Double-tube-pass cold trap and devolatilization device

Abstract

The invention provides a double-tube-pass cold trap and a devolatilization device. The double-tube-pass cold trap comprises a shell, a plurality of refrigerant tubes are arranged in the shell, all the refrigerant tubes are arranged in parallel in the horizontal direction, a plurality of heating medium tubes are arranged around the refrigerant tubes except the refrigerant tubes on the outer side, the heating medium tubes and the refrigerant tubes are arranged in parallel, the refrigerant tubes are rigidly connected with the surrounding heating medium tubes through first heat conduction fins, and the first heat conduction fins are arranged on the outer side of the shell. The first heat conduction fins are in an inclined state in the vertical direction. The multiple heating medium pipes are arranged to surround the refrigerant pipe, the refrigerant pipe is arranged to be rigidly connected with the surrounding heating medium pipes through the first heat conduction fins, a heat conduction channel can be formed through the first heat conduction fins, heat can be efficiently conducted to the refrigerant pipe from the heating medium pipes through the first heat conduction fins, and then the heating uniformity is improved; the heat exchange efficiency is improved; the refrigerant pipes and the heating medium pipes form an integral space network structure through the first heat conduction fins, and the integral space network structure can restrain the relative positions of the pipe bundles and prevent the pipe bundles from deforming or collapsing.

Description

Technical Field

[0001] This application relates to the field of chemical equipment technology, and in particular to a dual-pass cold trap and devolatilization device. Background Technology

[0002] In the production of polymers such as polyolefins, devolatilization (i.e., removal of volatile components) is a critical process, aiming to remove residual solvents, unreacted monomers, oligomers, and other volatile impurities. This process is typically carried out under reduced pressure, resulting in high-temperature tail gas rich in volatile organic compounds (VOCs) and easily crystallizable impurities, which requires tail gas treatment. The cold trap, as the core equipment for tail gas treatment, condenses easily crystallizable impurities in the tail gas using a refrigerant, and then melts the crystals using a heat transfer medium. Its function directly affects the vacuum stability, material recovery rate, and operating and maintenance costs of the entire system.

[0003] In related technologies, single-pass cold traps share a single pipe for both heating and cooling media. While this method offers the advantage of uniform heating, it suffers from drawbacks such as low heat exchange efficiency and significant waste of heating and cooling media, making it difficult to meet the efficiency and cost requirements of large-scale industrial production. Later, double-pass cold traps were developed. By separating the heating and cooling media pipes, double-pass cold traps effectively improve heat exchange efficiency and avoid problems such as waste of heating and cooling media. However, they have the following drawbacks: uneven heating in different areas and low heat exchange efficiency.

[0004] To improve the heat exchange efficiency of double-pass cold traps, finned structures have been introduced. For example, rectangular or H-shaped fins are welded to the surface of the heat transfer medium pipes to increase the heat exchange area, which can improve heat exchange efficiency to some extent. However, existing double-pass cold traps with finned structures have the following drawbacks in actual operation: the problem of uneven heating has not been fundamentally solved, and significant temperature differences in local areas can easily lead to thermal stress concentration, which not only reduces heat exchange efficiency but also accelerates pipe aging. For long-strand cold traps, the tube bundles, which can be several meters long in the middle, are prone to deformation such as bending and collapse under their own weight and the impact force of the hot and cold medium flow, seriously affecting the stability and service life of the equipment.

[0005] For example, related technologies disclose a finned / spiral fin combined two-tube heat exchanger, including an outer tube and an inner tube. A spiral fin is disposed between the inner tube and the outer tube, and an inner insert fin is disposed within the inner cavity of the inner tube. The inner insert fin has a triangular fin at an angle θ with the inner insert fin, with two adjacent triangular fins located on the upper and lower surfaces of the inner insert fin, respectively. However, in this design, the spiral fin has a 360° surround structure, which disperses heat transfer and easily interferes with the flow of the hot and cold medium in the two-tube pass; it can only be used for short-tube two-tube heat exchange and cannot solve the collapse problem of long tube bundles (i.e., tube bundles with a length greater than or equal to 6m).

