Novel shell-and-tube heat exchanger

Abstract

A novel shell-and-tube heat exchanger comprises a cylindrical shell and a plurality of baffle plates detachably arranged in the shell, and heat exchange tubes are arranged on the baffle plates. An arc-shaped protruding strip is arranged on the inner wall of the shell, an arc-shaped inserting groove attached to the inner wall of the shell is formed in one side of the protruding strip, the baffle plate comprises an arc-shaped connecting edge, and an arc-shaped inserting strip which protrudes towards one side and is inserted into the inserting groove is arranged on one side of the connecting edge. A plug pin which extends into the inserting groove and is matched with the inserting opening in an inserted mode is further arranged on the protruding strip in an inserted mode. According to the baffle plate, the insertion strips and the insertion grooves are matched in an inserted mode, the insertion holes are locked through the insertion pins, rapid assembly and disassembly of the baffle plate are achieved, the problem that cleaning is difficult due to welding and fixing is solved, meanwhile, the complex assembly process of a traditional pull rod type structure is simplified, and the maintenance efficiency is greatly improved.

Description

Technical Field

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

[0002] Shell-and-tube heat exchangers are widely used in chemical, energy, and pharmaceutical industries. Currently, the installation and fixing of baffles in shell-and-tube heat exchangers has the following drawbacks: Existing baffles are mostly directly welded to the inner wall of the shell or fixed using tie rods and spacers. While welding provides a robust structure, it makes the baffle and shell an inseparable unit. After a period of operation, scale or impurities easily accumulate on the shell side. When cleaning is required, the welded baffles severely hinder the movement and operation space of cleaning tools within the shell, easily creating cleaning dead zones, affecting cleaning effectiveness, and increasing downtime and maintenance time and costs. While tie rod fixing is slightly easier to disassemble than welding, its structure is relatively complex. Installation requires precise alignment of multiple parts (tilt rods, nuts, spacers), and disassembly is equally cumbersome. Furthermore, under fluid impact and temperature changes, loosening or decreased positioning accuracy may occur. Utility Model Content

[0003] To address the problems of difficult disassembly and inconvenient maintenance and cleaning caused by the fixed structure of baffles in existing shell-and-tube heat exchangers, this utility model provides a novel shell-and-tube heat exchanger.

[0004] The technical solution of this utility model is as follows:

[0005] A novel shell-and-tube heat exchanger includes a cylindrical shell and several baffles detachably disposed inside the shell, with heat exchange tubes mounted on the baffles. The inner wall of the shell has an arc-shaped protrusion, and one side of the protrusion has an arc-shaped slot that fits against the inner wall of the shell. Each baffle includes an arc-shaped connecting edge, and one side of the connecting edge has an arc-shaped insert that protrudes to one side and inserts into the slot. The insert has a socket, and the protrusion also has a pin that extends into the slot and engages with the socket. Through the engagement of the insert and the slot, and the locking of the socket by the pin, the baffles can be quickly assembled and disassembled, avoiding the cleaning difficulties caused by welding, and simplifying the complex assembly process of traditional tie-rod structures, significantly improving maintenance efficiency.

[0006] As described above, in this novel shell-and-tube heat exchanger, baffles are distributed axially along the shell and staggered vertically. This staggered arrangement of baffles creates multi-stage fluid flow paths, forcibly altering the direction of the shell-side fluid. The fluid abruptly turns at the edges of the baffles, generating vortices and recirculation zones, enhancing turbulence intensity, eliminating dead zones, improving heat transfer uniformity, and simultaneously reducing fluid resistance and preventing localized scaling and blockage.

[0007] Furthermore, the baffle also includes a corrugated turbulence edge located on the opposite side of the connecting edge. The corrugated turbulence edge further segments the fluid boundary layer, increases the fluid disturbance area, and works synergistically with the staggered arrangement of the baffle to enhance turbulence and improve heat exchange efficiency.

[0008] Furthermore, a flow gap is reserved between the turbulence edge and the inner wall of the shell, and the ratio of the flow area of ​​the flow gap to the area of ​​the cross-section of the shell cavity ranges from 20% to 35%. By precisely controlling the area ratio of the gap, the fluid resistance is balanced while maintaining high turbulence intensity. A ratio below 20% will lead to a sharp increase in pressure drop, while a ratio above 35% will weaken the turbulence effect. This range of area ratio takes into account both heat transfer enhancement and energy consumption optimization, avoiding a decrease in the system's energy efficiency ratio.

