A new type of shell and tube heat exchanger for organic rankine cycle

Abstract

The utility model relates to a kind of shell-and-tube heat exchanger for novel organic rankine cycle, including cylinder, its inner cavity is separated by baffle into preheating zone, evaporation zone and superheating zone sequentially communicated from liquid inlet pipe to gas outlet pipe. Tube sheet, fixed in the both ends of cylinder. Water inlet chamber and water outlet chamber, shaped in one end of cylinder. Backwater chamber, shaped in the other end of cylinder. Multiple groups of heat exchange tubes, including evaporation zone heat exchange tube and superheating zone heat exchange tube, two ends are connected water inlet chamber and backwater chamber respectively. Preheating zone heat exchange tube, two ends are connected backwater chamber and water outlet chamber respectively. Baffle, be in preheating zone, evaporation zone and superheating zone, cooperate with baffle to form refrigerant flow channel. Liquid inlet pipe, for refrigerant input. Gas outlet pipe, for refrigerant output. High-temperature heat source circulation path, by water inlet chamber, evaporation zone heat exchange tube, superheating zone heat exchange tube, backwater chamber, preheating zone heat exchange tube and water outlet chamber sequentially connected constitute. The scheme has the advantages of integration, high efficiency, simplifying system configuration.

Description

Technical Field

[0001] This utility model relates to the field of organic Rankine cycle technology, and in particular to a novel shell-and-tube heat exchanger for organic Rankine cycles. Background Technology

[0002] The Organic Rankine Cycle (ORC), as a highly efficient medium- and low-temperature heat recovery technology, is widely used in industrial waste heat power generation, geothermal power generation, and solar thermal utilization. Its core lies in using an organic working fluid to drive an expander through a phase change process at a low-temperature heat source, thereby converting heat energy into electrical energy. In this system, the heat exchanger is one of the key pieces of equipment, and its performance directly affects the cycle efficiency and overall operating costs.

[0003] Traditional shell-and-tube heat exchangers are commonly used in ORC systems for preheating, evaporation, and superheating of the working fluid. However, existing shell-and-tube heat exchangers generally suffer from the following problems: functional separation leads to structural complexity; traditional solutions typically use multiple independent heat exchangers to perform preheating, evaporation, and superheating functions separately, resulting in a large system size, complex piping connections, and increased installation and maintenance costs. Heat transfer efficiency is limited; conventional heat exchange tube designs (such as bare tubes or simple finned tubes) are insufficient to effectively enhance heat transfer, especially in the evaporation stage, where insufficient working fluid vaporization nuclei can easily lead to localized overheating or decreased heat transfer efficiency. Heat source utilization is inadequate; the high-temperature heat source flow path design of existing heat exchangers often fails to maximize countercurrent heat transfer, resulting in reduced waste heat recovery efficiency. Therefore, there is an urgent need for an integrated, high-efficiency shell-and-tube heat exchanger that can achieve preheating, evaporation, and superheating of the working fluid within a single device, while simultaneously optimizing heat transfer efficiency, reducing working fluid usage, and simplifying system configuration through structural innovation. This invention is proposed based on this technical requirement.

[0004] To address the aforementioned issues, existing technologies urgently need improvement. Summary of the Invention

[0005] To address the aforementioned problems, the purpose of this invention is to provide a novel shell-and-tube heat exchanger for organic Rankine cycles that offers advantages such as integration, high efficiency, and simplified system configuration.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] This application provides a novel shell-and-tube heat exchanger for organic Rankine cycles, with the following technical solution: It includes a shell body, the inner cavity of which is divided by baffles into a preheating zone, an evaporation zone, and a superheating zone, sequentially connected from the liquid inlet pipe to the gas outlet pipe. A tube sheet is fixed to both ends of the shell body. A water inlet chamber and a water outlet chamber are formed at one end of the shell body. A water return chamber is formed at the other end of the shell body. Multiple sets of heat exchange tubes, including heat exchange tubes in the evaporation zone and heat exchange tubes in the superheating zone, are connected at both ends to the water inlet chamber and the water return chamber, respectively. Heat exchange tubes in the preheating zone are connected at both ends to the water return chamber and the water outlet chamber, respectively. Baffles are disposed within the preheating zone, evaporation zone, and superheating zone, forming refrigerant flow channels in cooperation with the baffles. A liquid inlet pipe is located at the bottom of the shell body for refrigerant input. A gas outlet pipe is located at the top of the shell body for refrigerant output. The high-temperature heat source circulation path consists of the inlet chamber, the heat exchange tubes in the evaporation zone, the heat exchange tubes in the superheated zone, the return water chamber, the heat exchange tubes in the preheating zone, and the outlet chamber connected in sequence.

