A pre-cooling ejection system

Abstract

The present application relates to the technical field of aviation simulation experiment system, and discloses a pre-cooling ejection system, comprising: a storage tank; a pressure reducer connected with the output end of the storage tank, used for reducing the pressure of the primary flow provided by the storage tank; a heat storage pressure bearing integrated electric heating device connected with the output end of the pressure reducer, used for heating the primary flow output by the cold pressure reducer and outputting as an ejection gas flow for increasing the total temperature; a high-temperature gas negative pressure discharge cooling device used for absorbing the secondary flow generated by the simulation device and performing heat sink pre-cooling, and outputting as an ejection gas for reducing the total temperature; two-stage ejectors connected with the output end of the high-temperature gas negative pressure discharge cooling device, the first branch circuit and the second branch circuit of the heat storage pressure bearing integrated electric heating device, respectively, used for forming a low-pressure environment, and sucking the ejection gas from the high-temperature gas negative pressure discharge cooling device, so that the ejection gas and the ejection gas are mixed and ejected to the atmosphere in multiple stages.

Description

Technical Field

[0001] This invention relates to the field of aviation simulation experimental system technology, and in particular, to a pre-cooling ejector system. Background Technology

[0002] Ejectors are core equipment in ground testing facilities for aerospace applications, widely used in high-altitude engine simulation testing, ground testing of air-breathing propulsion systems, and special thermal energy engineering. Their core function is to create and maintain a low-pressure environment in the channel of the entrained flow (or passive flow) through the entrainment effect of a high-speed active flow (or "ejector flow"), simulating high-altitude or vacuum conditions, or achieving the transport and mixing of specific working fluids. The performance of an ejector is typically measured by its entrainment coefficient (the mass flow rate ratio of the entrained flow to the active flow) and the achievable outlet back pressure.

[0003] To improve ejector performance, the general technical approach in this field focuses on two aspects: first, enhancing the ejector driving potential by increasing the total temperature ratio between the active flow and the passive flow (i.e., increasing the total temperature of the active flow and decreasing the total temperature of the passive flow); and second, optimizing the aerodynamic structure and flow channel design of the ejector to improve energy exchange efficiency and reduce flow losses.

[0004] In terms of technical approaches to improving the total temperature ratio, existing solutions mainly involve pre-cooling the passive flow and heating the active flow. For example, one known implementation uses a plate-fin precooler to cool the passive flow. This precooler consists of multiple heat exchanger units, with cold and hot fluids exchanging heat through the internal plate-fin structure. However, such indirect cooling devices typically suffer from complex structures, demanding manufacturing processes, and significant flow resistance (pressure loss) along the flow path. Furthermore, the ambient temperature active flow used has limitations in driving potential, restricting further improvements in ejector performance. Another known implementation uses a gas generator to produce high-temperature, high-pressure gas as the active flow. While this approach increases the total temperature of the active flow, it relies on the combustion process, leading to issues such as operational stability affected by combustion fluctuations, susceptibility to ablation of high-temperature components, challenges to system safety, complex system integration and control, and high costs.

[0005] In optimizing ejector structures, common solutions include plate-type ejectors and annular ejectors. Plate-type ejectors (such as two-plate and four-plate structures) promote the mixing of the primary and passive flows through the wake region behind the plates, but the plates themselves introduce significant total pressure loss, which may weaken the ejection driving capability. While annular ejectors can maintain a relatively high total pressure to some extent, the contact and mixing efficiency of the primary and passive flows is often unsatisfactory. Both of these basic structural forms struggle to achieve an ideal balance between efficient mixing and maintaining a high total pressure ratio. Furthermore, to achieve higher ejection capabilities, existing technologies employ multi-stage ejector schemes composed of multiple independent nozzles, but these schemes generally suffer from complex system structures, low integration, and high manufacturing and assembly difficulties.

[0006] In summary, existing pre-cooling ejector technologies suffer from the following shortcomings: 1. Systems used to regulate the total working fluid temperature (such as indirect cooling systems and gas heating devices) suffer from complex structures, high pressure losses, poor operational stability and safety, or high costs; 2. Mainstream single-stage ejector structures struggle to balance high mixing efficiency with low total pressure loss; 3. Complex multi-stage ejector systems face challenges such as low integration and complex manufacturing processes. These factors collectively restrict the overall improvement of ejector systems in terms of performance, reliability, and economy. Therefore, a novel pre-cooling ejector system that can effectively overcome these deficiencies is urgently needed. Summary of the Invention

[0007] This invention provides a pre-cooling ejector system that heats the active flow using an integrated heat storage and pressure-bearing electric heating device and pre-cools the passive flow using a high-temperature gas negative pressure exhaust cooling device. It then employs a two-stage high-speed ejector with a "first-stage support plate and second-stage annular" design to achieve efficient ejection. This addresses the technical problems of low total temperature ratio adjustment efficiency, complex structure, and large pressure loss in existing ejector technologies, as well as the difficulty of achieving both high mixing efficiency and high total pressure ratio with a single-stage ejector.

[0008] This invention provides a pre-cooling ejector system, comprising: a storage tank for storing high-pressure ejector gas and providing a primary flow; a pressure reducer connected to the output end of the storage tank for reducing the pressure of the primary flow provided by the storage tank; a heat storage and pressure-bearing integrated electric heating device connected to the output end of the pressure reducer for heating the primary flow output by the pressure reducer and outputting it as an ejector gas stream to increase the total temperature; a high-temperature gas negative pressure emission cooling device for entraining the secondary flow generated by the simulation device and performing heat sink pre-cooling, and outputting it as the ejected gas with reduced total temperature; and a two-stage ejector connected to the output end of the high-temperature gas negative pressure emission cooling device, the first branch of the heat storage and pressure-bearing integrated electric heating device, and the second branch of the heat storage and pressure-bearing integrated electric heating device, respectively, for forming a low-pressure environment and drawing the ejected gas from the high-temperature gas negative pressure emission cooling device, thereby causing the ejected gas and the ejector gas to be mixed and ejected in multiple stages and discharged into the atmosphere.

[0009] Furthermore, the integrated heat storage and pressure bearing electric heating device includes a heat insulation layer, an electric heating layer, a heat storage component, an inlet pipe, an outlet pipe, a first diffusion cone, and a second diffusion cone; the heat insulation layer is the outermost layer, and the electric heating layer is the inner layer of the heat insulation layer, forming an inner heating cavity; the input end of the heat storage component is connected to the large end face of the first diffusion cone, the output end of the heat storage component is connected to the large end face of the second diffusion cone, the output end of the inlet pipe is configured as an air inlet screen, and the air inlet screen of the inlet pipe extends into the inner cavity of the first diffusion cone through the small end of the first diffusion cone, the small end of the second diffusion cone is connected to the outlet pipe, and the inlet pipe, the first diffusion cone, the heat storage component, the second diffusion cone, and the outlet pipe constitute an airflow conveying component; the airflow conveying component is suspended in the inner heating cavity and is arranged without contact with the electric heating layer; the inlet pipe is connected to the output end of the pressure reducer, and the outlet pipe is connected to the first branch and the second branch respectively.

[0010] Furthermore, the heat storage component includes multiple heat storage units; each heat storage unit is a cylindrical structure, and the end face of the cylindrical structure has multiple bidirectional through holes to form a honeycomb structure; the multiple heat storage units are welded together in sequence along the axial direction, and the holes of the multiple heat storage units are arranged in an axially through manner.

