Low-vacuum pipeline heat dissipation system based on reverse Brayton cycle and operation method
Through the low-vacuum pipeline heat dissipation system of the inverse Breton cycle, the isentropic compression, cooling and expansion process is used to solve the problem of difficult heat in the low-vacuum pipeline, achieving efficient and economical heat dissipation effect, and is suitable for low-vacuum pipelines with high power and long-term operation.
Patent Information
- Application Number
- CN202311839001.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2023-12-28
- Publication Date
- 2025-07-01
AI Technical Summary
The heat in the low-vacuum pipeline is difficult to quickly export. The existing heat dissipation system has high cost, complex structure, affects the operation of the equipment in the pipe and is difficult to maintain, and is difficult to achieve the ideal heat dissipation effect under large heat dissipation power and long-term operation.
A low-vacuum pipeline heat dissipation system based on the inverse Breton cycle is adopted, including a compressor, main heat exchanger, expander and pre-stage heat exchanger. Through isentropic compression, isentropic cooling, isentropic expansion and isopressurized heat absorption processes, the remaining air in the low-vacuum pipeline is used as the cooling medium to achieve efficient heat dissipation.
It realizes efficient heat dissipation in low-vacuum pipelines, does not change the original structure, reduces costs, simplifies maintenance, improves heat dissipation capabilities and system integration, and is suitable for long-term operation at high power.
Smart Images
Figure CN120239211A_ABST
Abstract
Description
Technical Field
[0001] This application relates to the technical fields of low-vacuum pipeline transportation and heat dissipation systems under low-vacuum conditions, and particularly relates to a low-vacuum pipeline heat dissipation system and an operation method based on the reverse Brayton cycle. Background Art
[0002] A pipeline train is a new transportation system that uses a train as a carrier, utilizes superconducting magnetic levitation technology to enable the train to be separated from the ground to eliminate frictional resistance, and uses an internal near-vacuum pipeline environment to greatly reduce air resistance, thereby achieving a theoretical train speed of over 1000 km / h. The low-vacuum pipeline train can greatly shorten the time and space distance between cities, and at the same time has many advantages such as being unaffected by weather conditions, not being restricted by air traffic flow, and having seamless connection with the urban rail system. Currently, the world's major economic and technological powers have carried out relevant technical research and industrial development. A representative example is the American Hyperloop One company, which has been researching vacuum pipeline trains since 2015 and has achieved a test speed of 387 km / h.
[0003] The low-vacuum pipeline provides an ideal operating environment for the train operation, which is stable, enclosed, and has low resistance. However, since the low-vacuum pipeline isolates the internal environment of the train from the external atmospheric environment of the pipeline, it is difficult to quickly export the heat entering the low-vacuum pipeline. At the same time, due to the relatively thin air in the low-vacuum pipeline, when heat (including equipment heat dissipation, external environment heat transfer, train operation aerodynamic heat, etc.) is released into the air in the low-vacuum pipeline, the internal air temperature will rise rapidly, which will threaten the safety of the equipment and the train in the pipeline. From the perspective of heat dissipation, the air in the low-vacuum pipeline is thin, the convective heat transfer coefficient is small, the heat sources are scattered along the pipeline, and the heat transfer means are restricted. The heat dissipation problem of the low-vacuum pipeline has become the key difficulty restricting the engineering application of low-vacuum pipeline technology.
[0004] The low-vacuum pipeline is a relatively new train operation scenario. Currently, the existing heat dissipation systems for low-vacuum pipelines mainly use direct / indirect contact heat transfer of working fluids, compression steam and other refrigeration methods for pipeline heat dissipation. These heat dissipation systems have the following problems in the working condition scenarios with large heat dissipation power and long-term operation: setting intricate heat dissipation pipelines or structures in the low-vacuum pipeline will, on the one hand, increase the design cost, and on the other hand, will change the existing low-vacuum pipeline structure, which is likely to affect the normal operation of other equipment (including vacuum pump groups) in the pipeline. The complex internal pipeline structure causes difficulties in maintenance, is greatly affected by the external environment, and it is difficult to achieve an ideal heat dissipation effect. Summary of the Invention
[0005] In order to solve one of the above technical defects, the embodiments of this application provide a low-vacuum pipeline heat dissipation system and an operation method based on the reverse Brayton cycle.
