A new economizer

Abstract

The utility model relates to heat exchange equipment technical field especially relates to a novel economizer, include: inner tube, the first flow channel that forms for the first medium circulation in the inner tube inside, and the inner tube inner wall is equipped with dentiform bulge, the outer tube is coaxially sleeved in the inner tube outside, and the outer tube and the inner tube between form the second flow channel for the second medium circulation, and the medium in the first flow channel and the second flow channel is through the inner tube wall and carries out heat exchange, a plurality of radial reinforcing rib, evenly distribute in the second flow channel along the circumference and connect the outer tube inner wall and the inner tube outer wall, the sealing plate is connected in the outer tube both ends and closes the second flow channel end, the import pipeline and the export pipeline, are located on the both ends of outer tube and with the both ends of second flow channel intercommunication. This scheme has the advantages of improving heat exchange efficiency, enhancing structural strength, reducing processing cost and improving fluid distribution uniformity.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange equipment technology, and in particular to a novel economical device. Background Technology

[0002] In industrial production and energy systems, economizers, as highly efficient heat exchange devices, are widely used in refrigeration, chemical, and power industries to recover waste heat or improve system energy efficiency. Traditional economizers typically employ shell-and-tube or plate structures, achieving energy transfer through heat exchange between internal and external media. However, existing technologies still have the following drawbacks:

[0003] Insufficient heat exchange efficiency is a major problem faced by conventional economizers. The inner tubes of conventional economizers typically have smooth walls, which easily leads to laminar flow of the fluid inside, resulting in increased thermal resistance and low heat exchange efficiency. Simultaneously, the flow channel between the outer and inner tubes lacks an effective turbulence-promoting structure, further limiting overall heat exchange performance. This design flaw prevents the heat exchange process from fully utilizing the heat transfer potential of the medium.

[0004] The trade-off between structural strength and cost is also a significant factor limiting the performance improvement of economizers. To enhance heat exchange efficiency, some improvement schemes add complex flow distribution structures or fins within the flow channels; however, such designs often result in high manufacturing difficulty and material costs. More seriously, these complex structures may reduce overall structural strength due to welding or assembly defects, affecting the equipment's service life and safety.

[0005] Uneven fluid distribution also plagues the performance of traditional economizers. When the flow channel between the outer and inner pipes lacks a proper support structure, differences in medium flow velocity lead to uneven fluid distribution, causing a decrease in heat exchange efficiency in localized areas. This uneven fluid distribution can also cause equipment vibration or noise, affecting the stable operation of the equipment.

[0006] To address the aforementioned issues, existing technologies urgently need improvement. Summary of the Invention

[0007] In order to solve the above problems, the purpose of this utility model is to provide a new type of economizer, which has the advantages of improving heat exchange efficiency, enhancing structural strength, reducing processing costs and improving fluid distribution uniformity.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] This application provides a novel economizer, the technical solution of which is as follows: A novel economizer, characterized in that it includes: an inner tube, the inside of which forms a first flow channel for the flow of a first medium, and the inner wall of the inner tube is provided with tooth-shaped protrusions;

[0010] An outer tube is coaxially sleeved on the outside of an inner tube, forming a second flow channel for the flow of a second medium between the outer tube and the inner tube. The medium in the first flow channel and the second flow channel exchange heat through the inner tube wall.

[0011] Multiple radial reinforcing ribs are evenly distributed circumferentially within the second flow channel and connect the inner wall of the outer tube to the outer wall of the inner tube.

[0012] A sealing plate is connected to both ends of the outer tube and seals the end of the second flow channel;

[0013] The inlet and outlet pipes are located at both ends of the outer pipe and are connected to both ends of the second flow channel.

[0014] Furthermore, this application also proposes that the inner wall of the inner tube has tooth-like protrusions evenly distributed along its circumference.

[0015] Furthermore, this application also proposes that the reinforcing ribs extend axially along the second flow channel, and the toothed protrusions extend axially along the inner tube.

[0016] Furthermore, this application also proposes that the outer tube, inner tube, reinforcing ribs, and toothed protrusions are integrally formed by stretching profiles.

