Self-vibration long-life turbolator, heat exchanger and design adjustment method

Abstract

The invention discloses a self-vibration long-service-life turbolator, a heat exchanger and a design adjusting method. The turbolator comprises a spoiler and a spring, wherein the spoiler comprises a rigid support rod, spoiler teeth and a resistor. The heat exchanger comprises an inlet tube box, an inlet tube plate, a heat exchange tube, an outlet tube plate and an outlet tube box, and further comprises the self-vibration long-service-life turbolator. According to the design adjustment method, the design adjustment of the application is completed according to the vibration frequency and the amplitude for the turbolator. The heat exchanger has the beneficial effects that heat transfer can be effectively enhanced under the dynamic working conditions (such as vibration and rolling), the service life is longer, the adjustability is better, the applicability is wider, and therefore the requirements of the industrial heat exchanger for the efficient, stable and long-acting heat transfer technology are met.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of enhanced heat transfer of chemical containers, and particularly relates to a self-vibrating long-service-life spoiler, a heat exchanger and a design adjustment method. BACKGROUND

[0002] Heat exchangers are widely used in mechanical manufacturing, energy chemical industry, transportation and other industries, and are important equipment for realizing efficient energy utilization and energy saving and emission reduction. The heat exchange performance directly affects the effective utilization rate of energy. Therefore, improving the heat transfer efficiency of the heat exchanger is an important research topic in the industrial field. With the increasing demand for energy saving and cost reduction, developing new high-efficiency enhanced heat transfer technology has become a key way to improve the performance of heat exchangers.

[0003] In the prior art, one of the methods for enhancing heat transfer in the pipe is to insert a spoiler element (such as a ribbon, a vortex generator, etc.) into the heat exchange pipe, to effectively improve the convective heat transfer coefficient by enhancing the degree of turbulence of the fluid and thinning the boundary layer thickness. Among them, the ribbon as a common means of heat transfer enhancement can produce obvious dispersion flow effect in the heat exchange pipe. Dispersion flow promotes the transition of fluid from laminar flow to turbulent flow by disturbing the flow state of the fluid, thereby realizing efficient heat transfer enhancement and improving the anti-fouling performance to some extent.

[0004] In actual application, when the thickness of the ribbon is thin and presents a sheet structure, it is easy to vibrate under the impact of medium flow. On the one hand, under the excitation of rolling or narrow band, the vibration of the ribbon helps to enhance the convective heat transfer and improve the anti-fouling performance, which is a performance improvement worthy of attention. On the other hand, in long-term operation, the ribbon itself and the connecting part between the ribbon and the fixed area of the heat exchange equipment are prone to fatigue damage, which leads to the decrease of the durability and stability of the equipment. This makes the technology based on the vibration of the ribbon for heat transfer enhancement difficult to be widely applied in long-term industrial equipment, especially in industrial environments requiring high reliability and long-term operation. In existing applications, thicker and more rigid ribbons are usually used to avoid or weaken the generation and influence of vibration, but this also loses the function of vibration for enhancing heat transfer.

[0005] In summary, the existing heat transfer enhancement technology based on the ribbon structure and vibration excitation, although it can provide certain heat transfer effect in the short term, its service life and reliability cannot meet the needs of industrial equipment under long-term and stable working conditions. Therefore, a new type of internal plug-in design is needed, which not only can effectively enhance heat transfer under dynamic working conditions (such as vibration, rolling, etc.), but also has a longer service life, better adjustability and wider applicability, so as to meet the needs of industrial heat exchangers for efficient, stable and long-term heat transfer technology. SUMMARY

[0006] The application provides a self-vibration long-life spoiler, a heat exchanger and a design adjustment method, fundamentally solves the problems of limited heat transfer enhancement effect, serious fatigue damage, insufficient service life and lack of adjustability in the prior art, and significantly improves the overall performance and industrial application value of the heat exchanger.

[0007] The application aims to solve the following problems: 1. Improve heat transfer performance and inhibit fouling. The existing mainstream internal insertion spoiler mainly depends on the change of the geometric structure to change the flow field to achieve heat transfer enhancement, and fails to fully utilize the vibration effect for enhancement. The application introduces a controllable self-vibration mechanism into the spoiler, so that the fluid forms periodic disturbance in the pipe, thereby further improving the heat transfer efficiency and effectively inhibiting the deposition of fouling in the heat exchange pipe, and improving the heat transfer stability under long-term operation.

