where ice blocking phenomenon is not detected, the system maintains the current operating state of the first refrigerant system and the water system, continues to prepare subcooled water, thereby reducing energy consumption and improving operating efficiency.

[0203] By employing the above method, this invention can flexibly address the ice blockage problem during the supercooling water preparation process, ensuring stable system operation under high subcooling 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.

[0204] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0205] The detailed descriptions listed above are merely specific descriptions of feasible embodiments of the present invention, and are not intended to limit the scope of protection of the present invention. All equivalent embodiments or modifications made without departing from the spirit of the present invention should be included within the scope of protection of the present invention.

Claims

1. A heat exchanger with adjustable outlet water temperature, characterized in that: The application relates to a heat exchange device, comprising: a plurality of first fluid channel sheets, each of which comprises a first heat exchange area, a pair of first inlets and outlets in communication with the first heat exchange area, a pair of first communication areas spaced apart from the first heat exchange area by a first dam, and a pair of first through areas; a plurality of second fluid channel sheets, each of which comprises a second heat exchange area, a pair of second inlets and outlets in communication with the second heat exchange area, a pair of second through areas spaced apart from the second heat exchange area by a second dam, and a pair of second through areas; a plurality of third fluid channel sheets, each of which comprises a third heat exchange area, a pair of third inlets and outlets in communication with the third heat exchange area, a pair of third through areas spaced apart from the third heat exchange area by a third dam, and a pair of third communication areas; the area of the third heat exchange area is smaller than the area of the first heat exchange area; wherein the first fluid channel sheets, the second fluid channel sheets and the third fluid channel sheets are arranged in layers along the O-Z direction, and the first fluid channel sheets are located between the second fluid channel sheets and the third fluid channel sheets; along the O-Z direction, a pair of first inlets and outlets are in communication with a pair of second through areas and a pair of third through areas to form a first inlet and outlet cavity, a pair of second inlets and outlets are in communication with a pair of first communication areas and a pair of third communication areas to form a second inlet and outlet cavity, and a pair of third inlets and outlets are in communication with a pair of first through areas and a pair of second through areas to form a third inlet and outlet cavity; the area of the second heat exchange area is 90% to 110% of the area of the first heat exchange area, the area of the third heat exchange area is 1 / 2 to 1 / 3 of the area of the first heat exchange area, and a plurality of microstructures are arranged in the first heat exchange area, the second heat exchange area and the third heat exchange area; the arrangement density of the microstructures in the third heat exchange area is greater than that in the first heat exchange area and the second heat exchange area.

2. The heat exchanger with adjustable outlet water temperature according to claim 1, characterized in that, The area of the second heat exchange area is consistent with the area of the first heat exchange area.

3. The heat exchanger of claim 2, wherein A pair of the first inlets and outlets comprises a first inlet and a first outlet. The projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the distance between the projection and the first inlet is smaller than the distance between the projection and the first outlet. Or, the projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the projection is located in the middle region of the first heat exchange area. Or, the projection of the third heat exchange area on the first fluid channel sheet along the O-Z direction is located in the first heat exchange area, and the distance between the projection and the first outlet is smaller than the distance between the projection and the first inlet.

4. The heat exchanger of claim 1, wherein The first heat exchange area is arranged in a recessed manner from a first surface to a second surface of the first fluid channel sheet, a pair of the first inlets and outlets are arranged on the two sides of the first heat exchange area along the O-X direction, and the first inlets and outlets are in communication with the first heat exchange area through a first transition area; a pair of the first communication areas are arranged on the two sides of the first heat exchange area along the O-Y direction, and a pair of the first through areas are arranged on one side of the first heat exchange area along the O-X direction, and a pair of the first through areas are arranged on the two sides of the first inlets and outlets along the O-Y direction. The second heat exchange region is recessed from the first surface to the second surface of the second fluid channel sheet, a pair of the second inlets and outlets are arranged on both sides of the second heat exchange region along the O-Y direction, and the second inlets and outlets are communicated with the second heat exchange region through a second transition region; a pair of the second through regions are arranged on both sides of the second heat exchange region along the O-X direction, and a pair of the second through regions are arranged on both sides of the second through region along the O-Y direction. The third heat exchange region is recessed from the first surface to the second surface of the third fluid channel sheet, a pair of the third through regions are arranged on both sides of the third heat exchange region along the O-X direction, a pair of the third through regions are arranged on both sides of the third heat exchange region along the O-Y direction, a pair of the third inlets and outlets are arranged on one side of the third heat exchange region along the O-X direction, and a pair of the third inlets and outlets are arranged on both sides of the third through region along the O-Y direction, and the third inlets and outlets are communicated with the third heat exchange region through a third transition region.

5. The heat exchanger of claim 1, wherein The water outlet temperature adjustable heat exchanger further comprises at least one temperature sensor arranged on at least one of the first fluid channel sheets.

6. The outlet water temperature adjustable heat exchanger according to claim 5, wherein The at least one temperature sensor is arranged in the projection of the third heat exchange region on the first fluid channel sheet along the O-Z direction.