[0017] Furthermore, this application also proposes that the profile is an aluminum profile.

[0018] Furthermore, this application also proposes that the tooth-like protrusions have a triangular or trapezoidal structure.

[0019] Furthermore, this application also proposes a reinforcing structure inserted into the inner tube, the reinforcing structure being a spiral baffle plate fixed to the inner wall of the inner tube and extending axially.

[0020] Furthermore, this application also proposes that the second medium flowing through the second channel and the first medium flowing through the first channel form a countercurrent heat exchange.

[0021] Furthermore, this application also proposes that the length of the inner tube is greater than the length of the outer tube, and that the two ends of the inner tube protrude from the sealing plates on both sides.

[0022] As can be seen from the above, the novel economizer provided in this application, along with its inner tube, outer tube, reinforcing ribs, sealing plate, inlet pipe, outlet pipe, and reinforcing structure, enhances the turbulence effect through the toothed protrusions of the inner tube, improves the structural stability through the reinforcing ribs, and reduces processing costs through the integrated profile. At the same time, it optimizes the fluid distribution and solves the problems of low heat exchange efficiency, insufficient structural strength, and uneven fluid distribution in traditional economizers. It has the advantages of improving heat exchange efficiency, enhancing structural strength, reducing processing costs, and improving the uniformity of fluid distribution. Attached Figure Description

[0023] Figure 1 A side view of a novel economic device provided in this application.

[0024] Figure 2 A cross-sectional schematic diagram of a novel economic device provided in this application.

[0025] Figure 3 This is a schematic diagram of the spiral spoiler provided in this application. Detailed Implementation

[0026] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0027] 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.

[0028] 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.

[0029] 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.

[0030] 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.

[0031] In existing technologies, economizers are widely used as heat exchange devices in refrigeration, chemical, and power industries. Traditional shell-and-tube or plate structures suffer from drawbacks such as insufficient heat exchange efficiency, a conflict between structural strength and cost, and uneven fluid distribution. For example, the smooth inner tube wall easily leads to laminar flow, increasing thermal resistance; the lack of support structure between the outer and inner tubes easily causes vibration; and complex flow distribution structures increase processing costs. In a waste heat recovery system at a chemical plant, the low heat exchange efficiency of traditional economizers resulted in the ineffective recovery of high-temperature waste gas, and frequent tube deformation occurred during equipment operation.

[0032] To solve the above problems, such as Figure 1-3 As shown, this application proposes a novel economizer, comprising an inner tube 2, an outer tube 1, radial reinforcing ribs 6, a sealing plate 5, and an inlet pipe 4 and an outlet pipe 3. The inner tube 2 forms a first flow channel and has toothed protrusions 8 on its inner wall. The outer tube 1 is coaxially fitted to form a second flow channel. Multiple radial reinforcing ribs 6 are evenly distributed circumferentially in the second flow channel and connect the inner and outer tube walls. The sealing plate 5 seals the ends of the second flow channel. The inlet pipe 4 and outlet pipe 3 are located at both ends of the outer tube 1 and communicate with the second flow channel. The inner tube 2 refers to the tubular structure through which the first medium flows, and can be formed using metal tubing. The toothed protrusions 8 on its inner wall increase the degree of fluid turbulence and disrupt the laminar boundary layer. The outer tube 1 refers to the tube body coaxially fitted to the outside of the inner tube 2, and can be made of the same material as the inner tube 2. Countercurrent heat exchange is achieved by forming a second flow channel through an annular gap. Radial stiffeners 6 refer to the supporting structure evenly distributed along the circumference. Specifically, they can be plate-shaped stiffeners integrally formed with the outer pipe 1, used to enhance the connection strength between the inner and outer pipes and guide the fluid to flow evenly. Sealing plate 5 refers to the sealing component welded or flanged to the end of the outer pipe 1, specifically a ring-shaped steel plate, used to seal the end of the second flow channel to prevent media leakage. Inlet pipe 4 and outlet pipe 3 refer to the tubular interfaces connected to both ends of the outer pipe 1, specifically standard flange interfaces, used to guide the second medium into and out of the second flow channel.

