Double-pipe heat exchanger and refrigeration device

Abstract

The utility model discloses a double pipe heat exchanger and refrigeration plant, including bush, the bush includes the inner tube and the outer tube of bushing in the outer of inner tube, the axial distribution has the spoiler ring between the inner tube with the outer tube, the fin of the spoiler ring circumferential distribution has, and the fin on adjacent spoiler ring is staggered arrangement in the axial. The utility model discloses through inner tube helical flow guide groove, spoiler ring and staggered fin design, the heat exchange area and fluid disturbance are increased significantly, and the heat transfer efficiency of refrigerant and heat exchange liquid is promoted. The coil structure and reasonable import and export arrangement optimize flow path, enhance the heat exchange uniformity, guarantee structural stability simultaneously, realize the technical advantage of high efficiency, compact, energy efficiency ratio of heat exchanger.

Description

Technical Field

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

[0002] Currently, common heat exchanger types include plate heat exchangers, shell-and-tube heat exchangers, and coaxial heat exchangers. Among them, coaxial heat exchangers are widely used in small and medium-sized heat pump water heaters due to their simple structure, ease of manufacturing, and convenient maintenance. However, traditional coaxial heat exchangers have a problem where the protruding part between the spiral grooves of the inner tube contacts the inner surface of the outer tube. This reduces the heat exchange area between the refrigerant and water, leading to a decrease in heat exchange efficiency and thus affecting the overall energy efficiency ratio of the unit. Utility Model Content

[0003] To solve at least one of the above-mentioned technical problems, on the one hand, this utility model provides a shell-and-tube heat exchanger, which greatly increases the heat exchange area and convective heat transfer by adding staggered fins in the flow channel between the inner and outer tubes. It has a simple structure and low cost.

[0004] On the other hand, this utility model also proposes a refrigeration device having the aforementioned shell-and-tube heat exchanger.

[0005] The technical solution adopted in this utility model is to design a shell-and-tube heat exchanger, including a shell. The shell includes an inner tube and an outer tube sleeved outside the inner tube. A turbulence ring is axially distributed between the inner tube and the outer tube. Fins are circumferentially distributed on the turbulence ring, and the fins on adjacent turbulence rings are staggered in the axial direction.

[0006] In some embodiments, the fins are stepped, convex-concave periodic structures formed by radially bending the ring body of the turbulence ring inward and outward.

[0007] In some embodiments, the turbulence ring is supported between the outer tube and the inner tube.

[0008] In some embodiments, adjacent turbulence rings are axially connected to form a circular tube fitted outside the inner tube.

[0009] In some embodiments, the end of the outer tube is fixedly connected to the inner tube by a bushing, and the inner tube is provided with an outer positioning protrusion, which limits the axial movement of the end of the outer tube along the inner tube.

[0010] In some embodiments, the bushing is provided with an inner positioning protrusion, which limits the axial movement of the circular tube.

[0011] In some embodiments, the outer tube is connected to the bushings at both ends, and the two bushings are respectively provided with an inlet and an outlet, wherein the inlet is larger than the outlet.

[0012] In some embodiments, a spiral guide groove is provided on the outer wall of the inner tube, and both ends of the guide groove extend into the bushing.

[0013] In some embodiments, the sleeve is bent into a coil-shaped structure, and the inlet is located above the outlet.

[0014] The refrigeration equipment includes the aforementioned shell-and-tube heat exchanger, wherein the outer tube is connected to the refrigerant of the refrigeration system, and the inner tube is connected to the heat exchange fluid.