[0008] 2. Prolong the service life. The traditional vibration enhancement technology relying on the deformation of the flexible spoiler body is prone to fatigue damage at the structure and connection parts under long-term vibration working conditions, and is difficult to meet the long-period operation requirements of industrial equipment. The application separates the flexible part from the spoiler body, so that it has independent replacement function, and realizes periodic vibration by using spring structure, thereby significantly improving the reliability and durability of the system, and meeting the application requirements of long service life of industrial heat exchangers.

[0009] 3. Has adjustability and wide applicability. After the design of the existing self-vibration heat transfer enhancement technology is completed, the vibration parameters (such as frequency, amplitude, etc.) usually cannot be adjusted, which limits its adaptability under different working conditions. The application introduces independent flexible parts (such as springs), counterweight modules and resistance blocks into the structure, so that the vibration presents controllable simple harmonic characteristics, thereby the vibration parameters can be flexibly adjusted. This design not only improves the universality, but also enables the device to adapt to different working conditions and various medium environments, thereby expanding the application range.

[0010] The application is achieved by the following technical solutions: A self-vibration long-life spoiler, comprising a spoiler part, the spoiler part comprising a rigid support rod, the front and rear sections of the rigid support rod being light rods, a plurality of spoiler teeth being arranged on the middle section of the rigid support rod along the rod, and a resistance sub being arranged on the middle and rear sections of the rigid support rod; further comprising a spring arranged on the rear side of the resistance sub.

[0011] Further, the spoiler part support further comprises an inlet support and an outlet support, the front and rear sections of the rigid support rod are arranged on the inlet support and the outlet support respectively, and the spring is arranged between the resistance sub and the outlet support.

[0012] Further, the spoiler part support comprises a support plate and a bushing, the support plate is provided with a medium opening and a rod opening, the bushing is arranged in the rod opening, and the rigid support rod is arranged in the bushing.

[0013] Further, the spoiler tooth is a spiny spoiler tooth, and the resistance sub is a conical structure with a conical surface facing forward.

[0014] Further, the rear section of the rigid support rod is provided with a detachable counterweight.

[0015] A heat exchanger comprises an inlet tube box, an inlet tube plate, heat exchange tubes, an outlet tube plate, and an outlet tube box, and further comprises the self-vibrating long-life spoiler described above, the front section of the rigid support rod is located in the inlet tube box and is arranged in the inlet support part, the middle section of the rigid support rod is arranged in the inlet tube plate, the heat exchange tubes, and the outlet tube plate, the resistance sub is opposite to the outlet of the heat exchange tubes, the rear section of the rigid support rod is located in the outlet tube box and is arranged in the outlet support part, and the spring is located between the resistance sub and the outlet support part.

[0016] Further, the heat exchanger further comprises the self-vibrating long-life spoiler described above, the inlet support part is arranged in the inlet tube box, and the outlet support part is arranged in the outlet tube box.

[0017] Further, the outlet of the heat exchange tube is provided with a turbulence generator.

[0018] A design adjustment method for the self-vibrating long-life spoiler described above: the weight of the counterweight is m the spring constant of the spring is k the distance between the resistance sub and the outlet of the heat exchange tube in the spring at rest is t the position of the resistance sub in the spring at rest is x = 0, and the direction pointing to the outlet is positive; the resistance is approximately (1); wherein the constant C needs to be calibrated by experiments or numerical simulation according to the shape of the resistance sub and the flow state of the medium; the spring force is (2); the state space representation form of the dynamic equation of the spoiler in the heat exchange tube along the axial direction is: (3); wherein, y is the displacement, v is the velocity, a is the acceleration; the numerical solution of equation (3) is obtained to obtain the displacement, velocity, and acceleration state corresponding to the time, and the vibration frequency and amplitude of the spoiler under this combination are obtained by analysis, and the design adjustment of the application is completed according to the vibration frequency and amplitude.

[0019] Further, the amplitude of the spoiler is controlled at 5-25% of the spring design deformation, and the mass of the spring is less than 5% of the weight of the spoiler.

[0020] The beneficial effects of the present application are: 1. Enhanced heat exchange, the vibration generated by the spoiler in the heat exchange tube greatly improves the heat transfer efficiency in the tube, and the strengthening effect is increased by 50-200% (here, the strengthening value is compared, the heat transfer coefficient in the twisted tube is increased by 30% compared with the smooth tube, the present application is increased by 90%, so the strengthening effect is increased by 200%). The heat transfer coefficient in the tube is increased by 100-450% compared with the smooth tube, which is particularly obvious for low Reynolds number conditions.

