High efficiency shell and tube heat exchanger

Abstract

The utility model relates to heat exchange equipment technical field especially relates to a kind of high-efficiency shell and tube heat exchanger, including: shell, its lateral wall is equipped with water inlet and water outlet;Two ends of shell are closed, and at least one end is provided with tube sheet;Its characterized in that: the outer end face of tube sheet is sealingly connected with first tube box and second tube box;First tube box is connected with refrigerant liquid interface;Second tube box is connected with refrigerant gas interface;Shell interior is provided with heat exchange tube bundle, and its both ends pipe orifice are respectively connected on the tube sheet in first tube box and second tube box.The scheme has the advantages of improving sealing performance, enhancing modularization expansibility and optimizing refrigerant distribution accuracy.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange equipment technology, and in particular to a high-efficiency shell and tube heat exchanger. Background Technology

[0002] Traditional shell-and-tube heat exchangers typically employ a cylindrical shell structure with heat exchange tube bundles fixed to a tube sheet inside, and a tube box on the outside of the tube sheet for refrigerant distribution. Existing technologies generally suffer from three key technical defects: First, the chamber structure within the tube box, separated by baffles, poses a sealing risk; when pressure differences exist between different chambers, refrigerant cross-flow can easily occur, severely impacting heat exchange efficiency. Second, the traditional integrated tube box structure lacks a modular design concept, making it impossible to flexibly adjust the number and layout of tubes according to actual operating conditions. Third, the refrigerant distribution system is poorly designed, particularly exhibiting uneven distribution of the gas-liquid two-phase flow, leading to an imbalance in the gas-liquid ratio within the upper heat exchange tubes and significantly reducing overall heat exchange performance.

[0003] Existing solutions are mostly limited to localized improvements on single problems, failing to systematically address the compatibility issues between distribution accuracy and process expansion. For example, conventional distribution structures struggle to simultaneously meet the multiple requirements of refrigerant buffering, gas-liquid separation, and precise distribution at the nozzle level, while fixed tube box designs restrict the flexibility of multi-process expansion. These problems severely limit the application effectiveness and energy efficiency of shell-and-tube heat exchangers under complex operating conditions.

[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 high-efficiency shell-and-tube heat exchanger that offers advantages such as improved sealing performance, enhanced modular expandability, and optimized refrigerant distribution accuracy.

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

[0007] This application provides a high-efficiency shell-and-tube heat exchanger, the technical solution of which is as follows: A high-efficiency shell-and-tube heat exchanger, comprising:

[0008] • The shell has an inlet and an outlet on its side wall;

[0009] The shell is closed at both ends, and at least one end is provided with a tube sheet; characterized in that:

[0010] • A first tube box and a second tube box are sealed and connected to the outer end face of the tube sheet;

[0011] • The first pipe box is connected to a refrigerant liquid interface;

[0012] • The second pipe box is connected to a refrigerant gas interface;

[0013] The shell contains a heat exchange tube bundle, with its two ends connected to the tube sheets in the first tube box and the second tube box, respectively.

[0014] Furthermore, this application also proposes that a gas equalization plate be provided inside the second tube box, the gas equalization plate being located between the refrigerant gas interface and the end of the heat exchange tube bundle.

[0015] Furthermore, this application also proposes that a primary distribution plate and a secondary distribution plate be provided inside the first pipe box;

[0016] • The primary distribution plate is located at the inner end of the refrigerant liquid interface;

[0017] The secondary distribution plate is installed at the inlet of the heat exchange tube bundle.

[0018] Furthermore, this application also proposes that the primary distribution plate has a hemispherical or cylindrical structure with distribution holes evenly distributed on its surface.

[0019] Furthermore, this application also proposes that the distribution holes of the secondary distribution plate have a flanged protrusion structure, with the protrusion direction facing the tube opening of the heat exchange tube bundle;

[0020] The number of distribution holes corresponds one-to-one with the number of heat exchange tubes in the heat exchange tube bundle.

[0021] Furthermore, this application also proposes that the lower end region of the first tube box is connected to a liquid refrigerant outlet.

[0022] Furthermore, this application also proposes that a third tube box is sealed and connected to the outer end face of the tube sheet;

[0023] The heat exchange tube bundle includes a first heat exchange tube bundle and a second heat exchange tube bundle.