[0011] Furthermore, the integrated heat storage and pressure bearing electric heating device includes a first support, a second support, and a third support; the first support is provided at the welding position between two adjacent heat storage units, and the first support is used to support the heat storage component so that the heat storage component is suspended in the inner heating cavity of the electric heating layer; the second support is used to support the first diffusion cone and / or support the connection between the first diffusion cone and the heat storage component so that the input end of the heat storage component is suspended in the inner heating cavity of the electric heating layer; the third support is used to support the second diffusion cone and / or support the connection between the second diffusion cone and the heat storage component so that the output end of the heat storage component is suspended in the inner heating cavity of the electric heating layer.

[0012] Furthermore, the high-temperature gas negative pressure emission cooling device includes an inlet air duct, a cooling body, and a heat dissipation and air cooling component; the input end of the inlet air duct is used to connect to the simulation device, the output end of the inlet air duct is connected to the cooling body, the output end of the cooling body is connected to the two-stage ejector, and the heat dissipation and air cooling component is located on the side of the inlet air duct.

[0013] Furthermore, the intake air passage is in the shape of a cone, and the large end face of the intake air passage is connected to the cooling body; multiple convex rings are arranged on the outer wall of the intake air passage, which are used for reinforcement and cooling; the multiple convex rings are arranged at intervals along the axial direction of the intake air passage.

[0014] Furthermore, the air intake channel is a cone-shaped body, and the heat dissipation and air cooling components include a fan, a bend, and an electric valve. The fan is located at the outer end of the bend, the inner end of the bend is connected to the air intake channel, and the bend is bent towards the cooling body. The electric valve is located on the bend.

[0015] Furthermore, the cooling body includes heat exchange plates and fins, with multiple heat exchange plates arranged in an array, and multiple fins arranged at intervals on each heat exchange plate; the spacing between the heat exchange plates gradually decreases from the input end to the output end of the cooling body.

[0016] Furthermore, the two-stage ejector includes a primary support plate ejector and a secondary annular ejector; the input end of the primary support plate ejector is axially connected to the output end of the high-temperature gas negative pressure emission cooling device, and the input end of the primary support plate ejector is laterally connected to the first branch; the output end of the primary support plate ejector is axially connected to the secondary annular ejector, and the input end of the secondary annular ejector is laterally connected to the second branch.

[0017] Furthermore, the first-stage ejector includes a support ejector section, a square-to-circular flow channel, and a first straight section arranged sequentially from the input end to the output end; the second-stage annular ejector includes an annular ejector section, a contraction section, a second straight section, and a diffuser section arranged sequentially from the input end to the output end, with the diffuser section connected to the atmosphere.

[0018] The present invention has the following beneficial effects: 1. Highly efficient improvement of the total temperature ratio between the active and passive streams, enhancing ejector driving potential energy: The integrated heat storage and pressure-bearing electric heating device heats the primary stream (active stream) non-contactly through external radiation, effectively avoiding direct erosion of the heating element by high-temperature gas. While ensuring the safety and reliability of the heating process, it significantly improves the initial total temperature of the active stream. The high-temperature gas negative pressure exhaust cooling device cools the secondary stream (passive stream) through the heat sink pre-cooling principle, eliminating the need for external cooling media such as liquid nitrogen. This effectively reduces the total temperature of the passive stream, simplifies the system structure, and lowers operating costs. The synergistic effect of heating the active stream and pre-cooling the passive stream, working together through two paths, maximizes the total temperature ratio between the active and passive streams. According to the ejector working principle, a higher total temperature ratio means stronger ejector driving potential energy, thus laying the energy foundation for the entire system to achieve a higher ejection coefficient (i.e., suction capacity).

[0019] 2. Optimize the ejector flow field structure to achieve a balance between mixing efficiency and total pressure recovery: The two-stage ejector adopts a unique structure combining a single-stage support plate type and a two-stage annular type. The single-stage support plate type ejector utilizes the wake region generated by its support plate structure to efficiently promote the initial intense mixing and momentum exchange between the cooled secondary flow and the first-stage heated primary flow. This stage focuses on high mixing efficiency. The pre-mixed airflow then serves as the passive flow for the second-stage ejector, merging again with the second-stage heated primary flow in the second-stage annular ejector. The annular flow channel design effectively reduces flow separation and impact losses, focusing on maintaining a high total pressure. Through this two-stage division of labor and structural coupling design, the system organically combines the advantages of high mixing efficiency of the support plate type ejector with the advantages of high total pressure recovery capability of the annular ejector, overcoming the technical contradiction that a single-structure ejector cannot simultaneously achieve both. This allows the ejection process to achieve deep mixing while maintaining lower flow losses, thereby improving the vacuum level (or back pressure) ultimately achieved by the ejection system.

[0020] 3. Improved system integration, reliability, and economy: The entire system adopts a modular and integrated design approach; the heating device uses an integrated heat storage and pressure bearing structure, and the cooling device uses a heat sink structure without moving parts, thus avoiding the inherent defects of traditional gas heating combustion instability and easy ablation, as well as the complex structure and high flow resistance of traditional indirect cooling systems; the integrated connection of the two-stage ejectors reduces connecting pipelines and potential leakage points compared to multi-stage ejector systems with separate arrangements, improving structural compactness and system reliability; neither heating nor cooling processes require a complex auxiliary medium supply system (such as fuel or large amounts of coolant), reducing the system's manufacturing cost, maintenance complexity, and long-term operating cost.

[0021] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0022] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings: Figure 1 This is a schematic diagram of the pre-cooling ejector system according to a preferred embodiment of the present invention; Figure 2 This is a schematic diagram of the structure of the integrated heat storage and pressure bearing electric heating device according to a preferred embodiment of the present invention; Figure 3 This is a schematic diagram of the structure of a high-temperature gas negative pressure emission cooling device according to a preferred embodiment of the present invention; Figure 4 This is a schematic diagram of the structure of a two-stage ejector according to a preferred embodiment of the present invention.

[0023] Legend: 100. Storage tank; 200. Pressure reducer; 300. Integrated electric heating device for heat storage and pressure bearing; 301. Thermal insulation layer; 302. Electric heating layer; 303. Heat storage component; 3031. Heat storage unit; 304. Inlet pipe; 305. Outlet pipe; 306. First diffuser cone; 307. Second diffuser cone; 308. First branch; 309. Second branch; 310. First support; 311. Second support; 312. Third support; 400. High-temperature gas negative pressure exhaust cooling device; 401. Inlet. Flow channel; 4011, convex ring; 402, cooling body; 4021, heat exchange plate; 4022, fins; 403, heat dissipation and air cooling assembly; 4031, fan; 4032, bend; 4033, electric valve; 500, two-stage ejector; 501, first-stage support plate ejector; 5011, support plate ejector section; 5012, square to round flow channel; 5013, first straight section; 502, second-stage annular ejector; 5021, annular ejector section; 5022, contraction section; 5023, second straight section; 5024, diffuser section. Detailed Implementation