[0008] Furthermore, this application also proposes that the preheating zone heat exchange tube is a condensation heat exchange tube with an internal tooth and external fin structure. The evaporation zone heat exchange tube has a microporous structure on its outer surface and a threaded structure on its inner wall. The superheated zone heat exchange tube is a high-efficiency heat exchange tube with an enhanced turbulence structure.

[0009] Furthermore, this application also proposes that the preheating zone is provided with multiple baffles arranged in an alternating pattern to form a meandering preheating zone channel. The superheating zone is also provided with multiple baffles arranged in an alternating pattern to form a meandering superheating zone channel.

[0010] Furthermore, this application also proposes that the heat exchange tubes in the evaporation zone are disposed in the lower region of the evaporation zone via a support plate. A vapor-liquid separation zone is formed above the heat exchange tubes in the evaporation zone.

[0011] Furthermore, this application also proposes that an inlet pipe is connected to the inlet chamber and an outlet pipe is connected to the outlet chamber. The inlet chamber and the outlet chamber are separated by a partition.

[0012] Furthermore, this application also proposes that the mounting base plate is connected to the lower end of the tube sheet.

[0013] Furthermore, this application also proposes that the microporous structure surface of the heat exchange tube in the evaporation zone has uniformly distributed vaporization nuclei, and the pitch of the inner wall threads is 0.5-2.0 mm. The fin height of the inner tooth and outer fin structure of the heat exchange tube in the preheating zone is 0.8-1.5 mm, and the tooth spacing is 1.0-3.0 mm.

[0014] Furthermore, this application also proposes that the mounting base plate is equipped with shock-absorbing pads. The support plate is connected to the cylinder by welding or bolts.

[0015] As can be seen from the above, the novel shell-and-tube heat exchanger for organic Rankine cycles and its optimized structure provided in this application achieve the functions of preheating, evaporation and superheating of the working fluid in a single device through integrated design. At the same time, it optimizes heat transfer efficiency, reduces the amount of working fluid, and simplifies system configuration through structural innovation, and has the advantages of integration, high efficiency and simplified system configuration. Attached Figure Description

[0016] Figure 1 This is a cross-sectional schematic diagram of a novel shell-and-tube heat exchanger for an organic Rankine cycle provided in this application.

[0017] Figure 2 A schematic diagram of the end face of a novel shell-and-tube heat exchanger for an organic Rankine cycle provided in this application. Detailed Implementation

[0018] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0019] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0020] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more, unless otherwise expressly defined.

[0021] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. They can refer to a mechanical connection or an electrical connection. They can refer to a direct connection or an indirect connection through an intermediate medium, or a connection within two components. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] like Figure 1 and 2 As shown, this embodiment relates to a novel shell-and-tube heat exchanger for organic Rankine cycles, comprising:

