Liquid-liquid countercurrent heat exchanger and supercooled water unit

Abstract

The invention provides a liquid-liquid countercurrent heat exchanger and a supercooled water unit. The liquid-liquid countercurrent heat exchanger is characterized in that a heat exchange shell defines a mounting cavity; the heat exchange core body is mounted in the mounting cavity, the heat exchange core body is formed in the mode that a metal plate internally provided with a plurality of parallel flow channels is rolled into a spiral shape, and a first medium flow channel is formed in the heat exchange core body; the heat exchange core and the heat exchange shell jointly define a second medium flow channel, the flow area of the first medium flow channel is set to be smaller than that of the second medium flow channel, and the flow direction of a first medium in the first medium flow channel is opposite to that of a second medium in the second medium flow channel. According to the liquid-liquid countercurrent heat exchanger, the flow speed of the first medium in the first medium flow channel can be increased, efficient heat exchange between the first medium and the second medium is guaranteed, the heat transfer area of the heat exchange core and the accumulation amount of the first medium are reduced, heat is provided for micro ice crystal ablation of inlet water of a supercooling water unit, and the supercooling degree of the first medium is increased; and the energy efficiency ratio of the supercooling water unit is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of supercooling water unit manufacturing, and in particular to a liquid-liquid countercurrent heat exchanger and a supercooling water unit having the same. Background Art

[0002] With the advancement of society and the improvement of people's quality of life, chillers have become essential equipment for creating comfortable building environments and meeting the requirements of industrial and agricultural production processes. With the transformation of energy structures, the efficient utilization of renewable electricity, which is both cyclical and random, particularly the effective absorption and utilization of peak power from wind and photovoltaic power, has become a future technical challenge. Research has shown that ice slurry cold storage offers the advantages of readily storing cold and rapidly retrieval, making it an important means of absorbing renewable electricity to meet the cooling needs of cooling users. Because ice slurry is converted from supercooled water with a certain degree of subcooling, ice slurry cold storage requires the production of supercooled water by a subcooling unit. After the ice slurry generator releases the cold, it is converted into ice slurry and stored in an ice slurry tank. The remaining 0°C cold water in the ice slurry tank then passes through the chiller's evaporator, absorbing the cold released by the refrigerant to form supercooled water. This cycle continuously generates ice slurry from the cold water in the ice slurry tank.

[0003] However, the 0°C cold water drawn from the ice slurry pool and fed into the subcooling unit contains trace amounts of ice crystals (microcrystals). Once this water enters the evaporator, it freezes there, blocking the flow of subcooled water (ice blockage). This not only prevents continuous subcooled water production but, in severe cases, can also cause evaporator piping to rupture and damage the unit. To address this issue, an external heat source is used to heat the evaporator inlet water containing microcrystals, raising its temperature to 0.2-1°C before it enters the evaporator, preventing ice blockage on the subcooled water side of the evaporator.

[0004] In the existing technical solutions, most of them use external heat sources above 0℃, such as cooling water prepared by cooling towers and hot water from solar collectors, for heating, which will inevitably lead to the loss of cooling capacity produced by the subcooled water unit and reduce the energy efficiency of the unit; there are also shell and tube, sleeve or plate heat exchangers as preheaters, and use the high-temperature liquid refrigerant flowing out of the condenser of the chiller refrigeration system as a heat source to heat the evaporator inlet water. Although this can increase the subcooling degree of the high-pressure liquid at the outlet of the unit condenser to increase the cooling capacity of the unit, it can offset the loss of cooling capacity caused by the evaporator inlet water heating. However, due to the huge difference in mass flow rates between the liquid refrigerant and the cold water (the flow rate on the water side is 10 to 100 times the mass flow rate on the refrigerant side, and the temperature difference between the inlet and outlet of the water side is only within 0.5°C, while the temperature difference between the inlet and outlet of the refrigerant side is often above 15°C), the structure of the above-mentioned preheater determines that the flow rate on the refrigerant side is extremely low and the heat transfer coefficient is very small, which will inevitably lead to a large heat transfer area and more consumables of the heat exchanger. At the same time, the storage volume of the refrigerant in the heat exchanger is large, the cost is high, and once it leaks, it will have a serious impact on the environment. Summary of the Invention

[0005] Based on the above background, when designing the preheater of a subcooled water unit, in addition to meeting the heat exchange requirements of small temperature rise on the water side and large temperature drop on the refrigerant side, it is also necessary to solve the problems of improving the heat transfer coefficient on the refrigerant side, reducing the heat exchange area and material consumption, and reducing the refrigerant storage volume in the preheater, so as to improve the energy efficiency ratio of the subcooled water unit, reduce the cost of the subcooled water unit, and promote the advancement of ice slurry energy storage technology.

[0006] The present invention aims to solve the technical difficulties existing in the prior art and proposes a liquid-liquid countercurrent heat exchanger with a simple structure and low manufacturing cost. It can increase the flow rate of the first medium to improve the heat transfer coefficient, and ensure the flow rate of the second medium to improve the heat transfer coefficient of the heat exchanger, ensure reliability of use, and improve the user experience.