[0024] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0025] like Figure 1As shown, the pre-cooling ejector system of this embodiment includes: a storage tank 100 for storing high-pressure ejector gas and providing a primary flow; a pressure reducer 200 connected to the output end of the storage tank 100 for reducing the pressure of the primary flow provided by the storage tank 100; a heat storage and pressure-bearing integrated electric heating device 300 connected to the output end of the pressure reducer 200 for heating the primary flow output by the pressure reducer and outputting it as an ejector gas stream to increase the total temperature; a high-temperature gas negative pressure emission cooling device 400 for entraining the secondary flow generated by the simulation device and performing heat sink pre-cooling, and outputting it as the ejected gas with reduced total temperature; and two-stage ejectors 500 connected to the output end of the high-temperature gas negative pressure emission cooling device 400, the first branch 308 of the heat storage and pressure-bearing integrated electric heating device 300, and the second branch 309 of the heat storage and pressure-bearing integrated electric heating device 300, respectively, for forming a low-pressure environment and drawing the ejected gas from the high-temperature gas negative pressure emission cooling device 400, thereby causing the ejected gas and the ejector gas to be mixed and ejected in multiple stages and discharged into the atmosphere. This invention relates to a pre-cooling ejector system, comprising a heat storage and pressure-bearing integrated electric heating device 300. This device uses external radiation to heat the primary flow (active flow) non-contactly, effectively preventing direct erosion of the heating element by high-temperature gas. While ensuring a safe and reliable heating process, it significantly increases the initial total temperature of the active flow. A high-temperature gas negative pressure exhaust cooling device 400 cools the secondary flow (passive flow) through a heat sink pre-cooling principle, eliminating the need for external cooling media such as liquid nitrogen. This effectively reduces the total temperature of the passive flow, simplifies the system structure, and lowers operating costs. The synergistic effect of heating the active flow and pre-cooling the passive flow, working together through two paths, maximizes the total temperature ratio between the active and passive flows. According to the ejector's working principle, a higher total temperature ratio means stronger ejection driving potential energy, thus laying the energy foundation for the entire system to achieve a higher ejection coefficient (i.e., suction capacity). The two-stage ejector 500 adopts a unique structure combining a single-stage support plate type and a two-stage annular type. The single-stage support plate type ejector utilizes the wake region generated by its support plate structure to efficiently promote the initial intense mixing and momentum exchange between the cooled secondary flow and the first-stage heated primary flow. This stage focuses on high mixing efficiency. The pre-mixed airflow then serves as the passive flow for the second-stage ejector, and merges again with the second-stage heated primary flow in the second-stage annular ejector 502. The annular flow channel design effectively reduces flow separation and impact losses, focusing on maintaining a high total pressure. Through this two-stage division of labor and structural coupling design, the system organically combines the advantages of the high mixing efficiency of the support plate type ejector with the advantages of the high total pressure recovery capability of the annular ejector, overcoming the technical contradiction that a single-structure ejector cannot simultaneously achieve both. This allows the ejection process to achieve deep mixing while maintaining lower flow losses, thereby improving the vacuum level (or back pressure) ultimately achieved by the ejection system.The entire system adopts a modular and integrated design concept; the heating device adopts an integrated heat storage and pressure bearing structure, and the cooling device adopts a heat sink structure without moving parts, which avoids the inherent defects of traditional gas heating combustion instability and easy ablation, as well as the complex structure and high flow resistance of traditional indirect wall coolers from the source; the integrated connection of the two-stage ejector 500 reduces the connecting pipelines and potential leakage points compared with the separate arrangement of multi-stage ejector systems, and improves the structural compactness and system reliability; neither heating nor cooling processes require a complex auxiliary medium supply system (such as fuel, large amount of coolant), which reduces the system's manufacturing cost, operation and maintenance complexity and long-term operating cost. This invention's pre-cooling ejector system establishes high total temperature ratio conditions efficiently and economically by combining regenerative external radiation heating with heat sink-type medium-free pre-cooling. Furthermore, through a two-stage ejector structure, it achieves synergistic optimization of high mixing efficiency and high total pressure recovery capability. The entire system not only improves ejector performance but also possesses comprehensive advantages such as compact structure, stable and reliable operation, and low cost. It solves the technical problems of low efficiency and high risk in existing total temperature ratio adjustment methods, as well as the difficulty in balancing mixing and pressurization performance and poor system integration in ejector structures.

[0026] like Figure 1 and Figure 2As shown, in this embodiment, the integrated heat storage and pressure bearing electric heating device 300 includes a heat insulation layer 301, an electric heating layer 302, a heat storage component 303, an inlet pipe 304, an outlet pipe 305, a first diffusion cone 306, and a second diffusion cone 307. The heat insulation layer 301 is the outermost layer, and the electric heating layer 302 is the inner layer of the heat insulation layer 301, forming an inner heating cavity. The input end of the heat storage component 303 is connected to the large end face of the first diffusion cone 306, and the output end of the heat storage component 303 is connected to the large end face of the second diffusion cone 307. The output end of the inlet pipe 304 is configured as an inlet... The air intake screen of the inlet pipe 304 extends into the inner cavity of the first diffuser cone 306 through the small end of the first diffuser cone 306, and the small end of the second diffuser cone 307 is connected to the outlet pipe 305. The inlet pipe 304, the first diffuser cone 306, the heat storage component 303, the second diffuser cone 307 and the outlet pipe 305 constitute an airflow conveying component. The airflow conveying component is suspended in the inner heating cavity and is arranged without contact with the electric heating layer 302. The inlet pipe 304 is connected to the output end of the pressure reducer 200, and the outlet pipe 305 is connected to the first branch 308 and the second branch 309 respectively. By suspending the entire airflow conveying assembly, including the inlet pipe 304, diffuser cone, heat storage component 303, and outlet pipe 305, within the inner heating cavity formed by the electric heating layer 302, and ensuring that it is arranged without contact with the electric heating layer 302, complete isolation between the high-pressure airflow channel and the electric heating element is achieved. During the heating process, electrical energy is first converted into heat energy and heated through radiation and convection to the air cavity and heat storage component 303. After the heat storage component 303 accumulates heat, it heats the gas flowing inside through heat conduction and radiation. This "external radiation, internal heat storage, and indirect heat exchange" mode eliminates the risks of element ablation, short circuit, and breakdown caused by direct impact or contact between high-pressure, high-speed airflow and electric heating elements (such as resistance wires). It is especially suitable for the harsh working conditions of high-pressure gas heating and significantly improves the safety, stability, and service life of the heating process. A first diffusion cone 306 is provided at the inlet end of the airflow conveying component. After the high-pressure gas is initially diffused by the air intake screen at the end of the inlet pipe 304, it enters the cavity of the first diffusion cone 306. The cone-shaped structure can reduce the gas flow velocity, so that the airflow can be uniform and stable before entering the subsequent heat storage component 303, avoiding local severe impact or excessive pressure loss caused by high-speed airflow on the heat storage body. The gas then enters the heat storage component 303 and travels through the complex flow channel composed of a specific structure (such as a porous honeycomb structure), and has a sufficient and long-term heat exchange with the heat storage body with high heat capacity. This increases the effective contact area and contact time between the gas and the hot solid, ensuring that heat is efficiently and uniformly transferred to the gas, thereby achieving a significant increase in the total temperature of the primary flow. The second diffusion cone 307 at the outlet end helps to guide the heated gas smoothly into the outlet pipe 305, reducing flow loss.The pressure-bearing shell (the external structure formed by the thermal insulation layer 301 and the electric heating layer 302), the heating element (electric heating layer 302), and the core heat exchange channel (airflow conveying assembly) are highly integrated. The thermal insulation layer 301 is located on the outermost layer, which minimizes the heat loss of the device to the environment and improves the thermal energy utilization efficiency. The airflow conveying assembly, as an integral pressure-bearing unit, can withstand the primary flow pressure after being reduced by the pressure reducer 200 (such as reducing the primary flow pressure from 35MPa to less than 10MPa). This avoids the need for external high-pressure heat exchangers, complex connecting pipelines, and additional insulation measures that may be required in traditional heating schemes. This makes the device structure more compact and more integrated, reduces potential leakage points, and facilitates installation and maintenance. The 300 integrated pressurized and thermally regenerated electric heating device solves the safety and reliability problems of high-pressure gas electric heating through a suspended non-contact design of the airflow delivery component. By combining inlet diffusion and uniform flow with deep heat exchange in the regenerator, it achieves efficient and uniform heating of the gas, effectively increasing the total temperature of the active flow. Furthermore, the integrated "pressurization-heating-insulation" system optimizes the system structure and improves thermal efficiency. The entire pre-cooling ejector system provides the hardware foundation for high total temperature ratio, high reliability, and high stability active flow heating. It is an effective technical means to solve the problems of high safety risks, poor stability, and complex structures existing in traditional gas heating or contact electric heating solutions.