[0006] For example, related technologies disclose a double-tube, double-window aluminum busbar, comprising two parallel tubes connected by fins. The fins have multiple sets of windows, each set including two windows. The window structure is as follows: a section is cut into the fin, leaving one side connected to it; the cut section is bent along the edge connected to the fin to form the window; one window in each set is bent towards one side of the fin, and the other window is bent towards the other side. In this solution, the fins are an integral structure, which only increases the heat exchange area but cannot precisely connect to the heat transfer pipes, failing to solve the problem of heat exchange dead zones; the fins are fixedly connected to the pipes, making individual disassembly and maintenance impossible when the double-tube pass is narrow; it is only suitable for short tube bundle heat exchange and cannot solve the problem of long tube bundle collapse.

[0007] For example, related technologies disclose a dual-tube evaporator, including evaporation tubes and fins. Several parallel fins are provided with two insertion holes at each end. The two evaporation tubes are U-shaped, and the straight tubes at both ends of the two U-shaped tubes are inserted into the corresponding insertion holes. In this solution, the fins are a flat integral structure, and there is a heating dead zone at the turning point of the dual-tube pass; the suitable tube bundle length is less than or equal to 1m, which cannot solve the problem of long tube bundle collapse.

[0008] As industrial production moves towards larger scale and higher efficiency, the demand for long-tube bundle cold traps is increasing. Existing technologies cannot simultaneously solve the three core problems of heating uniformity, tube bundle support stability, and efficient heat transfer in long-tube bundle double-pass cold traps, which seriously restricts the technological upgrading and application expansion of cold trap equipment.

[0009] In summary, there is an urgent need for a cold trap that can be adapted to long tube bundles and double-pass cold traps while also ensuring heating uniformity, structural stability, and efficient heat exchange. Summary of the Invention

[0010] This application provides a dual-pass cold trap and devolatilization device to solve the above-mentioned technical problems.

[0011] To achieve the above objectives, the technical solution of the present invention is as follows:

[0012] This application provides a dual-pass cold trap, which includes a shell and a plurality of refrigerant pipes inside the shell. All refrigerant pipes are arranged in parallel in the horizontal direction. Except for the outer refrigerant pipes, a plurality of heat pipes are arranged around the refrigerant pipes. The heat pipes are arranged in parallel with the refrigerant pipes. The refrigerant pipes are rigidly connected to the surrounding heat pipes through a first heat-conducting fin, which is inclined in the vertical direction.

[0013] The principle of this application is as follows: By arranging several heat transfer pipes around a refrigerant pipe, and rigidly connecting the refrigerant pipe to the surrounding heat transfer pipes via first heat-conducting fins, a heat conduction channel can be formed through the first heat-conducting fins. Heat can be efficiently conducted from the heat transfer pipes to the refrigerant pipes via the first heat-conducting fins, thereby improving heating uniformity and increasing heat exchange efficiency. Simultaneously, the refrigerant pipes and heat transfer pipes can form an integrated spatial network structure (honeycomb beam) through the first heat-conducting fins. This integrated spatial network structure can constrain the relative position of the pipe bundle, preventing deformation or collapse. By setting the first heat-conducting fins to an inclined position in the vertical direction, the first heat-conducting fins can extend obliquely downwards, facilitating the automatic flow of molten liquid along the first heat-conducting fins to the drain port located at the bottom of the cold trap, reducing liquid stagnation, shortening the cleaning cycle, and lowering maintenance costs.

[0014] In one embodiment of this application, the two ends of the first heat-conducting fin are connected to the refrigerant pipe and the heat-conducting pipe respectively via a first clip and a second clip.

[0015] In this application, by setting the two ends of the first heat-conducting fins to be connected to the refrigerant pipe and the heat-conducting pipe respectively through the first and second clips, the heat exchange area of ​​the refrigerant pipe and the heat-conducting pipe can be increased, so as to achieve uniform heat exchange of the refrigerant pipe and further improve the heat exchange effect.