[0015] Compared with the prior art, the present invention has the following beneficial effects:

[0016] This invention employs an innovative shell-and-tube heat exchanger design. A turbulence ring is placed between the inner and outer tubes, with staggered fins arranged circumferentially around the ring. The fins are designed with a stepped, convex-concave periodic structure, effectively enhancing fluid disturbance and turbulence formation, significantly improving the heat transfer efficiency between the refrigerant and the heat exchange fluid. The turbulence ring is axially connected into a circular tube structure, and the inner and outer tubes, as well as the circular tube itself, are stably fixed using a bushing and positioning protrusions. This ensures a constant flow channel morphology, avoids axial displacement and assembly deviations, and improves the structural reliability and durability of the heat exchanger. The combination of the spiral guide groove on the outer side of the inner tube and the bushing causes the fluid to form a swirling flow after entering the heat exchange channel, extending the flow path, increasing heat exchange time, and further enhancing the heat transfer effect. The coiled shell structure and the design of the inlet located above the outlet optimize fluid distribution and flow direction, reducing local stagnation and short-circuiting phenomena, and improving overall heat exchange uniformity. Furthermore, the heat exchanger of this patent can be directly applied to refrigeration equipment. The outer tube is connected to the refrigerant, and the inner tube is connected to the heat exchange fluid, achieving efficient heat transfer and significantly improving the overall energy efficiency ratio (COP). The overall solution is compact, easy to manufacture, and has high heat transfer efficiency, while also possessing assembly stability and operational reliability, providing a high-performance heat exchange solution for refrigeration equipment. Attached Figure Description

[0017] The present invention will now be described in detail with reference to specific embodiments and accompanying drawings. To illustrate the details and facilitate understanding of its principles, the drawings are not necessarily to scale, and similar reference numerals may describe similar components in different views. The accompanying drawings generally illustrate the embodiments discussed herein by way of example and not limitation. Wherein:

[0018] Figure 1 This is a schematic diagram of the overall structure of a shell-and-tube heat exchanger.

[0019] Figure 2 This is a structural cross-sectional view of the main body of a shell-and-tube heat exchanger.

[0020] Figure 3 This is a schematic diagram of the exterior of the shell-and-tube heat exchanger.

[0021] Figure 4 This is a schematic diagram of the inner tube structure.

[0022] Figure 5 This is a schematic diagram of the structure of a cylindrical trapezoidal staggered fin.

[0023] Figure 6 This is a schematic diagram of the outer tube structure.

[0024] Figure 7 This is a schematic diagram of the refrigerant outlet bushing.

[0025] Figure 8 This is a schematic diagram of the refrigerant inlet bushing.

[0026] Figure 9 This is a schematic diagram of a periodic structural unit of trapezoidal misaligned fins.

[0027] Figure 10 This is a schematic diagram of the trapezoidal misaligned fin structure.

[0028] Figure 11 This is a process flow diagram for the manufacturing of a shell-and-tube heat exchanger.

[0029] In the diagram, 100 is the sleeve; 200 is the first fixing foot; 300 is the inlet temperature sensor; 400 is the second fixing foot; 500 is the outlet pipe; 600 is the outlet temperature sensor; 700 is the inlet pipe; 800 is the connecting plate; 101 is the inner pipe; 102 is the outer pipe; 103 is the fin; 104 is the outer positioning protrusion; 105 is the inlet bushing; 106 is the inner positioning protrusion; 107 is the spiral guide groove; 108 is the refrigerant flow channel; 109 is the outlet bushing; 111 is the inner pipe inlet; 112 is the liquid inlet; 113 is the liquid outlet; and 114 is the inner pipe outlet. Detailed Implementation

[0030] The following are specific embodiments of this utility model, and the technical solution of this utility model will be further described with reference to the accompanying drawings. However, this utility model is not limited to these embodiments, and the following embodiments do not limit the utility model involved in the claims. In addition, all combinations of features described in the embodiments are not necessarily necessary for the solution of the utility model.

[0031] The principle and structure of this utility model will be described in detail below with reference to the accompanying drawings and embodiments.