[0021] 2. Low cost, the present application utilizes turbulent flow velocity fluctuation and appropriate vibration design, relies on medium excitation vibration and provides energy to maintain vibration, without additional energy source, without electric or internal combustion engine vibration generating device to provide vibration. At the same time, the present application uses spring as the flexible part required for vibration generation, and the cost of spring as a standard part commonly used in industry is much lower than that of special material required for flexible spoiler.

[0022] 3. Good applicability, the present application provides adjustable counterweight, independent spring, spoiler and other designs, which can be designed and controlled by adjusting the shape of the resistance block, the weight m of the counterweight, the spring constant k of the spring, and the distance between the resistance block and the outlet of the heat exchange tube in the static state of the spring, to adapt to different configurations of heat exchangers with different media, flow, heat exchange tube diameter, etc.

[0023] 4. Long service life, the present application uses spring as the flexible part required for vibration generation, and limits the vibration to the axial direction through reasonable support design, which is consistent with the compression or lifting direction of the spring design. By reasonably designing the amplitude, the spring compression or stretching stress is controlled below the fatigue limit of the spring material, which theoretically has infinite service life. At the same time, the installation spring side support plate is designed to be detachable, and the spring can be replaced if necessary. On the other hand, the present method includes replaceable bushing design, which can be replaced after wear.

[0024] 5. High reliability, the present application utilizes turbulent flow velocity fluctuation and appropriate vibration design, relies on medium velocity fluctuation to excite vibration and provides energy to maintain vibration, without additional energy source, actuator, control system and redundant components, simple system, not easy to fail. At the same time, there is no need to increase the opening on the surface of the pressure vessel pressure shell for the energy source and control system, which will not bring additional risk points to the pressure vessel.

[0025] The foregoing main scheme and each further selected scheme of the present application can be freely combined to form multiple schemes, which are all the schemes that can be adopted and claimed by the present application; and the present application can also be freely combined between each non-conflicting selected scheme and between and other selected schemes. Those skilled in the art can understand that there are multiple combinations according to the prior art and common knowledge after understanding the schemes of the present application, which are all the technical schemes claimed by the present application, and are not listed here. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 is the structural explosion diagram of the spoiler and heat exchanger of the present application.

[0027] Figure 2 is the structural cross-sectional view of the spoiler and heat exchanger of the present application.

[0028] Figure 3 is the structural schematic diagram of the spoiler support of the present application.

[0029] Figure 4 is the structural schematic diagram of the spoiler of the present application.

[0030] Figure 5 is the structural schematic diagram of the turbulence generator of the present application.

[0031] Figure 6 is the schematic diagram of the spoiler lasting simple harmonic vibration of the present application.

[0032] Figure 7 is the comparison schematic diagram of Nu variation law with Re.

[0033] Figure 8 is the comparison schematic diagram of resistance coefficient f variation law with Re.

[0034] In the figure: 1-pipe side inlet, 2-inlet tube box, 3-tube plate, 3a-inlet tube plate, 3b-outlet tube plate, 4-heat exchange tube, 5-shell side inlet, 6-shell side outlet, 7-shell, 8-outlet tube box, 9-pipe side outlet, 10-spoiler support, 10a-inlet support, 10b-outlet support, 101-supporting plate, 102-bushing, 11-spring, 12-spoiler, 121-rigid support rod, 122-spoiler tooth, 123-resistance sub, 124-counterweight, 13-turbulence generator. DETAILED DESCRIPTION

[0035] The following non-limiting examples are used to illustrate the present application.

[0036] Example 1 Reference Figure 1 and Figure 2 As shown in the figure, a self-vibrating long-life spoiler includes a spoiler support 10, a spring 11 and a spoiler 12.

[0037] The spoiler support 10 is used to support the spoiler 12, so that the spoiler 12 has the ability of axial sliding and axial rotation. The spoiler support 10 includes an inlet support 10a and an outlet support 10b, and the front and rear sections of the rigid support rod 121 of the spoiler 12 are respectively arranged on the inlet support 10a and the outlet support 10b, so as to realize the support of the front and rear of the spoiler 12 and ensure the stability of the spoiler 12. Similarly, the spoiler 12 can also be supported by the structure of the heat exchanger itself.