[0027] like Figure 1 and Figure 2As shown, in this embodiment, the heat storage component 303 includes multiple heat storage units 3031; the heat storage unit 3031 is a cylindrical structure, and the end face of the cylindrical structure has multiple bidirectional through holes to form a honeycomb structure; the multiple heat storage units 3031 are welded together in sequence along the axial direction, and the holes of the multiple heat storage units 3031 are arranged in an axial through manner. The heat storage unit 3031 adopts a cylindrical structure with multiple bidirectional through-holes on the end face, forming a standard honeycomb porous medium. This structure provides a large internal surface area per unit volume. When the high-temperature gas flows through these dense and regular circular channels, the gas can have sufficient contact and heat exchange with the solid wall of the heat storage body. The regularity of the honeycomb channels is conducive to the formation of stable laminar or turbulent flow (depending on the Reynolds number), reducing the local dead zones and flow resistance caused by disordered flow, thereby achieving efficient and uniform gas heating while ensuring a low pressure drop. Each circular channel is equivalent to a miniature heat exchange pipe, ensuring that heat is quickly and uniformly transferred from the wall of the heat storage unit 3031 to the flowing gas. Multiple heat storage units 3031 are sequentially welded together along the axial direction to form a whole. The welding process forms a strong metallurgical bond between the heat storage units 3031, enabling the entire heat storage assembly 303 to withstand the thermal stress caused by airflow pressure, temperature changes, and its own weight as a whole, exhibiting excellent structural integrity and pressure resistance. Welding ensures reliable airtightness at the connection points of adjacent heat storage units 3031, preventing leakage or cross-flow of high-pressure gas inside the assembly and ensuring that all gas flows through the designed honeycomb channels for heat exchange. Axial welding also allows heat to be conducted to a certain extent through solid materials along the axial direction, helping to balance the axial temperature distribution of the entire heat storage assembly 303 and reducing local overcooling or overheating. The heat storage assembly 303 is composed of multiple standardized heat storage units 3031 welded together, which embodies a modular design concept and facilitates the manufacturing, processing (such as extrusion molding, machining of round holes) and quality control of heat storage materials. In extreme cases, if the heat storage assembly 303 is partially damaged, it can be maintained by replacing the entire assembly or a specific unit segment. Compared with a single giant heat storage body, this improves the potential maintainability and replaceability. By controlling the number of heat storage units 3031 and the welding process, the total length and heat capacity of the heat storage assembly 303 can be flexibly adjusted to meet the needs of different flow rates and heating power.

[0028] like Figure 1 and Figure 2As shown, in this embodiment, the integrated heat storage and pressure bearing electric heating device 300 includes a first support 310, a second support 311, and a third support 312. The first support 310 is provided at the welding position between two adjacent heat storage units 3031. The first support 310 is used to support the heat storage component 303 so that the heat storage component 303 is suspended in the inner heating cavity of the electric heating layer 302. The second support 311 is used to support the first diffusion cone 306 and / or to support the connection between the first diffusion cone 306 and the heat storage component 303 so that the input end of the heat storage component 303 is suspended in the inner heating cavity of the electric heating layer 302. The third support 312 is used to support the second diffusion cone 307 and / or to support the connection between the second diffusion cone 307 and the heat storage component 303 so that the output end of the heat storage component 303 is suspended in the inner heating cavity of the electric heating layer 302. With the combined support of the first support 310, the second support 311, and the third support 312, the airflow conveying assembly, including the inlet pipe 304, the first diffusion cone 306, the second diffusion cone 307, the heat storage component 303, and the outlet pipe 305, is stably and non-contactly suspended in the inner heating cavity formed by the electric heating layer 302. This non-contact heating mode of external radiation, internal heat storage, and inter-wall heat exchange ensures that the high-pressure airflow channel and the outer electric heating layer 302 maintain the designed and stable distance, eliminating the risk of short circuit, breakdown, or mechanical damage caused by accidental contact due to thermal expansion, gravity, or airflow vibration, thus ensuring the safety of the heating process and the long-term operational reliability. During heating and cooling, metal components such as the heat storage assembly 303, the first diffusion cone 306, and the second diffusion cone 307 will undergo significant thermal expansion and contraction due to temperature changes. By placing the first support 310 at the welding point between adjacent heat storage units 3031, and placing the second support 311 and the third support 312 at the connection points between the heat storage assembly 303 and the first diffusion cone 306 at the input end and the second diffusion cone 307 at the output end, this support system cleverly places the support points at locations with high structural strength at the component connections. This provides the expected guidance and constraint for the axial and radial thermal expansion of each component, preventing irregular deformation. Since the support points are located at the connection points, direct constraint is avoided at weak points in the non-connection areas of the heat storage unit 3031 or the diffusion cone body. This effectively disperses thermal stress, reduces the risk of buckling, deformation, or cracking of components (especially the slender heat storage assembly 303) due to thermal cycle stress concentration, and improves the structural integrity and service life of the entire assembly under alternating hot and cold conditions.Through the suspension design formed by the support system, an annular and continuous air gap is constructed between the airflow conveying component and the electric heating layer 302. This air gap is not only a safe insulation distance, but also constitutes a highly efficient radiative heat exchange cavity. The heat radiation from the electric heating layer 302 can be evenly projected onto the outer wall of the airflow conveying component. The heated air naturally convections within this gap, further promoting the uniform transfer of heat to the main body of the component. The reasonable layout of the support avoids the formation of large thermal bridges or unnecessary local obstruction, which helps to achieve uniform heating of the entire outer wall of the airflow conveying component, especially the outer wall of the heat storage component 303, thereby ensuring the uniformity of internal airflow heating and improving thermal energy utilization efficiency.