[0007] According to an embodiment of the present invention, a liquid-liquid countercurrent heat exchanger includes: a heat exchange shell, which defines an installation cavity; a heat exchange core, which is installed in the installation cavity, and the heat exchange core is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape, and a first medium flow channel is formed in the heat exchange core; wherein the heat exchange core and the heat exchange shell jointly define a second medium flow channel, the flow area of ​​the first medium flow channel is set to be smaller than the flow area of ​​the second medium flow channel, and the flow directions of the first medium in the first medium flow channel and the second medium in the second medium flow channel are opposite.

[0008] According to the liquid-liquid countercurrent heat exchanger of an embodiment of the present invention, the heat exchange core is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape, and the heat exchange core and the heat exchange shell jointly define a second medium flow channel, which can simplify the structure of the liquid-liquid countercurrent heat exchanger and reduce manufacturing costs. At the same time, the flow area of ​​the first medium flow channel is set to be smaller than the flow area of ​​the second medium flow channel, which can increase the flow rate of the first medium in the first medium flow channel, thereby increasing the heat transfer coefficient on the first medium side and ensuring the flow rate of the second medium. Further, when the temperature difference between the first medium flow channel and the second medium flow channel is large, the heat transfer coefficient of the liquid-liquid countercurrent heat exchanger can be increased, ensuring efficient heat exchange between the first medium and the second medium, reducing the heat transfer area of ​​the heat exchange core and the accumulation of the first medium, providing heat for the melting of micro-ice crystals in the water inlet of the subcooling unit, increasing the subcooling degree of the first medium, improving the energy efficiency ratio of the subcooling unit, and having better use effect and a wider range of applications.

[0009] According to some embodiments of the present invention, the liquid-liquid countercurrent heat exchanger, the heat exchange core is provided with a first inlet header and a first outlet header, the first inlet header and the first outlet header are respectively connected to the first medium flow channel;

[0010] And / or, the heat exchange shell is provided with a second inlet header and a second outlet header, and the second inlet header and the second outlet header are respectively communicated with the second medium flow channel.

[0011] According to some embodiments of the liquid-liquid counterflow heat exchanger of the present invention, one of the first inlet header and the first outlet header is configured to be led outward from the radially outer side of the heat exchange shell, and the other is configured to be led outward from the axial end of the heat exchange shell;

[0012] And / or, one of the second inlet header and the second outlet header is configured to be led outward from the radial outer side of the heat exchange shell, and the other is configured to be led outward from the axial end of the heat exchange shell.

[0013] According to the liquid-liquid countercurrent heat exchanger of some embodiments of the present invention, the first inlet header is configured to be conducted outward from the end portion of one axial end of the heat exchange shell, and the second outlet header is configured to be conducted outward from the end portion of the other axial end of the heat exchange shell.

[0014] According to the liquid-liquid countercurrent heat exchanger of some embodiments of the present invention, a protruding confluence portion is formed on the radial outer side of the heat exchange shell, the second inlet manifold is arranged on the confluence portion, and the confluence portion and the first outlet manifold are distributed side by side on the radial outer side of the heat exchange shell.

[0015] According to the liquid-liquid countercurrent heat exchanger of some embodiments of the present invention, the first medium flow channel includes a plurality of microchannels distributed side by side, the extension direction of the plurality of microchannels is the same as the extension direction of the heat exchange core, and both ends of the plurality of microchannels are constructed to be connected to the first inlet header and the first outlet header, respectively.

[0016] According to the liquid-liquid countercurrent heat exchanger of some embodiments of the present invention, a flow direction of the first medium in the first medium flow channel is opposite to a flow direction of the second medium in the second medium flow channel.

[0017] According to some embodiments of the present invention, the liquid-liquid counterflow heat exchanger comprises a main shell, a first cover plate, and a second cover plate, wherein the first cover plate and the second cover plate are respectively connected to two ends of the main shell to jointly define the installation cavity;

[0018] Wherein, one end of the heat exchange core is in close contact with the first cover plate and the other end is in close contact with the second cover plate, so as to jointly define the second medium flow channel.

[0019] According to some embodiments of the present invention, a liquid-liquid countercurrent heat exchanger is provided at the connection between the main shell and the first cover plate. The first sealing member is configured as an annular sealing member.

[0020] And / or, a second sealing member is provided at the connection between the main shell and the second cover plate, and the second sealing member is configured as an annular sealing member.

[0021] The invention also provides a supercooling water unit.

[0022] A subcooling water unit according to an embodiment of the present invention includes any of the above-mentioned liquid-liquid countercurrent heat exchangers.

[0023] The subcooling water unit and the above-mentioned liquid-liquid countercurrent heat exchanger can improve the heat transfer coefficient in the first medium flow channel, reduce the heat transfer area and material consumption of the heat exchange core, reduce the refrigerant storage volume in the liquid-liquid countercurrent heat exchanger, reduce the cost of the subcooling water unit, and improve the reliability of use.

[0024] The specific implementation method and the positive effects achieved will be described below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which:

[0026] Figure 1 is a cross-sectional view of a liquid-liquid countercurrent heat exchanger according to an embodiment of the present invention Figure 1 ;

[0027] Figure 2 is a cross-sectional view of a liquid-liquid countercurrent heat exchanger according to an embodiment of the present invention Figure 2 ;

[0028] Figure 3 This is a schematic diagram of the structure of a liquid-liquid countercurrent heat exchanger according to an embodiment of the present invention. Figure 1 ;

[0029] Figure 4 This is a schematic diagram of the structure of a liquid-liquid countercurrent heat exchanger according to an embodiment of the present invention. Figure 2 ;

[0030] Figure 5 is a structural schematic diagram of a heat exchange core according to an embodiment of the present invention;

[0031] Figure 6 3 is a schematic diagram of the partial structure of a heat exchange core according to an embodiment of the present invention.