[0024] The cylinder 3 has its internal cavity divided by baffles 5 into a preheating zone, an evaporation zone, and a superheating zone, sequentially connected from the liquid inlet pipe 8 to the gas outlet pipe 9. A tube sheet 1 is fixed to both ends of the cylinder 3. A water inlet chamber 6 and a water outlet chamber 12 are formed at one end of the cylinder 3. A water return chamber 7 is formed at the other end of the cylinder 3. Multiple sets of heat exchange tubes include: evaporation zone heat exchange tube 13 and superheating zone heat exchange tube 14, with their ends connected to the water inlet chamber 6 and the water return chamber 7, respectively. A preheating zone heat exchange tube 15 is connected to the water return chamber 7 and the water outlet chamber 12, respectively. Baffles 4 are located in the preheating zone, evaporation zone, and superheating zone, forming refrigerant flow channels in conjunction with the baffles 5. The liquid inlet pipe 8 is located at the bottom of the cylinder 3 for refrigerant input. The gas outlet pipe 9 is located at the top of the cylinder 3 for refrigerant output. The high-temperature heat source circulation path consists of an inlet chamber 6, an evaporation zone heat exchange tube 13, a superheated zone heat exchange tube 14, a return water chamber 7, a preheating zone heat exchange tube 15, and an outlet chamber 12 connected sequentially. This technical solution divides the inner cavity of the cylinder 3 into preheating, evaporation, and superheating zones, and forms refrigerant flow channels through baffles 5 and baffles 4, achieving preheating, evaporation, and superheating of the working fluid within a single device. The use of multiple sets of heat exchange tubes optimizes heat transfer efficiency and reduces the amount of working fluid required. The design of the high-temperature heat source circulation path simplifies system configuration and improves overall operating efficiency. Compared with existing technologies, this solution, through integrated design, avoids the use of multiple independent heat exchangers, reduces system volume and piping complexity, and optimizes heat transfer efficiency and improves waste heat recovery through structural innovation.

[0025] Furthermore, the preheating zone heat exchange tube 15 adopts a condensing heat exchange tube with an internal tooth and external fin structure, the evaporation zone heat exchange tube 13 has a microporous structure on its outer surface and a threaded structure on its inner wall, and the superheated zone heat exchange tube 14 is a high-efficiency heat exchange tube with enhanced turbulence structure. The internal tooth and external fin structure of the condensing heat exchange tube significantly increases the heat exchange area by setting tooth-like structures on the inner wall and fins on the outer wall, thereby improving the heat transfer efficiency of the preheating zone. The internal tooth and external fin structure of the condensing heat exchange tube can be achieved by machining tooth-like protrusions on the inner side of the tube wall and fins on the outer side. The height and spacing of the tooth-like protrusions and fins can be adjusted according to specific needs to achieve the best heat transfer effect. The application of the microporous outer surface and the threaded inner wall in the evaporation zone heat exchange tube 13 can effectively enhance the distribution of the working fluid's vaporization nucleus and optimize the heat transfer effect during the evaporation process. The high-efficiency heat exchange tube with enhanced turbulence structure further improves the heat transfer efficiency of the superheated zone by increasing the degree of fluid turbulence. The outer surface of the microporous structure can be achieved through laser drilling or chemical etching, while the inner wall of the threaded structure can be completed through threading. High-efficiency heat exchange tubes with enhanced turbulence structures can be achieved by installing baffles inside the tube or changing the tube's geometry. Therefore, this application significantly improves the heat transfer efficiency of the heat exchanger by optimizing the heat exchange tube structure in the preheating, evaporation, and superheating zones. The internal tooth and external fin structure increases the heat transfer area in the preheating zone, the microporous and threaded structures optimize the distribution of vaporization nuclei in the evaporation zone, and the enhanced turbulence structure strengthens the turbulence in the superheating zone. These technical features work together to solve the technical problem of improving the heat transfer efficiency of the heat exchanger. Compared with existing technologies, this application achieves preheating, evaporation, and superheating of the working fluid within a single device, optimizes heat transfer efficiency through structural innovation, reduces the amount of working fluid used, and simplifies system configuration.