[0016] In one embodiment of this application, two adjacent first heat-conducting fins are symmetrically distributed along the radial cross-section of the middle of the cold trap.

[0017] In this application, if two adjacent first heat-conducting fins are tilted in the same direction, forming a parallelogram with the refrigerant pipe and the heat pipe, when the middle part is subjected to a downward sag due to gravity, the refrigerant pipe and the heat pipe exert horizontal shear stress on the connection point of the first heat-conducting fins. Over time, this will cause deformation of the first and second clips, thus affecting their service life and limiting their anti-collapse effect. To solve the above technical problem, this application sets the two adjacent first heat-conducting fins to be symmetrically distributed along the radial cross-section of the middle of the cold trap. The two adjacent first heat-conducting fins form an isosceles trapezoid with the refrigerant pipe and the heat pipe. When the middle part is subjected to a downward sag due to gravity, the horizontal shear stress exerted by the refrigerant pipe and the heat pipe on the connection point of the first heat-conducting fins is offset from left to right. That is, the refrigerant pipe and the heat pipe will not have a tendency to slip relative to each other, achieving the effects of drainage and anti-collapse, thereby improving stability and extending the service life of the first and second clips.

[0018] In one embodiment of this application, the inner side of the first buckle is provided with anti-slip teeth.

[0019] In this application, by adding anti-slip teeth to the inner side of the first buckle, the mechanical engagement between the first buckle and the outer surface of the refrigerant pipe can be achieved through the anti-slip teeth, thereby improving structural stability.

[0020] In one embodiment of this application, both the first buckle and the second buckle are elastic buckles.

[0021] In one embodiment of this application, the first buckle is an openable circular buckle.

[0022] In one embodiment of this application, the second buckle is a semi-circular arc buckle.

[0023] In one embodiment of this application, the inner side of the refrigerant pipe located on the outer side is rigidly connected to the adjacent heat medium pipe through a first heat-conducting fin, and a second heat-conducting fin is installed on the outer side of the refrigerant pipe located on the outer side.

[0024] In this application, only a portion of the outer side of the refrigerant pipe is heated by the heat transfer medium. By installing a second heat-conducting fin on the outer side of the refrigerant pipe, uniform heat exchange of the outer refrigerant pipe can be achieved through heat conduction by the second heat-conducting fin.

[0025] In one embodiment of this application, the heat transfer pipes surrounding the refrigerant pipe are evenly distributed around the refrigerant pipe.

[0026] In this application, by setting the heat transfer pipes around the refrigerant pipes to be evenly distributed around the refrigerant pipes, the heat transfer uniformity and heat transfer effect can be improved.

[0027] This application also provides a devolatilization device, which includes a dual-pass cold trap as described above. Attached Figure Description

[0028] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. It is obvious that the drawings described below are merely some embodiments of this application, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort.

[0029] In the attached diagram: Figure 1 This is a schematic diagram of the structure of the dual-tube cold trap of this application; Figure 2 for Figure 1 Schematic diagram of the distribution of refrigerant pipes and heat pipes; Figure 3 for Figure 1 A schematic diagram of the assembly structure of the first heat-conducting fin with the first and second clips; Figure 4 for Figure 1 A schematic diagram of the structure of the first buckle in the middle; Figure 5 This is a schematic diagram of the stress structure of an isosceles trapezoid formed by two adjacent first heat-conducting fins, a refrigerant pipe, and a heat-conducting pipe. Figure 6 This is a schematic diagram of the stress structure in this application.

[0030] The attached figures are labeled as follows: 1-Shell, 11-Refrigerant inlet, 12-Heating medium inlet, 13-Drain port, 14-Refrigerant outlet, 15-Heating medium outlet, 16-Air inlet, 17-Air outlet; 2-Refrigerant pipe; 3-Heat medium pipe; 4-First heat-conducting fin; 5-First buckle, 51-Anti-slip teeth; 6-Second buckle; 7-Outer tube sheet, 71-First tube hole; 8-Inner tube sheet, 81-Second tube hole.