[0006] According to the first aspect of the embodiments of the present application, a low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is provided, including a low-vacuum pipeline. Heat dissipation units are arranged at high-temperature regions inside the low-vacuum pipeline. Each heat dissipation unit includes a compressor, a main heat exchanger, and an expander arranged outside the low-vacuum pipeline. A main intake pipeline and a main exhaust pipeline are arranged on the low-vacuum pipeline. The input end of the compressor is connected to the inside of the high-temperature region through the main intake pipeline, the output end of the compressor is connected to the input end of the main heat exchanger, the output end of the main heat exchanger is connected to the input end of the expander, and the output end of the expander is connected to the inside of the high-temperature region through the main exhaust pipeline.
[0007] Furthermore, the present application further includes a pre-stage heat exchanger arranged outside the low-vacuum pipeline. The pre-stage heat exchanger includes a cold pipe module and a heat pipe module arranged closely. The input end of the cold pipe module is connected to the main intake pipeline, the output end of the cold pipe module is connected to the input end of the compressor, the input end of the heat pipe module is connected to the output end of the compressor, and the output end of the heat pipe module is connected to the input end of the main heat exchanger.
[0008] Furthermore, a plurality of bypass intake pipelines and a plurality of bypass exhaust pipelines are also arranged on the low-vacuum pipeline. One ends of the plurality of bypass intake pipelines are respectively connected to the inside of the high-temperature region, the other ends of the plurality of bypass intake pipelines are aggregated and then connected to the main intake pipeline, one ends of the plurality of bypass exhaust pipelines are respectively connected to the inside of the high-temperature region, and the other ends of the plurality of bypass exhaust pipelines are aggregated and then connected to the main exhaust pipeline.
[0009] Furthermore, a gas storage tank is connected to the output end of the compressor.
[0010] Furthermore, a vacuum pump group is installed on the low-vacuum pipeline, and the vacuum pump group can maintain the pressure stability inside the low-vacuum pipeline.
[0011] According to the second aspect of the embodiments of the present application, an operation method of a low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is provided. The low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is any one of the above-mentioned low-vacuum pipeline heat dissipation systems based on the reverse Brayton cycle. The operation method includes the following steps:
[0012] S10. Isentropic compression: The high-temperature and low-pressure gas G1 in the high-temperature region enters the compressor through the main intake pipeline for isentropic compression, and the temperature rises to obtain a high-temperature and high-pressure gas G2;
[0013] S20. Isobaric cooling: The high-temperature and high-pressure gas G2 enters the main heat exchanger for isobaric cooling. The high-temperature and high-pressure gas G2 exchanges heat efficiently with the low-temperature air outside the low-vacuum pipeline, and the temperature drops to obtain a cooled gas G3;
[0014] S30. Isentropic expansion: The cooled gas G3 enters the expander for isentropic expansion, and the temperature is further reduced to obtain a low-temperature and low-pressure gas G4.
[0015] S40. Isobaric heat absorption: The low-temperature and low-pressure gas G4 enters the low-vacuum pipeline through the main exhaust pipeline and exchanges heat with the high-temperature and low-pressure gas G1 in the high-temperature area on the low-vacuum pipeline, realizing heat dissipation and cooling of the high-temperature area.
[0016] Furthermore, step S10 further includes the following steps:
[0017] S101. Pre-stage heat exchange: The high-temperature and low-pressure gas G1 sequentially passes through the main intake pipeline and the cold tube module and then enters the compressor for isentropic compression. The high-temperature and high-pressure gas G2 obtained after compression enters the main heat exchanger through the heat pipe module. Before entering the main heat exchanger, the high-temperature and low-pressure gas G1 in the cold tube module exchanges heat with the high-temperature and high-pressure gas G2 in the heat pipe module to reduce the temperature of the high-temperature and high-pressure gas G2, realizing pre-stage heat exchange.