[0009] In a preferred embodiment, the central angle corresponding to the protrusion is 120°-150°. Limiting the curvature range of the protrusion ensures it provides sufficient structural support strength. An angle that is too small will reduce the installation stability of the baffle, while an angle that is too large will increase manufacturing difficulty and cause unnecessary waste. A central angle of 120°-150° ensures mechanical reliability while reducing processing costs.

[0010] In a preferred embodiment, the spacing between adjacent baffles is not less than 1 / 5 of the shell diameter and not greater than the shell diameter. If the spacing between baffles is too small, it can easily cause flow channel blockage and increased pressure drop; if it is too large, it will weaken the baffle effect. Matching the spacing range between baffles to the physical constraints of the shell size ensures that the fluid forms continuous turbulence between multiple baffles and avoids the decrease in heat exchange efficiency due to spacing mismatch.

[0011] Furthermore, the inserts on the baffles face the same side of the shell. This uniform insert orientation allows all baffles to slide along a single axis, simplifying the assembly process, eliminating the risk of positioning errors caused by multi-directional operations, and improving assembly efficiency. This is particularly suitable for the modular installation of large heat exchangers.

[0012] The beneficial effects of this utility model are as follows: This utility model is a new type of shell and tube heat exchanger. By using the insertion and engagement of the insert and slot and the locking of the insertion port by the pin, the baffle plate can be quickly installed and removed, which solves the problems of difficult installation and removal and inconvenient maintenance and cleaning of existing baffle plates. Attached Figure Description

[0013] The advantages and solutions of this application will become clear to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this invention.

[0014] In the attached diagram:

[0015] Figure 1This is a schematic diagram of the disassembled structure of the shell and baffles of the shell-and-tube heat exchanger in the embodiment;

[0016] Figure 2 This is a schematic diagram of the assembly structure of the shell and baffles of the shell-and-tube heat exchanger in the embodiment;

[0017] Figure 3 This is a top view of the shell-and-tube heat exchanger in the embodiment;

[0018] Figure 4 This is a schematic diagram of the overall structure of the shell-and-tube heat exchanger in the embodiment.

[0019] The components represented by the various reference numerals in the diagram are:

[0020] 1. Shell; 2. Raised bar; 21. Slot; 3. Pin; 4. Baffle; 41. Insert; 42. Inlet; 5. Heat exchange tube. Detailed Implementation

[0021] Exemplary embodiments of this disclosure will now be described in more detail with reference to the accompanying drawings.

[0022] Example

[0023] This embodiment provides a novel shell-and-tube heat exchanger, comprising a cylindrical shell 1 (3000mm in length and 600mm in diameter) and five detachable baffles 4 disposed inside the shell 1, with heat exchange tubes 5 mounted on the baffles 4. The inner wall of the shell 1 has an arc-shaped protrusion 2, with an arc-shaped slot 21 on one side of the protrusion 2 that fits against the inner wall of the shell 1. The baffles 4 include an arc-shaped connecting edge, with an arc-shaped insert 41 protruding to one side and inserted into the slot 21 on one side of the connecting edge. The insert 41 has a circular insertion port 42, and a pin 3 is inserted into the slot 21 and engages with the insertion port 42. Through the engagement of the insert 41 with the slot 21 and the locking of the insertion port 42 by the pin 3, the baffles 4 can be quickly assembled and disassembled, avoiding the cleaning difficulties caused by welding fixation. This also simplifies the complex assembly process of traditional tie-rod structures and significantly improves maintenance efficiency.