[0031] 9-Baffle plate. Detailed Implementation

[0032] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0033] It should be noted that all directional indicators (such as top, bottom, left, right, inside, outside, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicator will also change accordingly.

[0034] In this invention, unless otherwise explicitly specified and limited, the terms "connection," "fixed," etc., should be interpreted broadly. For example, "fixed" can mean a fixed connection, a detachable connection, or an integral part; it can mean a mechanical connection or an electrical connection; it can mean a direct connection or an indirect connection through an intermediate medium; it can mean the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0035] Please see Figures 1 to 4One embodiment of this application provides a dual-pass cold trap, which includes a shell 1. The shell 1 is provided with a plurality of refrigerant pipes 2. All refrigerant pipes 2 are arranged in parallel in the horizontal direction. Except for the outer refrigerant pipes 2, a plurality of heat pipes 3 are arranged around the refrigerant pipes 2. The heat pipes 3 around the refrigerant pipes 2 are evenly distributed around the refrigerant pipes 2. All heat pipes 3 are arranged in parallel with the refrigerant pipes 2. The refrigerant pipes 2 are rigidly connected to the surrounding heat pipes 3 through a first heat-conducting fin 4. The two ends of the first heat-conducting fin 4 are connected to the refrigerant pipes 2 and the heat pipes 3 through a first buckle 5 and a second buckle 6, respectively. The first heat-conducting fin 4 is inclined in the vertical direction, and the two adjacent first heat-conducting fins 4 are symmetrically distributed on the left and right along the radial section of the middle of the cold trap. Both the first buckle 5 and the second buckle 6 are elastic buckles; the inner side of the first buckle 5 is provided with anti-slip teeth 51, the first buckle 5 is an openable circular buckle, and the second buckle 6 is a semi-circular buckle.

[0036] The inner side of the refrigerant pipe 2 located on the outside is rigidly connected to the adjacent heat medium pipe 2 through the first heat-conducting fin 4, and the outer side of the refrigerant pipe 2 located on the outside is equipped with a second heat-conducting fin.

[0037] Another embodiment of this application provides a devolatilization device, which includes a dual-pass cold trap as described above.

[0038] Furthermore, in this invention, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the word "and / or" throughout the text means including three parallel solutions; taking "A and / or B" as an example, it includes solution A, solution B, or a solution that simultaneously satisfies A and B. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0039] Please see Figure 1 , Figure 1 This is a schematic diagram of a dual-tube cold trap provided as an exemplary embodiment of this application.

[0040] Please see Figure 1 and Figure 2The dual-pass cold trap includes a shell 1. The bottom of the shell 1 has a refrigerant inlet 11, a heat transfer medium inlet 12, and a drain outlet 13. The top of the shell 1 has a refrigerant outlet 14, a heat transfer medium outlet 15, an air inlet 16, and an air outlet 17. Several refrigerant pipes 2 are installed inside the shell 1. All refrigerant pipes 2 are arranged horizontally and are fixed inside the shell 1 by two vertically arranged outer tube plates 7. The two outer tube plates 7 are located on the left and right sides inside the shell 1, respectively, and each outer tube plate 7 has a first tube hole 71 for the refrigerant pipes 2 to pass through. In addition to the outer refrigerant pipes 2, several heat transfer medium pipes 3 are arranged around the refrigerant pipes 2. The heat transfer medium pipes 3 are evenly distributed around the refrigerant pipes 2, and all heat transfer medium pipes 3 are arranged parallel to the refrigerant pipes 2; in other words, all heat transfer medium pipes 3 are arranged horizontally. All heat medium pipes 3 are fixed inside the shell 1 by two inner tube sheets 8. The inner tube sheets 8 have second pipe holes 81 for the heat medium pipes 3 and refrigerant pipes 2 to pass through. The two inner tube sheets 8 are located between two outer tube sheets 7, and are arranged parallel to each other. The distance between the inner tube sheet 8 and the outer tube sheet 7 on the same side is 200-400 mm; that is, the distance between the outer tube sheet 7 on the left and the inner tube sheet 8 on the left is 200-400 mm, and the distance between the outer tube sheet 7 on the right and the inner tube sheet 8 on the right is 200-400 mm. Several baffles 9 are also provided inside the shell 1, located between the air inlet 16 and the air outlet 17. All baffles 9 are arranged parallel to each other in the vertical direction. Some baffles 9 are fixed at one end to the top wall of the shell 1, and the remaining baffles 9 are fixed at one end to the bottom wall of the shell 1. The baffle 9 is used to force the gas to flow in a deflected manner multiple times inside the shell 1, rather than passing through in a straight line, ensuring that gas molecules have more time to condense and improving heat exchange efficiency. The inner tube sheet 8 and the outer tube sheet 7 are made of Q235 high-strength carbon steel or 304 stainless steel.