[0024] • The two ends of the first heat exchange tube bundle are respectively connected to the tube sheets in the first tube box and the third tube box;

[0025] The two ends of the second heat exchange tube bundle are respectively connected to the tube sheets inside the third tube box and the second tube box.

[0026] Furthermore, this application also proposes that the two ends of the shell are closed by end plates and tube sheets, respectively;

[0027] • Both the first heat exchanger tube bundle and the second heat exchanger tube bundle contain at least two heat exchanger tubes.

[0028] • The inner ends of adjacent heat exchange tubes are connected by U-shaped joints.

[0029] Furthermore, this application also proposes that a water distribution plate be installed at both the inlet and outlet.

[0030] • The water distribution plate adopts a gradually expanding flow channel structure;

[0031] • Multiple sets of baffles are installed inside the shell between the inlet and outlet to form a meandering flow channel.

[0032] Furthermore, this application also proposes that the heat exchange tubes be made of copper, stainless steel or titanium.

[0033] Furthermore, this application also proposes that the first tube box, the second tube box, and the third tube box are sealed and fixed to the tube sheet by welding, bonding, or flange connection structures.

[0034] As can be seen from the above, the high-efficiency shell-and-tube heat exchanger and its distribution structure and multi-flow expansion system provided in this application effectively solve the problems of poor sealing, uneven distribution and limited flow expansion of traditional heat exchangers through independent tube box sealing connection, gas distribution plate and graded distribution plate design, and multi-tube box combination expansion. It has the advantages of improving sealing performance, enhancing modular expansion and optimizing refrigerant distribution accuracy. Attached Figure Description

[0035] Figure 1 This is a schematic cross-sectional view of the first structure of a high-efficiency shell-and-tube heat exchanger provided in this application.

[0036] Figure 2 This is a schematic diagram of the first structural end face of a high-efficiency shell-and-tube heat exchanger provided in this application.

[0037] Figure 3 This is a schematic cross-sectional view of a second structure of a high-efficiency shell-and-tube heat exchanger provided in this application.

[0038] Figure 4 This is a schematic diagram of the second structural end face of a high-efficiency shell-and-tube heat exchanger provided in this application. Detailed Implementation

[0039] The embodiments of this utility model are described in detail below, examples of which are shown in the accompanying drawings, wherein the embodiments are consistent throughout.

[0040] Same or similar reference numerals denote 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 intended to explain the present invention, and should not be construed as limiting the present invention.

[0041] 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.

[0042] 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.

[0043] 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; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0044] 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.

[0045] In existing technologies, shell-and-tube heat exchangers are widely used in industrial refrigeration systems. Their core structure includes the shell, tube sheet, and internal heat exchange tube bundle. In traditional designs, the tube box and tube sheet are integrated, with internal partitions separating the chambers to achieve multi-pass heat exchange. However, this structure has inherent drawbacks: insufficient sealing between different chambers within the tube box allows refrigerant to easily cross-contaminate due to pressure differences; furthermore, the integrated tube box makes it difficult to flexibly adjust the number of passes, limiting modular expansion. For example, in evaporator applications, after liquid refrigerant enters the tube box, uneven distribution leads to an imbalance in the gas-liquid mixing ratio in some heat exchange tubes, significantly reducing heat exchange efficiency.

[0046] To address the aforementioned issues, the research and development process revealed that the root cause of cross-contamination risks and uneven refrigerant distribution lay in insufficient sealing and a lack of buffer space within the tube box's internal chambers. By rethinking the connection between the tube box and the tube sheet, an attempt was made to independently install the tube box on the outer end face of the tube sheet, forming a completely isolated refrigerant buffer chamber. This approach not only eliminates leakage paths caused by pressure differences between chambers but also creates space for optimized installation of the distribution structure. Further considering modular requirements, a split-type tube box design was adopted, allowing process expansion without modifying the main shell structure; multiple process switching can be achieved simply by adding or removing tube boxes.