[0018] Furthermore, step S40 further includes the following steps:
[0019] S401. Distributed heat dissipation: After the low-temperature and low-pressure gas G4 enters the high-temperature area through the main exhaust pipeline, driven by the train running back and forth in the low-vacuum pipeline, it evenly flows to other positions in the low-vacuum pipeline, realizing heat dissipation and cooling throughout the low-vacuum pipeline.
[0020] Furthermore, step S40 further includes the following steps:
[0021] S402. Diffusion heat dissipation: After the low-temperature and low-pressure gas G4 passes through the main exhaust pipeline, it freely diffuses in the high-temperature area through multiple bypass exhaust pipelines, realizing heat dissipation and cooling of the high-temperature area.
[0022] Furthermore, step S30 further includes the following steps:
[0023] S301. Pressure regulation: Before the isobaric heat absorption in step S40, the low-temperature and low-pressure gas G4 adjusts the outlet pressure through the expander and the bypass exhaust pipeline, making the pressure of the low-temperature and low-pressure gas G4 equal to the pressure of the high-temperature and low-pressure gas G1, realizing isobaric heat absorption.
[0024] Adopting a low-vacuum pipeline heat dissipation system and an operation method based on the reverse Brayton cycle provided in the embodiments of the present application, the high-temperature gas inside the low-vacuum pipeline further increases in temperature after being pressurized by a compressor. After the high-temperature and high-pressure gas exchanges heat efficiently with the low-temperature gas outside the pipeline and its temperature decreases, it then undergoes isentropic expansion through an expander. After the air temperature significantly decreases, it is recharged into the low-vacuum pipeline to achieve temperature reduction. The heat dissipation system project of the present application has high engineering feasibility, does not change the existing low-vacuum pipeline structure, and does not affect the normal operation of other equipment (including the vacuum pump group) inside the pipeline; the overall integration degree of the heat dissipation system is high, and it can be compactly arranged at one or several positions on the low-vacuum pipeline. It has strong theoretical heat dissipation capacity, and is easy to expand and deploy mobilely; the economy of the heat dissipation system is good, using the remaining air itself inside the low-vacuum pipeline as the cooling medium, with relatively convenient maintenance and low cost. Description of the Drawings
[0025] The drawings described herein are used to provide a further understanding of the present application, and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation to the present application. In the drawings:
[0026] Figure 1 It is a schematic diagram of the principle of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle provided by the embodiments of the present application;
[0027] Figure 2 It is a schematic diagram of the secondary heat exchanger provided by the embodiments of the present application;
[0028] Figure 3 It is a flowchart of the operation method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle provided by the embodiments of the present application;
[0029] Among them, 10 is the low-vacuum pipeline, 101 is the main intake pipeline, 102 is the main exhaust pipeline, 103 is the bypass intake pipeline, 104 is the bypass exhaust pipeline, 20 is the compressor, 30 is the main heat exchanger, 40 is the expander, 50 is the pre-heat exchanger, 501 is the cold tube module, 502 is the heat pipe module, 60 is the vacuum pump group, 70 is the gas storage tank, and 80 is the dryer. Detailed Embodiments
[0030] In order to make the technical solutions and advantages in the embodiments of the present application clearer and more understandable, the following further elaborates on the exemplary embodiments of the present application in detail. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than an exhaustive list of all embodiments. It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments can be combined with each other. Figures 1-3
[0031] In the process of implementing the present application, the inventors found that the low-vacuum pipeline provides an ideal operating environment with stability, enclosure, and low resistance for train operation. However, since the low-vacuum pipeline isolates the internal environment of the train from the external atmospheric environment, it is difficult to quickly export the heat entering the low-vacuum pipeline. At the same time, due to the relatively thin air in the low-vacuum pipeline, when heat (including equipment heat dissipation, external environment heat transfer, train operation aerodynamic heat, etc.) is released into the air in the low-vacuum pipeline, the internal air temperature will rapidly increase, thereby threatening the safety of the equipment and the train inside the pipeline. From the perspective of heat dissipation, the air in the low-vacuum pipeline is thin, the convective heat transfer coefficient is small, the heat sources are dispersed along the pipeline, and the heat transfer means are restricted. The heat dissipation problem of the low-vacuum pipeline has become the key difficulty restricting the engineering application of the low-vacuum pipeline technology.