[0033] Specifically, when the first medium flows in the first flow channel of the inner tube 2, the toothed protrusions 8 cause the fluid to rotate and turbulent, disrupting the laminar flow state and enhancing heat transfer efficiency. The second medium enters the second flow channel from the inlet pipe 4 at the end of the outer tube 1, and is evenly distributed circumferentially under the guidance of the radial reinforcing ribs 6. When flowing through the annular space between the inner and outer tubes, it exchanges heat with the first medium in a counter-current manner through the tube wall. The sealing plate 5 ensures that the second flow channel forms a complete closed loop, preventing medium short-circuiting or leakage. The radial reinforcing ribs 6 support the inner and outer tubes while dividing the second flow channel into multiple fan-shaped regions, balancing the velocity differences in each region. The coaxial arrangement of the inner tube 2 and the outer tube 1 minimizes the heat conduction path, and the tube wall directly serves as the heat transfer interface to improve the heat transfer rate.

[0034] Compared with existing technologies, traditional economizers with smooth inner tubes result in high laminar thermal resistance. This solution actively disrupts laminar flow through toothed protrusions 8. Traditional outer and inner tubes lack supporting structures, leading to vibration. This solution simultaneously strengthens the structure and distributes fluid through circumferentially evenly distributed radial reinforcing ribs 6. Traditional end-sealing structures are complex and prone to leakage. This solution uses a sealing plate 5 to form a simple closed flow channel with the inlet pipe 4 and outlet pipe 3. Through these technical solutions, this application solves the problem of low heat exchange efficiency by promoting turbulence and reducing thermal resistance through toothed protrusions 8; eliminates the contradiction between structural strength and cost by using integrally molded radial reinforcing ribs 6 to enhance support while reducing processing difficulty; and avoids uneven fluid distribution by using circumferentially evenly distributed reinforcing ribs 6 to guide uniform medium flow, preventing localized decreases in heat exchange efficiency and vibration.

[0035] Furthermore, the inner wall of the inner tube 2 is uniformly distributed with toothed protrusions 8 along its circumference. These toothed protrusions 8 are triangular or trapezoidal structures. Specifically, the toothed protrusions 8 refer to a continuous arrangement of protrusions on the wall of the inner tube 2. They can be formed using a triangular or trapezoidal cross-section through stamping, extrusion, or stretching processes. This structure increases the contact area between the fluid and the tube wall and divides the fluid flow path, thus breaking the laminar boundary layer. The uniform circumferential distribution means that the toothed protrusions 8 are arranged at equal intervals along the circumference of the inner tube 2. This can be achieved by setting symmetrically distributed grooves during mold forming. This layout ensures that the fluid is uniformly disturbed along the circumference when flowing through the inner tube 2, preventing laminar flow residue in localized areas due to structural deficiencies. The triangular structure refers to a geometric shape with three sides and at least one acute angle. It can be implemented using isosceles or right triangles, whose sharp angles can induce localized vortices in the fluid. A trapezoidal structure is a geometric shape with a pair of parallel sides and the other two sides being non-parallel. Specifically, it can be achieved using symmetrical trapezoids or right-angled trapezoids. Its smooth transition surface enhances fluid disturbance while reducing flow resistance.

[0036] Specifically, when the first medium flows through the inner tube 2, the toothed protrusions 8 generate periodic disturbances to the fluid, dividing the laminar flow into multiple tiny vortices. The circumferentially uniformly distributed toothed protrusions 8 create a continuous resistance gradient in the fluid flow direction, forcing the fluid to generate velocity components in the radial and tangential directions, thereby disrupting the stability of the laminar boundary layer. Since the toothed protrusions 8 cover the entire circumferential wall of the inner tube 2, the fluid is subjected to uniform turbulent excitation at any cross-sectional position, ensuring that the heat exchange process remains uniform throughout the entire circumference of the tube wall. The triangular or trapezoidal toothed protrusions 8 disrupt the laminar boundary layer formed by the fluid within the flow channel by altering the geometry of the inner tube 2 wall. When the fluid flows through the toothed protrusions 8, the flow path is forced to change periodically, resulting in turbulent effects. The sharp angles of the triangular structure cause the fluid to form separation vortices behind the protrusions, increasing the contact area between the fluid and the tube wall; the trapezoidal structure guides the fluid to gradually change its flow direction through gentle slopes, reducing pressure drop while maintaining high turbulence intensity. Both structures enhance the heat exchange efficiency between the pipe wall and the fluid by increasing the radial mixing of the fluid.

