A rapid temperature change test chamber with a surrounding air duct

Abstract

This invention relates to the field of temperature change experimental equipment technology, specifically a rapid temperature change experimental chamber with a surrounding air duct. It includes an inner chamber with guide tubes at each of the four corners. Each guide tube has an air inlet at its lower end and a guide cavity within it. The cross-sectional area of ​​the guide cavity gradually decreases vertically. An air outlet communicating with the guide cavity is opened on the outer wall of the guide tube. The air outlet is tangential to the inner wall of the guide cavity, and the air outlet's ejection direction is set at an angle of 5° to 15° to the side wall of the inner chamber, with the outlet facing an adjacent guide tube on one side. This invention, by setting gradually narrowing guide cavities at the four corners of the inner chamber in conjunction with a self-rotating oscillator assembly, can cut the airflow into pulsating high-speed airflow without additional power. Combined with the tangential air outlet design, it directly forms a three-dimensional vortex field surrounding the loading area inside the inner chamber, eliminating the temperature shielding dead zones of traditional unidirectional flow and improving the temperature uniformity of various areas within the experimental chamber.

Description

Technical Field

[0001] This invention relates to the field of temperature change test chamber technology, specifically a rapid temperature change test chamber with a surrounding air duct. Background Technology

[0002] In temperature change experiments on copper-clad ceramic plates, the industry-standard rapid temperature change test chambers generally adopt an air circulation mode of "rear fan + rear air outlet". The airflow is processed by the heat exchanger at the back of the chamber, then blown into the working chamber in a horizontal or vertical unidirectional flow through the outlet, and then drawn back through the bottom return air vent. To improve the temperature change rate, existing technologies often use methods such as increasing the power of the centrifugal fan or installing grille guide vanes at the outlet to attempt to enhance the airflow penetration and distribution uniformity.

[0003] However, during temperature change experiments, copper-clad ceramic plates are typically stacked in a matrix arrangement. The unidirectional airflow is easily blocked by the front racks and plates, resulting in a significant "wind-affected zone" and dead airflow in the rear area. This leads to excessively large local temperature gradients within the chamber, failing to meet the spatial consistency required for rapid temperature changes. Furthermore, the existing unidirectional airflow pattern means that the airflow can only exchange heat intensely with one side or a local edge of the plate. During rapid heating and cooling, instantaneous temperature differences occur between the front and back of the ceramic plate, as well as between the edges and the center. This asymmetrical thermal shock easily causes abnormal warping, delamination, or even microcracks in the ceramic substrate, severely interfering with the accuracy of the experimental results. Although the airflow direction can be adjusted manually via a grille, the grille position is fixed. Without complex electronic control algorithms, it is impossible to achieve dynamic "wrapping" and circling of the airflow around the storage space solely through mechanical structures. When facing experimental requirements with different loading rates, the existing airflow structure struggles to balance wind speed stability and efficient heat exchange.

[0004] Therefore, there is an urgent need for an experimental chamber structure with a surrounding air duct that can use the optimization of the mechanical structure to change the airflow path and achieve all-round uniform flushing of the copper-clad ceramic plate, so as to meet the strict requirements of high-quality electronic ceramic components for simulating complex thermal environments. Summary of the Invention

[0005] The purpose of this invention is to provide a rapid temperature change test chamber with a surrounding air duct to solve the problems mentioned in the background art, such as uneven flow field distribution in traditional unidirectional air supply structures, which easily generate additional stress leading to distorted test results, and the existence of heat exchange dead zones in dense sample arrays, affecting the consistency of experiments on samples of the same batch.