[0032] The low-vacuum pipeline is a relatively new train operation scenario. Currently, the existing heat dissipation systems for low-vacuum pipelines mainly use direct / indirect contact heat transfer of working fluids, compression steam and other refrigeration methods for pipeline heat dissipation. These heat dissipation systems have the following problems in the working condition scenarios with large heat dissipation power and long-term operation: setting intricate heat dissipation structures in the low-vacuum pipeline will, on the one hand, increase costs, and on the other hand, change the existing low-vacuum pipeline structure, affecting the normal operation of other equipment (including vacuum pump groups) inside the pipeline, and it is not easy to repair, is greatly affected by the external environment, and it is difficult to achieve an ideal heat dissipation effect.
[0033] In view of the above problems, according to the first aspect of the embodiments of the present application, a low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is provided, as Figure 1 shown, including: a low-vacuum pipeline 10, there is a high-temperature area inside the low-vacuum pipeline 10, and heat dissipation units are arranged at the high-temperature areas. The heat dissipation unit includes a compressor 20, a main heat exchanger 30, and an expander 40 arranged outside the low-vacuum pipeline 10. A main intake pipeline 101 and a main exhaust pipeline 102 are arranged on the low-vacuum pipeline 10. The input end of the compressor 20 is connected to the inside of the high-temperature area through the main intake pipeline 101, the output end of the compressor 20 is connected to the input end of the main heat exchanger 30, the output end of the main heat exchanger 30 is connected to the input end of the expander 40, and the output end of the expander 40 is connected to the inside of the high-temperature area through the main exhaust pipeline 102.
[0034] Specifically, the present invention is a semi-open / closed reverse Brayton cycle, as Figure 1 shown, a vacuum pump group 60 is installed on the low-vacuum pipeline 10, and the vacuum pump group 60 can maintain the pressure stability inside the low-vacuum pipeline 10; as Figure 2As shown in the figure, components such as an air storage tank 70 can be added to the output end of the compressor and a dryer 80 can be added to the output end of the expander according to the actual situation and requirements in the low-vacuum pipeline 10; the heat dissipation units in this embodiment can be deployed at multiple locations on the low-vacuum pipeline in a distributed manner, and the heat exchange amount can be adjusted according to the heat dissipation requirements to achieve a centralized layout of the low-vacuum pipeline environment control system.
[0035] During specific implementation, the low-vacuum pipeline 10 will accumulate heat due to equipment heat dissipation, aerodynamic heat, and environmental heat transfer (such as solar radiation, etc.), forming a high-temperature area. When it is necessary to dissipate heat from the low-vacuum pipeline 10, the compressor 20 is turned on, and high-temperature and low-pressure gas is inhaled from the high-temperature area on the low-vacuum pipeline 10 through the main intake pipeline 101 and sent into the compressor 20 for compression. The gas temperature rises, and the high-temperature and high-pressure gas obtained after compression is sent into the main heat exchanger 30 for efficient heat exchange with the low-temperature air outside the low-vacuum pipeline 10. The temperature decreases, and then isentropic expansion is achieved through the expander 40. After the gas temperature drops significantly, it is recharged into the low-vacuum pipeline 10 through the main exhaust pipeline 102 to achieve temperature reduction. The continuous operation of the system can provide continuous cooling and heat dissipation.