[0032] Example

[0033] like Figure 1 , 2As shown in Figure 3, a shell-and-tube heat exchanger 100 is used to realize heat exchange between two fluids. It includes a shell-and-tube 100, which includes an inner tube 101 and an outer tube 102 sleeved outside the inner tube 101. A turbulence ring is axially distributed between the inner tube 101 and the outer tube 102. Fins 103 are circumferentially distributed on the turbulence ring. The fins 103 on adjacent turbulence rings are staggered in the axial direction.

[0034] The described shell-and-tube heat exchanger uses a turbulence ring between the inner tube 101 and the outer tube 102, with fins 103 arranged circumferentially on the turbulence ring. This causes turbulence and secondary flow in the fluid as it flows through the heat exchange channel, thereby breaking the boundary layer and enhancing convective heat transfer. The fins 103 on adjacent turbulence rings are arranged in an axially staggered pattern, preventing the formation of stable flow channels within the flow path and effectively increasing the contact opportunities between the fluid and the walls of the inner and outer tubes 102, while significantly expanding the heat exchange area. This not only improves the heat transfer efficiency between the refrigerant and water and alleviates the problem of uneven local heat transfer, but also enhances the overall energy efficiency ratio, achieving a simple structure and high heat exchange efficiency.

[0035] Furthermore, the fin 103 is a stepped, concave-convex periodic structure formed by bending the ring body of the turbulence ring in the radial direction.

[0036] The fins 103 are formed by radially and radially bending of the turbulence-inner ring body into a stepped, convex-concave periodic structure, which enhances the formation of local turbulence and eddies, thereby further reducing the fluid boundary layer thickness. This structure not only increases the effective heat transfer area of ​​the fins 103, but also extends the fluid flow path through the periodic convex-concave shape, improving the mixing degree between hot and cold fluids. This significantly improves heat transfer efficiency and heat exchange uniformity, while achieving a further increase in energy efficiency ratio under the premise of a compact structure.

[0037] Furthermore, the turbulence ring is supported between the outer tube 102 and the inner tube 101.

[0038] The turbulence ring, supported between the outer tube 102 and the inner tube 101, not only positions and fixes the relative positions of the inner and outer tubes 102, but also effectively maintains the stable structure of the annular flow channel, preventing the inner and outer tubes 102 from shifting due to fluid scouring or pressure fluctuations. Simultaneously, as a supporting component, the turbulence ring ensures structural strength while forming a flow channel partition, guiding and turbulent the fluid as it flows through, further promoting the full utilization of the heat exchange surface. This design combines structural stability with enhanced heat transfer, thereby improving the overall performance and reliability of the heat exchanger.

[0039] Furthermore, such as Figure 5As shown, adjacent turbulence rings are axially connected to form a circular tube sleeved outside the inner tube 101, that is, the turbulence rings are connected to form a tube body. The length of the circular tube can be adjusted according to the pressure drop of the shell-and-tube heat exchanger 100. Increasing the length will increase the pressure drop of the refrigerant flow channel 108, and decreasing the length will decrease the pressure drop of the refrigerant flow channel 108.

[0040] Adjacent turbulence rings are axially connected to form a circular tube surrounding the inner tube 101, creating a continuous, integrated structure that avoids assembly misalignment and flow dead zones that can occur when individual turbulence rings are installed independently. This circular tubular structure maintains a stable geometric shape in the axial direction, facilitating installation and mass production. Simultaneously, it provides continuous turbulence and guidance during fluid flow, ensuring uniform disturbance of the fluid throughout the flow channel. This not only improves the consistency and overall efficiency of heat transfer but also enhances the structural strength and durability of the heat exchanger.

[0041] A series of staggered, periodic arrangement of turbulence rings is used, with the lower surface of fins 103 in contact with the outer surface of the inner tube 101, and the upper surface of fins 103 in contact with the inner surface of the outer tube 102. The circular tube is made of 430 stainless steel sheet with a thickness of 0.3mm-0.8mm. 430 stainless steel is inexpensive, saving costs. During processing, stepped concave-convex structures are sequentially bent along the strip-shaped sheet, and then the strip-shaped sheet is rolled into a circular tube to form the aforementioned turbulence rings.