[0047] like Figure 1-4 As shown, this embodiment relates to a high-efficiency shell-and-tube heat exchanger, including a shell 1 with an inlet 8 and an outlet 9 on its side wall. The shell 1 is closed at both ends, and at least one end is provided with a tube sheet 2. A first tube box 4 and a second tube box 3 are sealed and connected to the outer end face of the tube sheet 2. The first tube box 4 is connected to a refrigerant liquid interface 10. The second tube box 3 is connected to a refrigerant gas interface 11. A heat exchange tube bundle is disposed inside the shell 1, with its two ends connected to the tube sheet 2 inside the first tube box 4 and the second tube box 3, respectively. The shell 1 refers to the main structure containing the heat exchange medium, which can be implemented as a cylindrical metal shell. The inlet 8 and outlet 9 on the side wall are used for shell-side medium circulation. The tube sheet 2 refers to the supporting component that fixes the heat exchange tube bundle, which can be implemented as a steel plate with through holes. The through holes are used to pass through the heat exchange tubes 51 and form a sealed connection with the tube box. The sealed connection refers to the leak-free fixing method between the tube box and the tube sheet 2, which can be implemented by welding or flange connection to ensure that the refrigerant buffer chamber is independently sealed. The refrigerant liquid interface 10 and gas interface 11 refer to the channels for conveying liquid and gaseous refrigerant respectively. These can be implemented using flange joints or threaded interfaces to achieve phase separation of the refrigerant input. The heat exchange tube bundle is the core component for heat exchange, and can be implemented using straight tubes or U-shaped tube arrays, with both ends fixed to the tube sheet 2 by expansion joints or welding.

[0048] Specifically, liquid refrigerant enters the first tube box 4 through the refrigerant liquid interface 10, and gaseous refrigerant enters the second tube box 3 through the refrigerant gas interface 11. After the two tube boxes are sealed and connected to the tube sheet 2, two completely isolated chambers are formed, eliminating the risk of differential pressure leakage caused by traditional partitioned chambers. The two ends of the heat exchange tube bundle are fixed to the corresponding tube sheets 2 of the two tube boxes, forming refrigerant flow channels. When the liquid refrigerant flows in the heat exchange tube 51, it absorbs heat from the shell-side medium and partially evaporates. After the gas-liquid mixture enters the second tube box 3, the gaseous refrigerant is discharged from the gas interface 11. The shell-side medium enters the shell 1 through the water inlet 8, and under the guidance of the baffle 6, it laterally washes the heat exchange tube bundle and is discharged through the water outlet 9, completing the heat exchange.

[0049] Traditional integrated tube boxes separate chambers using internal partitions. The welded seals between the partitions and the inner wall of the tube box are difficult to guarantee long-term reliability and are prone to micro-cracks due to thermal stress, leading to cross-contamination. This solution independently positions the first tube box 4 and the second tube box 3 on the outer end face of the tube sheet 2, completely isolating the two chambers through an external sealing connection, fundamentally eliminating cross-contamination paths. Furthermore, the split tube box design allows for process expansion by adding or removing tube boxes; for example, adding a third tube box 17 can create a multi-process structure without replacing the shell 1 or the integral tube sheet 2, significantly improving modular assembly efficiency. Through this technical solution, refrigerant liquid and gas enter independently sealed tube boxes, avoiding media cross-contamination due to pressure differences. The split tube box structure provides independent space for the installation of the distribution plate, ensuring uniform distribution of the gas and liquid phases to each heat exchange tube 51. The detachable connection between the tube box and the tube sheet 2 supports rapid addition or removal of process modules, meeting diverse heat exchange needs.

[0050] like Figure 1 and 3 As shown, a gas equalization plate 15 is provided in the second tube box 3, which is located between the refrigerant gas interface 11 and the end of the heat exchange tube bundle.

[0051] The gas equalization plate 15 refers to a plate-shaped component with a flow-guiding structure, which can be implemented as a perforated plate or a flow-guiding grid. Its surface has uniformly distributed flow-guiding holes or grooves to disperse the concentrated flow of gaseous refrigerant. The gas equalization plate 15 is positioned between the refrigerant gas interface 11 and the end of the heat exchange tube bundle, directly intercepting the gas flow entering from the interface and changing the airflow direction through the physical segmentation effect of the flow-guiding holes or grooves. Specifically, after the gaseous refrigerant enters the second tube box 3 from the refrigerant gas interface 11, it first impacts the surface of the gas equalization plate 15. The flow-guiding holes or grooves on the surface of the gas equalization plate 15 divide the concentrated airflow into multiple smaller streams, forcing the gas to undergo turbulent mixing as it passes through the flow-guiding structure. The segmented airflow forms a secondary diffusion within the cavity between the gas equalization plate 15 and the end of the heat exchange tube bundle, and the gas velocity is redistributed within the cavity space. Before entering the heat exchange tube bundle, the airflow direction of the airflow passing through the equalization plate 15 is adjusted to be perpendicular to the end face of the tube bundle, making the airflow at each heat exchange tube inlet more even. This solution, through the guiding and dividing effect of the equalization plate 15, fundamentally eliminates the phenomenon of concentrated gas flow, ensuring the uniformity of gas distribution in each heat exchange tube 51. Through the above technical solution, this application achieves uniform distribution of gaseous refrigerant at the inlet of the heat exchange tube bundle, avoiding tube wall erosion losses caused by excessively high local flow velocities, while ensuring that the gas flow rate of all heat exchange tubes 51 is consistent, thus improving the overall heat exchange efficiency of the heat exchange tube bundle.