[0032] Reference numerals:

[0033] Liquid-liquid countercurrent heat exchanger 100,

[0034] Heat exchange shell 1, main shell 11, confluence part 111, first cover plate 12, second cover plate 13, installation cavity 14, heat exchange core 2, first medium flow channel 21, microchannel 211, second medium flow channel 3, second inlet header 31, second outlet header 32, first inlet header 4, first outlet header 5, first seal 6, second seal 7, connector 8, flange 9. DETAILED DESCRIPTION

[0035] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0036] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0037] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0038] Reference below Figures 1-6 A liquid-liquid countercurrent heat exchanger according to an embodiment of the present invention is described, which has a simple structure and low manufacturing cost. It can increase the flow rate of the first medium and ensure the flow rate of the second medium, thereby improving the heat exchange efficiency of the liquid-liquid countercurrent heat exchanger, ensuring reliability in use, and improving the user experience.

[0039] like Figures 1-6As shown, a liquid-liquid countercurrent heat exchanger 100 according to one embodiment of the present invention includes: a heat exchange shell 1 and a heat exchange core 2.

[0040] An installation cavity 14 is defined in the heat exchange shell 1, and the heat exchange core 2 is installed in the installation cavity 14. The heat exchange core 2 is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape. A first medium flow channel 21 is formed in the heat exchange core 2; wherein, the heat exchange core 2 and the heat exchange shell 1 jointly define a second medium flow channel 3, and the flow area of ​​the first medium flow channel 21 is set to be smaller than the flow area of ​​the second medium flow channel 3, and the flow directions of the first medium in the first medium flow channel 21 and the second medium in the second medium flow channel 3 are opposite.

[0041] The liquid-liquid countercurrent heat exchanger 100 can be installed in a subcooled water chiller, and particularly relates to a heat exchanger for exchanging heat between low-flow and high-flow liquid media. A subcooled water chiller is a type of chiller and an important device for producing ice slurry. The subcooled water produced by the subcooled water chiller is converted into ice slurry after passing through an ice slurry generator and stored in an ice slurry tank. The 0°C cold water at the bottom of the ice slurry tank then passes through the chiller evaporator, absorbing the cold released by the refrigerant to form subcooled water. This cycle repeats continuously, continuously converting the cold water in the ice slurry tank into ice slurry.

[0042] With the transformation of energy structures, the efficient utilization of renewable electricity, which is both cyclical and random, particularly the effective absorption and utilization of peak power from wind and photovoltaic power, has become a technological challenge for the future. Research has shown that ice slurry cooling offers the advantages of immediate cold storage and rapid cold withdrawal, making it an important means of absorbing renewable electricity to meet the cooling needs of cooling users. As a key component of ice slurry production, the reliability, efficiency, and cost-effectiveness of supercooling units are crucial for the widespread adoption of ice slurry cooling.

[0043] Specifically, the liquid-liquid countercurrent heat exchanger 100 can be set to aluminum or steel, etc. The liquid-liquid countercurrent heat exchanger 100 is provided with a heat exchange shell 1, which is arranged at the outermost side of the liquid-liquid countercurrent heat exchanger 100. An installation cavity 14 is formed inside the heat exchange shell 1. The internal structure of the liquid-liquid countercurrent heat exchanger 100 can be installed in the installation cavity 14, that is, the heat exchange shell 1 can provide an installation point for the internal structure of the liquid-liquid countercurrent heat exchanger 100, and the heat exchange shell 1 can protect the internal structure of the liquid-liquid countercurrent heat exchanger 100 to ensure the operational reliability of the liquid-liquid countercurrent heat exchanger 100.

[0044] The liquid-liquid countercurrent heat exchanger 100 is also provided with a heat exchange core 2, which can be installed in the installation cavity 14, and a first medium flow channel 21 is formed in the heat exchange core 2. The first medium can be set to a liquid refrigerant, etc. The first medium can flow in the first medium flow channel 21, so that the heat exchange core 2 can exchange heat through the first medium.

[0045] The heat exchange core 2 is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape. This can shorten the length of the heat exchange core 2 to reduce the space occupied by the liquid-liquid countercurrent heat exchanger 100. The heat exchange core 2 is installed in the installation cavity 14. The heat exchange core 2 can be connected to the heat exchange shell 1 by welding or other methods to fix the heat exchange core 2. The heat exchange core 2 and the heat exchange shell 1 can jointly define a second medium flow channel 3. The second medium can be set to water, etc., thereby avoiding the need to set up a separate second medium flow channel 3, simplifying the structure of the liquid-liquid countercurrent heat exchanger 100 and reducing the installation cost. The first medium flow channel 21 defines the second medium flow channel 3, so that the second medium flow channel 3 is set closely to the first medium flow channel 21, so that the first medium flow channel 21 can exchange heat with the second medium flow channel 3, ensuring the heat exchange effect. Among them, a microchannel tube group is provided in the heat exchange core 2, and the microchannel tube group has the first medium flow channel 21, that is, the first medium can flow in the microchannel tube group.