[0038] Referring to Figure 3 As shown in the figure, the spoiler support 10 includes a support plate 101 and a bushing 102. The support plate 101 is provided with a medium opening and a rod opening, and the medium opening ensures that the medium can flow through the support plate 101, avoiding the influence of the support plate 101 on the medium flow in the heat exchanger tube box. The bushing 102 is arranged in the rod opening, and the rigid support rod 121 is arranged in the bushing 102. The bushing 102 is used to reduce the friction of the sliding of the rigid support rod 121 and avoid the abrasion of the support plate 101. When the temperature is lower than 220 degrees, the bushing 102 is recommended to use Teflon material, and when the temperature is higher than 220 degrees, the bushing 102 is recommended to use low-carbon soft steel.

[0039] Referring to Figure 4 As shown in the figure, the spoiler 12 includes a rigid support rod 121, a spoiler tooth 122, a resistance sub 123 and a counterweight 124. The rigid support rod 121, the spoiler tooth 122 and the resistance sub 123 are preferably an integral structure, and the front and rear sections of the rigid support rod 121 are both smooth rods, which are used to be arranged on the spoiler support 10 to ensure the smoothness of the sliding movement of the spoiler 12.

[0040] The middle section of the rigid support rod 121 is fixedly provided with a plurality of spoiler teeth 122 along the rod direction, and the spoiler teeth 122 protrude from the surface of the rigid support rod 121 to interfere with and hinder the flowing medium, thereby increasing the Reynolds number Re of the medium and enhancing the heat exchange effect. Preferably, the spoiler teeth 122 are ratchet-shaped spoiler teeth, and a plurality of turns of the spoiler teeth 122 are arranged at equal intervals along the rod direction of the rigid support rod 121, each turn is arranged at equal intervals along the circumferential direction of the rigid support rod 121 (for example, three), and the spoiler teeth 122 of adjacent two turns are staggered with each other to improve the spoiler effect.

[0041] The middle and rear section of the rigid support rod 121 is provided with a resistance sub 123, and the resistance sub 123 protrudes from the surface of the rigid support rod 121 and is opposite to the outlet of the heat exchange tube 4. Therefore, the resistance sub 123 is impacted by the medium discharged from the heat exchange tube 4, and the whole rigid support rod 121 is pushed to move backward. The resistance sub 123 is a conical structure with a tapered surface facing forward, has a smooth transition surface, and the conical structure of the resistance sub 123 is helpful to control the overall pressure drop and spring mass of the device.

[0042] The rear section of the rigid support rod 121 is provided with a detachable counterweight 124, which is used to adjust the overall weight of the spoiler 12 and the overall vibration frequency and amplitude of the spoiler 12. Preferably, the counterweight 124 is connected to the tail of the rigid support rod 121 in a threaded form.

[0043] Referring to Figure 6 As shown, the spring 11 is arranged at the rear side of the resistance sub 123, preferably the spring 11 is installed between and fixed to the resistance sub 123 and the outlet support 10b, and the rear section of the spoiler 12 passes through the spring 11 for fixation. When the rigid support rod 121 moves rearward, the spring 11 is compressed, and at the same time, the resistance sub 123 driven by the rearward movement of the rigid support rod 121 reduces the blocking area of the outlet of the heat exchange tube 4, so the impact of the medium on the resistance sub 123 is weakened. Therefore, when moving rearward to a certain limit position, the rigid support rod 121 moves forward again under the action of the spring 11, thereby forming continuous simple harmonic vibration of the spoiler 12. The spoiler 12 forms periodic disturbance in the heat exchange tube 4, improves the heat transfer efficiency of the heat exchanger, and effectively inhibits the deposition of scale in the heat exchange tube 4, thereby improving the heat transfer stability under long-term operation.

[0044] Embodiment 2 Referring to Figures 1 to 6 As shown, a heat exchanger includes a tube side inlet 1, an inlet tube box 2, a tube plate 3 (an inlet tube plate 3a and an outlet tube plate 3b), a heat exchange tube 4, a shell side inlet 5, a shell side outlet 6, a shell 7, an outlet tube box 8, and a tube side outlet 9, which is a typical shell-and-tube heat exchanger, and further includes the self-vibrating long-life spoiler of embodiment 1. Figure 1 and Figure 2 The heat exchanger structure in the figure is a BEM type heat exchanger defined in GB\T151, which is only used as a heat exchanger schematic, but the application is not limited to this type of heat exchanger.