[0024] In this embodiment, the baffles 4 are distributed along the axial direction of the shell 1, with staggered positions. The distance between adjacent baffles 4 is not less than 1 / 5 of the diameter of the shell 1 and not greater than the diameter of the shell 1, preferably 500 mm. The staggered arrangement of the baffles 4 forms a multi-stage fluid flow path, forcibly changing the direction of the shell-side fluid flow. The fluid suddenly turns at the edge of the baffle 4, generating eddies and backflow zones, enhancing turbulence intensity, eliminating dead zones, improving heat transfer uniformity, and reducing fluid resistance while avoiding local scaling and blockage. If the spacing between the baffles 4 is too small, it can easily cause flow channel blockage and increased pressure drop; if it is too large, it weakens the baffle effect. Matching the spacing range between the baffles 4 to the physical constraints of the shell 1 dimensions ensures that the fluid forms continuous turbulence between the multi-stage baffles, avoiding the decrease in heat exchange efficiency due to spacing mismatch.

[0025] Furthermore, the baffle 4 also includes a wave-shaped turbulence-inducing edge located on the opposite side of the connecting edge. A flow gap is reserved between the turbulence-inducing edge and the inner wall of the shell 1, and the ratio of the flow area of ​​the flow gap to the area of ​​the cross-section of the inner cavity of the shell 1 ranges from 20% to 35%, with a preferred ratio of 30%. The wave-shaped turbulence-inducing edge further segments the fluid boundary layer, increases the fluid disturbance area, and works synergistically with the staggered arrangement of the baffle 4 to enhance turbulence and improve heat exchange efficiency. By precisely controlling the area ratio of the gap, the fluid resistance is balanced while maintaining high turbulence intensity. A ratio below 20% will lead to a sharp increase in pressure drop, while a ratio above 35% weakens the turbulence effect. This range of area ratio values ​​takes into account both heat transfer enhancement and energy consumption optimization, avoiding a decrease in the system's energy efficiency ratio.

[0026] Furthermore, the inserts 41 on the baffle 4 face the upper side of the housing 1. This uniform orientation of the inserts 41 allows all baffles 4 to slide along a single axis, simplifying the assembly process, eliminating the risk of positioning errors caused by multi-directional operations, and improving assembly efficiency. This is particularly suitable for the modular installation of large heat exchangers.

[0027] Furthermore, the protrusion 2 is welded to the inner wall of the housing 1. The central angle of the protrusion 2 is 120°-150°, preferably 130°. Limiting the curvature range of the protrusion 2 ensures it provides sufficient structural support strength. An angle that is too small will reduce the installation stability of the baffle 4, while an angle that is too large will increase manufacturing difficulty and cause unnecessary waste. A central angle of 130° ensures mechanical reliability while reducing processing costs.

Claims

1. A novel shell and tube heat exchanger characterized in that, It includes a cylindrical shell (1) and several baffles (4) detachably disposed inside the shell (1), and heat exchange tubes (5) are provided on the several baffles (4); The inner wall of the housing (1) is provided with an arc-shaped protrusion (2), and one side of the protrusion (2) is provided with an arc-shaped slot (21) that fits against the inner wall of the housing (1). The baffle plate (4) includes an arc-shaped connecting edge, and one side of the connecting edge is provided with an arc-shaped insert (41) that protrudes to one side and is inserted into the slot (21). The insert (41) is provided with a socket (42), and the protrusion (2) is also provided with a pin (3) that extends into the slot (21) and engages with the socket (42).

2. The novel shell-and-tube heat exchanger according to claim 1, characterized in that, Several of the baffles (4) are distributed along the axial direction of the shell (1) and their positions are staggered vertically.

3. A novel shell-and-tube heat exchanger according to claim 1, characterized in that, The baffle plate (4) also includes a turbulence side located on the opposite side of the connecting side, which has a wave-shaped structure.

4. A novel shell-and-tube heat exchanger according to claim 3, characterized in that, A flow gap is reserved between the turbulence edge and the inner wall of the shell (1), and the ratio of the flow area of ​​the flow gap to the area of ​​the cross-section of the inner cavity of the shell (1) is in the range of 20%-35%.

5. A novel shell-and-tube heat exchanger according to claim 1, characterized in that, The central angle corresponding to the convex strip (2) is 120°-150°.

6. A novel shell-and-tube heat exchanger according to claim 1, characterized in that, The spacing between adjacent baffles (4) is not less than 1 / 5 of the diameter of the shell (1) and not greater than the diameter of the shell (1).

7. A novel shell-and-tube heat exchanger according to claim 1, characterized in that, The inserts (41) on several of the baffles (4) face the same side of the housing (1).

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