[0046] When the liquid-liquid countercurrent heat exchanger 100 is in operation, the first medium flows in the first medium flow channel 21, and the second medium flows in the second medium flow channel 3. The temperature of the first medium is higher and the temperature of the second medium is lower, so that there is a temperature difference between the second medium and the first medium, and thus the heat in the second medium can be transferred to the first medium through the heat exchange core 2 to heat the second medium, thereby ensuring the reliability of the liquid-liquid countercurrent heat exchanger 100.

[0047] Furthermore, at least a portion of the first medium flow channel 21 extends in the same direction as the second medium flow channel 3. This means that the extension direction of a portion of the first medium flow channel 21 can be set to be the same as the extension direction of the second medium flow channel 3, or the entire first medium flow channel 21 can be set to be the same as the extension direction of the second medium flow channel 3. The heat exchange core 2 is constructed in a spiral shape, so that the first medium flow channel 21 also extends in a spiral shape, and thus the second medium flow channel 3 also extends in a spiral shape. This reduces the overall space occupied by the liquid-liquid countercurrent heat exchanger 100, improves its lightweight, increases the heat exchange area between the first and second media, and forms the second medium flow channel 3 on both the inner and outer radial sides of the heat exchange core 2 to enhance the heat exchange effect.

[0048] At the same time, the flow area of ​​the first medium flow channel 21 is set to be smaller than the flow area of ​​the second medium flow channel 3, that is, the flow area of ​​the first medium flow channel 21 is set to be smaller, and the flow area of ​​the second medium flow channel 3 is set to be larger, so that the flow rate of the first medium is smaller and the flow velocity of the first medium in the first medium flow channel 21 is faster, and the flow rate of the second medium is larger and the flow velocity of the second medium in the second medium flow channel 3 is slower. In this way, when the temperature difference in the first medium flow channel 21 is large and the temperature difference in the second medium flow channel 3 is small, the heat exchange efficiency of the first medium and the second medium can be guaranteed, so that the first medium and the second medium can fully exchange heat, improve the heat exchange effect of the liquid-liquid countercurrent heat exchanger 100, reduce the injection amount of the first medium, and thus reduce the refrigerant charge of the subcooling water unit, protecting the environment and reducing costs.

[0049] Moreover, the flow direction of the first medium is opposite to that of the second medium, that is, the first medium that has just entered the first medium flow channel 21 can exchange heat with the second medium that is ready to flow out of the second medium flow channel 3 after heat exchange. At this time, the second medium has been heated after heat exchange. When the first medium has just entered the first medium flow channel 21, the temperature is relatively high, so that the second medium can still exchange heat with the first medium to further heat the second medium. When the first medium is ready to flow out of the first medium flow channel 21 after heat exchange, the second medium with a lower temperature has just entered the second medium flow channel 3. At this time, the temperature of the first medium is still higher than that of the second medium, so that the first medium can perform preliminary heat exchange with the second medium.

[0050] In this way, the flow direction of the first medium in the first medium flow channel 21 is set to be opposite to the flow direction of the second medium in the second medium flow channel 3, so that the first medium at each location in the first medium flow channel 21 and the second medium at the corresponding position in the second medium flow channel 3 have a temperature difference, thereby allowing the first medium at each location in the first medium flow channel 21 and the second medium at the corresponding position in the second medium flow channel 3 to exchange heat, thereby ensuring the reliability of heat exchange.

[0051] According to the liquid-liquid countercurrent heat exchanger 100 of the embodiment of the present invention, the heat exchange core 2 is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape, and the heat exchange core 2 and the heat exchange shell 1 jointly define the second medium flow channel 3, which can simplify the structure of the liquid-liquid countercurrent heat exchanger 100 and reduce the manufacturing cost. At the same time, the flow area of ​​the first medium flow channel 21 is set to be smaller than the flow area of ​​the second medium flow channel 3, which can increase the flow rate of the first medium in the first medium flow channel 21 and ensure the flow rate of the second medium. Therefore, when the temperature difference between the first medium flow channel 21 and the temperature of the second medium flow channel 3 is large, the heat transfer coefficient of the liquid-liquid countercurrent heat exchanger 100 can be improved, ensuring efficient heat exchange between the first medium and the second medium, reducing the heat transfer area of ​​the heat exchange core 2 and the accumulation of the first medium, and providing heat for the melting of micro-ice crystals in the water inlet of the subcooling unit, increasing the subcooling degree of the first medium, improving the energy efficiency ratio of the subcooling unit, and having better use effect and a wider range of applications.

[0052] In some embodiments, the heat exchange core 2 is provided with a first inlet header 4 and a first outlet header 5 , and the first inlet header 4 and the first outlet header 5 are respectively communicated with the first medium flow channel 21 .

[0053] Specifically, the heat exchange core 2 is arranged in the heat exchange shell 1, and as Figure 1-Figure 4 As shown, the heat exchange core 2 is provided with a first inlet header 4 and a first outlet header 5. The first inlet header 4 is connected to one end of the heat exchange core 2, and the first outlet header 5 is connected to the other end of the heat exchange core 2. The first inlet header 4 is connected to the first medium flow channel 21, and the first outlet header 5 is also connected to the first medium flow channel 21.

[0054] In this way, the first medium can flow into one end of the heat exchange core 2 through the first inlet manifold 4, and then flow to the other end of the heat exchange core 2 through the first medium flow channel 21. When the first medium flows in the first medium flow channel 21, it can exchange heat with the second medium in the second medium flow channel 3. The first medium after releasing heat and cooling can flow out of the heat exchange core 2 through the first outlet manifold 5, which increases the subcooling degree of the refrigeration system and ensures the flow length of the first medium in the heat exchange core 2 to ensure the heat exchange effect.