[0045] The tube side medium flows into the tube side of the heat exchanger from the tube side inlet 1, passes through the inlet tube box 2, the inlet tube plate 3a, the heat exchange tube 4, the outlet tube plate 3b, and the outlet tube box 8, and then flows out from the tube side outlet 9. The shell side medium flows into the heat exchanger from the shell side inlet 5, passes through the shell side space between the shell 7 and the heat exchange tube 4, and then flows out from the shell side outlet 6. In practice, baffles or support plates are usually arranged in the shell side space to provide support for the heat exchange tube and to enhance heat transfer.

[0046] The front section of the rigid support rod 121 is located in the inlet tube box 2 and passes through the inlet support part, and the rear section of the rigid support rod 121 is located in the outlet tube box 8 and passes through the outlet support part. Preferably, the inlet support 10a is arranged in the inlet tube box 2 and serves as the inlet support part, and the outlet support 10b is arranged in the outlet tube box 8 and serves as the outlet support part. The inlet support 10a is fixed to the inlet tube box 2, and the outlet support 10b is fixed to the outlet tube box 8 in a detachable form (screws or reserved cutting and welding material allowance).

[0047] The middle section of the rigid support rod 121 is arranged in the inlet tube plate 3a, the heat exchange tube 4 and the outlet tube plate 3b. The spoiler 12 is a rod-shaped structure and is arranged in the heat exchange tube 4. The two end straight sections of the spoiler 12 extend out of the heat exchange tube 4 and pass through the openings of the spoiler support 10 respectively. The two end straight sections of the spoiler 12 and the openings of the spoiler support 10 are in clearance fit. The spoiler support 10 allows the spoiler 12 to slide along the axial direction and rotate around the axial direction and restricts other four degrees of freedom. The number of the rigid support rods 121 corresponds to the number of the heat exchange tubes 4.

[0048] The resistance sub 123 is opposite to the outlet of the heat exchange tube 4. The spring 11 is located between the resistance sub 123 and the outlet support, i.e. the outlet support 10b. Then the resistance sub 123 is impacted by the medium discharged from the heat exchange tube 4. The spring 11 is compressed and stretched during the axial movement of the spoiler 12.

[0049] Reference Figure 6 As shown in the figure, the resistance sub 123, the spring 11 and the counterweight 124 work together. When the spring 11 is stretched, the position of the spoiler 12 is close to the side of the inlet tube box 2. At this time, the resistance sub 123 is close to the outlet of the heat exchange tube 4. The gap between the resistance sub 123 and the outlet of the heat exchange tube 4 is small. The resistance sub 123 is impacted by the medium discharged from the heat exchange tube 4, and a large thrust is generated. The spoiler 12 is pushed to the side of the outlet tube box and the spring 11 is compressed. With the movement of the spoiler 12 to the outlet side, the resistance sub 123 is away from the outlet of the heat exchange tube 4. The gap between the resistance sub 123 and the outlet of the heat exchange tube 4 is increased. The impact force of the medium discharged from the heat exchange tube 4 is reduced. At the same time, the spring compression makes the spring force increase. When the spring force and the thrust generated by the medium impacting the resistance sub 123 are balanced, the speed of the spoiler 12 is not zero. Under the action of inertia (adjusted by the counterweight 124), the spoiler 12 continues to move to the outlet side until the speed potential energy is reduced to 0 and stops.

[0050] At this time, the spring 11 is further compressed, and the spring force is much larger than the thrust generated by the medium impacting the resistance sub 123. The spoiler 12 is pushed to the side of the inlet tube box 2. With the movement of the spoiler 12 to the inlet side, the resistance sub 123 is close to the outlet of the heat exchange tube 4. The gap between the resistance sub 123 and the outlet of the heat exchange tube 4 is reduced. The thrust generated by the impact of the medium discharged from the heat exchange tube 4 is increased. At the same time, the spring compression amount is reduced, and the spring force is reduced. When the spring force and the thrust generated by the medium impacting the resistance sub 123 are balanced, the speed of the spoiler 12 is not zero. Under the action of inertia (adjusted by the counterweight 124), the spoiler 12 continues to move to the inlet side until the speed potential energy is reduced to 0 and stops. At this time, the spring has passed the static position, and a pull-up is generated. The spring force and the thrust generated by the medium impacting the resistance sub 123 are in the same direction. The spoiler 12 will move to the outlet side and re-enter the above-mentioned axial reciprocating motion cycle of the spoiler 12. Finally, a continuous simple harmonic vibration is formed.