[0041] Specifically, in this embodiment, by arranging the heat transfer pipes 3 around the refrigerant pipe 2 in a uniformly distributed manner, heat transfer uniformity and efficiency can be improved. Furthermore, since the refrigerant pipes 2 and 3 are located within the shell, independent circulation of the refrigerant and heat transfer media can be achieved, avoiding the mixing and waste issues associated with single-pass structures. In this embodiment, by adding an inner tube sheet 8 and an outer tube sheet 7 within the shell 1, and setting the distance between the inner tube sheet 8 and the outer tube sheet 7 located on the same side to 200-400mm, a separate flow space for the refrigerant and heat transfer media can be formed. This allows for the fixation of the refrigerant pipes 2 and 3, ensuring the separate layout of the dual-pass piping and preventing mutual interference between the refrigerant pipes 2 and 3. Since the inner tube sheet 8 and outer tube sheet 7 are made of Q235 high-strength carbon steel or 304 stainless steel, their high strength provides end support for the entire cold trap, enhancing the overall rigidity of the equipment.

[0042] Please see Figure 1 , Figure 3 and Figure 4The refrigerant pipe 2 is rigidly connected to the surrounding heat medium pipe 3 via a first heat-conducting fin 4. The two ends of the first heat-conducting fin 4 are connected to the refrigerant pipe 2 and the heat medium pipe 3 respectively via a first clip 5 and a second clip 6. Specifically, the first end of the first heat-conducting fin 4 is connected to the refrigerant pipe 2 via the first clip 5, and the second end is connected to the heat medium pipe 3 via the second clip 6. The first heat-conducting fin 4 is inclined in the vertical direction; specifically, the angle between the first heat-conducting fin 4 and the refrigerant pipe 2 is 10°-20°. Two adjacent first heat-conducting fins 4 are symmetrically distributed along the radial section of the center of the cold trap. The first heat-conducting fin 4 is rectangular. The inner side of the outer refrigerant pipe 2 is rigidly connected to the adjacent heat medium pipe 3 via the first heat-conducting fin 4, and a second heat-conducting fin (not shown) is installed on the outer side of the outer refrigerant pipe 2. The first end of the second heat-conducting fin is connected to the outside of the refrigerant pipe 2 via the first clip 5, and the included angle between the second heat-conducting fin and the refrigerant pipe 2 is 10°-20°. The second heat-conducting fin 4 is rectangular. Both the first clip 5 and the second clip 6 are elastic clips. The inner side of the first clip 5 is provided with anti-slip teeth 51. The first clip 5 is an openable circular clip, and the second clip 6 is a semi-circular arc clip. The first clip 5 and the second clip 6 can be made of Q235 high-strength carbon steel clips or 304 stainless steel clips. The first heat-conducting fin 4 and the second heat-conducting fin can be made of Q235 high-strength carbon steel fins or 304 stainless steel fins. The openable circular clips and the semi-circular arc clips are existing technologies and will not be described in detail here.