[0055] In other embodiments, the heat exchange shell 1 is provided with a second inlet header 31 and a second outlet header 32 , and the second inlet header 31 and the second outlet header 32 are respectively communicated with the second medium flow channel 3 .

[0056] Specifically, the heat exchange core 2 and the heat exchange shell 1 jointly define the second medium flow channel 3, and as Figure 1-Figure 4As shown, the heat exchange shell 1 is provided with a second inlet manifold 31 and a second outlet manifold 32. The second inlet manifold 31 and the second outlet manifold 32 are both connected to the installation cavity 14, and the second inlet manifold 31 is connected to the second medium flow channel 3, and the second outlet manifold 32 is also connected to the second medium flow channel 3.

[0057] In this way, the second medium can flow into one end of the second medium flow channel 3 through the second inlet manifold 31, so as to flow from the second medium flow channel 3 to the other end of the second medium flow channel 3, and when the second medium flows in the second medium flow channel 3, it can exchange heat with the first medium in the first medium flow channel 21. The second medium after absorbing heat and heating can flow out of the heat exchange shell 1 through the second outlet manifold 32, and then flow to the remaining structures of the subcooling unit to ensure the refrigeration reliability of the subcooling unit, and can ensure the circulation length of the second medium in the second medium flow channel 3, so as to ensure the heat exchange effect and improve the user experience.

[0058] In some embodiments, one of the first inlet header 4 and the first outlet header 5 is configured to be led outward from the radial outer side of the heat exchange shell 1 , and the other is configured to be led outward from the axial end of the heat exchange shell 1 .

[0059] Specifically, the first inlet manifold 4 and the first outlet manifold 5 are respectively connected to the first medium flow channel 21, so that the first medium can enter the heat exchange core 2 through the first inlet manifold 4 and flow out of the heat exchange core 2 through the first outlet manifold 5. One of the first inlet manifold 4 and the first outlet manifold 5 is constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the other is constructed to be conducted outward from the axial end of the heat exchange shell 1. That is, the first inlet manifold 4 can be constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the first outlet manifold 5 can be constructed to be conducted outward from the axial end of the heat exchange shell 1. The first outlet manifold 5 can also be constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the first inlet manifold 4 can be constructed to be conducted outward from the axial end of the heat exchange shell 1.

[0060] In this embodiment, if Figure 1-Figure 4 As shown, the first outflow header 5 is configured to extend outward from the radially outer side of the heat exchange shell 1, and the first inflow header 4 is configured to extend outward from the axial end of the heat exchange shell 1. The heat exchange core 2 is constructed in a spiral shape, that is, the two ends of the heat exchange core 2 extend radially outward and radially inward of the heat exchange shell 1, respectively. Thus, structuring the first outflow header 5 to extend outward from the radially outer side of the heat exchange shell 1 and the first inflow header 4 to extend outward from the axial end of the heat exchange shell 1 ensures that the heat exchange core 2 extends within the heat exchange shell 1, thereby increasing the heat exchange area of ​​the heat exchange core 2 and improving the heat exchange effect.

[0061] In other embodiments, one of the second inlet header 31 and the second outlet header 32 is configured to be led outward from the radial outer side of the heat exchange shell 1 , and the other is configured to be led outward from the axial end of the heat exchange shell 1 .

[0062] Specifically, the second inlet manifold 31 and the second outlet manifold 32 are respectively connected to the second medium flow channel 3, so that the second medium can enter the heat exchange shell 1 through the second inlet manifold 31 and flow out of the heat exchange shell 1 through the second outlet manifold 32. One of the second inlet manifold 31 and the second outlet manifold 32 is constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the other is constructed to be conducted outward from the axial end of the heat exchange shell 1. That is, the second inlet manifold 31 can be constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the second outlet manifold 32 can be constructed to be conducted outward from the axial end of the heat exchange shell 1. The second outlet manifold 32 can also be constructed to be conducted outward from the radial outer side of the heat exchange shell 1, and the second inlet manifold 31 can be constructed to be conducted outward from the axial end of the heat exchange shell 1.

[0063] In this embodiment, if Figure 1-Figure 4 As shown, the second inlet manifold 31 is configured to extend outward from the radially outer side of the heat exchange housing 1, and the second outlet manifold 32 is configured to extend outward from the axial end of the heat exchange housing 1. The heat exchange core 2 is constructed in a spiral shape, that is, the second medium flow channel 3 is also constructed in a spiral shape, so that the two ends of the second medium flow channel 3 extend radially outward and radially inward of the heat exchange housing 1, respectively. In this way, the second inlet manifold 31 is configured to extend outward from the radially outer side of the heat exchange housing 1, and the second outlet manifold 32 is configured to extend outward from the axial end of the heat exchange housing 1. This ensures that the second medium flow channel 3 extends within the heat exchange housing 1. This in turn increases the heat exchange area between the second medium flow channel 3 and the heat exchange core 2, improving the heat exchange effect.

[0064] In some embodiments, the first inlet manifold 4 is configured to be conducted outward from one axial end of the heat exchange shell 1 , and the second outlet manifold 32 is configured to be conducted outward from the other axial end of the heat exchange shell 1 .