[0029] like Figure 1 and Figure 3As shown, in this embodiment, the high-temperature gas negative pressure emission cooling device 400 includes an inlet air duct 401, a cooling body 402, and a heat dissipation and air cooling assembly 403. The input end of the inlet air duct 401 is used to connect to the simulation device, the output end of the inlet air duct 401 is connected to the cooling body 402, the output end of the cooling body 402 is connected to the two-stage ejector 500, and the heat dissipation and air cooling assembly 403 is located to the side of the inlet air duct 401. The inlet air duct 401 serves as a dedicated interface for connecting to upstream simulation devices (such as rocket engine high-performance models). Its structural design ensures that the high-temperature secondary flow can be directionally and smoothly introduced into the cooling device, avoiding severe turbulence, impact, or backflow of the airflow at the inlet, thus creating favorable initial flow field conditions for the subsequent stable cooling process. The side-arranged heat dissipation and air cooling component 403 can cool the outer wall of the air intake channel 401, reducing the risk of excessively high wall temperature, thermal deformation, or material performance degradation caused by continuous scouring of high-temperature gas. This improves the heat resistance and service life of the air intake channel 401 itself, and ensures the safe and reliable operation of the inlet section of the device. The cooling function of the high-temperature gas negative pressure exhaust cooling device 400 is achieved by the cooling body working in conjunction with the heat dissipation and air cooling component 403 under the negative pressure environment created by the ejector. The high-temperature secondary flow from the inlet channel 401 enters the cooling body and forms a high-speed flow in the cooling body due to the suction effect of the downstream ejector, which enhances the convective heat transfer efficiency between the gas and the heat exchange surface inside the cooling body (such as fins, ribs and other heat exchange structures). The heat dissipation and air cooling component 403 (such as a fan, blower, etc.) placed on the side provides forced air cooling to the inner cavity and internal heat exchange surface of the cooling body, transferring the high-temperature gas inside to the wall or external surface, and continuously and efficiently removing the heat and dissipating it into the ambient air. This mode of internal ejector negative pressure driven convection and external forced air cooling heat dissipation means that the entire cooling process does not need to rely on external cooling media such as liquid nitrogen and cooling water and their complex circulation supply system. It can effectively pre-cool the high-temperature airflow by cleverly utilizing the system's own working conditions (ejector negative pressure) and conventional air cooling methods, which reduces the system's operating complexity and energy consumption cost. The air intake duct 401, cooling body, and heat dissipation air-cooling component 403 are integrated into a single functional unit, resulting in a compact structure. The air intake duct 401 is responsible for airflow introduction and initial protection, the cooling body serves as the core heat exchange area, and the heat dissipation air-cooling component 403 and cooling body restore the heat dissipation capacity. This integrated design reduces piping connections and external accessories, lowers system complexity and potential leakage points, and improves the reliability and maintainability of the device. Furthermore, the entire device functions as a module, facilitating customized design or complete replacement according to different cooling requirements.

[0030] like Figure 1 and Figure 3As shown, in this embodiment, the air intake channel 401 is a conical body, and the large end face of the air intake channel 401 is connected to the cooling body 402; the outer wall surface of the air intake channel 401 is provided with a plurality of convex rings 4011, which are used for reinforcement and cooling; the plurality of convex rings 4011 are arranged at intervals along the axial direction of the air intake channel 401. Multiple convex rings 4011 spaced axially on the outer wall of the conical cylinder form annular reinforcing ribs distributed along the flow channel axis. When high-temperature and high-pressure gas flows through the conical flow channel, the flow channel wall bears the internal gas pressure, thermal stress, and possible vibration loads. This effectively increases the moment of inertia of the flow channel wall, thereby significantly enhancing its resistance to bending and deformation, suppressing the cylinder breathing effect (periodic expansion and contraction) or local instability caused by pressure fluctuations or thermal loads, and ensuring that the inlet flow channel 401, especially in the inlet transition area that is in direct contact with high-temperature and high-speed airflow, can maintain a stable geometry, preventing the stability of airflow from being affected by structural deformation, thus ensuring the smooth progress of the subsequent cooling process and improving the structural integrity and durability of the entire cooling device under harsh working conditions. The protruding ring 4011 disposed on the outer wall significantly increases the contact surface area between the intake air passage 401 and the external cooling medium (air). This allows the heat transferred from the high-temperature gas inside the intake air passage 401 to the wall surface to be dissipated to the external environment more quickly and efficiently through the surface of the protruding ring 4011. This provides efficient thermal protection for the intake air passage 401 itself, effectively controls the wall temperature of the intake air passage 401, and prevents overheating. The inlet air passage 401 adopts a conical structure, with its large end face connected to the cooling body 402, forming a gradually expanding transition channel. When the high-temperature secondary flow (lower pressure but higher velocity and temperature) enters from the relatively small outlet of the simulation device, the conical flow passage can smoothly decelerate and diffuse the airflow, which helps to make the unstable incoming flow, which may have a large turbulence, more uniform and stable, and then guide it into the cooling body 402. This smooth transition reduces flow losses such as separation and eddies caused by sudden expansion of the airflow at the inlet, which is conducive to maintaining the continuity and stability of the entire flow and creates good flow conditions for efficient and uniform heat exchange in the cooling body 402.

[0031] like Figure 1 and Figure 3As shown, in this embodiment, the air intake channel 401 is a cone-shaped body, and the heat dissipation and air cooling assembly 403 includes a fan 4031, a bend 4032, and an electric valve 4033. The fan 4031 is arranged at the outer end of the bend 4032, the inner end of the bend 4032 is connected to the air intake channel 401, and the bend 4032 is bent toward the cooling body 402. The electric valve 4033 is arranged on the bend 4032. The fan 4031 is positioned at the outer end of the bend 4032, and the airflow is directed towards the intake duct 401 via the bend 4032, which bends towards the cooling body 402. This allows the cooling airflow generated by the fan 4031 to be precisely and concentratedly directed to the outer wall of the intake duct 401, particularly to the connection area between the intake duct 401 and the cooling body 402. This area is typically the part of the intake duct 401 with the highest temperature and heat load, as it is closest to the upstream high-temperature air source and is the convergence point before the airflow enters the cooling body 402. By preferentially and intensively guiding the cooling airflow to this high-heat-flux area, focused and enhanced cooling can be achieved, effectively preventing thermal stress concentration, material performance degradation, or deformation on the wall surface due to overheating. This enhances the heat resistance and service life of the intake duct 401. Compared to unorganized or simple side-blowing natural cooling, this "active, directional, and enhanced" air-cooling method significantly improves cooling efficiency. The bent pipe 4032, curving towards the cooling body 402, not only serves as a guide, but its bending shape also allows the cooling airflow blown by the fan 4031 to form a certain tangential or sweeping flow when it contacts the wall of the inlet air passage 401. This disrupts the static thermal boundary layer on the wall and enhances the turbulent heat transfer effect between the cooling airflow and the wall. An electric valve 4033 is installed on the bent pipe 4032, allowing the operator to remotely and precisely adjust the airflow through it. When the high-temperature gas negative pressure exhaust cooling device 400 is not in operation, by controlling the opening of the electric valve 4033, the cooling intensity of the heat dissipation air-cooling component 403 can be flexibly and in real-time adjusted according to the real-time wall temperature of the inlet air passage 401 and / or the preset cooling requirements of the cooling body 402. By reducing the temperature of the inlet air passage 401 and the cooling body 402, the performance of the cooling device can be quickly restored.