[0051] The turbulence teeth 122 vibrate along the axial direction in the heat exchange tube with the turbulence member 12, greatly strengthening the heat and mass transfer in the heat exchange tube and improving the anti-fouling performance. At the same time, since the turbulence member support 10 does not limit the rotation of the turbulence member 12 around the axial direction, the turbulence teeth 122 are affected by the turbulence in the tube, driving the turbulence member 12 to form random free rotation, further promoting the heat and mass transfer in the heat exchange tube and improving the anti-fouling performance.

[0052] The vibration of the turbulence member 12 is excited by the speed fluctuation of the turbulence in the fluid flowing out of the heat exchange tube 4, and due to the viscosity of the medium, the vibration energy is dissipated, which is manifested as damping. When the turbulence intensity in the tube is limited, there may be no continuous speed fluctuation to excite vibration, resulting in the turbulence member being stationary. Therefore, for the working condition where the Reynolds number Re of the tube flow is less than 5000, in order to solve the problem that the speed fluctuation of the medium flow may not be sufficient to continuously excite vibration, as shown in FIG. 8, a toothed turbulence generator 13 needs to be arranged at the outlet of the heat exchange tube 4 to excite more intense turbulence speed fluctuation to ensure that it excites the vibration of the turbulence member. For the working condition where the Reynolds number is greater than 5000, the flow is already in the fully developed turbulence range, and with the vibration of the turbulence member, the turbulence speed fluctuation is sufficient to excite the vibration of the turbulence member, and there is no need to arrange a turbulence generator. Figure 5

[0053] Embodiment 3 A design adjustment method for the self-vibrating long-life turbulence sub of embodiment 1. The weight of the counterweight 124 is m , the spring constant of the spring 11 is k , the distance between the resistance sub 123 and the outlet of the heat exchange tube 4 in the resting state of the spring 11 is t , and the position of the resistance sub 123 in the resting state of the spring 11 is x = 0, pointing to the outlet direction is positive. The amplitude and frequency of the vibration can be controlled by changing the shape of the resistance sub 123, the weight of the counterweight 124, the spring constant of the spring 11, and the distance between the resistance sub 123 and the outlet of the heat exchange tube 4 in the resting state of the spring 11. m k t , thereby adjusting the heat transfer enhancement performance and adapting to heat exchangers of different structures.

[0054] Under given working conditions, the flow rate is constant, the flow area between the outlet of the heat exchange tube 4 and the resistance sub 123 is proportional to the distance between them, so the flow rate through the gap is inversely proportional to the distance between them. At the same time, referring to the resistance formula, the thrust (resistance) generated by the medium flowing out of the heat exchange tube 4 impacting the resistance sub 123 is inversely proportional to the square of the distance between the outlet of the heat exchange tube 4 and the resistance sub 123. Therefore, the resistance is approximately (1); wherein the constant C ​​​Experimental calibration or numerical simulation calibration is required based on the dynamometer shape and the flow state of the medium. According to Hooke's law, the spring force is: (2); Based on this, the state-space representation of the dynamic equation of the turbulence-disrupting element 12 vibrating axially within the heat exchange tube 4 is as follows: (3); in, y For displacement, v For speed, a For acceleration; solve equation (3) numerically to obtain the displacement, velocity and acceleration state at the corresponding time, and analyze the vibration frequency and amplitude of the turbulence component 12 under this combination, and complete the design adjustment of the application based on the vibration frequency and amplitude.

[0055] To ensure long-term operation of the present invention, the amplitude of the spoiler 12 is controlled within 5%-25% of the design deformation of the spring 11, and the mass of the spring 11 is less than 5% of the weight of the spoiler 12.

[0056] Case 1 This case study describes a preheater in a steam generation system. The shell-side medium is molten salt, and the tube-side medium is water. The equipment has a diameter of 900 mm, with heat exchange tubes 1.5 m long, 16 mm outer diameter, and 14 mm inner diameter. A triangular tube arrangement is used with a 25 mm cross-section, comprising 1080 heat exchange tubes. Spring-loaded baffles are arranged on the shell side with a 15% window ratio and a center-to-center distance of 300 mm. The design operating conditions are: molten salt inlet temperature 347.2°C, outlet temperature 302.5°C; water inlet temperature 250°C, outlet temperature 300°C; tube-side pressure 15 MPa; shell-side pressure 0.6 MPa; 100% operating conditions: tube-side water flow rate 12.5 kg / s; shell-side molten salt flow rate 47 kg / s; heat load 3.15 MW. Without this application, the actual tube-side water outlet temperature is 296°C, the shell-side molten salt temperature is 306°C, and the heat load is only 2.9 MW. Calculations show that the heat exchanger has an area margin of -15%, which means it cannot meet the performance targets.