[0037] This solution utilizes circumferentially uniformly distributed toothed protrusions 8 to achieve continuous turbulent excitation without adding additional flow-diverting components, achieving this solely through pipe wall structure optimization. This overcomes the limitations of traditional structures that rely on high flow velocities or complex flow-guiding devices to improve heat transfer efficiency. Through this technical solution, this application effectively addresses the problem of low heat transfer efficiency caused by laminar flow in the inner pipe 2. The circumferentially uniform distribution of the toothed protrusions 8 creates global disturbance, prompting the fluid to transition from laminar to turbulent flow, increasing the heat exchange intensity between the fluid and the pipe wall, while simultaneously avoiding uneven heat transfer caused by local structural deficiencies.

[0038] In a further embodiment, the reinforcing rib 6 extends axially along the second flow channel, and the toothed protrusion 8 extends axially along the inner tube 2. The axial extension of the reinforcing rib 6 refers to the continuous arrangement of the support structure connecting the inner wall of the outer tube 1 and the outer wall of the inner tube 2 along the length of the flow channel. Specifically, this can be achieved using a strip-shaped protrusion structure extending coaxially with the outer tube 1, maintaining the stability of the distance between the inner and outer tubes through continuous axial support. The axial extension of the toothed protrusion 8 refers to the protrusion structure on the inner wall of the inner tube 2 forming continuous grooves along the fluid flow direction. Specifically, this can be achieved using a straight or wavy protrusion structure parallel to the axis of the inner tube 2, changing the fluid flow pattern through axially continuous concave and convex surfaces. The axially extending reinforcing rib 6 forms a uniformly distributed longitudinal support within the second flow channel, ensuring a constant cross-section in the annular space between the outer tube 1 and the inner tube 2, preventing flow channel deformation due to medium pressure fluctuations. Simultaneously, the axial arrangement of the reinforcing rib 6 guides the second medium to form a stable laminar flow along the length of the flow channel, reducing eddy current losses generated by circumferential flow. When the toothed protrusions 8 extend axially along the inner tube 2, the concave and convex structures within the first flow channel form a continuous turbulence path, forcing the first medium to repeatedly change its velocity direction during flow, disrupting the laminar boundary layer and enhancing the turbulent effect. The axial extension design of both works synergistically, improving structural strength and fluid distribution uniformity through the reinforcing ribs 6, and enhancing the heat transfer efficiency of the inner tube 2 wall through the toothed protrusions 8.

[0039] Furthermore, the outer tube 1, inner tube 2, reinforcing rib 6, and toothed protrusion 8 are formed by integral stretching of the profile. Integral stretching refers to a processing technology that continuously stretches and forms metal materials in a mold, specifically using aluminum, copper, or alloy materials through extrusion or drawing processes. This process allows the outer tube 1, inner tube 2, reinforcing rib 6, and toothed protrusion 8 to form a seamless, integrated structure during the forming process, avoiding the welding or assembly steps required in traditional separate processing. The toothed protrusion 8 refers to a regular geometric protrusion structure distributed circumferentially along the inner wall of the inner tube 2, which can be simultaneously formed through the grooves on the inner wall of the profile stretching mold. This structure forms a continuous transition with the wall of the inner tube 2 during the stretching process, eliminating the need for additional welding or bonding, thus eliminating stress concentration problems caused by joints. The reinforcing rib 6 refers to a radial support structure connecting the inner wall of the outer tube 1 and the outer wall of the inner tube 2, which can be simultaneously formed through the rib grooves of the profile stretching mold. This structure forms an integrated support network with the outer tube 1 and inner tube 2 during the stretching process, directly improving the compressive and deformation resistance between the flow channels.