[0006] To achieve the above objectives, the present invention provides the following technical solution: A rapid temperature change test chamber with a surrounding air duct includes an inner liner. Each of the four corners of the inner liner has a guide pipe, and the lower end of each guide pipe has an air inlet. A guide cavity is located within each guide pipe, with the cross-sectional area of ​​the guide cavity gradually decreasing vertically. An air outlet communicating with the guide cavity is opened on the outer wall of each guide pipe. The air outlet is tangent to the inner wall of the guide cavity, and the ejection direction of the air outlet is set at an angle of 5° to 15° to the side wall of the inner liner. The air outlet faces an adjacent guide pipe on one side. A return air inlet is located at the center of the bottom of the inner liner. A self-rotating sub-assembly is rotatably mounted inside the guide pipe. The self-rotating sub-assembly includes a rotating main shaft and multiple self-driving blades fixed on the rotating main shaft. The multiple self-driving blades are all located within the guide cavity and are arranged spirally along the central axis of the rotating main shaft.

[0007] By installing guide pipes with gradually narrowing guide cavities at the four corners of the inner liner, during the operation of the experimental chamber, the airflow generated by the circulating fan enters the guide cavity through the air inlet. As the cross-sectional area of ​​the guide cavity gradually decreases in the vertical direction, the airflow is physically compressed and accelerated inside the cavity, thereby achieving mechanical pressurization of the airflow and significantly increasing the initial velocity of the outlet air. In this process, the high-speed airflow impacts the spirally arranged self-driving blades, driving the spinning rotor assembly to generate high-frequency spin without external power, cutting the continuous airflow beam into high-speed airflow with pulse characteristics.

[0008] Furthermore, the airflow is ejected from the outlets on the sidewalls of the guide tubes. Since the outlets are tangential to the inner wall of the guide cavity, and the ejection direction maintains a specific angle of 5°–15° with the inner wall, the pulsating airflow from the four sets of guide tubes creates a tangential thrust between the inner wall and the loading area. This effectively avoids kinetic energy loss caused by direct wall-flow or direct center collision, causing the four airflows to interfere and superimpose within the inner space, ultimately synthesizing a three-dimensional vortex field rotating around the loading area. This achieves all-around thermal encapsulation of the copper-clad ceramic plate, effectively solving the shielding dead zone problem in traditional unidirectional flow structures.

[0009] Furthermore, compared to traditional vertical or horizontal airflow modes, the swirling vortex field of this invention, combined with the pulsating effect generated by the spiral blades, produces stronger turbulent disturbances, forcefully stripping the air boundary layer from the surface of the copper-clad ceramic plate, and greatly improving instantaneous heat exchange efficiency. Even under harsh conditions of rapid heating and cooling, the dynamic balance of the vortex field ensures a high degree of temperature uniformity between the center and edge areas of the inner liner, effectively preventing warping or delamination damage to the copper-clad ceramic plate caused by uneven heating, and significantly improving the reliability and accuracy of the experiment.

[0010] Preferably, the self-driving blades are set at an angle of 15° to 45° with the center line of the rotating main shaft, the pitch of the multiple self-driving blades is equal, the rotating main shaft and the inner wall of the guide tube form a guide cavity, and the rotating main shaft is a frustoconical shape with the large end facing up.

[0011] By setting the centerline of the self-driving blades and the rotating main shaft within an angle range of 15° to 45°, it is possible to ensure that the conversion efficiency of dynamic pressure into rotational tangential force when the airflow impacts the blades is balanced. Within this angle range, the airflow can not only overcome the rotor's own rotational inertia to achieve rapid start-up, but also avoid exhaust obstruction caused by excessive angle. Combined with the design of equal pitch, the mechanical cutting force experienced by the airflow when passing through multiple sets of blades has a high degree of consistency, thereby ensuring that the frequency and intensity distribution of the ejected air bullets are uniform and avoiding instantaneous pulsation instability of the flow field.

[0012] Furthermore, the rotating main shaft is designed as a frustum-shaped cone with the large end facing upwards, and together with the inner wall of the guide tube, it forms a guide cavity. As the airflow moves downwards, the radial space of the guide cavity changes in a stepwise manner due to the gradual reduction in the diameter of the central main shaft. This, combined with the overall tapering structure of the guide tube, creates an acceleration, causing the airflow to move closer to the center of the rotating main shaft and be further compressed while being cut by the blades, significantly enhancing the axial penetration force of the airflow.