[0036] This application is based on the principle of the reverse Brayton cycle and constructs a low-vacuum pipeline heat dissipation system relying on the low-vacuum pipeline system, including four thermodynamic processes: isentropic compression, isobaric cooling, isentropic expansion, and isobaric heat absorption. Utilize the temperature increase during isentropic compression to efficiently exchange heat to the outside of the pipeline, realizing the export of heat inside the pipeline to the outside of the pipeline. Subsequently, the temperature decreases through isentropic expansion to achieve continuous refrigeration inside the pipeline, effectively solving the problem of efficiently exporting the high-power, distributed, and long-term accumulated heat of the low-vacuum pipeline. The engineering feasibility of this application is high, without changing the existing low-vacuum pipeline structure and not affecting the normal operation of other equipment (including the vacuum pump group) inside the pipeline; the overall integration degree of the heat dissipation system is high, and it can be compactly arranged at one or several positions on the low-vacuum pipeline. The theoretical heat dissipation capacity is strong, and it is easy to expand and move for deployment; the economy is good, using the remaining air inside the low-vacuum pipeline itself as the cooling medium, with relatively convenient maintenance and low cost.
[0037] As a preferred solution, as Figure 2 shown, this embodiment also includes a pre-stage heat exchanger 50 arranged outside the low-vacuum pipeline 10. The pre-stage heat exchanger 50 includes a cold pipe module 501 and a heat pipe module 502 arranged closely. The input end of the cold pipe module 501 is connected to the main intake pipeline 101, the output end of the cold pipe module 501 is connected to the input end of the compressor 20, the input end of the heat pipe module 502 is connected to the output end of the compressor 20, and the output end of the heat pipe module 502 is connected to the input end of the main heat exchanger 30.
[0038] During specific implementation, the high-temperature and low-pressure gas generated in the high-temperature region of the low-vacuum pipeline 10 first passes through the cold pipe module 501 before being sent into the compressor 20 for compression. The high-temperature and high-pressure gas output after compression by the compressor 20 first passes through the heat pipe module 502 before entering the main heat exchanger 30. The gas in the cold pipe module 501 exchanges heat and cools with the gas in the heat pipe module 502 once, reducing the temperature of the high-temperature and high-pressure gas output by the compressor 20, and then enters the main heat exchanger 30 for secondary heat exchange.
[0039] To ensure sufficient temperature reduction, in this application, a cold pipe module and a heat pipe module are respectively arranged at the input end and the output end of the compressor. The high-temperature and high-pressure gas output by the compressor is first heat-exchanged and cooled with the high-temperature and low-pressure gas in the low-vacuum pipeline once, and then secondary heat-exchange cooling is realized through an external main heat exchanger. After two heat-exchange coolings, the cooling effect of the entire heat dissipation system is further improved.
[0040] As a preferred solution, as Figure 1 shown, a plurality of bypass intake pipelines 103 and a plurality of bypass exhaust pipelines 104 are further arranged on the low-vacuum pipeline 10. One ends of the plurality of bypass intake pipelines 103 are respectively communicated with the inside of the low-vacuum pipeline 10, and the other ends of the plurality of bypass intake pipelines 103 are aggregated and connected to the main intake pipeline 101. One ends of the plurality of bypass exhaust pipelines 104 are respectively communicated with the inside of the low-vacuum pipeline 10, and the other ends of the plurality of bypass exhaust pipelines 104 are aggregated and connected to the main exhaust pipeline 102.
[0041] According to the second aspect of the embodiments of the present application, an operation method of a low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is provided. As Figure 3 shown, the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is any one of the above-mentioned low-vacuum pipeline heat dissipation systems based on the reverse Brayton cycle. The operation method includes the following steps:
[0042] S10. Isentropic compression: The high-temperature and low-pressure gas G1 in the high-temperature region enters the compressor 20 through the main intake pipeline 101 for isentropic compression, and the temperature rises to obtain high-temperature and high-pressure gas G2;
[0043] S20. Isobaric cooling: The high-temperature and high-pressure gas G2 enters the main heat exchanger 30 for isobaric cooling. The high-temperature and high-pressure gas G2 exchanges heat efficiently with the low-temperature air outside the low-vacuum pipeline 10, and the temperature drops to obtain the cooled gas G3;
[0044] S30. Isentropic expansion: The cooled gas G3 enters the expander 40 for isentropic expansion, and the temperature further drops to obtain low-temperature and low-pressure gas G4;
[0045] S40, Isobaric heat absorption: The low-temperature and low-pressure gas G4 enters the low-vacuum pipeline 10 through the main exhaust pipeline 102, exchanges heat with the high-temperature and low-pressure gas G1 in the high-temperature area on the low-vacuum pipeline 10, and realizes the heat dissipation and cooling of the high-temperature area.