[0032] like Figure 1 and Figure 3As shown, in this embodiment, the cooling body 402 includes heat exchange plates 4021 and fins 4022. Multiple heat exchange plates 4021 are arranged in an array, and each heat exchange plate 4021 has multiple fins 4022 spaced apart. The spacing between the heat exchange plates 4021 gradually decreases from the input end to the output end of the cooling body 402. The input end of the cooling body 402 receives uncooled high-temperature secondary flow, which has a high temperature and enthalpy. At this point, the cooling demand for the airflow is most urgent. Setting a larger spacing between the heat exchange plates 4021 in this area means that within a unit flow length, the contact area between the airflow and the solid heat exchange surface is relatively small. This ensures a larger flow cross-sectional area and lower flow resistance in the gas channel, allowing the high-temperature, high-velocity airflow to smoothly enter the cooling body 402. This avoids excessive pressure drop, flow blockage, or backflow at the inlet due to sudden narrowing of the flow channel or excessive density of heat exchange elements, ensuring flow stability and providing a good initial flow field for efficient heat exchange. As the airflow flows towards the output end, the gas... After flowing through the front heat exchange plate 4021 and fins 4022, the temperature gradually decreases, and the heat dissipation capacity per unit volume is relatively weakened. However, the overall cooling still needs to continue to reach the target temperature. At this point, the gradually decreasing spacing of the heat exchange plates 4021 significantly increases the effective heat exchange surface area of ​​the airflow channel per unit length. The airflow has more sufficient contact with the heat exchange plates 4021, the flow channel becomes narrower, and the turbulence of the airflow is enhanced. This results in stronger heat transfer in the later stage, ensuring that the airflow can be deeply cooled to the required temperature. This gradient arrangement with a sparse front and dense back is essentially an optimized spatial distribution of heat transfer intensity, allowing the limited heat transfer volume and materials to achieve higher overall cooling efficiency. The inlet end of the cooling body 402 is connected to the inlet air passage 401 and directly bears the high-speed airflow discharged from the upstream simulation device. If the heat exchange plates 4021 are arranged too densely at this point, a huge local resistance will be formed immediately. This will not only cause a significant total pressure loss and reduce the driving energy of the airflow entering the ejector, but may also disrupt the stable negative pressure environment required by the ejector, or even cause flow separation or surge. The use of a larger plate spacing at the input end alleviates the flow resistance in the inlet area, allowing the high-temperature airflow to enter the cooling area smoothly with a relatively small pressure loss. This is crucial for maintaining the total pressure recovery of the entire ejector-cooling circuit and ensuring that the ejector has stable and sufficient suction power.The heat exchange plates 4021 are arranged in an array, together with the spaced fins 4022 on them, forming a complex and regular multi-channel, multi-flow heat exchange network. This allows the high-temperature airflow to be effectively divided and guided, and to make full contact with a large area of ​​solid surface. The gradually decreasing plate spacing, combined with the reinforcing effect of the fins 4022, makes the airflow path more tortuous and the turbulence stronger in the later stage, thereby promoting the uniformity of airflow temperature and reducing the temperature difference between the center and the edge, and between the mainstream and the gas near the wall. This more uniform temperature distribution not only helps to improve the overall heat exchange efficiency, but also reduces the risk of excessive thermal stress, deformation or cracking caused by local overheating of the heat exchange plates 4021 and fins 4022, thereby improving the structural durability and long-term operational reliability of the cooling body 402.

[0033] like Figure 1 and Figure 4As shown, in this embodiment, the two-stage ejector 500 includes a primary support plate ejector 501 and a secondary annular ejector 502; the input end of the primary support plate ejector 501 is axially connected to the output end of the high-temperature gas negative pressure emission cooling device 400, and the input end of the primary support plate ejector 501 is laterally connected to the first diversion branch 308; the output end of the primary support plate ejector 501 is axially connected to the secondary annular ejector 502, and the input end of the secondary annular ejector 502 is laterally connected to the second diversion branch 309. The primary ejector 501, through its support plate structure, can actively interfere with and separate the incoming flow. When the pre-cooled secondary flow (passive flow) flows in axially and merges with the lateral incoming flow from the first branch 308 (active flow), strong vortices and turbulent disturbances are generated in the wake region behind the support plate, forcing the two airflows to undergo intense mixing and momentum exchange within the flow channel. This achieves rapid, preliminary, yet efficient gas mixing in the first stage. The pre-mixed gas then flows into the secondary annular ejector 502. The structural characteristics of the annular flow channel result in relatively low internal flow resistance, which helps maintain the total pressure of the airflow, allowing for preliminary mixing in this region. The gas following (which acts as the "passive flow" of the secondary ejector at this point) further merges with the lateral airflow from the second branch 309 (the secondary active flow) within the annular channel. The annular structure facilitates more thorough diffusion and uniform mixing of the two airflows with a smaller additional pressure loss, and primarily achieves the function of deceleration and pressurization. This tiered functional division, with the first stage focusing on efficient mixing and the second stage focusing on pressurization and recovery, allows each ejector to operate under its optimal working mechanism, overcoming the contradiction that a single-stage ejector cannot simultaneously achieve high mixing rate and high total pressure recovery. This results in a higher overall ejection coefficient and outlet pressure recovery capability on a macroscopic level. The two-stage ejectors 500 operate in series, creating and utilizing progressively decreasing pressure. The first-stage ejector 501 utilizes the high-speed kinetic energy of the active flow to first create a low-pressure zone in the mixing chamber, successfully drawing out the pre-cooled secondary flow from the upstream cooling device. After the first-stage mixing, the gas velocity and pressure are initially adjusted, but remain at a relatively low pressure level. Subsequently, this mixed gas, as the passive flow of the second-stage ejector, encounters another high-speed active flow at the inlet of the second-stage annular ejector 502. Driven by the second-stage active flow, a lower and more stable low-pressure zone than the first-stage outlet is formed at the beginning of the second-stage mixing chamber. This relay-style pressure reduction process allows the combined structure of the two-stage ejectors 500 to achieve a lower ultimate back pressure than any single-stage ejector, thereby creating a stronger and more stable negative pressure or suction environment for upstream equipment (such as the high-temperature gas negative pressure exhaust cooling device 400), ensuring that the upstream gas source can be continuously and stably drawn in and cooled, which is a key condition required for applications such as high-altitude simulation experiments.Compared to complex multi-nozzle or multi-stage series structures, this invention employs a primary support plate and a secondary annular series structure, resulting in a relatively compact structure with fewer turns and abrupt changes in the airflow channel, reducing local flow separation and impact losses caused by complex flow channels. In particular, the secondary annular ejector has a smooth flow channel, effectively converting the kinetic energy (velocity) of the airflow into pressure energy (static pressure), exhibiting excellent pressurization and recovery characteristics. This reduces the total pressure loss of the two-stage ejector 500, allowing the energy of the active flow to be more effectively used to draw in and accelerate the passive flow, thereby improving energy utilization efficiency. This two-stage series structure is more adaptable to different incoming flow conditions (such as changes in active flow pressure and passive flow temperature), maintaining a stable ejection effect over a wider range of operating parameters, thus improving the overall system's operational stability and reliability. The axial series connection and lateral diversion injection design of the primary support plate ejector 501 and the secondary annular ejector 502 constitute a highly efficient ejector system with clear functional zoning, progressive energy utilization, and complementary performance advantages. Through the two-stage diversion operation, it achieves deep and efficient mixing of the primary and passive flows while maximizing the recovery of the total airflow pressure. This solves the technical problem that a single-structure ejector cannot simultaneously achieve high mixing efficiency and high total pressure recovery. It can create a lower and more stable ejector back pressure, and achieve the suction of the passive flow with higher overall efficiency.