[0040] The integrated stretching process for profiles integrates the coaxial sleeve structure of the outer tube 1 and inner tube 2, the circumferential distribution of the reinforcing ribs 6, and the geometry of the toothed protrusions 8 into a single processing flow through mold design. During the stretching process, the metal material flows axially to fill the mold cavity, allowing the wall thickness of the outer tube 1 and inner tube 2, the cross-sectional dimensions of the reinforcing ribs 6, and the height of the toothed protrusions 8 to be formed simultaneously through plastic deformation of the material. Since there is no need for separate processing followed by welding or assembly, the processing steps are reduced to a single stretching step, while avoiding material strength reduction or assembly misalignment problems caused by the heat-affected zone of welding.

[0041] This solution utilizes an integrated profile stretching process, enabling all functional structures to be completed in a single molding process. This eliminates connection defects and simplifies the production process. Through this technical solution, this application replaces traditional multi-stage, modular manufacturing with a single processing step, reducing material waste and labor costs. Simultaneously, the seamless integrated structure enhances the mechanical strength and sealing of the flow channels. This process also avoids fluid leakage or localized stress concentration caused by welding or assembly errors, thereby ensuring the economizer maintains stable heat exchange performance during long-term operation.

[0042] like Figure 1 As shown, the inner tube 2 is longer than the outer tube 1, and both ends of the inner tube 2 protrude from the sealing plates 5 on both sides. The inner tube 2 being longer than the outer tube 1 means that the axial extension of the inner tube 2 exceeds the end face of the outer tube 1. This can be achieved by cutting the outer tube 1 into a prefabricated profile shorter than the inner tube 2. This structural difference causes misalignment at the connection interface between the inner tube 2 and the outer tube 1. The sealing plates 5 connecting to both ends of the outer tube 1 and sealing the second flow channel end means fixing the plate to the end of the outer tube 1 by welding or flange connection. Specifically, an annular sealing ring can be used to form a contact seal with the outer wall of the inner tube 2. This structure provides a positioning reference for the inner tube 2 to protrude. The inner tube 2 protruding from the sealing plates 5 means that the end face of the inner tube 2 extends to the outside of the sealing plates 5. This can be achieved by creating a through hole in the center of the sealing plates 5 and filling it with flexible sealing material. This protrusion structure forms an axial displacement compensation space.

[0043] like Figure 2 and 3As shown, this application further proposes a reinforcing structure 7 inserted inside the inner tube 2. The reinforcing structure 7 is a spiral baffle, which is fixed to the inner wall of the inner tube 2 and extends axially. The spiral baffle refers to a plate-like structure with a continuous spiral surface, specifically formed by rolling a thin metal sheet and then welding or bonding it. Its spiral angle range can be 30° to 60°. This structure guides the fluid to rotate and flow through the spiral surface, disrupting the laminar boundary layer. "Fixed to the inner wall of the inner tube 2 and extending axially" means that the spiral baffle forms continuous contact with the wall of the inner tube 2, which can be achieved using laser welding or integral stretching forming processes. This connection method ensures structural stability while avoiding additional assembly steps. The spiral baffle forms a continuous spiral flow channel inside the inner tube 2. When the first medium flows through it, it is guided by the spiral surface to generate rotational motion. The rotational motion of the fluid increases the radial velocity component, periodically disrupting the laminar boundary layer, thereby enhancing the convective heat transfer between the fluid and the wall of the inner tube 2. Meanwhile, the spiral baffles, arranged axially, form a continuous support structure inside the inner tube 2. The geometric stiffness of the spiral shape resists the deformation of the pipe wall caused by fluid pressure fluctuations, thus avoiding structural failure due to vibration.

[0044] The spiral baffle in this design achieves gradual fluid disturbance through a continuous spiral surface, resulting in a significantly lower pressure drop increment at the same flow rate compared to discrete baffle structures. Furthermore, existing technologies typically require additional independent supports to enhance structural strength, while the spiral baffle combines both baffle and support functions, reducing the number of components. Through this technical solution, this application can enhance the heat exchange efficiency of the inner tube 2 through the secondary flow effect generated by the spiral baffle without significantly increasing processing complexity, while simultaneously improving the inner tube 2's resistance to deformation through the continuity of the spiral structure. The rotational motion of the fluid within the spiral channel makes the temperature gradient distribution more uniform, avoiding significant temperature differences between the near-wall and mainstream regions under laminar flow conditions, thereby reducing thermal resistance. The integrated connection between the spiral baffle and the inner tube 2 eliminates the stress concentration problems that may occur with traditional welded supports, ensuring long-term operational reliability.