[0026] Furthermore, the microporous structure surface of the heat exchange tube 13 in the evaporation zone has uniformly distributed vaporization nuclei, and the pitch of the inner wall threads is 0.5-2.0 mm. The fin height of the internal toothed and external finned structure of the heat exchange tube 15 in the preheating zone is 0.8-1.5 mm, and the tooth spacing is 1.0-3.0 mm. Specifically, the uniform distribution of vaporization nuclei on the microporous structure surface of the heat exchange tube 13 in the evaporation zone helps to form more vaporization nuclei during the vaporization process of the working fluid, thereby improving vaporization efficiency and avoiding local overheating. The pitch of the inner wall threads is 0.5-2.0 mm, which can enhance the flow disturbance of the working fluid in the tube and further improve the heat transfer effect. The internal toothed and external finned structure of the heat exchange tube 15 in the preheating zone, with a fin height of 0.8-1.5 mm and a tooth spacing of 1.0-3.0 mm, significantly improves the heat transfer efficiency of the preheating zone by increasing the heat exchange surface area and optimizing the fluid flow path. Therefore, the technical solution of this application effectively solves the problems of insufficient vaporization core in the evaporation zone heat exchange tube 13 and low heat transfer efficiency in the preheating zone heat exchange tube 15 by optimizing the structural design of the heat exchange tube 13 in the evaporation zone and the heat exchange tube 15 in the preheating zone, thereby improving the overall performance of the heat exchanger. Compared with the prior art, the technical solution of this application has significant advantages in terms of vaporization efficiency and heat transfer efficiency, and its structure is simple and easy to implement.

[0027] like Figure 1 As shown, multiple staggered baffles 4 are arranged in the preheating zone, forming a meandering preheating zone channel. Similarly, multiple staggered baffles 4 are arranged in the superheating zone, forming a meandering superheating zone channel. The staggered distribution of the baffles 4 makes the refrigerant flow path more complex in the preheating and superheating zones. Specifically, the baffles 4 can be arranged horizontally, vertically, or obliquely, thereby increasing the contact area and contact time between the refrigerant and the heat exchange tubes. As a preferred embodiment, the shape of the baffles 4 can be rectangular, trapezoidal, or wavy to further optimize the flow path. Furthermore, the spacing of the baffles 4 can be adjusted according to the refrigerant flow rate and heat exchange requirements. For example, a smaller spacing can increase turbulence, while a larger spacing can reduce flow resistance. By setting up staggered baffles 4 in the preheating and superheating zones to form a meandering channel, the flow path length of the refrigerant in the preheating and superheating zones is increased, extending the contact time between the refrigerant and the heat exchange tubes, thereby improving heat exchange efficiency. The staggered distribution design of the baffles 4 generates more turbulence during refrigerant flow, further enhancing the heat transfer effect and solving the problems of single refrigerant flow path and low heat exchange efficiency in traditional heat exchangers. Compared with existing technologies, this solution significantly improves the overall performance of the heat exchanger by optimizing the flow path and increasing turbulence, while simplifying the structural design and reducing manufacturing costs and maintenance difficulty.

[0028] Furthermore, the heat exchange tubes 13 in the evaporation zone are positioned in the lower part of the evaporation zone via a support plate 10, and a vapor-liquid separation zone 19 is formed above the heat exchange tubes 13. The support plate 10 serves to fix the position of the heat exchange tubes 13 in the evaporation zone, ensuring their stable arrangement within the evaporation zone. The vapor-liquid separation zone above the heat exchange tubes 13 allows for effective separation of the liquid and gaseous working fluids during evaporation, preventing gas-liquid mixing from affecting heat exchange efficiency. The liquid refrigerant, after being carried upwards, condenses and falls back down, thus continuing to evaporate.