[0042] Furthermore, the end of the outer tube 102 is fixedly connected to the inner tube 101 via a bushing, and the inner tube 101 is provided with an outer positioning protrusion 104, which limits the axial movement of the end of the outer tube 102 along the inner tube 101.

[0043] The outer tube 102 is fixedly connected to the inner tube 101 at its end via a bushing, ensuring the coaxiality and sealing of the inner and outer tubes 102 assembly. Simultaneously, the outer positioning protrusion 104 on the inner tube 101 limits the end of the outer tube 102, preventing axial slippage or loosening. This structure simplifies the assembly process of the inner and outer tubes 102, improves the reliability of the connection, and avoids relative displacement caused by vibration or thermal expansion and contraction during operation. This ensures stable flow channel dimensions, maintains the design effect of the turbulence ring and fins 103, and thus improves the overall performance and service life of the heat exchanger.

[0044] The outer positioning protrusion 104 on the inner tube 101 can realize the rapid positioning of the bushing during installation and welding.

[0045] Furthermore, an inner positioning protrusion 106 is provided inside the bushing, which limits the axial movement of the circular tube.

[0046] The bushing is equipped with an inner positioning protrusion 106, which abuts against the end of the circular tube to limit and fix the tube in the axial direction. This design prevents the circular tube from axial displacement under fluid impact or thermal expansion and contraction, thereby ensuring the stability of the predetermined position of the turbulence ring and fins 103. This not only improves the assembly accuracy and operational reliability of the overall structure, but also ensures a constant flow channel shape, avoiding the impact of positional deviation on fluid disturbance, thus maintaining the long-term stability of heat exchange efficiency and overall performance.

[0047] The inner positioning protrusion 106 is on the inner surface of the inlet bushing 105, and its purpose is to achieve rapid positioning of the round tube during installation and welding.

[0048] Furthermore, such as Figure 6 , 7 As shown in Figure 8, both ends of the outer tube 102 are connected to the bushings, namely the inlet bushing 105 and the outlet bushing 109. The two bushings are respectively provided with an inlet 112 and an outlet 113, and the diameter of the inlet 112 is larger than that of the outlet 113.

[0049] Both ends of the outer tube 102 are connected to bushings, forming a stable end structure that facilitates the arrangement and sealing of the inlet and outlet. The two bushings are respectively equipped with an inlet 112 and an outlet 113. The diameter of the inlet 112 is larger than that of the outlet 113, resulting in a lower fluid velocity and less resistance, which is conducive to smooth fluid intake. The smaller diameter outlet 113, on the other hand, increases the flow velocity after the fluid passes through the channel, enhancing the fluid's carrying and discharge capacity. This structure optimizes the fluid flow state within the heat exchanger, reduces energy consumption, and improves heat exchange uniformity and overall heat transfer efficiency.

[0050] Furthermore, such as Figure 4 As shown, a spiral guide groove 107 is provided on the outer wall of the inner tube 101, and both ends of the guide groove extend into the bushing.

[0051] A spiral guide groove 107 is formed on the outer wall of the inner tube 101, with both ends extending into the bushing. This allows the fluid to be guided spirally immediately upon entering the flow channel, causing the fluid to swirl along the outer wall of the inner tube 101. This design effectively extends the flow path of the fluid within the flow channel, increases the contact time with the heat exchange surface, and enhances the turbulence and mixing effect of the fluid. The extension of both ends of the guide groove into the bushing ensures that the inlet and outlet areas also possess swirling characteristics, avoiding dead zones and further improving overall heat transfer efficiency and heat exchange uniformity.