[0046] During specific implementation, theoretically, the reverse Brayton cycle includes four thermodynamic processes: isentropic compression, isobaric cooling, isentropic expansion, and isobaric heat absorption. It circulates according to the steps from S10 to S40. By using the temperature increase during isentropic compression, efficient heat exchange with the outside of the pipeline is achieved. Subsequently, the temperature decreases during isentropic expansion to realize continuous refrigeration.
[0047] As a preferred solution, step S10 further includes the following steps:
[0048] S101, Pre-stage heat exchange: The high-temperature and low-pressure gas G1 sequentially passes through the main intake pipeline 101 and the cold pipe module 501 and then enters the compressor 20 for isentropic compression. The high-temperature and high-pressure gas G2 obtained after compression passes through the heat pipe module 502 and then enters the main heat exchanger 30. Before entering the main heat exchanger 30, the high-temperature and low-pressure gas G1 in the cold pipe module 501 exchanges heat with the high-temperature and high-pressure gas G2 in the heat pipe module 502 to reduce the temperature of the high-temperature and high-pressure gas G2 and realize pre-stage heat exchange.
[0049] During specific implementation, as Figure 2 shown, the high-temperature and low-pressure gas generated in the high-temperature area in the low-vacuum pipeline 10 first passes through the cold pipe module 501 before being sent into the compressor 20 for compression. The high-temperature and high-pressure gas output after being compressed by the compressor 20 first passes through the heat pipe module 502 before entering the main heat exchanger 30. The gas in the cold pipe module 501 exchanges heat and cools with the gas in the heat pipe module 502 once to reduce the temperature of the high-temperature and high-pressure gas output by the compressor 20, and then enters the main heat exchanger 30 to realize secondary heat exchange.
[0050] To ensure sufficient temperature reduction, in this application, a cold pipe module and a heat pipe module are respectively arranged at the input end and the output end of the compressor. The high-temperature and high-pressure gas output by the compressor is first cooled by exchanging heat with the high-temperature and low-pressure gas or low-temperature and low-pressure gas in the low-vacuum pipeline once, and then secondary heat exchange cooling is realized through the external main heat exchanger. After two heat exchange coolings, the cooling effect of the entire heat dissipation system is further improved.
[0051] As a preferred solution, step S40 further includes the following steps:
[0052] S401, Distributed heat dissipation: After the low-temperature and low-pressure gas G4 enters the high-temperature area through the main exhaust pipeline 102, driven by the train traveling back and forth in the low-vacuum pipeline 10, it evenly flows to other positions in the low-vacuum pipeline 10 to realize the heat dissipation and cooling of the entire low-vacuum pipeline 10.
[0053] As another preferred solution, step S40 further includes the following steps:
[0054] S402. Diffusion heat dissipation: After the low-temperature and low-pressure gas G4 passes through the main exhaust pipe 102, it freely diffuses in the high-temperature area through a plurality of bypass exhaust pipelines 104 to achieve heat dissipation and cooling of the high-temperature area.
[0055] During specific implementation, step S401 and step S402 are carried out simultaneously in the low-vacuum pipeline 10. On the one hand, the reflux cooling gas can freely diffuse to achieve pipeline refrigeration, and at the same time, it can also drive the reciprocating movement of the train in the pipeline to achieve rapid temperature balance in the pipeline, and jointly cooperate to achieve heat dissipation and cooling in the entire low-vacuum pipeline 10.