[0057] In this application, the spoiler 12 weighs 6.5 kg, the counterweight weighs 1 kg, and the spring... k Value 400 N / mm. The diameter d of the rigid support rod 121 of the spoiler 12. r It is 0.36 times the inner diameter of the heat exchange tube. The rudder is a 45-degree tapered shape, and the outer diameter of the tapered bottom is the diameter d of the turbulence support rod. r Four times that of the spring, with the distance from the junction of the spring-loaded resistance cone and the support rod to the heat exchange tube outlet being 10mm. Under this configuration, the constant required for resistance calculation is approximately... C=5.3. Meanwhile, the spiny disturbance section in the disturbance member 12 is made by welding a square steel section with a support rod, and the square steel section has a size of 1.5 mm*3 mm. After forming, the outer diameter of the square steel section is 0.9 times the inner diameter of the heat exchange pipe, so as to ensure that the square steel section does not contact the inner wall of the heat exchange pipe. The square steel sections are arranged in groups of three and are uniformly distributed in the vertical axis plane, and are arranged with a spacing of two times the diameter of the support rod. The square steel sections in each group are rotated by 60 degrees, so as to form a spiny disturbance structure. In this case, the Reynolds number Re in the pipe is 11185, which is in the turbulent flow range, and the tooth-shaped turbulent flow generator is not needed. In this case, the medium flow excites a vibration with a frequency of 1.2 Hz, and the axial amplitude is 6 mm. The disturbance member is made of Q235R carbon steel, and the support plate bushing is made of 20 soft steel.

[0058] After the application of the present application, the temperature of the side water outlet is 303 degrees, the temperature of the shell side molten salt is 302 degrees, and the heat load is 3.3 mw. According to the calculation, compared with the actual working condition, the area margin of the heat exchanger after the application of the present application is about 10%. The total heat exchange coefficient of the heat exchanger is increased by 28.5%, and the heat transfer coefficient in the pipe is increased by 120%.

[0059] Case 2 The heat exchange pipe is 200 mm long and has an inner diameter of 14 mm, and the medium is normal temperature water. In the application of the present application in this case, the weight of the disturbance member 12 is 0.6 kg, the counterweight mass is 1.5 kg, the spring k value is 400 N / mm. The diameter d r of the support rod of the disturbance member is 0.36 times the inner diameter of the heat exchange pipe, the resistance sub is a 60-degree cone, the outer diameter of the cone bottom is 4 times the diameter d r of the support rod of the disturbance member, and the distance from the intersection position of the cone surface of the resistance sub in the static state of the spring and the support rod to the outlet of the heat exchange pipe is 10 mm. In this configuration, the constant C required for resistance calculation is about 3.7. The disturbance member is made of pps-cf material by additive manufacturing (after forming, polishing is performed, and the contact section with the support plate bushing 102 is polished), and the support plate bushing is made of Teflon material. The structure of the spiny disturbance section is the same as that in case 1. The Reynolds number Re is tested from 500 to 30000 by changing the medium flow rate, and the test is compared with the smooth pipe. In this case, the tooth-shaped turbulent flow generator is set in the laminar flow condition with the Reynolds number Re=2500, and the tooth-shaped turbulent flow generator is not set in the other conditions. In this case, the vibration frequency of the disturbance member is about 2.1 Hz, and the axial amplitude is between 4 mm and 8 mm.

[0060] Figure 7 is a comparison diagram of the Nu variation law with Re. The Nu of the present application is obviously higher than that of the smooth pipe under the same working condition, and the enhancement is more than 350% under the Re=2500 condition. Compared with the smooth pipe, the Nu is increased by 88%-373%, and the heat transfer enhancement effect of the present application is outstanding.

[0061] Figure 8is a schematic diagram of the resistance coefficient f variation law comparison, the resistance of the application is obviously higher than that of the same working condition light pipe. Because the Reynolds number Re=2500 of the laminar flow condition is set to the tooth-shaped turbulent flow generator, the flow resistance is generated, and under this condition, the resistance coefficient is about 4.5 times that of the light pipe, and the resistance coefficient f of the application is 205%-350% higher than that of the light pipe.