[0052] The spiral guide groove 107 on the inner tube 101 can increase the heat exchange area of ​​the inner tube 101 on the one hand, and serve as a refrigerant flow channel on the other hand, thus avoiding the blockage of the refrigerant flow channel 108 at the bend of the sleeve 100.

[0053] The outer pipe 102 is connected to the refrigerant inlet bushing 105 and the refrigerant outlet bushing 109, forming a pipe nested on the outer surface of the inner pipe 101. The space between the inner surfaces of the outer pipe 102, the refrigerant inlet bushing 105 and the refrigerant outlet bushing 109 and the outer surface of the inner pipe 101 is the refrigerant flow channel 108.

[0054] Furthermore, the sleeve 100 is bent into a coil-shaped structure, and the liquid inlet 112 is located above the liquid outlet 113.

[0055] The sleeve 100 is bent into a coil shape, allowing the fluid to complete multi-stage flow within a limited space, increasing the effective heat transfer length and heat exchange time of the heat exchanger. Simultaneously, the liquid inlet 112 is located above the liquid outlet 113, utilizing natural gravity and the downward flow direction of the fluid to promote uniform fluid distribution within the coil, reducing local stagnation and short-circuiting. This design not only improves the contact efficiency between the fluid and the heat exchange surface but also optimizes the overall flow path, thereby significantly enhancing the heat transfer performance and overall energy efficiency ratio of the heat exchanger.

[0056] It also includes a first fixing foot 200 and a second fixing foot 400. The first fixing foot 200 and the second fixing foot 400 are fixed to the inside of the coil-shaped coil by welding. On the one hand, they are fixedly connected to each layer of the sleeve 100 to increase the overall structural strength of the sleeve 100 heat exchanger. On the other hand, they can be fixed to other equipment through the first fixing foot 200 and the second fixing foot 400, thereby realizing the installation and fixation of the entire heat exchanger.

[0057] It also includes an inlet temperature sensor 300 and an outlet temperature sensor 600. The inlet temperature sensor 300 and the outlet temperature sensor 600 are respectively installed near the inlet and outlet of the inner tube 101. They are used to install temperature sensors, so that the water temperature at the inlet and outlet can be monitored by the temperature sensors.

[0058] It also includes a connecting plate, which is used to fix the topmost sleeve 100 of the heat exchanger body. The purpose of the connecting plate is to increase the overall structural strength of the sleeve 100 heat exchanger and prevent the topmost sleeve 100 from shaking. The purpose of bending the sleeve 100 heat exchanger into a spiral shape here is to reduce the volume of the sleeve 100 heat exchanger and make the structure of the sleeve 100 heat exchanger compact.

[0059] The refrigeration equipment includes the aforementioned shell-and-tube heat exchanger 100, wherein the outer tube 102 is connected to the refrigerant of the refrigeration system, and the inner tube 101 is connected to the heat exchange fluid, such as water.

[0060] The refrigeration equipment achieves efficient heat exchange between the refrigerant and the heat exchange fluid through a shell-and-tube heat exchanger (type 100). The outer tube 102 is connected to the refrigerant in the refrigeration system, allowing the refrigerant to absorb or release heat during its flow. The inner tube 101 is connected to the heat exchange fluid, enabling the heat exchange fluid to generate sufficient turbulence and mixing under the action of the spiral guide groove 107, the turbulence ring, and the fins 103. Through the efficient heat exchange and fluid turbulence of the inner and outer tubes 102, the heat transfer rate is significantly improved, and the problem of uneven local heat exchange is alleviated, thereby improving the overall energy efficiency ratio and operational stability of the unit, achieving the technical effect of compact structure and high heat exchange efficiency of the refrigeration equipment.

[0061] Water flows into the inner tube 101 of the sleeve 100 from the inlet and then flows out from the outlet of the inner tube 101, while the refrigerant flows in the opposite direction in the refrigerant flow channel 108 from the inlet 112 and finally flows out from the outlet 113. By reversing the flow of water and refrigerant, the heat exchange time can be greatly increased, thereby improving the heat exchange efficiency.