[0052] like Figure 1 and 3 As shown, a primary distribution plate 13 and a secondary distribution plate 14 are provided inside the first tube box 4. The primary distribution plate 13 is located at the inner end of the refrigerant liquid interface 10, and the secondary distribution plate 14 is located at the inlet of the heat exchange tube bundle. The primary distribution plate 13 refers to the porous structure located at the end of the refrigerant liquid interface 10, used for the initial diffusion of the refrigerant entering the tube box. The secondary distribution plate 14 refers to the flow-guiding structure covering the inlet of the heat exchange tube bundle, used to directionally guide the refrigerant into the corresponding inlet. Specifically, after the refrigerant enters the first tube box 4 from the liquid interface, it first passes through the distribution holes of the primary distribution plate 13, where the flow velocity is dispersed and a uniform initial distribution is formed. Subsequently, the fluid flows to the secondary distribution plate 14, where the flanged protrusions guide the refrigerant along a fixed path into the heat exchange tube 51, avoiding flow differences between different inlets. Through these two distribution processes, the flow state of the gas-liquid mixed refrigerant is adjusted step by step, ultimately achieving uniform distribution at the inlet of each heat exchange tube 51.

[0053] Furthermore, the primary distribution plate 13 has a hemispherical or cylindrical structure with uniformly distributed distribution holes on its surface. The primary distribution plate 13 refers to the plate-like structure located at the inner end of the refrigerant liquid interface 10, used for the initial distribution of the incoming refrigerant. The hemispherical or cylindrical structure refers to a geometric shape with an outwardly convex curved surface, which can be achieved using metal stamping or casting processes. The curved surface structure guides the fluid to diffuse along the tangential direction, reducing fluid impact caused by right-angled or planar structures. The uniformly distributed distribution holes refer to through holes arranged on the plate surface with the same spacing and diameter, which can be achieved using laser cutting or drilling processes. The uniformly distributed through holes enable uniform spatial distribution of the refrigerant as it flows through. In use, after the refrigerant liquid enters the pipe box, it first impacts the curved area of ​​the primary distribution plate 13, forming a diffuse flow along the tangential direction under the guidance of the curved surface, reducing local stagnation. Subsequently, the refrigerant is divided into multiple streams with similar flow rates through uniformly distributed distribution holes, providing uniform initial conditions for subsequent secondary distribution. The curved surface structure changes the direction of fluid movement, enabling the gas and liquid phases to achieve initial separation under centrifugal force, thus preventing gas from accumulating in the upper region of the distribution plate.

[0054] Furthermore, the distribution holes of the secondary distribution plate 14 are flanged protrusions, with the protrusions facing the inlets of the heat exchange tube bundle. The number of distribution holes corresponds one-to-one with the number of heat exchange tubes 51 in the heat exchange tube bundle. The flanged protrusion structure refers to the edge of the distribution hole extending axially to form a guide surface, which can be achieved using stamping or spinning processes. This structure changes the fluid flow direction, causing it to enter the inlet along the axial direction of the heat exchange tube 51. The one-to-one correspondence of the number of distribution holes means that the central axis of each distribution hole coincides with the central axis of the corresponding heat exchange tube 51. This can be achieved using laser positioning or mold positioning processes. This design ensures that the refrigerant flow channel and the inlet of the heat exchange tube 51 form a deviation-free connection. In use, when the refrigerant flows through the secondary distribution plate 14, the guide surface of the flanged protrusion structure constrains the fluid movement direction to be parallel to the axial direction of the heat exchange tube 51, suppressing phase separation caused by inertial differences during the distribution process of the gas-liquid two-phase flow. The one-to-one correspondence between the distribution holes and the heat exchange tubes 51 allows the fluid to directly enter the target heat exchange tube 51 after leaving the distribution plate, avoiding momentum loss caused by collisions between the fluid and adjacent tube openings in a free jet state. The annular guiding channel formed by the flanged protrusion can reduce the turbulence intensity of the fluid at the tube opening, allowing the gas-liquid mixture to enter the heat exchange tube 51 in a laminar flow state.