[0013] Furthermore, the truncated cone-shaped main shaft with the larger end facing upwards utilizes the contraction effect in fluid mechanics to generate local negative pressure gain as airflow passes through the blade area, resulting in better self-centering stability of the rotor at high speeds. Compared to a constant-diameter main shaft, the truncated cone-shaped main shaft can guide airflow more smoothly across the blade surface, reducing airflow retention and energy loss at the blade root, thereby ensuring that the pulsating vortex ejected from the outlet has higher kinetic energy and stability.

[0014] Preferably, a flow-rectifying grille is provided at the air inlet at the lower end of the flow guide pipe, and the flow-rectifying grille has multiple through holes that penetrate the upper and lower sides, and the multiple through holes are honeycomb-shaped.

[0015] By setting a flow-rectifying grid with honeycomb-shaped through holes at the air inlet of the guide tube, the original turbulent airflow before entering the guide cavity can be physically constrained and directionally guided. The multiple through holes of the honeycomb structure form a set of tiny guide channels. When the airflow passes through, its non-axial component force is blocked and trimmed by the hole walls, thereby transforming the chaotic vortex into a parallel straight beam of airflow. This provides a stable fluid basis for the physical pressurization of the subsequent airflow in the converging guide cavity, ensuring that the airflow energy can act stably on the self-driving blades and avoiding rotor speed fluctuations caused by airflow turbulence.

[0016] Furthermore, the honeycomb structure maximizes the effective opening ratio of the grille while ensuring the rectification effect, reducing the local resistance loss when the airflow passes through the air inlet. Compared with the traditional grid or round hole structure, the honeycomb through hole can achieve the highest rectification stiffness at the lowest power consumption cost, allowing more of the kinetic energy of the circulating fan to be transferred to the inside of the guide cavity, ensuring the rigidity and impact force of the airflow ejected from the end air outlet.

[0017] Furthermore, the honeycomb-shaped rectifier grille not only stabilizes the flow field but also effectively filters large-scale pulsating noise in the circulating airflow. When the airflow impacts the spirally arranged self-driving blades in a parallel straight beam, the impact load on the blades is more uniform, reducing the mechanical vibration and noise that the self-rotating rotor may generate at high speed from the source.

[0018] Preferably, the outer wall of the guide tube is hinged with a guide vane, which is located between the air outlet and the inner wall of the inner liner. An adjustment plate is hinged to the upper side of the end of the guide vane away from the guide tube, and the other end of the adjustment plate is hinged to the guide tube. The adjustment plate includes a first plate and a second plate, which are fixedly connected. The first plate is hinged to the guide vane, and the second plate is hinged to the guide tube. Both the first plate and the second plate are made of shape memory metal material. The first plate shrinks when heated, and the second plate expands when heated.

[0019] By setting guide vanes driven by shape memory metal adjustment plates at the air outlet, the air outlet angle is dynamically and adaptively adjusted according to the temperature change inside the chamber. The guide vanes can adjust their deflection angle relative to the air outlet according to the real-time ambient temperature through the deformation combination of the first and second vanes. When the temperature inside the chamber rises, the first vane heats up and contracts, while the second vane heats up and extends. The two work together to drive the guide vanes to swing outward or inward, thereby dynamically changing the tangential component of the airflow ejected from the air outlet. This effectively solves the nonlinear difference in wind speed and air volume requirements of the copper-clad ceramic plate under different temperature gradients, ensuring the consistency of the flow field throughout the entire temperature range.

[0020] Furthermore, by utilizing the temperature-sensing properties of shape memory metal as a power source, the adjustment process of the air guide vanes is entirely based on physical temperature change response, eliminating the need for additional electric drive devices or complex electronic control sensors. This improves the reliability of the internal mechanism of the experimental chamber under extreme high and low temperature alternating environments, avoids the risk of conventional electronic actuators failing at high temperatures or freezing at low temperatures, and ensures the accuracy and durability of airflow regulation.