[0029] By fixing the support plate 10 and forming the vapor-liquid separation zone, the problem of poor vapor-liquid separation caused by unreasonable arrangement of the heat exchange tubes 13 in the evaporation zone is solved, thus improving the overall performance of the heat exchanger. Specifically, the support plate 10 can be implemented in various forms. For example, the support plate 10 can be a flat structure or a structure with grooves or protrusions to better fix the heat exchange tubes 13 in the evaporation zone. In addition, the support plate 10 can be fixed to the cylinder 3 by welding or bolting to ensure its stability. The arrangement of the heat exchange tubes 13 in the evaporation zone can also be adjusted according to actual needs. For example, multiple rows or staggered arrangements can be used to optimize the heat exchange effect. The design of the vapor-liquid separation zone can be achieved by adjusting the distance between the heat exchange tubes 13 in the evaporation zone and the top of the cylinder 3 to ensure that the gaseous working fluid can rise smoothly and separate. In this respect, the working principle of this technical solution is that, through the fixing effect of the support plate 10, the arrangement of the heat exchange tubes 13 in the evaporation zone is more reasonable, avoiding the problem of poor vapor-liquid separation caused by improper arrangement. Meanwhile, the vapor-liquid separation zone formed above the heat exchange tube 13 in the evaporation zone allows for effective separation of the liquid and gaseous working fluids during evaporation, avoiding the impact of gas-liquid mixing on heat exchange efficiency. Compared with existing technologies, this technical solution significantly improves the overall performance of the heat exchanger through structural optimization and solves technical problems in practical applications.

[0030] Furthermore, an inlet pipe 16 is connected to the inlet chamber 6, and an outlet pipe 17 is connected to the outlet chamber 12. The inlet chamber 6 and the outlet chamber 12 are separated by a partition 18. The inlet pipe 16 is used to input liquid into the inlet chamber 6, and the outlet pipe 17 is used to output liquid from the outlet chamber 12. The design of the partition 18 completely separates the inlet chamber 6 and the outlet chamber 12 spatially, ensuring that the liquids do not interfere with each other during flow. The partition 18 can be made of metal, plastic, or other corrosion-resistant materials, depending on the properties of the liquid and the operating environment. In addition, the thickness and shape of the partition 18 can be adjusted according to actual needs to optimize the control effect of liquid flow. The connection method between the inlet pipe 16 and the outlet pipe 17 can be threaded, flanged, or welded to ensure the sealing and stability of the connection. The baffle 18 can be installed in a fixed or detachable manner. A fixed baffle 18 is fixed inside the cylinder 3 by welding or bolts, while a detachable baffle 18 is installed and removed quickly using a sealing ring or snap-fit ​​structure. As a preferred embodiment, the baffle 18 can be designed with a flow guide groove to further optimize the liquid flow path and reduce flow resistance. This technical solution connects the inlet chamber 6 and outlet chamber 12 to the inlet pipe 16 and outlet pipe 17 respectively, and separates them using the baffle 18, achieving effective control of the liquid flow. The design of the baffle 18 not only ensures that the liquids do not interfere with each other during flow but also simplifies liquid flow management and improves the system's operating efficiency and stability. Compared with existing technologies, this solution, through structural innovation, avoids the intersection and interference of liquid flow paths, thereby significantly improving the control accuracy of liquid flow and the overall performance of the system.

[0031] Furthermore, the mounting base plate 11 is connected to the lower end of the tube sheet 1. The mounting base plate 11 can be connected to the lower end of the tube sheet 1 by welding, bolting, or other fixing methods. As a preferred embodiment, the mounting base plate 11 may be equipped with shock-absorbing pads to further reduce the risk of loosening or damage caused by vibration or external forces. In addition, the material of the mounting base plate 11 can be high-strength steel or other materials with good mechanical properties to ensure that it can provide stable support for the tube sheet 1. Through this connection method, the mounting base plate 11 can provide stable support for the tube sheet 1, thereby enhancing the structural stability of the entire heat exchanger. Specifically, the connection between the mounting base plate 11 and the tube sheet 1 is more robust, reducing the risk of loosening or damage caused by vibration or external forces, and ensuring the long-term stable operation of the heat exchanger. Compared with the prior art, this design not only simplifies the structure but also improves the reliability and service life of the heat exchanger, solving the technical problem of unstable connection between the mounting base plate 11 and the tube sheet 1.