[0062] The inlet 112 and outlet 113 have different diameters, meaning the refrigerant inlet is larger than the refrigerant outlet. This is to prevent airlocks and improve the refrigerant's flow characteristics. The larger inlet reduces the flow velocity, avoiding pressure loss due to excessive velocity. Furthermore, a smaller outlet is prone to airlocks within the pipe, affecting heat transfer and potentially causing localized overheating or equipment damage. The larger inlet facilitates smooth gas discharge, reducing the risk of airlocks. Alternatively, refrigerant inlets and outlets of the same size can be chosen if needed. Therefore, the refrigerant outlet bushing 109 and refrigerant inlet bushing 105 are identical, offering interchangeability and further reducing manufacturing costs. The refrigerant inlet connects to the inlet pipe 700, and the refrigerant outlet connects to the outlet pipe 500.

[0063] like Figure 11As shown, when processing the inner tube 101, a straight copper tube with a diameter of 32mm and a wall thickness of 1.5mm is first cut into a 2000mm long copper tube. Then, a spiral groove is formed by twisting the tube using a twisting machine to create a spiral guide groove 107. Next, an outer positioning protrusion 104 is processed at one end 50mm from the tube opening. This completes the processing of the inner tube 101 of the shell-and-tube 100 type heat exchanger. When processing the circular tubular trapezoidal staggered fins 103, a 0.5mm thick 430 stainless steel sheet is roll-formed to obtain the trapezoidal staggered fins 103. 3. Then, the fins 103 are punched to a suitable size and rolled into a round tube, thus obtaining the round tube trapezoidal staggered fins 103; when processing the outer tube 102, the straight copper tube raw material with a diameter of 40.6 mm and a wall thickness of 1.5 mm is first cut into a copper tube with a length of 1780 mm, and then the two ends are widened, thus completing the outer tube 102 of the shell-and-tube 100 heat exchanger; the main body of the refrigerant inlet bushing 105 and the refrigerant outlet bushing 109 are both made by narrowing the ends of copper tubes with a length of 65 mm, a wall thickness of 1.5 mm and an outer diameter of 44.6 mm.

[0064] like Figure 9 , 10 As shown, the entire process flow of the shell-and-tube 100 type heat exchanger is as follows: First, the refrigerant inlet bushing 105 is quickly positioned and installed using the outer positioning protrusion 104 on the outside of the inner tube 101. At this time, one end of the refrigerant inlet bushing 105 is welded and fixed to the inner positioning protrusion 106 of the inner tube 101. The welding quality must be reliable and leak-proof. Then, the circular tubular trapezoidal staggered fins 103 are quickly installed using the positioning protrusion on the inner surface of the refrigerant inlet bushing 105. The two ends of the circular tubular trapezoidal fins 103 need to be spot welded to fix the fins 103 to the inner tube 101. The purpose of the first step is to prevent the fins 103 from shifting during bending of the sleeve 100. Next, the outer tube 102 and the refrigerant outlet bushing 109 are installed. The flared ends of the outer tube 102 mate with the constricted ends of the refrigerant inlet bushing 105 and the refrigerant outlet bushing 109, respectively. The constricted end of the refrigerant outlet mates with the inner tube 101. The mating points are fixedly connected by welding, ensuring a secure and leak-proof weld. After welding, the sleeve 100 is bent into a spiral shape using a bending forming method, thereby reducing the footprint of the sleeve 100. Finally, the first fixing foot 200, the second fixing foot 400, the connecting plate, the inlet temperature sensor 300 (sleeve 100), the outlet temperature sensor 600 (sleeve 100), the refrigerant inlet pipe, and the refrigerant outlet pipe are welded and installed, thus completing the sleeve 100 type heat exchanger. The installation and welding between the inner pipe 101, the outer pipe 102, the refrigerant inlet bushing 105 and the refrigerant outlet bushing 109 must be secure to ensure that the refrigerant flow channel 108 is airtight.