[0021] Furthermore, the linkage structure of the guide vanes and the regulating vanes allows for subtle dynamic disturbances in the flow area and jet angle between the air outlet and the inner wall of the liner. Compared to a guide structure with a fixed angle, the slight deformation of the shape memory metal introduces dynamic compensation for the surrounding vortex field inside the liner during rapid heating and cooling. This allows for real-time optimization of the airflow scouring force and enveloping path for the different surface characteristics of the copper-clad ceramic plate under high-temperature expansion and low-temperature contraction conditions, thereby achieving higher-dimensional thermal stress balance control and reducing the probability of abnormal failure of experimental samples.

[0022] Preferably, a conical air guide seat is provided above the return air vent, and the conical surface of the conical air guide seat forms an angle of 30° to 60° with the bottom plane of the inner liner.

[0023] By setting a conical air guide above the bottom center return air inlet, the vortex air field rotating and sinking in the inner liner can be precisely guided. The conical surface is at an angle of 30° to 60° with the bottom plane. When the rotating airflow converges from the periphery of the inner liner to the center, the conical surface provides a smooth physical slope, forcibly guiding the airflow from centrifugal motion to convergence at the return air inlet, thereby ensuring that the airflow can smoothly enter the return air inlet and avoiding turbulence and kinetic energy dissipation caused by the airflow directly hitting the bottom plane of the inner liner.

[0024] Preferably, the surfaces of the guide tube, the rotating main shaft, and the self-driving blades are all coated with polytetrafluoroethylene, and the surface roughness is less than Ra0.8.

[0025] By applying a polytetrafluoroethylene (PTFE) coating to the surfaces of core flow components such as the guide tube, rotating main shaft, and self-driving blades, the extremely low coefficient of friction and excellent non-adhesive properties of this material reduce the frictional resistance of the airflow within the guide cavity. Due to the PTFE coating's high chemical stability and hydrophobic and oleophobic properties, it effectively prevents condensation droplets or trace impurities that may be generated during the experiment from dripping or accumulating on the rotating components and the inner walls of the duct, thus ensuring the dynamic balance accuracy of the self-rotating component during long-term operation and avoiding speed reduction or mechanical vibration caused by surface deposits.

[0026] Furthermore, in accordance with the precision process requirement of a surface roughness of less than Ra0.8, the turbulent friction between the airflow and the solid wall is reduced, thereby reducing the mechanical energy consumption during the heat conversion process and further suppressing the air shear noise generated by the spiral blades when rotating at high speed, thus improving the acoustic quality of the experimental chamber during operation.

[0027] Furthermore, the polytetrafluoroethylene coating has a high and low temperature operating range of -190℃ to +250℃. During rapid heating and cooling cycles, the coating can act as a thermal buffer layer between the flow guide tube and the metal substrate, mitigating the instantaneous impact of thermal shock on the mechanical structure and effectively extending the service life of the flow guide assembly.

[0028] Preferably, the inner wall of the inner liner is provided with a plurality of inwardly protruding baffles, and the plurality of baffles on the inner wall of each inner liner are distributed in an alternating matrix between two adjacent guide pipes, and the surface of the baffles is spherical.

[0029] By setting up spherical turbulence heads in an alternating matrix distribution on the inner wall of the liner, when high-speed airflow passes through the side wall area between two adjacent guide tubes, the spherical turbulence heads act as protruding obstacles, forcibly disrupting the linear flow state formed by the airflow on the wall surface, generating multiple tiny local vortices. These micro-vortices can effectively strip away the air boundary layer that is tightly attached to the wall surface, enhancing the airflow activity near the side wall of the liner, thereby further improving the overall space heat exchange efficiency of the liner.

[0030] Furthermore, the turbulence head adopts an interlaced matrix distribution design, which requires the airflow to undergo continuous contraction and expansion path transitions when flowing through this area. The repeated changes in airflow introduce a moderate turbulence component into the flow field, which can generate stronger physical penetration and guide some of the airflow adhering to the wall to deflect towards the center of the inner liner. Combined with the smooth transition of the spherical structure, it can ensure sufficient turbulence intensity without causing a sudden drop in total airflow due to drastic drag changes, thus achieving the correction of the path of the surrounding vortex field.