[0062] The foregoing basic examples and each further selected example of the application can be freely combined to form a plurality of embodiments, all of which are embodiments that can be used and claimed by the application. In the application scheme, each selected example can be arbitrarily combined with any basic example and selected example.

[0063] The above only describes the preferred embodiments of the application and does not limit the application. Any modification, equivalent replacement and improvement made within the spirit and principle of the application shall be included in the protection scope of the application.

Claims

1. A self-oscillating long-life spoiler comprising a spoiler element (12), characterized in that: The spoiler (12) comprises a rigid support rod (121), the front section and the rear section of the rigid support rod (121) are light rods, the middle section of the rigid support rod (121) is provided with a plurality of spoiler teeth (122) along the rod, and the rear middle section of the rigid support rod (121) is provided with a resistance sub (123); and the spoiler (12) further comprises a spring (11) arranged at the rear side of the resistance sub (123).

2. The self-oscillating long-life spoiler of claim 1, wherein: The spoiler (12) further comprises a spoiler support (10), the spoiler support (10) comprises an inlet support (10a) and an outlet support (10b), the front section and the rear section of the rigid support rod (121) are arranged on the inlet support (10a) and the outlet support (10b) respectively, and the spring (11) is arranged between the resistance sub (123) and the outlet support (10b).

3. The self-oscillating long-life spoiler of claim 2, wherein: The spoiler support (10) comprises a support plate (101) and a bushing (102), the support plate (101) is provided with a medium opening and a rod opening, the bushing (102) is arranged in the rod opening, and the rigid support rod (121) is arranged in the bushing (102).

4. The self-oscillating long-life spoiler according to any one of claims 1 to 3, characterized in that: The spoiler teeth (122) are in the form of ratchet-shaped spoiler teeth, and the resistance sub (123) is in the form of a conical structure with a tapered surface facing forward.

5. The self-oscillating long-life spoiler according to any one of claims 1 to 3, characterized in that: The rear section of the rigid support rod (121) is provided with a detachable counterweight (124).

6. A heat exchanger comprising an inlet tube sheet (2), an inlet tube plate (3a), heat exchange tubes (4), an outlet tube plate (3b) and an outlet tube sheet (8), characterized in that: The self-vibrating long-service-life spoiler comprises the self-vibrating long-service-life spoiler according to any one of claims 1-5, the front section of the rigid support rod (121) is arranged in the inlet pipe box (2) and arranged on the inlet support part, the middle section of the rigid support rod (121) is arranged in the inlet pipe plate (3a), the heat exchange pipe (4) and the outlet pipe plate (3b), the resistance sub (123) is opposite to the outlet of the heat exchange pipe (4), the rear section of the rigid support rod (121) is arranged in the outlet pipe box (8) and arranged on the outlet support part, and the spring (11) is arranged between the resistance sub (123) and the outlet support part.

7. The heat exchanger of claim 6, wherein: The self-vibrating long-service-life spoiler comprises the self-vibrating long-service-life spoiler according to claim 2, the inlet support (10a) is arranged on the inlet pipe box (2) and serves as the inlet support part, and the outlet support (10b) is arranged on the outlet pipe box (8) and serves as the outlet support part.

8. The heat exchanger of claim 6, wherein: The outlet of the heat exchange pipe (4) is provided with a turbulence generator (13).

9. A design adjustment method characterized by comprising: The self-vibrating long-service-life spoiler according to claim 5: weight of the counterweight (124) m spring constant of the spring (11) k distance between the resistance sub (123) and the outlet of the heat exchange tube (4) in the static state of the spring (11) t position of the resistance sub (123) in the static state of the spring (11) x = 0, positive in the outlet direction The resistance is approximately: （1）； wherein the constant C Need to be calibrated according to the resistance sub-morphology and medium flow state or numerical simulation calibration; The spring force is: （2）； The state space representation form of the dynamic equation of the spoiler (12) vibrating in the axial direction of the heat exchange pipe (4) is: （3）； wherein, y is the displacement amount, v is the velocity, a is the acceleration; The numerical solution of equation (3) is obtained to obtain the displacement, velocity and acceleration states corresponding to the time, and the vibration frequency and amplitude of the spoiler (12) are analyzed under the combination, and the design adjustment of the application is completed according to the vibration frequency and amplitude.

10. The design adjustment method of claim 9, wherein: The amplitude of the spoiler (12) is controlled to be 5%-25% of the design deformation amount of the spring (11), and the mass of the spring (11) is less than 5% of the weight of the spoiler (12).

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