7. The outlet water temperature adjustable heat exchanger according to claim 5, wherein The at least one temperature sensor is arranged at an upstream inlet of the projection of the third heat exchange region on the first fluid channel sheet along the O-Z direction.

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 arranged in sequence along the O-Z direction as a repeating unit of the second fluid channel sheet, the first fluid channel sheet and the third fluid channel sheet. The first fluid channel sheet, the second fluid channel sheet and the third fluid channel sheet are arranged in sequence along the O-Z direction as a repeating unit of the second fluid channel sheet, the first fluid channel sheet and the third fluid channel sheet.

9. A metastable water production system comprising a first coolant system providing a first coolant, a second coolant system providing a second coolant, a water system providing water, a heat exchanger, and a control system, characterized in that, The heat exchanger is the water outlet temperature adjustable heat exchanger of any one of claims 1-8, a pair of the first inlets and outlets are connected with the water system to form a path for the water flow, a pair of the second inlets and outlets are connected with the first cold carrier system to form a loop for the first cold carrier flow, a pair of the third inlets and outlets are connected with the second cold carrier system to form a loop for the second cold carrier flow, and the control system is communicatively connected with the first cold carrier system, the water system and the second cold carrier system.

10. The system of claim 9, wherein the system is configured to: The temperature of the first cold carrier is lower than the freezing point of water, and the temperature of the second cold carrier is not higher than the temperature of the first cold carrier.

11. The system of claim 10, wherein the system is configured to: The metastable water preparation system further comprises a third cold carrier system for providing a third cold carrier, the third cold carrier system is connected with a pair of the third inlets and outlets to form a loop for the third cold carrier flow, and the temperature of the third cold carrier is higher than the freezing point of water.

12. The system of claim 9, wherein the system is configured to produce water in a metastable state. The temperature of the first cold carrier is lower than the freezing point of water, and the temperature of the second cold carrier is higher than the freezing point of water.

13. The system of claim 9, wherein the system is configured to produce water in a metastable state. 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.

14. A method for preparing a metastable water, implemented on the basis of a system for preparing a metastable water according to any one of claims 9 to 13, characterized in that, The metastable water preparation method comprises the following steps: Starting the first coolant system and the water system, and obtaining the temperature of the water after running for a predetermined time; Determining whether the temperature of the water after the heat exchanger reaches a preset temperature, and if so, maintaining the current running state of the first coolant system and the water system, and if not, starting the second coolant system to supply cold or heat to the water.

15. The method of claim 14, wherein the method is a method of preparing metastable water. According to the difference between the temperature of the water and the preset temperature, calculating the heat or cold required to be supplied to the water, and based on the heat or cold, controlling the temperature and / or flow rate of the second coolant provided by the second coolant system.

16. The method of claim 14, wherein the method is a method of preparing metastable water. The temperature of the first coolant is lower than the freezing point of water, and whether ice blocking occurs is detected, and if so, a third coolant system is started in parallel with the second coolant system to the third inlet and outlet cavity, and a third coolant with a temperature higher than the freezing point of water is input into the heat exchanger. The detection of whether ice blocking occurs comprises: Detecting the flow rate of the water after the heat exchanger, and if the flow rate is lower than the rated flow rate, it is determined that ice blocking occurs; And / or, detecting the amount of water after the heat exchanger in a unit of time, and if the amount of water is less than the rated amount of water, it is determined that ice blocking occurs; And / or, detecting the temperature of the water after the heat exchanger, and if the temperature of the water is not less than 0℃, it is determined that ice blocking occurs.

17. A method of producing supercooled water, implemented based on the metastable water production system according to claim 9, characterized by, The metastable water preparation method comprises the following steps: Starting the first coolant system and the water system, and obtaining the temperature of the water after running for a predetermined time; Determining whether the temperature of the water after the heat exchanger reaches a preset temperature, and if so, maintaining the current running state of the first coolant system and the water system, and if not, starting the second coolant system to supply cold or heat to the water. According to the difference between the temperature of the water and the preset temperature, calculating the heat or cold required to be supplied to the water, and based on the heat or cold, controlling the temperature and / or flow rate of the second coolant provided by the second coolant system. The temperature of the first coolant is lower than the freezing point of water, and whether ice blocking occurs is detected, and if so, a third coolant system is started in parallel with the second coolant system to the third inlet and outlet cavity, and a third coolant with a temperature higher than the freezing point of water is input into the heat exchanger. The detection of whether ice blocking occurs comprises: Detecting the flow rate of the water after the heat exchanger, and if the flow rate is lower than the rated flow rate, it is determined that ice blocking occurs; And / or, detecting the amount of water after the heat exchanger in a unit of time, and if the amount of water is less than the rated amount of water, it is determined that ice blocking occurs; And / or, detecting the temperature of the water after the heat exchanger, and if the temperature of the water is not less than 0℃, it is determined that ice blocking occurs.

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