[0031] Furthermore, compared to the smooth inner wall, the spherical baffle head, through the splitting and reorganization of airflow, pushes the cold / heat that has accumulated near the wall due to centrifugal force more evenly to the loading area, so that the copper-clad ceramic plate is in a highly active and extremely uniform heat exchange environment, which can more realistically simulate the actual extreme thermal shock conditions.

[0032] Preferably, the conical guide seat is provided with a carrier frame, which is in the shape of a hollow grid. During the temperature change experiment, the copper-clad ceramic plate is vertically installed on the carrier frame.

[0033] By setting a perforated grid-shaped carrier on the conical air guide seat, the perforated grid ensures that the airflow can penetrate the carrier area as it is guided from the conical surface of the conical air guide seat to the return air inlet. This not only ensures the continuity of the flow field but also avoids local vortex dead zones caused by the excessive size of the carrier, thereby ensuring the uniformity of energy exchange inside the experimental chamber.

[0034] Furthermore, since the airflow ejected from the four corners merges into a horizontally rotating vortex at the center of the inner liner, the surface normal of the vertically placed ceramic plate forms an efficient scouring angle with the tangential force direction of the rotating vortex. This installation method allows the airflow to penetrate deep into the narrow gap between two adjacent vertical ceramic plates. Combined with the pulsating airflow, it can generate a very strong convective heat transfer effect, significantly improving the instantaneous temperature change rate of the ceramic plate surface.

[0035] Compared with the prior art, the beneficial effects of the present invention are as follows: 1. This invention, by setting tapered guide cavities at the four corners of the inner liner in conjunction with a self-rotating oscillator assembly, can cut the airflow into pulsating high-speed airflow without additional power. Combined with the tangential air outlet design, it directly forms a three-dimensional vortex field surrounding the loading area inside the inner liner, eliminating the temperature shielding dead zone of traditional unidirectional flow, thereby improving the temperature uniformity of various areas in the experimental chamber.

[0036] 2. By setting self-driving blades and a frustum-shaped rotating main shaft, this invention not only ensures the energy conversion efficiency of airflow impacting the rotor, but also improves the stability of rotor operation by utilizing the contraction effect, enhances the axial penetration of the ejected airflow, and ensures the stable and uniform flow field output.

[0037] 3. This invention employs a shape memory metal-driven adaptive airflow guide vane structure, which can automatically adjust the air outlet angle according to the real-time temperature inside the chamber. It can achieve dynamic compensation of the flow field without additional electronic control devices, adapting to the deformation and heat transfer requirements of experimental samples at different temperatures, and improving the reliability of the mechanism's operation under extreme temperature change environments.

[0038] 4. By setting a honeycomb-shaped rectifier grille at the air inlet, the present invention not only completes the sorting and regularization of the incoming airflow, but also minimizes the airflow resistance, while filtering out large-scale pulsating noise, thus ensuring the smooth operation of the spinner from the source and reducing the mechanical vibration and noise of the whole machine. Attached Figure Description

[0039] Figure 1 This is a schematic diagram of the rapid temperature change test chamber of the present invention; Figure 2 This is a schematic diagram of the outer shell of the experimental section in the rapid temperature change experimental chamber of the present invention; Figure 3 This is a schematic diagram of the internal structure of the experimental section in the rapid temperature change test chamber of the present invention; Figure 4 This is a front view of the experimental section in the rapid temperature change test chamber of the present invention; Figure 5 for Figure 4 Full sectional view at point AA; Figure 6 for Figure 4 Full sectional view at point BB; Figure 7 for Figure 4 Full sectional view at point CC; Figure 8 This is a schematic diagram of the flow guide tube in the rapid temperature change test chamber of the present invention; Figure 9 for Figure 8 A magnified view of a section at point D; Figure 10 This is a schematic diagram of the rotating spindle in the rapid temperature change test chamber of the present invention; Figure 11 for Figure 10 A magnified view of a section at point E in the middle.