[0065] Specifically, if Figure 1-Figure 4 As shown, the heat exchange core 2 is arranged in the installation cavity 14, and the first inlet manifold 4 and the second outlet manifold 32 are both arranged to extend along the axial direction of the heat exchange shell 1. The first inlet manifold 4 is constructed to be conducted outward from the end of one axial end of the heat exchange shell 1, that is, the first inlet manifold 4 can extend into the installation cavity 14 along the axial direction of the heat exchange shell 1 to be connected with one end of the heat exchange core 2 in the installation cavity 14, so that the first inlet manifold 4 can be connected with the first medium flow channel 21 in the installation cavity 14, so that the first medium can immediately exchange heat with the second medium after entering the installation cavity 14 through the first inlet manifold 4, thereby improving the heat exchange efficiency.

[0066] The second outlet manifold 32 is constructed to be conducted outward from the end of the other axial end of the heat exchange shell 1, and the outlet end of the second medium flow channel 3 can extend to the middle of the installation cavity 14. The second outlet manifold 32 is constructed to be conducted outward from the end of the other axial end of the heat exchange shell 1, which can extend the extension length of the second medium flow channel 3 and increase the heat exchange time of the second medium. After the first medium enters the installation cavity 14, it can exchange heat with the second medium located in the outlet end of the second medium flow channel 3, further exchange heat with the second medium, and improve the heat exchange effect. The second outlet manifold 32 is provided with a flange 9 at the end away from the heat exchange shell 1. The second outlet manifold 32 can be connected to the remaining structures through the flange 9 to ensure connection reliability.

[0067] In some embodiments, a protruding confluence portion 111 is formed on the radial outer side of the heat exchange shell 1 , the second inlet manifold 31 is provided at the confluence portion 111 , and the confluence portion 111 and the first outlet manifold 5 are distributed side by side on the radial outer side of the heat exchange shell 1 .

[0068] Specifically, the heat exchange shell 1 is formed with a confluence portion 111, and as shown in FIG. Figure 1 and Figure 3-Figure 4 As shown, the confluence portion 111 is arranged on the radial outside of the heat exchange shell 1 and protrudes outward in the radial direction of the heat exchange shell 1. The confluence portion 111 is communicated with the installation cavity 14. The second inlet manifold 31 is extended radially along the heat exchange shell 1, and the second inlet manifold 31 is arranged at the confluence portion 111. One end of the second inlet manifold 31 is provided with a flange 9, and the other end of the second inlet manifold 31 is communicated with the confluence portion 111, so that the second inlet manifold 31 can be connected to the remaining structure through the flange 9, and the second medium can flow into the confluence portion 111 through the second inlet manifold 31, and then enter the second medium flow channel 3 through the confluence portion 111.

[0069] Furthermore, the outlet end of the first medium flow channel 21 extends to the heat exchange shell 1, and the first outlet manifold 5 is arranged outside the heat exchange shell 1 and extends axially. The outlet end of the first medium flow channel 21 can be connected to the first outlet manifold 5 outside the heat exchange shell 1, and the confluence portion 111 and the first outlet manifold 5 are distributed side by side on the radial outside of the heat exchange shell 1, so that when the first medium flows through the first medium flow channel 21 to the first outlet manifold 5, it can exchange heat with the second medium flowing into the confluence portion 111, so as to perform preliminary heat exchange on the second medium, and the first medium can be fully utilized, thereby improving the heat exchange effect of the liquid-liquid countercurrent heat exchanger 100.

[0070] In this way, the first inlet manifold 4 can be arranged close to the second outlet manifold 32, and the first outlet manifold 5 can be arranged close to the second inlet manifold 31, so that the extension directions of the first medium flow channel 21 and the second medium flow channel 3 are the same at all locations, so as to increase the heat exchange area of ​​the first medium flow channel 21 and the second medium flow channel 3, and increase the heat exchange time between the first medium and the second medium, improve the heat exchange effect, and ensure the reliability of the liquid-liquid countercurrent heat exchanger 100.

[0071] In some embodiments, the first medium flow channel 21 includes a plurality of microchannels 211 distributed side by side, the extension direction of the plurality of microchannels 211 is the same as the extension direction of the heat exchange core 2, and both ends of the plurality of microchannels 211 are constructed to be connected to the first inlet manifold 4 and the first outlet manifold 5 respectively.

[0072] Specifically, a first medium flow channel 21 is provided in the heat exchange core 2, and the first medium can exchange heat in the first medium flow channel 21. Figure 6 As shown, the first medium flow channel 21 is provided with multiple microchannels 211, and the extension direction of the multiple microchannels 211 is the same as the extension direction of the heat exchange core 2. That is, the heat exchange core 2 can be provided with multiple microchannels 211, and the multiple microchannels 211 can be distributed side by side along the axial direction of the heat exchange core 2. As a result, when the first medium circulates in the heat exchange core 2, it can be evenly distributed throughout the heat exchange core 2. This ensures that the second medium in the second medium flow channel 3 can fully exchange heat with the first medium, and prevents the first medium from converging on one side of the first medium flow channel 21 due to gravity and other reasons, thereby ensuring heat exchange reliability. In addition, the provision of multiple microchannels 211 in the first medium flow channel 21 can reduce the flow area of ​​each microchannel 211, thereby increasing the flow rate of the first medium in each microchannel 211, thereby improving the heat exchange effect.