[0056] As a preferred solution, step S30 further includes the following steps:
[0057] S301. Pressure regulation: Before isobaric heat absorption in step S40, the low-temperature and low-pressure gas G4 passes through the expander 40 and the bypass exhaust pipeline 104 to regulate the outlet pressure, so that the pressure of the low-temperature and low-pressure gas G4 is equal to the pressure of the high-temperature and low-pressure gas G1, achieving isobaric heat absorption.
[0058] A low-vacuum pipeline heat dissipation system and operation method based on the reverse Brayton cycle provided in this embodiment adopt a cycle air refrigeration method based on the reverse Brayton, and are constructed relying on the low-vacuum pipeline system. It can efficiently export the heat accumulation caused by equipment heat dissipation, aerodynamic heat, environmental heat transfer (such as solar radiation), etc. in the low-vacuum pipeline, has good engineering implementability and economy, avoids arranging more heat exchange units inside and outside the low-vacuum pipeline, and has relatively convenient maintainability. In addition to improving the temperature in the low-vacuum pipeline, it will not cause changes in other internal environmental factors, and has the advantages of strong heat dissipation ability, small influence by the external environment, and easy expansion and deployment. Especially for the heat dissipation system of large-size low-vacuum pipelines, it is suitable for use in working conditions with large heat dissipation power and long-term operation, and has strong practicability.
[0059] This application is described with reference to the flowcharts and / or block diagrams of methods, devices (systems), and computer program products according to the embodiments of this application. It should be understood that each process and / or block in the flowchart and / or block diagram can be implemented by computer program instructions, and the combination of the processes and / or blocks in the flowchart and / or block diagram can also be implemented by computer program instructions. These computer program instructions can be provided to the processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing devices to generate a machine, so that the instructions executed by the processor of the computer or other programmable data processing devices generate a device for implementing the functions specified in Figure 1 one process or multiple processes and / or blocks Figure 1 one block or multiple blocks.
[0060] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.
[0061] In addition, the terms "first" and "second" are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined.
[0062] In the present application, unless otherwise clearly specified and defined, the terms "mounted", "connected", "coupled", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection, an electrical connection, or a connection capable of mutual communication; it may be directly connected, or indirectly connected through an intermediate medium, and may be the internal communication of two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.
[0063] Although the preferred embodiments of the present application have been described, those skilled in the art can make additional changes and modifications once they learn the basic creative concept. Therefore, the appended claims are intended to be construed as including the preferred embodiments as well as all changes and modifications falling within the scope of the present application.
[0064] Obviously, those skilled in the art can make various changes and modifications to the present application without departing from the spirit and scope of the present application. Thus, if these modifications and variations of the present application fall within the scope of the claims of the present application and their equivalent technologies, the present application is also intended to include these changes and modifications.
Claims
1. A low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle, characterized in that Including: A low-vacuum pipeline (10), heat dissipation units are arranged at high-temperature areas inside the low-vacuum pipeline (10). The heat dissipation unit includes a compressor (20), a main heat exchanger (30), and an expander (40) arranged on the outer side of the low-vacuum pipeline (10). A main intake pipeline (101) and a main exhaust pipeline (102) are arranged on the low-vacuum pipeline (10). The input end of the compressor (20) is connected to the inside of the high-temperature area through the main intake pipeline (101). The output end of the compressor (20) is connected to the input end of the main heat exchanger (30). The output end of the main heat exchanger (30) is connected to the input end of the expander (40). The output end of the expander (40) is connected to the inside of the high-temperature area through the main exhaust pipeline (102).
2. The low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 1, wherein It further includes a pre-stage heat exchanger (50) arranged on the outer side of the low-vacuum pipeline (10). The pre-stage heat exchanger (50) includes a cold tube module (501) and a heat pipe module (502) arranged closely. The input end of the cold tube module (501) is connected to the main intake pipeline (101). The output end of the cold tube module (501) is connected to the input end of the compressor (20). The input end of the heat pipe module (502) is connected to the output end of the compressor (20). The output end of the heat pipe module (502) is connected to the input end of the main heat exchanger (30).