[0045] This application further proposes a counter-current heat exchange mechanism where the second medium flowing through the second channel and the first medium flowing through the first channel form a counter-current heat exchange. Counter-current heat exchange refers to a heat exchange method where the two media flow in opposite directions within adjacent channels. Specifically, this can be achieved by setting an inlet pipe 4 and an outlet pipe 3 at both ends of the outer pipe 1, and ensuring the medium flow direction in the first channel is opposite to that in the second channel. This method enhances the heat transfer driving force by maintaining the temperature gradient between the two media throughout the heat exchange path. Specifically, when the first medium flows into the inner pipe 2 from one end and towards the other, the second medium enters the second channel from the other end of the outer pipe 1 and flows towards the inlet end of the first medium. During the flow, the two media continuously exchange heat, with the heat from the high-temperature medium consistently transferred to the low-temperature medium, avoiding the problem of reduced heat transfer efficiency due to a small temperature difference at the ends, as seen in co-current heat exchange. Because the two media flow in opposite directions, the effective length of the heat exchange path is extended, resulting in more efficient heat transfer.

[0046] In summary, the advantages of this scheme are:

[0047] (1) It can be formed by aluminum profiles, with simple structure and low cost;

[0048] (2) The channel has uniformly distributed reinforcing ribs, which can improve the uniformity of fluid distribution and enhance heat exchange.

[0049] (3) The inner tube has internal teeth and spiral baffles to improve the heat exchange efficiency of the fluid inside the inner tube.

[0050] 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.

[0051] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention.

Claims

1. A novel economic device, characterized in that, include: The inner tube (2) has a first flow channel inside which the first medium flows, and the inner wall of the inner tube (2) is provided with tooth-shaped protrusions (8); An outer tube (1) is coaxially sleeved on the outside of the inner tube (2). A second flow channel for the second medium to flow is formed between the outer tube (1) and the inner tube (2). The medium in the first flow channel and the medium in the second flow channel exchange heat through the inner tube wall. Multiple radial reinforcing ribs (6) are evenly distributed circumferentially in the second flow channel and connect the inner wall of the outer tube (1) and the outer wall of the inner tube (2); The sealing plate (5) is connected to both ends of the outer tube (1) and seals the end of the second flow channel; The inlet pipe (4) and outlet pipe (3) are located at both ends of the outer pipe (1) and are connected to both ends of the second flow channel.

2. The novel economic device according to claim 1, characterized in that: The inner wall of the inner tube (2) has tooth-shaped protrusions (8) evenly distributed along its circumference.

3. The novel economic device according to claim 1 or 2, characterized in that: The reinforcing rib (6) extends axially along the second flow channel, and the toothed protrusion (8) extends axially along the inner tube (2).

4. The novel economic device according to claim 3, characterized in that: The outer tube (1), inner tube (2), reinforcing rib (6) and toothed protrusion (8) are formed by integral stretching of profiles.

5. The novel economic device according to claim 4, characterized in that: The profile is an aluminum profile.

6. The novel economic device according to claim 1, characterized in that: The toothed protrusions (8) are triangular or trapezoidal in shape.

7. The novel economic device according to claim 1, characterized in that: It also includes a reinforcing structure (7) inserted into the inner tube (2), the reinforcing structure (7) being a spiral baffle plate, which is fixed to the inner wall of the inner tube (2) and extends axially.

8. The novel economic device according to claim 1, characterized in that: The second medium flowing through the second channel forms a countercurrent heat exchange with the first medium flowing through the first channel.

9. The novel economic device according to claim 1, characterized in that: The inner tube (2) is longer than the outer tube (1), and the two ends of the inner tube (2) pass through the sealing plates (5) on both sides.

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