[0073] The two ends of the first medium flow channel 21 are respectively connected to the first inlet manifold 4 and the first outlet manifold 5, so that the two ends of the multiple microchannels 211 are also respectively connected to the first inlet manifold 4 and the first outlet manifold 5, thereby allowing the first medium to enter the multiple microchannels 211 at the same time through the first inlet manifold 4, and the first medium in the multiple microchannels 211 can simultaneously flow out of the liquid-liquid countercurrent heat exchanger 100 through the first outlet manifold 5 after heat exchange, which can reduce the setting of pipelines, simplify the structure, and reduce the setting cost.

[0074] In some embodiments, the heat exchange shell 1 includes a main shell 11, a first cover plate 12 and a second cover plate 13, and the first cover plate 12 and the second cover plate 13 are respectively connected to the two ends of the main shell 11 to jointly define an installation cavity 14; wherein, one end of the heat exchange core 2 is in close contact with the first cover plate 12 and the other end is in close contact with the second cover plate 13 to jointly define the second medium flow channel 3.

[0075] Specifically, the heat exchange shell 1 is arranged at the outermost side of the liquid-liquid countercurrent heat exchanger 100, and Figure 3-Figure 4 As shown, the heat exchange shell 1 is provided with a main shell 11, a first cover plate 12 and a second cover plate 13. The first cover plate 12 and the second cover plate 13 are respectively connected to the two ends of the main shell 11, that is, the main shell 11 is constructed as an annular structure. The first cover plate 12 and the second cover plate 13 can respectively seal the two ends of the main shell 11 along the axis. The first cover plate 12 and the second cover plate 13 can be connected to the main shell 11 by welding or the like, so that the main shell 11, the first cover plate 12 and the second cover plate 13 can jointly define the installation cavity 14, which is simple to install.

[0076] Furthermore, the heat exchange core 2 is arranged in the installation cavity 14, and one end of the heat exchange core 2 can be in close contact with the first cover plate 12 by welding or the like, and the other end of the heat exchange core 2 can be in close contact with the second cover plate 13 by welding or the like, and the heat exchange core 2 is constructed in a spiral shape, so that the heat exchange core 2, the first cover plate 12 and the second cover plate 13 can jointly define a spiral second medium flow channel 3. The flow area of ​​the first medium flow channel 21 is small, and the pressure on the heat exchange core 2 is large. Setting the heat exchange core 2 as a separate structure can ensure the structural strength of the heat exchange core 2, and thereby ensure the reliability of the circulation of the first medium, and thereby ensure the overall reliability of the liquid-liquid countercurrent heat exchanger 100.

[0077] In some embodiments, a first sealing member 6 is provided at the connection between the main housing 11 and the first cover plate 12 , and the first sealing member 6 is configured as an annular sealing member.

[0078] Specifically, if Figure 1 and Figure 4 As shown, the liquid-liquid countercurrent heat exchanger 100 is further provided with a first seal 6, which can be connected to the first cover plate 12 through a connector 8 or the like. The connector 8 can be set to a bolt or the like, with a simple structure and convenient installation. The first seal 6 can be set to a material such as rubber, and the first seal 6 is set at the connection between the first cover plate 12 and the main shell 11. The flow area of ​​the second medium flow channel 3 is large and the flow rate of the second medium is low, so that the pressure at the connection between the first cover plate 12 and the main shell 11 is small. The first seal 6 can seal the connection between the main shell 11 and the first cover plate 12 to prevent the second medium from overflowing out of the heat exchange shell 1, so as to ensure the reliability of the liquid-liquid countercurrent heat exchanger 100.

[0079] Furthermore, the first sealing member 6 is constructed as an annular sealing member, so that the first sealing member 6 can seal the connection between the main housing 11 and the first cover plate 12 at any position in the circumferential direction to ensure sealing reliability.

[0080] In some other embodiments, a second sealing member 7 is provided at the connection between the main housing 11 and the second cover plate 13 , and the second sealing member 7 is configured as an annular sealing member.

[0081] Specifically, if Figure 1 and Figure 4 As shown, the liquid-liquid countercurrent heat exchanger 100 is further provided with a second seal 7, which can be connected to the second cover plate 13 through a connector 8 or the like. The connector 8 can be set to a bolt or the like, with a simple structure and convenient installation. The second seal 7 can be set to a material such as rubber, and the second seal 7 is arranged at the connection between the second cover plate 13 and the main shell 11. The flow area of ​​the second medium flow channel 3 is large and the flow rate of the second medium is low, so that the pressure at the connection between the second cover plate 13 and the main shell 11 is small. The second seal 7 can seal the connection between the main shell 11 and the second cover plate 13 to prevent the second medium from overflowing out of the heat exchange shell 1, so as to ensure the reliability of the liquid-liquid countercurrent heat exchanger 100.

[0082] Furthermore, the second sealing member 7 is constructed as an annular sealing member, so that the second sealing member 7 can seal the connection between the main housing 11 and the second cover plate 13 at any position in the circumferential direction to ensure sealing reliability.

[0083] The invention also provides a supercooling water unit.

[0084] A subcooling water unit according to an embodiment of the present invention includes any one of the above-mentioned liquid-liquid countercurrent heat exchangers 100 .

[0085] The subcooling water unit is provided with an evaporator and a condenser. The first medium is the high-pressure liquid refrigerant flowing out of the condenser of the subcooling water unit, and the second medium is the cold water from the ice slurry tank that has not yet entered the evaporator of the subcooling water unit.