[0055] In addition, a liquid refrigerant outlet 12 is connected to the lower region of the first tube box 4. The liquid refrigerant outlet 12 refers to the drainage structure connected to the bottom region of the tube box, which can be implemented using a flanged or threaded interface, used to discharge the liquid refrigerant accumulated at the bottom of the tube box. The lower region refers to the liquid collection area formed by the downward extension of the bottom of the tube box, which can be achieved by optimizing the inclination angle or curvature of the inner wall of the tube box, allowing the liquid refrigerant to flow naturally to the outlet position under gravity. In heating mode, the liquid working fluid formed after the refrigerant gas condenses after passing through the heat exchange tube bundle collects downward along the inner wall of the tube box, flows out through this outlet, and re-enters the circulation system, thereby maintaining the dynamic balance of the gas-liquid two-phase flow inside the tube box. Through the above technical solution, this application effectively eliminates the phenomenon of liquid refrigerant residue in the tube box, ensures the uniform distribution of the gas-liquid mixed working fluid in the heat exchange tube bundle, improves the evaporation heat exchange efficiency, and provides a liquid working fluid recovery channel for multi-process heat exchange systems, avoiding waste of working fluid during the circulation process.

[0056] like Figure 3 and 4 As shown, a third tube box 17 is sealed and connected to the outer end face of the tube sheet 2, dividing the heat exchange tube bundle into a first heat exchange tube bundle 5a and a second heat exchange tube bundle 5b. The two ends of the first heat exchange tube bundle 5a are connected to the tube sheet 2 inside the first tube box 4 and the third tube box 17, respectively. The two ends of the second heat exchange tube bundle 5b are connected to the tube sheet 2 inside the third tube box 17 and the second tube box 3, respectively. The third tube box 17 is a sealed cavity independent of the first tube box 4 and the second tube box 3. It can be fixed to the outer end face of the tube sheet 2 by welding, bonding, or flange connection, forming a refrigerant buffer space to isolate media in different processes and achieve staged flow. Specifically, after the refrigerant enters the first heat exchange tube bundle 5a from the first tube box 4 for initial heat exchange, it flows into the third tube box 17 for buffering, then enters the second heat exchange tube bundle 5b for secondary heat exchange, and finally exits through the second tube box 3. The third tube box 17 serves as an intermediate buffer chamber, isolating the flow media between the first heat exchange tube bundle 5a and the second heat exchange tube bundle 5b, and forming multiple flow paths through a staged connection. Increasing the number of tube boxes does not change the structure of the shell 1; process expansion can be achieved simply by adding a sealed, independent chamber to the outer end face of the tube sheet 2.

[0057] Compared to existing technologies, traditional solutions use integrated tube boxes to separate chambers, which pose a risk of cross-contamination due to insufficient sealing, and the number of flow paths is fixed and cannot be adjusted. This solution, through modular stacking of independent tube boxes, achieves flexible configuration of the number of flow paths while ensuring the sealing of each chamber. In existing technologies, the refrigerant flow path is limited by the layout of a single tube box partition, while this solution extends the flow path and improves heat exchange efficiency through staged tube bundle connections. Through the above technical solutions, this application solves the problem of media leakage caused by poor sealing of the tube box structure and eliminates pressure difference interference between different flow paths. The modular tube box connection method allows for flow expansion without modifying the shell 1; the heat exchange path length can be adjusted simply by increasing or decreasing the number of tube boxes to adapt to different operating conditions. The staged tube bundle design extends the residence time of the refrigerant in the heat exchange tubes 51, improving heat exchange efficiency.