[0065] The specific embodiments described herein are merely illustrative examples illustrating the spirit of this utility model. Those skilled in the art to which this utility model pertains may make various modifications or additions to the described specific embodiments or use similar methods to replace them, without departing from the spirit of this utility model or exceeding the scope defined by the appended claims.

[0066] Although this document uses a number of technical terms, the possibility of using other terms is not excluded. These terms are used merely for the convenience of describing and explaining the essence of this invention; interpreting them as any additional limitation would contradict the spirit of this invention. The order of actions, steps, etc., in the apparatus and methods shown in the specification and drawings can be implemented in any order unless a specific order is explicitly specified, and as long as the output of a preceding process is not used in a subsequent process. Similar sequential terms used for descriptive convenience (e.g., "firstly," "next," "secondly," "again," "then," etc.) do not imply that the actions must be performed in such an order.

[0067] Those skilled in the art will understand that all directional references (e.g., above, below, up, up, down, down, top, bottom, left, right, vertical, horizontal, etc.) are used descriptively in the drawings to aid the reader's understanding and do not imply (e.g., a limitation on the scope of the invention as defined by the appended claims) a limitation on the scope of the invention as defined by the appended claims. They are merely for the purpose of facilitating the description of this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a particular orientation or be constructed and operated in a particular orientation. The directional terms "inside" and "outside" refer to inside or outside relative to the outline of the respective components themselves.

[0068] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0069] Additionally, some vague terms (e.g., substantially, certain, generally, etc.) may refer to slight inaccuracies or minor deviations in conditions, quantities, values, or dimensions, some of which are within manufacturing tolerances or limits. It should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components; unless otherwise stated, these terms have no special meaning and therefore should not be construed as limiting the scope of protection of this application.

Claims

1. A shell-and-tube heat exchanger, comprising a shell and an outer tube sleeved around the inner tube, characterized in that, A turbulence ring is axially distributed between the inner tube and the outer tube, and fins are circumferentially distributed on the turbulence ring. The fins on adjacent turbulence rings are staggered in the axial direction.

2. The shell-and-tube heat exchanger according to claim 1, characterized in that, The fins are stepped, convex-concave periodic structures formed by bending the ring body of the turbulence ring inward and outward in the radial direction.

3. The shell-and-tube heat exchanger according to claim 2, characterized in that, The turbulence ring is supported between the outer tube and the inner tube.

4. The shell-and-tube heat exchanger according to claim 1, characterized in that, The adjacent turbulence rings are axially connected to form a circular tube sleeved outside the inner tube.

5. The shell-and-tube heat exchanger according to claim 4, characterized in that, The end of the outer tube is fixedly connected to the inner tube by a bushing. The inner tube is provided with an outer positioning protrusion, which limits the axial movement of the end of the outer tube along the inner tube.

6. The shell-and-tube heat exchanger according to claim 5, characterized in that, The bushing is provided with an inner positioning protrusion, which limits the axial movement of the round tube.

7. The shell-and-tube heat exchanger according to claim 5, characterized in that, Both ends of the outer tube are connected to the bushings, and the two bushings are respectively provided with an inlet and an outlet, with the inlet having a larger diameter than the outlet.

8. The shell-and-tube heat exchanger according to claim 7, characterized in that, A spiral guide groove is provided on the outer wall of the inner tube, and both ends of the guide groove extend into the bushing.

9. The shell-and-tube heat exchanger according to claim 7, characterized in that, The sleeve is bent into a coil-shaped structure, and the liquid inlet is located above the liquid outlet.

10. A refrigeration device, characterized in that, Includes a shell-and-tube heat exchanger as described in any one of claims 1 to 9, wherein the outer tube is connected to the refrigerant of the refrigeration system and the inner tube is connected to the heat exchange fluid.

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