[0034] like Figure 1 and Figure 4As shown, in this embodiment, the primary ejector 501 includes a support ejector section 5011, a square-to-circular flow channel 5012, and a first straight section 5013 arranged sequentially from the input end to the output end; the secondary annular ejector 502 includes an annular ejector section 5021, a contraction section 5022, a second straight section 5023, and a diffuser section 5024 arranged sequentially from the input end to the output end, with the diffuser section 5024 connected to the atmosphere. In the first-stage ejector 501, the airflow sequentially flows through the ejector section 5011, the square-to-circular flow channel 5012, and the first straight section 5013. In the ejector section 5011, the ejector structure actively generates a strong vortex system, causing the first active flow from the side and the pre-cooled secondary flow (passive flow) flowing in from the axis to undergo intense forced mixing and momentum exchange, which is the core area for achieving preliminary efficient mixing. The mixed airflow then enters the square-to-circular flow channel 5012, where the airflow, which may still have inhomogeneities after mixing and has a rectangular (or near-rectangular, to adapt to the ejector layout) cross-section, is further mixed. The flow smoothly and without significant separation transitions into an axisymmetric circular channel, creating uniform inflow conditions for the subsequent second-stage annular ejector and avoiding additional pressure loss and flow instability caused by abrupt changes in channel shape. Subsequently, the airflow enters the first straight section 5013, where the airflow, after initial mixing and channel transformation, further develops, and the velocity and pressure distribution becomes more uniform, providing stable and high-quality inlet conditions for entering the second-stage ejector. This three-stage design of "mixing-transformation-development" ensures the complete and efficient realization of the first-stage ejector function.In the secondary annular ejector 502, the airflow sequentially flows through the annular ejector section 5021, the contraction section 5022, the second isostatic section 5023, and the diffuser section 5024. In the annular ejector section 5021, the second active flow from the second branch 309 encounters the mixed airflow (which acts as a passive flow) from the primary ejector within the annular channel, achieving secondary mixing and energy injection under a lower back pressure environment. Subsequently, the mixed airflow enters the contraction section 5022, where its cross-sectional area gradually decreases, accelerating the airflow and converting some pressure energy into kinetic energy to maintain a sufficiently high flow velocity, thereby ensuring that the ejector can maintain a low static pressure and continuously generate a suction effect. Then, the high-speed airflow enters the second isostatic section 5024. Section 23 is the fully mixed development section, ensuring that the two airflows can complete the final and in-depth momentum and energy exchange before final discharge, making the flow field parameters (such as velocity, temperature, and pressure) more uniformly distributed across the cross section and avoiding efficiency losses due to insufficient mixing. Finally, the airflow enters the diffuser section 5024, which is a key kinetic energy recovery device. The cross section of the diffuser section 5024 gradually expands, allowing the high-speed airflow to decelerate and pressurize within a controllable range, effectively converting most of its kinetic energy into pressure energy (static pressure increase), and finally discharging smoothly at a pressure close to the ambient atmospheric pressure, maximizing energy recovery, improving the overall efficiency of the system, and reducing the impact and noise problems that may be caused by the direct discharge of high-speed airflow into the atmosphere. The segmented structural design, especially the setting of the straight section, provides a stable and homogenized space for airflow at key nodes, preventing phenomena such as uneven mixing and flow separation caused by excessively short flow paths and insufficient flow field development. The square-to-circular flow channel 5012 achieves an optimized transition in geometry, while the contraction section 5022 and the diffuser section 5024 respectively achieve precise control over the airflow state (acceleration and deceleration). This refined and phased management of the airflow path makes the flow field organization orderly throughout the ejection process, with mixing deepening step by step, and energy conversion (conversion of kinetic energy and pressure energy) highly efficient and controllable. As a result, the two-stage ejector 500 as a whole can achieve a higher ejection coefficient (suction capacity) and a higher outlet pressure recovery coefficient with lower internal flow losses, thereby stably and efficiently creating the low-pressure environment required by the system.

[0035] In practice, a pre-cooling ejector system is provided. This system uses a heat storage and pressure-bearing integrated electric heating device 300 to heat the active flow and a high-temperature gas negative pressure exhaust cooling device 400 to pre-cool the passive flow, increasing the overall temperature ratio between the active and passive flows. A two-stage ejector 500, consisting of a primary support plate and a secondary annular stage, draws in airflow to create a negative pressure environment. This device significantly improves ejector performance while maintaining low cost and high reliability.

[0036] The pre-cooling ejector system of the present invention, such as Figure 1As shown, the system includes a storage tank 100, a pressure reducer 200, a thermal regeneration and pressure-bearing integrated electric heating device 300, a high-temperature gas negative pressure emission cooling device 400, and a two-stage ejector 500. The storage tank 100 stores high-pressure ejector gas, providing the primary flow to the system; the pressure reducer 200 reduces the pressure of the primary flow provided by the storage tank 100, decreasing the pressure from 35 MPa to below 10 MPa, thus facilitating mixing with the secondary flow; the thermal regeneration and pressure-bearing integrated electric heating device 300 heats the ejector gas, increasing the overall temperature of the primary flow; the high-temperature gas negative pressure emission cooling device 400 pre-cools the ejected gas, reducing the overall temperature of the passive flow; and the two-stage ejector 500 draws in the secondary flow and creates a low-pressure environment.

[0037] The pre-cooling ejector system works as follows: High-pressure gas stored in tank 100 flows through pipelines to pressure reducer 200, where it is depressurized and then enters integrated heat storage and pressure bearing electric heating device 300 for external radiation heating. This process heats the primary flow. Exhaust gas from rocket engine high-profile platform and other devices is entrained in high-temperature gas negative pressure emission cooling device 400 for heat sink cooling, which pre-cools the secondary flow. Gas in pressure reducer 200 is split into primary and secondary ejectors. The primary flow entering the primary ejector mixes with the secondary flow cooled in the cooling device. The mixed gas passes through square-to-circular flow channel 5012 and straight section into the secondary ejector as the ejected gas, mixing with the gas split from pressure reducer 200 to the secondary ejector. The mixed gas generated by the secondary ejection passes through straight section and expansion section before being discharged into the atmosphere, completing the ejection process.

[0038] like Figure 2 The image shows an integrated electric heating device 300 with external radiation heating, capable of storing heat and bearing pressure. Figure 2 Cross-sectional view. The high-pressure gas stored in the device is reduced in pressure by pressure reducer 200 and then enters the integrated heat storage and pressure bearing electric heating device 300 for heating. Unlike the traditional method of heating the primary flow with gas, this integrated heat storage and pressure bearing electric heating device 300 uses radiation heating to heat the high-temperature primary flow. Subsequently, the heated primary flow enters the primary branch ejector 501 and the secondary annular ejector 502 along the pipeline to participate in mixing.

[0039] like Figure 3The diagram shows a high-temperature gas negative pressure emission cooling device 400. The secondary flow enters the inlet channel 401 and then enters the device through the expansion section. As the secondary flow passes through the heat exchange plate 4021 in the device, it undergoes convective heat exchange with the plate, reducing its temperature to approximately 400K. A cooling fan is positioned above the cooling device, and the two are connected by a pipe. During operation, the electric valve 4033 is closed, isolating the fan 4031 from the cooling device to ensure its heat exchange efficiency. After cooling is complete, the electric valve 4033 opens, and the fan 4031 supplies air to the cooling device, lowering the temperature of the heat exchange plate 4021 and quickly restoring the cooling device's performance. The cooled secondary flow is then drawn into the primary support ejector 501 through the contraction section for mixing.

[0040] like Figure 4 As shown, a two-stage ejector 500 is used, consisting of a primary support ejector 501 and a secondary annular ejector 502. The secondary stream, after undergoing heating and pre-cooling processes, enters the primary support ejector 501 for mixing. After primary ejection, the mixed gas flow enters a square-to-round transition channel for further mixing before entering a straight section for more thorough mixing. The mixed gas flow after primary ejection enters the secondary ejector from the straight section, serving as the ejected gas, and undergoes secondary ejection with the primary gas flowing from the electric heating device to the secondary ejector. After secondary ejection by the secondary annular ejector 502, the mixed gas generated by secondary ejection is discharged into the atmosphere through the straight section and the diffuser section 5024.

[0041] This pre-cooling ejector system improves upon previous primary flow heating, secondary flow pre-cooling, and ejector systems. While ensuring ejection performance, it is cost-effective, stable, and reliable. The ejection effect is enhanced by increasing the total temperature ratio of the primary and passive flows.

[0042] The beneficial effects of the pre-cooling ejector system of the present invention are as follows: 1. In the pre-cooling ejector system, the device for heating the primary flow is a regenerative electric heating device, which ensures that the high-temperature airflow does not come into contact with the resistance wire and has high stability; the device for cooling the secondary flow does not require a cooling medium and has a low cost; the two-stage ejector 500 is an integrated structure composed of a first-stage support plate ejector 501 and a second-stage annular ejector 502, which combines the advantages of both support plate ejectors and annular ejectors, with good mixing and a high pressure ratio.