[0040] In the diagram: 1. Outer shell of the experimental section; 2. Inner liner; 201. Return air inlet; 202. Air inlet; 203. Diverter pipe; 204. Baffle head; 3. Insulation layer; 4. Guide pipe; 401. Guide cavity; 402. Air inlet; 403. Air outlet; 5. Rotating main shaft; 501. Mounting part; 502. Compression part; 6. Self-driving blades; 7. Rectifying grille; 701. Through hole; 8. Guide vane; 9. Adjusting vane; 901. Vane No. 1; 902. Vane No. 2; 10. Conical guide seat; 11. Carrier rack; 12. Top cover; 13. Base; 14. Control module; S1. Air outlet direction; S2. Swirl direction. Detailed Implementation

[0041] Please see Figures 1 to 11 This invention provides a rapid temperature change test chamber with a surrounding air duct, the technical solution of which is as follows: Please refer to a rapid temperature change test chamber with a surrounding air duct. Figures 1 to 11The system includes a base 13, an inner liner 2, and a control module 14. The base 13 is mounted on the ground, the inner liner 2 is located on the upper part of the base 13, and the control module 14 is located on the upper side of the inner liner 2. An experimental section shell 1 is located between the base 13 and the control module 14, and the inner liner 2 is located inside the experimental section shell 1. A heat insulation layer 3 is located between the experimental section shell 1 and the inner liner 2. Each of the four corners of the inner liner 2 is equipped with a guide pipe 4, and the lower end of the guide pipe 4 is equipped with an air inlet 402. A flow rectifier grille 7 is provided at the air inlet 402 at the lower end of the guide pipe 4. The flow rectifier grille 7 has multiple through holes 701 that penetrate the upper and lower sides in a honeycomb pattern. The lower end of the inner liner 2 is equipped with two diversion pipes 203, which are located on the left and right sides respectively. Two diversion pipes 203 are connected to two guide pipes 4 on the left and right sides respectively, and the diversion pipes 203 on the left and right sides are connected to the guide cavities 401 inside the guide pipes 4 on the left and right sides respectively. An air inlet 202 is provided at the middle of the lower end of each diversion pipe 203. A guide cavity 401 is provided inside the guide pipe 4. The cross-sectional area of ​​the guide cavity 401 gradually decreases in the vertical direction. An air outlet 403 is opened on the outer wall of the guide pipe 4, which is connected to the guide cavity 401. The air outlet 403 is tangent to the inner wall of the guide cavity 401, and the spray direction of the air outlet 403 is set at a 6° angle to the side wall of the inner liner 2. The air outlet 403 faces the adjacent guide pipe 4 on one side. A return air inlet 201 is provided at the center of the bottom of the inner liner 2. Above the return air inlet 201 A conical guide seat 10 is provided, with its conical surface forming a 60° angle with the bottom plane of the inner liner 2. A carrier 11 is mounted on the conical guide seat 10, and the carrier 11 is in the form of a perforated grid. During temperature change experiments, the copper-clad ceramic plate is vertically mounted on the carrier 11. A circulating fan (not shown) is installed inside the base 13. The air inlet of the circulating fan is connected to the return air inlet 201, and the air outlet of the circulating fan is connected to the inlet air inlet 202. A heat exchanger (not shown) is installed between the air outlet and the inlet air inlet 202 of the circulating fan. The heat exchanger is used to heat or cool the gas. A self-rotating sub-assembly is rotatably installed inside the guide pipe 4. The self-rotating sub-assembly includes a rotating main shaft 5 and multiple self-driving blades 6 fixed on the rotating main shaft 5. The upper end of the flow tube 4 is provided with an upper end cover 12. The rotating main shaft 5 includes two mounting parts 501 and a compression part 502. The two mounting parts 501 are respectively located at the upper and lower ends of the compression part 502. The upper and lower mounting parts 501 are rotatably connected to the upper end cover 12 and the rectifier grid 7 through bearings. Multiple self-driven blades 6 are all located on the side wall of the compression part 502. Multiple self-driven blades 6 are all located in the guide cavity 401. The multiple self-driven blades 6 are spirally arranged along the central axis of the rotating main shaft 5. The self-driven blades 6 are arranged at an angle of 30° with the center line of the rotating main shaft 5. The pitch of the multiple self-driven blades 6 is equal. The rotating main shaft 5 and the inner wall of the guide tube 4 form the guide cavity 401. The rotating main shaft 5 is a frustum-shaped cone with the large end facing up.