[0043] Specifically, in this embodiment, by setting the first heat-conducting fin 4 to be inclined in the vertical direction, and in particular by setting the included angle between the first heat-conducting fin 4 and the refrigerant pipe 2 to 10°-20°, the first heat-conducting fin 4 can extend obliquely downward, facilitating the automatic flow of molten liquid along the first heat-conducting fin 4 to the drain port 13 located at the bottom of the cold trap, reducing liquid retention, shortening the cleaning cycle, and reducing maintenance costs. If two adjacent first heat-conducting fins 4 are inclined in the same direction, the two adjacent first heat-conducting fins 4 form a parallelogram with the refrigerant pipe 2 and the heat-conducting pipe 3. When the middle part is subjected to the downward tendency of gravity, the refrigerant pipe 2 and the heat-conducting pipe 3 will form horizontal shear stress at the connection of the first heat-conducting fin 4. Over time, this will cause deformation of the first and second clips, thereby affecting the service life and limiting the anti-collapse effect. To solve the above-mentioned technical problems, in this embodiment, two adjacent first heat-conducting fins 4 are arranged symmetrically along the radial cross-section of the middle of the cold trap, and the two adjacent first heat-conducting fins 4 form an isosceles trapezoid with the refrigerant pipe 2 and the heat-conducting pipe 3 (e.g., Figure 5As shown in the diagram, where F1 is the external pressure, F2 is the external pressure, and F3 is the internal axial pressure, when the middle part experiences a downward tendency due to gravity, the horizontal shear stress formed by the refrigerant pipe 2 and the heat transfer pipe 3 at the connection point of the first heat-conducting fin 4 is offset from left to right. That is, the refrigerant pipe 2 and the heat transfer pipe 3 will not have a tendency to slip relative to each other, achieving the effects of drainage and anti-collapse, thereby improving stability and extending the service life of the first and second clips. In this embodiment, by setting the two ends of the first heat-conducting fin 4 to be connected to the refrigerant pipe 2 and the heat transfer pipe 3 respectively through the first clip 5 and the second clip 6, the heat exchange area of ​​the refrigerant pipe 2 and the heat transfer pipe 3 can be increased, achieving uniform heat exchange and further improving the heat exchange effect. In this embodiment, by adding anti-slip teeth 51 to the inner side of the first clip 5, the anti-slip teeth 51 can achieve mechanical engagement between the first clip 5 and the outer surface of the refrigerant pipe 6, improving structural stability. In this embodiment, by setting the first heat-conducting fin 4 located on the inner side to be rectangular, the technical problems of heat dissipation dispersion and easy interference with the flow of cold and hot medium in the traditional annular fins can be avoided. In this embodiment, only a part of the outer side of the refrigerant pipe 2 is heat-conducted by the heat medium pipe. By installing the second heat-conducting fin on the outer side of the refrigerant pipe 2, uniform heat exchange of the outer refrigerant pipe can be achieved through the heat conduction of the second heat-conducting fin.