[0043] 2. The pre-cooling ejector system can significantly improve the total temperature ratio of the primary and secondary flows by heating the primary flow and pre-cooling the secondary flow, thereby improving ejection performance. Furthermore, by combining the two-stage ejector 500 scheme with this system, the overall design has been improved, reducing costs and ensuring stable and reliable performance.

[0044] 3. The heating method adopts an integrated electric heating device with external radiation heating, which is safe and reliable.

[0045] 4. The cooling method uses a high-temperature gas negative pressure exhaust cooling device, which requires no cooling medium and has a low cost. It can be operated efficiently multiple times in short periods.

[0046] 5. The ejector device adopts a two-stage ejector 500. Through the combination of the first-stage support plate ejector 501 and the second-stage annular ejector 502, a combination of high mixing efficiency and high boost ratio is achieved.

[0047] Matters not covered in this invention are common knowledge.

[0048] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0049] The embodiments described above are merely examples of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention.

[0050] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A pre-cooling ejector system, characterized in that, include: Storage tank (100) is used to store high-pressure ejector gas and provide a primary flow; A pressure reducer (200) is connected to the output end of the storage tank (100) and is used to reduce the pressure of the primary flow provided by the storage tank (100); The integrated electric heating device (300) for heat storage and pressure bearing is connected to the output end of the pressure reducer (200) and is used to heat the primary flow output by the pressure reducer and to output as a jet airflow to increase the total temperature. High-temperature gas negative pressure exhaust cooling device (400) is used to entrain the secondary flow generated by the simulation device and perform heat sink pre-cooling, and output as the entrained gas with reduced total temperature; The two-stage ejector (500) is connected to the output end of the high-temperature gas negative pressure emission cooling device (400) and the first branch (308) and second branch (309) of the heat storage and pressure-bearing integrated electric heating device (300), respectively, to form a low-pressure environment and to draw the ejected gas from the high-temperature gas negative pressure emission cooling device (400), thereby enabling the ejected gas and the ejector gas to be mixed and ejected in multiple stages and discharged into the atmosphere.

2. The pre-cooling ejector system according to claim 1, characterized in that, The integrated electric heating device (300) for heat storage and pressure bearing includes a heat insulation layer (301), an electric heating layer (302), a heat storage component (303), an inlet pipe (304), an outlet pipe (305), a first diffusion cone (306), and a second diffusion cone (307). The heat insulation layer (301) is the outermost layer, and the electric heating layer (302) is the inner layer of the heat insulation layer (301) and encloses it to form an inner heating cavity; The input end of the heat storage component (303) is connected to the large end face of the first diffusion cone (306), the output end of the heat storage component (303) is connected to the large end face of the second diffusion cone (307), the output end of the inlet pipe (304) is configured as an air intake screen and the air intake screen of the inlet pipe (304) extends into the inner cavity of the first diffusion cone (306) through the small end of the first diffusion cone (306), and the small end of the second diffusion cone (307) is connected to the outlet pipe (305). The inlet pipe (304), the first diffusion cone (306), the heat storage component (303), the second diffusion cone (307) and the outlet pipe (305) constitute an airflow conveying component. The airflow delivery component is suspended in the inner heating cavity and is arranged without contact with the electric heating layer (302); The inlet pipe (304) is connected to the output end of the pressure reducer (200), and the outlet pipe (305) is connected to the first branch (308) and the second branch (309) respectively.

3. The pre-cooling ejector system according to claim 2, characterized in that, The heat storage assembly (303) includes multiple heat storage units (3031); The heat storage unit (3031) has a cylindrical structure, and the end face of the cylindrical structure has multiple bidirectional through holes to form a honeycomb structure. Multiple heat storage units (3031) are welded together in sequence along the axial direction, and the circular holes of the multiple heat storage units (3031) are arranged in an axially continuous manner.

4. The pre-cooling ejector system according to claim 3, characterized in that, The integrated electric heating device (300) for heat storage and pressure bearing includes a first support (310), a second support (311) and a third support (312). A first bracket (310) is provided at the welding position between two adjacent heat storage units (3031). The first bracket (310) is used to support the heat storage component (303) so that the heat storage component (303) is suspended in the inner heating cavity of the electric heating layer (302). The second bracket (311) is used to support the first diffusion cone (306) and / or support the connection between the first diffusion cone (306) and the heat storage component (303) so that the input end of the heat storage component (303) is suspended in the inner heating cavity of the electric heating layer (302); The third bracket (312) is used to support the second diffusion cone (307) and / or support the connection between the second diffusion cone (307) and the heat storage component (303) so that the output end of the heat storage component (303) is suspended in the inner heating cavity of the electric heating layer (302).

5. The pre-cooled ejector system according to any one of claims 1 to 4, characterized in that, The high-temperature gas negative pressure exhaust cooling device (400) includes an air inlet channel (401), a cooling body (402), and a heat dissipation air cooling component (403). The input end of the air intake channel (401) is used to connect to the simulation device, the output end of the air intake channel (401) is connected to the cooling body (402), the output end of the cooling body (402) is connected to the two-stage ejector (500), and the heat dissipation air cooling component (403) is located on the side of the air intake channel (401).

6. The pre-cooling ejector system according to claim 5, characterized in that, The air intake channel (401) is in the shape of a cone, and the large end face of the air intake channel (401) is connected to the cooling body (402). The outer wall of the air intake passage (401) is provided with multiple protruding rings (4011), which are used for reinforcement and cooling; Multiple convex rings (4011) are arranged at intervals along the axial direction of the air intake channel (401).

7. The pre-cooling ejector system according to claim 6, characterized in that, The air intake channel (401) is in the shape of a cone. The heat dissipation and air cooling assembly (403) includes a fan (4031), a bend (4032) and an electric valve (4033). The fan (4031) is located at the outer end of the bend (4032). The inner end of the bend (4032) is connected to the air intake channel (401). The bend (4032) is bent towards the cooling body (402). The electric valve (4033) is located on the bend (4032).

8. The pre-cooling ejector system according to claim 7, characterized in that, The cooling body (402) includes heat exchange plates (4021) and fins (4022). Multiple heat exchange plates (4021) are arranged in an array, and multiple fins (4022) are arranged at intervals on each heat exchange plate (4021). The spacing between the heat exchange plates (4021) gradually decreases from the input end to the output end of the cooling body (402).

9. The pre-cooled ejector system according to any one of claims 1 to 4, characterized in that, The two-stage ejector (500) includes a first-stage support plate ejector (501) and a second-stage annular ejector (502). The input end of the primary branch ejector (501) is axially connected to the output end of the high-temperature gas negative pressure exhaust cooling device (400), and the input end of the primary branch ejector (501) is laterally connected to the first branch (308). The output end of the primary support plate ejector (501) is axially connected to the secondary ring ejector (502), and the input end of the secondary ring ejector (502) is laterally connected to the second branch (309).

10. The pre-cooling ejector system according to claim 9, characterized in that, The first-stage support plate ejector (501) includes a support plate ejector section (5011), a square-to-circular flow channel (5012), and a first straight section (5013) arranged sequentially from the input end to the output end. The secondary annular ejector (502) includes an annular ejector section (5021), a contraction section (5022), a second isostatic section (5023), and a diffuser section (5024) arranged sequentially from the input end to the output end. The diffuser section (5024) is connected to the atmosphere.

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