[0042] For further details, please refer to Figure 8 and Figure 9 A guide vane 8 is hinged to the outer wall of the guide pipe 4. The guide vane 8 is located between the air outlet 403 and the inner wall of the inner liner 2. An adjusting plate 9 is hinged to the upper side of the end of the guide vane 8 away from the guide pipe 4. The other end of the adjusting plate 9 is hinged to the guide pipe 4. The adjusting plate 9 includes a first plate 901 and a second plate 902. The first plate 901 and the second plate 902 are fixedly connected. The first plate 901 is hinged to the guide vane 8, and the second plate 902 is hinged to the guide pipe 4. Both the first plate 901 and the second plate 902 are made of shape memory metal. The first plate 901 contracts when heated, and the second plate 902 expands when heated. Please refer to [link to relevant documentation]. Figure 4 and Figure 6 The inner wall of the inner liner 2 is provided with multiple inwardly protruding baffle heads 204. The multiple baffle heads 204 on the inner wall of each inner liner 2 are distributed in an interlaced matrix between two adjacent guide pipes 4, and the surface of the baffle head 204 is spherical.

[0043] It should also be noted that the surfaces of the guide tube 4, the rotating main shaft 5 and the self-driving blade 6 are all coated with polytetrafluoroethylene, and the surface roughness is less than Ra0.8.

[0044] Working principle: Please refer to Figures 1 to 11 After the circulating fan starts, the airflow, which is temperature-controlled by the heat exchanger, enters the diversion pipe 203 from the air inlet 202. The airflow entering the diversion pipe 203 enters the guide cavity 401 from the air inlet 402. The airflow entering the air inlet 402 from the diversion pipe 203 first passes through the honeycomb rectifier grille 7 to complete rectification. After filtering the large-scale airflow pulsation, it flows downward along the guide cavity 401, impacting the spirally distributed self-driving blades 6, which drive the entire self-rotating sub-assembly to rotate freely around the rotating main shaft 5. The rotating blades cut the continuous airflow into periodic pulsating airflow, and at the same time use the spiral lift to transport the airflow upward. As the cross-sectional area of ​​the guide cavity 401 gradually decreases from top to bottom, combined with the squeezing effect of the frustum-shaped rotating main shaft 5, the airflow velocity gradually increases, and finally it is ejected from the tangentially set air outlet 403. The airflow ejected from the air outlet 403 is along the S1 direction.

[0045] After the airflow exits through the outlet 403, it acts on plates 901 and 902. When the temperature inside the inner liner 2 rises, plate 901 contracts and plate 902 extends, together pulling the guide vane 8 to rotate slightly outward, increasing the flow area between the outlet 403 and the side wall of the inner liner 2, and slightly adjusting the airflow angle. When the temperature inside the inner liner 2 decreases, plate 901 extends and plate 902 contracts, causing the guide vane 8 to rotate inward, reducing the flow area and adjusting the airflow angle in the opposite direction. The entire adjustment process is automatically completed by the deformation of the shape memory metal with temperature, without the need for additional material. The electrically driven components can match the flow field requirements of different temperature change stages. The tangentially ejected pulsating airflow flows along the side wall of the inner liner 2. Under the action of the spherical turbulence heads 204 distributed in a staggered manner on the side wall of the inner liner 2, the boundary layer attached to the wall is stripped and the flow field path is corrected. Finally, the airflow ejected from all the air outlets 403 forms a three-dimensional rotating vortex around the shelf 11 along the S2 direction inside the inner liner 2. It evenly washes the copper-clad ceramic plate placed vertically on the shelf 11. After completing the heat exchange, the airflow rotates and sinks to the bottom of the inner liner 2. Under the guidance of the conical guide seat 10, it smoothly merges into the central return air port 201 and re-enters the circulating fan to complete the next cycle of heat exchange.