[0032] In summary, this technical solution simplifies the system structure and reduces installation and maintenance costs by integrating the preheating zone, evaporation zone, and superheating zone into a single shell 3. The use of multiple heat exchange tubes and baffles 4 optimizes the refrigerant flow path and improves heat exchange efficiency. The design of the high-temperature heat source circulation path maximizes counter-current heat exchange and improves waste heat recovery efficiency. Compared with existing technologies, this solution has significant advantages in structural integration, heat exchange efficiency, and full utilization of the heat source, effectively solving the technical problems of complex structure, limited heat exchange efficiency, and insufficient heat source utilization caused by the functional separation of traditional shell-and-tube heat exchangers in organic Rankine cycle systems.

[0033] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions 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 one or more embodiments or examples.

[0034] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention.

Claims

1. A novel shell-and-tube heat exchanger for organic Rankine cycles, characterized in that, include: - The inner cavity of the cylinder (3) is divided by a baffle (5) into a preheating zone, an evaporation zone and a superheating zone that are connected sequentially from the liquid inlet pipe (8) to the gas outlet pipe (9); - Tube sheet (1), fixed to both ends of cylinder (3); - The inlet chamber (6) and the outlet chamber (12) are formed at one end of the cylinder (3); the return chamber (7) is formed at the other end of the cylinder (3); - Multiple heat exchange tubes, including: - Evaporation zone heat exchange tube (13) and superheated zone heat exchange tube (14), with their ends connected to the water inlet chamber (6) and the water return chamber (7), respectively. - The heat exchange tube (15) in the preheating zone is connected to the return water chamber (7) and the outlet water chamber (12) at both ends respectively; - Baffle (4) is installed in the preheating zone, evaporation zone and superheating zone, and works with baffle (5) to form a refrigerant flow channel; - Liquid inlet pipe (8), located at the bottom of the cylinder (3), is used for refrigerant input; - Gas outlet pipe (9), located at the top of the cylinder (3), is used for refrigerant output; - The high-temperature heat source circulation path is composed of the water inlet chamber (6), the heat exchange tube in the evaporation zone (13), the heat exchange tube in the superheated zone (14), the return water chamber (7), the heat exchange tube in the preheating zone (15), and the water outlet chamber (12) connected in sequence.

2. The shell-and-tube heat exchanger according to claim 1, characterized in that: - The heat exchange tube (15) in the preheating zone is a condensation heat exchange tube with an internal tooth and external fin structure; - The outer surface of the heat exchange tube (13) in the evaporation zone has a microporous structure and the inner wall has a threaded structure; - The heat exchange tube (14) in the superheated zone is a high-efficiency heat exchange tube with enhanced turbulent flow structure.

3. The shell-and-tube heat exchanger according to claim 1, characterized in that: - The preheating zone is equipped with multiple staggered baffles (4) to form a circuitous preheating zone channel; - The superheated zone is provided with multiple baffles (4) arranged in an alternating manner to form a meandering superheated zone channel.

4. The shell-and-tube heat exchanger according to claim 1, characterized in that: - The heat exchange tube (13) in the evaporation zone is installed in the lower part of the evaporation zone via a support plate (10); - A vapor-liquid separation zone (19) is formed above the heat exchange tube (13) in the evaporation zone.

5. The shell-and-tube heat exchanger according to claim 1, characterized in that: - The inlet chamber (6) is connected to the liquid inlet pipe (16), and the outlet chamber (12) is connected to the liquid outlet pipe (17). - The inlet chamber (6) and the outlet chamber (12) are separated by a partition (18).

6. The shell-and-tube heat exchanger according to claim 4, characterized in that: - The mounting base plate (11) is connected to the lower end of the tube sheet (1).

7. The shell-and-tube heat exchanger according to claim 2, characterized in that: - The microporous structure of the heat exchange tube (13) in the evaporation zone has uniformly distributed vaporization cores on its surface, and the pitch of the inner wall thread is 0.5-2.0 mm; - The fin height of the inner toothed outer fin structure of the heat exchange tube (15) in the preheating zone is 0.8-1.5 mm, and the tooth spacing is 1.0-3.0 mm.

8. The shell-and-tube heat exchanger according to claim 6, characterized in that: - The mounting base plate (11) is provided with shock-absorbing pads; - The support plate (10) is connected to the cylinder (3) by welding or bolting.

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