[0058] like Figure 3 and 4As shown, the two ends of the shell 1 are sealed by end plates 7 and tube sheets 2, respectively. The first heat exchange tube bundle 5a and the second heat exchange tube bundle 5b each contain at least two heat exchange tubes 51. The inner ends of adjacent heat exchange tubes 51 are connected by U-shaped joints 52. The sealing by end plates 7 and tube sheets 2 means that the two ends of the shell 1 are respectively sealed by the combination of end plates 7 and tube sheets 2, which can be achieved by flange connection or welding. The heat exchange tube bundle containing at least two heat exchange tubes 51 means that each heat exchange tube bundle consists of multiple independent heat exchange tubes 51, which can be copper or stainless steel tubes fixed to the tube sheet 2 by mechanical flaring. The U-shaped joint 52 connection means that the ends of adjacent heat exchange tubes 51 are connected by a bent tube structure, which can be manufactured by stamping or brazing. This structure forms a continuous flow channel through a detachable connection, while reducing the number of tube sheets 2 on one side to simplify the overall layout. Specifically, the two ends of the shell 1 are sealed by the combination of end plates 7 and tube sheets 2, forming mutually isolated sealed chambers. The first heat exchange tube bundle 5a and the second heat exchange tube bundle 5b each contain at least two independent heat exchange tubes 51, allowing the tube bundles to be assembled or replaced independently. The inner ends of adjacent heat exchange tubes 51 are connected by U-shaped joints 52, which allows the tube bundle modules to expand the flow without changing the structure of the shell 1 while maintaining the continuity of medium flow. For example, when a third tube box 17 needs to be added, only the connection sequence of the U-shaped joints 52 needs to be adjusted to achieve the switch from a two-flow to a four-flow system, without modifying the shell 1. This solution achieves physical isolation of the chambers through the split end plate 7 and the tube sheet 2 closed structure, completely eliminating medium cross-permeability. Through the combination of modular heat exchange tube bundles and U-shaped joints 52, the flow expansion only requires adjusting the tube bundle connection method without changing the main structure of the shell 1. Through the above technical solution, this application solves the cross-cavity problem caused by insufficient sealing in traditional shell-and-tube heat exchangers, and realizes independent sealed operation between different processes. The modular tube bundle design and detachable U-shaped joint 52 enable the heat exchanger to expand the process without changing the structure of the shell 1, reducing equipment modification costs and maintenance difficulty.

[0059] This application further proposes to install water distribution plates 16 at the inlet 8 and outlet 9. The water distribution plates 16 adopt a gradually expanding flow channel structure, and multiple sets of baffles 6 are arranged inside the shell 1 between the inlet 8 and outlet 9 to form a meandering flow channel. The water distribution plates 16 refer to flow guiding components installed at the inlet and outlet of the shell-side medium. Specifically, they can be plate-shaped structures with a cross-sectional area that gradually increases along the flow direction. Their gradually expanding flow channels can reduce the medium velocity and uniformly disperse the fluid. This structure reduces the impact kinetic energy, allowing the fluid to smoothly enter the shell 1 and avoiding uneven distribution caused by local turbulence. The baffles 6 refer to flow guiding devices fixed to the inner wall of the shell 1. Specifically, they can be alternately arranged arc-shaped or segmental plates. The meandering flow channels they form can forcibly change the flow direction of the shell-side medium. This structure, by extending the medium flow path, increases the frequency of lateral scouring of the heat exchange tube bundle, eliminating the heat exchange dead zone formed by straight flow. During operation, when the shell-side medium enters from the inlet 8, the gradually expanding distribution plate 16 reduces the fluid velocity gradient and achieves uniform velocity distribution through the gradual expansion of the flow channel cross-section. The medium at the outlet of the distribution plate 16 enters the baffle plate 6 region in a stable state. Multiple sets of baffle plates 6, arranged alternately, form a serpentine channel, forcing the medium to repeatedly change its flow direction. This optimized flow path extends the residence time of the medium within the shell 1 and enhances the scouring effect of the lateral flow on the surface of the heat exchange tube bundle, increasing turbulence intensity. The meandering flow channel formed by the baffle plates 6 also avoids the problem of insufficient heat transfer caused by the medium flowing out rapidly in a straight direction.

[0060] This application further proposes that the heat exchange tube 51 be made of copper, stainless steel, or titanium. Copper tubes refer to tubular structures made of copper alloys, specifically T2 copper or TP2 phosphorus-deoxidized copper. The high thermal conductivity of copper improves the heat transfer efficiency between the refrigerant and the shell-side medium. Stainless steel tubes refer to tubular structures made of austenitic or duplex stainless steel, specifically 304 or 316L stainless steel. The corrosion resistance of stainless steel extends its service life in chemically corrosive or high-humidity environments. Titanium tubes refer to tubular structures made of industrial pure titanium or titanium alloys, specifically TA2 pure titanium or Ti-6Al-4V alloy tubes. The corrosion resistance of titanium tubes allows it to withstand extreme corrosive media such as seawater, strong acids, and strong alkalis.