[0046] The specific embodiment of the present invention has been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the embodiments described above. For those skilled in the art, various changes, modifications, substitutions, and variations made to these embodiments without departing from the principles and ideas of the present invention should still fall within the protection scope of the present invention.

Claims

1. A rapid temperature change test chamber with a surrounding air duct, characterized in that, The device includes an inner liner (2), with guide pipes (4) at each of the four corners. Each guide pipe (4) has an air inlet (402) at its lower end and a guide cavity (401) inside. The cross-sectional area of ​​the guide cavity (401) gradually decreases in the vertical direction. An air outlet (403) communicating with the guide cavity (401) is opened on the outer wall of the guide pipe (4). The air outlet (403) is tangent to the inner wall of the guide cavity (401), and the ejection direction of the air outlet (403) is at a 5° angle to the side wall of the inner liner (2). The air outlet (403) is set at an angle of 100° to 15° and faces the adjacent guide pipe (4) on one side. The bottom center of the inner liner (2) is provided with a return air outlet (201). The guide pipe (4) is rotatably installed with a self-rotating sub-assembly. The self-rotating sub-assembly includes a rotating main shaft (5) and multiple self-driving blades (6) fixed on the rotating main shaft (5). The multiple self-driving blades (6) are all located in the guide cavity (401), and the multiple self-driving blades (6) are spirally arranged along the central axis of the rotating main shaft (5).

2. The rapid temperature change test chamber with a surrounding air duct according to claim 1, characterized in that, The self-driving blade (6) is set at an angle of 15° to 45° with the center line of the rotating main shaft (5). The pitch of the multiple self-driving blades (6) is equal. The rotating main shaft (5) and the inner wall of the guide tube (4) form a guide cavity (401). The rotating main shaft (5) is a frustum-shaped cone with the large end facing up.

3. A rapid temperature change test chamber with a surrounding air duct according to claim 2, characterized in that, A flow-rectifying grille (7) is provided at the air inlet (402) at the lower end of the flow guide pipe (4). The flow-rectifying grille (7) has multiple through holes (701) that pass through both the upper and lower sides. The multiple through holes (701) are honeycomb-shaped.

4. A rapid temperature change test chamber with a surrounding air duct according to claim 1, characterized in that, The outer wall of the guide tube (4) is hinged with a guide vane (8). The guide vane (8) is located between the air outlet (403) and the inner wall of the inner liner (2). An adjustment plate (9) is hinged to the upper side of the end of the guide vane (8) away from the guide tube (4). The other end of the adjustment plate (9) is hinged to the guide tube (4). The adjustment plate (9) includes a first plate (901) and a second plate (902). The first plate (901) and the second plate (902) are fixedly connected. The first plate (901) is hinged to the guide vane (8). The second plate (902) is hinged to the guide tube (4). The first plate (901) and the second plate (902) are both made of shape memory metal. The first plate (901) shrinks when heated, and the second plate (902) elongates when heated.

5. A rapid temperature change test chamber with a surrounding air duct according to claim 1, characterized in that, A conical guide seat (10) is provided above the return air vent (201), and the conical surface of the conical guide seat (10) forms an angle of 30° to 60° with the bottom plane of the inner liner (2).

6. A rapid temperature change test chamber with a surrounding air duct according to claim 1, characterized in that, The surfaces of the guide tube (4), the rotating main shaft (5) and the self-driving blade (6) are all coated with polytetrafluoroethylene, and the surface roughness is less than Ra0.

8.

7. A rapid temperature change test chamber with a surrounding air duct according to claim 1, characterized in that, The inner wall of the inner liner (2) is provided with a plurality of inwardly protruding baffles (204). The plurality of baffles (204) on the inner wall of each inner liner (2) are distributed in an alternating matrix between two adjacent guide pipes (4), and the surface of the baffles (204) is spherical.

8. A rapid temperature change test chamber with a surrounding air duct according to claim 5, characterized in that, The conical flow guide seat (10) is provided with a carrier (11), which is in the shape of a hollow grid. During the temperature change experiment, the copper-clad ceramic plate is vertically installed on the carrier (11).

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