[0086] According to the subcooling water unit of the embodiment of the present invention, the inlet of the evaporator of the subcooling water unit is provided with a liquid-liquid countercurrent heat exchanger 100, and the liquid-liquid countercurrent heat exchanger 100 is provided with a heat exchange core 2. The heat exchange core 2 is a metal plate with multiple parallel flow channels inside, which is rolled into a spiral shape. The heat exchange core 2 and the heat exchange shell 1 jointly define the second medium flow channel 3, which can simplify the structure of the liquid-liquid countercurrent heat exchanger 100 and reduce the manufacturing cost. At the same time, the flow area of ​​the first medium flow channel 21 is set to be smaller than the flow area of ​​the second medium flow channel 3, which can improve the flow of the first medium in the heat exchanger. The flow rate in the first medium flow channel 21 increases the heat transfer coefficient on the first medium side and ensures the flow rate of the second medium. Furthermore, when the temperature difference in the first medium flow channel 21 and the inlet and outlet temperature difference of the second medium flow channel 3 are relatively large, the heat transfer coefficient of the liquid-liquid countercurrent heat exchanger 100 can be increased, the heat transfer area of ​​the heat exchange core 2 and the storage amount of the first medium in the heat exchange core can be reduced, and the reliability of the liquid-liquid countercurrent heat exchanger 100 can be improved to reduce the volume and material consumption of the subcooling water unit, improve user experience, achieve better use effects, and have a wider range of applications.

[0087] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative uses of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0088] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A liquid-liquid countercurrent heat exchanger (100), characterized in that: include: A heat exchange housing (1), wherein a mounting cavity (14) is defined within the heat exchange housing (1); A heat exchange core (2), the heat exchange core (2) being installed in the installation cavity (14), the heat exchange core (2) being a metal plate having a plurality of parallel flow channels therein and rolled into a spiral shape, and a first medium flow channel (21) being formed in the heat exchange core (2); The heat exchange core (2) and the heat exchange shell (1) jointly define a second medium flow channel (3), the flow area of ​​the first medium flow channel (21) is set to be smaller than the flow area of ​​the second medium flow channel (3), and the flow directions of the first medium in the first medium flow channel (21) and the second medium in the second medium flow channel (3) are opposite.

2. The liquid-liquid countercurrent heat exchanger (100) according to claim 1, characterized in that: The heat exchange core (2) is provided with a first inlet header (4) and a first outlet header (5), and the first inlet header (4) and the first outlet header (5) are respectively communicated with the first medium flow channel (21); And / or, the heat exchange shell (1) is provided with a second inlet header (31) and a second outlet header (32), and the second inlet header (31) and the second outlet header (32) are respectively connected to the second medium flow channel (3).

3. The liquid-liquid countercurrent heat exchanger (100) according to claim 2, characterized in that: One of the first inlet header (4) and the first outlet header (5) is configured to be led outward from the radial outer side of the heat exchange shell (1), and the other is configured to be led outward from the axial end of the heat exchange shell (1); And / or, one of the second inlet header (31) and the second outlet header (32) is configured to be conducted outward from the radial outer side of the heat exchange shell (1), and the other is configured to be conducted outward from the axial end of the heat exchange shell (1).

4. The liquid-liquid countercurrent heat exchanger (100) according to claim 3, characterized in that: The first inlet manifold (4) is configured to be conducted outward from the end of one axial end of the heat exchange shell (1), and the second outlet manifold (32) is configured to be conducted outward from the end of the other axial end of the heat exchange shell (1).

5. The liquid-liquid countercurrent heat exchanger (100) according to claim 3, characterized in that: A protruding confluence portion (111) is formed on the radial outer side of the heat exchange shell (1), the second inlet manifold (31) is arranged on the confluence portion (111), and the confluence portion (111) and the first outlet manifold (5) are distributed side by side on the radial outer side of the heat exchange shell (1).

6. The liquid-liquid countercurrent heat exchanger (100) according to claim 2, characterized in that: The first medium flow channel (21) comprises a plurality of microchannels (211) distributed side by side, the extension direction of the plurality of microchannels (211) being the same as the extension direction of the heat exchange core (2), and both ends of the plurality of microchannels (211) being configured to be in communication with the first inlet manifold (4) and the first outlet manifold (5), respectively.

7. The liquid-liquid countercurrent heat exchanger (100) according to claim 1, characterized in that: The heat exchange housing (1) comprises a main housing (11), a first cover plate (12) and a second cover plate (13); the first cover plate (12) and the second cover plate (13) are respectively connected to two ends of the main housing (11) to jointly define the installation cavity (14); One end of the heat exchange core (2) is in close contact with the first cover plate (12), and the other end is in close contact with the second cover plate (13), so as to jointly define the second medium flow channel (3).

8. The liquid-liquid countercurrent heat exchanger (100) according to claim 7, characterized in that: A first sealing member (6) is provided at the connection between the main housing (11) and the first cover plate (12), and the first sealing member (6) is configured as an annular sealing member; And / or, a second sealing member (7) is provided at the connection between the main housing (11) and the second cover plate (13), and the second sealing member (7) is constructed as an annular sealing member.

9. A subcooling water unit, characterized in that: The invention comprises the liquid-liquid countercurrent heat exchanger (100) according to any one of claims 1 to 8.

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