[0044] The principle of this embodiment is as follows: by arranging several heat medium pipes 3 around the refrigerant pipe 2, and by rigidly connecting the refrigerant pipe 2 to the surrounding heat medium pipes 3 through the first heat-conducting fins 4, a heat conduction channel can be formed through the first heat-conducting fins 4, and heat can be efficiently conducted from the heat medium pipes 3 to the refrigerant pipes 2 through the first heat-conducting fins 4, thereby improving heating uniformity and increasing heat exchange efficiency; at the same time, the refrigerant pipes 2 and the heat medium pipes 3 can form an integral spatial network structure (honeycomb beam) through the first heat-conducting fins 4. This integral spatial network structure can constrain the relative position of the tube bundle and prevent the tube bundle from deforming or collapsing. Specifically, this embodiment fundamentally changes the stress mode of the tube bundle - the main stress-bearing element is no longer a bundle of independently deflecting "cantilever beams", but a "simply supported truss beam" with extremely high rigidity at both ends. Its enormous rigidity does not depend on the thickness of the fins themselves, but rather on the combined cross-sectional effect of the overall spatial network structure: when the tube bundle is bent, all pipes are locked and deformed collaboratively through the first heat-conducting fin 4, making the bending moment of inertia equivalent to a solid beam with a thickness equal to the entire diameter of the tube bundle, thus achieving bending stiffness exceeding that of a single pipe by tens of thousands of times. The load is efficiently transferred to the end plates through the tensile, compressive, and shear stresses within the overall spatial network structure, achieving a large-span rigid crossing without external support. When subjected to gravity, gravity induces a bending tendency. The overall spatial network structure of this embodiment achieves load redistribution and transfer through an internal self-balancing force system. When the tube bundle bears gravity, the first heat-conducting fin 4 connecting the refrigerant pipe 2 and the heat-conducting pipe 3 acts as a rigid link. The first heat-conducting fin 4 is subjected to external pressures F1 and F2 (such as... Figure 6 As shown, where F1 is the external pressure, F2 is the external force, and F3 is the internal axial force, the axial force is the internal force borne by the first heat-conducting fin as a "two-force bar". It enables the first heat-conducting fin 4 to generate an upward supporting reaction force on the upper tube and a downward constraining reaction force on the lower tube, thereby locking the relative displacement trends of the two tubes together and forming a rigid connection point. This mechanism of "external pressure action (F1, F2) → internal axial compression state (F3)" enables the overall spatial network structure to achieve rigid support. In short, each first heat-conducting fin 4, while achieving its own force balance, transmits the axial force it bears as a "load" through the connection point to the other tubes connected to it. Countless node units that have achieved their own force balance are connected in series, thereby redirecting and converging the dispersed loads, and finally guiding them all to the unique and solid support point of the structure - the tube sheets on both sides. The support reaction force provided by the tube sheets achieves overall balance.

[0045] Not limited thereto, another embodiment of this application also provides a devolatilization device, which includes a dual-pass cold trap as described above.

[0046] The above embodiments are merely illustrative of the principles and effects of this application and are not intended to limit this application. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of this application. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in this application should still be covered by the claims of this application.

Claims

1. A dual-pass cold trap, the dual-pass cold trap comprising a shell, wherein a plurality of refrigerant pipes are disposed within the shell, all refrigerant pipes being arranged parallel to each other in a horizontal direction, characterized in that, In addition to the outer refrigerant pipe, several heat transfer pipes are arranged around the refrigerant pipe. The heat transfer pipes are arranged parallel to the refrigerant pipe. The refrigerant pipe is rigidly connected to the surrounding heat transfer pipe through a first heat-conducting fin, which is inclined in the vertical direction.

2. The dual-tube cold trap as described in claim 1, characterized in that, The first heat-conducting fin is connected to the refrigerant pipe and the heat-conducting pipe at both ends by the first and second clips, respectively.

3. The dual-tube cold trap as described in claim 2, characterized in that, The two adjacent first heat-conducting fins are symmetrically distributed along the radial cross-section of the middle of the cold trap.

4. The dual-tube cold trap as described in claim 2, characterized in that, The first buckle has anti-slip teeth on its inner side.

5. The dual-tube cold trap as described in claim 2, characterized in that, Both the first and second buckles are elastic buckles.

6. The dual-tube cold trap as described in claim 2, characterized in that, The first buckle is an openable circular buckle.

7. The dual-tube cold trap as described in claim 2, characterized in that, The second buckle is a semi-circular arc buckle.

8. The dual-tube cold trap as described in claim 1, characterized in that, The inner side of the refrigerant pipe located on the outer side is rigidly connected to the adjacent heat transfer pipe through the first heat-conducting fin, and the outer side of the refrigerant pipe located on the outer side is equipped with a second heat-conducting fin.

9. The dual-tube cold trap as described in claim 1, characterized in that, The heat transfer pipes surrounding the refrigerant pipe are evenly distributed around the refrigerant pipe.

10. A devolatilization device, characterized in that, The devolatilization device includes a dual-pass cold trap as described in any one of claims 1-9.

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