[0061] The selection of the three materials mentioned above covers the diverse requirements of different operating conditions for the corrosion resistance, thermal conductivity, and mechanical strength of the heat exchanger tube 51, allowing the heat exchanger to flexibly match the optimal material combination according to the actual application scenario. This solution, by limiting the selection to three materials—copper tubes, stainless steel tubes, and titanium tubes—preserves the high-efficiency thermal conductivity advantage of copper tubes under normal operating conditions, while expanding the applicability of the heat exchanger in corrosive environments through stainless steel and titanium tubes, thus avoiding the problem of reduced equipment reliability due to material limitations.

[0062] 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.

[0063] 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 high-efficiency shell-and-tube heat exchanger, comprising: - The shell (1) has an inlet (8) and an outlet (9) on its side wall; - The shell is closed at both ends, and at least one end is provided with a tube sheet (2). Its features are: - The outer end face of the tube sheet (2) is sealed with a first tube box (4) and a second tube box (3); - The first pipe box (4) is connected to a refrigerant liquid interface (10); - The second pipe box (3) is connected to a refrigerant gas interface (11); - The shell (1) is equipped with a heat exchange tube bundle, and its two ends are connected to the tube sheet (2) in the first tube box (4) and the second tube box (3) respectively.

2. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - A gas equalization plate (15) is provided inside the second tube box (3), and the gas equalization plate (15) is located between the refrigerant gas interface (11) and the end of the heat exchange tube bundle.

3. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - The first pipe box (4) is provided with a primary distribution plate (13) and a secondary distribution plate (14). - The primary distribution plate (13) is disposed at the inner end of the refrigerant liquid interface (10); - The secondary distribution plate (14) is disposed on the inlet of the heat exchange tube bundle.

4. The high-efficiency shell-and-tube heat exchanger according to claim 3, characterized in that: - The primary distribution plate (13) is a hemispherical or cylindrical structure with distribution holes evenly distributed on its surface.

5. The high-efficiency shell-and-tube heat exchanger according to claim 3, characterized in that: - The distribution hole of the secondary distribution plate (14) is a flanged protrusion structure, with the protrusion facing the tube opening of the heat exchange tube bundle; - The number of distribution holes corresponds one-to-one with the number of heat exchange tubes (51) in the heat exchange tube bundle.

6. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - The lower end region of the first tube box (4) is also connected to a liquid refrigerant outlet (12).

7. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - A third tube box (17) is also sealed and connected to the outer end face of the tube sheet (2); - The heat exchange tube bundle includes a first heat exchange tube bundle (5a) and a second heat exchange tube bundle (5b); - The two ends of the first heat exchange tube bundle (5a) are respectively connected to the tube sheet (2) inside the first tube box (4) and the third tube box (17); - The two ends of the second heat exchange tube bundle (5b) are respectively connected to the tube sheet (2) in the third tube box (17) and the second tube box (3).

8. The high-efficiency shell-and-tube heat exchanger according to claim 7, characterized in that: - The two ends of the shell are respectively closed by end plate (7) and tube plate (2); - The first heat exchange tube bundle (5a) and the second heat exchange tube bundle (5b) each contain at least two heat exchange tubes (51); - The inner ends of adjacent heat exchange tubes (51) are connected by U-shaped joints (52).

9. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - A water distribution plate (16) is provided at both the inlet (8) and the outlet (9); - The water distribution plate (16) adopts a gradually expanding flow channel structure; - Multiple sets of baffles (6) are set inside the shell (1) between the inlet (8) and the outlet (9) to form a meandering flow channel.

10. The high-efficiency shell-and-tube heat exchanger according to claim 1, characterized in that: - The heat exchange tube (51) is made of copper, stainless steel or titanium.

11. The high-efficiency shell-and-tube heat exchanger according to any one of claims 1-7, characterized in that: - The first tube box (4), the second tube box (3) and the third tube box (17) are sealed and fixed to the tube sheet (2) by welding, bonding or flange connection structure.

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