3. The low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 2, characterized in that, A plurality of bypass intake pipelines (103) and a plurality of bypass exhaust pipelines (104) are further arranged on the low-vacuum pipeline (10). One ends of the plurality of bypass intake pipelines (103) are respectively connected to the inside of the high-temperature area. The other ends of the plurality of bypass intake pipelines (103) are aggregated and connected to the main intake pipeline (101). One ends of the plurality of bypass exhaust pipelines (104) are respectively connected to the inside of the high-temperature area. The other ends of the plurality of bypass exhaust pipelines (104) are aggregated and connected to the main exhaust pipeline (102).
4. The low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 1, wherein, A vacuum pump group (60) is installed on the low-vacuum pipeline (10). The vacuum pump group (60) can maintain the pressure stability inside the low-vacuum pipeline (10).
5. The low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 1, characterized in that, The output end of the compressor (20) is connected to a gas storage tank (70).
6. The operation method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle, wherein the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle is any one of the low-vacuum pipeline heat dissipation systems based on the reverse Brayton cycle in claims 1-5, and is characterized in that, The described operation method includes the following steps: S10. Isentropic compression: The high-temperature and low-pressure gas G1 in the high-temperature area enters the compressor (20) through the main intake pipeline (101) for isentropic compression, the temperature rises, and a high-temperature and high-pressure gas G2 is obtained; S20. Isobaric cooling: The high-temperature and high-pressure gas G2 enters the main heat exchanger (30) for isobaric cooling. The high-temperature and high-pressure gas G2 exchanges heat efficiently with the low-temperature air outside the low-vacuum pipeline (10), the temperature drops, and a cooled gas G3 is obtained; S30. Isentropic expansion: The cooled gas G3 enters the expander (40) for isentropic expansion, the temperature further drops, and a low-temperature and low-pressure gas G4 is obtained; S40. Isobaric heat absorption: The low-temperature and low-pressure gas G4 enters the low-vacuum pipeline (10) through the main exhaust pipeline (102), exchanges heat with the high-temperature and low-pressure gas G1 in the high-temperature area on the low-vacuum pipeline (10), and realizes the heat dissipation and cooling of the high-temperature area.
7. The operating method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 6, characterized in that, The step S10 further includes the following steps: S101. Pre-stage heat exchange: The high-temperature and low-pressure gas G1 sequentially passes through the main intake pipeline (101) and the cold pipe module (501) and then enters the compressor (20) for isentropic compression. The high-temperature and high-pressure gas G2 obtained after compression passes through the heat pipe module (502) and then enters the main heat exchanger (30). Before entering the main heat exchanger (30), the high-temperature and low-pressure gas G1 in the cold pipe module (501) exchanges heat with the high-temperature and high-pressure gas G2 in the heat pipe module (502) to reduce the temperature of the high-temperature and high-pressure gas G2 and realize pre-stage heat exchange.
8. The operating method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 6, characterized in that, The step S40 further includes the following steps: S401. Distributed heat dissipation: After the low-temperature and low-pressure gas G4 enters the high-temperature area through the main exhaust pipeline (102), it is driven by the train running back and forth in the low-vacuum pipeline (10) and evenly flows to other positions in the low-vacuum pipeline (10), realizing the heat dissipation and cooling in the entire low-vacuum pipeline (10).
9. The operating method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 6, characterized in that The step S40 further includes the following steps: S402. Diffusion heat dissipation: After the low-temperature and low-pressure gas G4 passes through the main exhaust pipeline (102), it freely diffuses in the high-temperature area through multiple bypass exhaust pipelines (104), realizing the heat dissipation and cooling of the high-temperature area.
10. The operation method of the low-vacuum pipeline heat dissipation system based on the reverse Brayton cycle according to claim 6, characterized in that, The step S30 further includes the following steps: S301. Pressure regulation: Before the isobaric heat absorption in step S40, the low-temperature and low-pressure gas G4 passes through the expander (40) and the bypass exhaust pipeline (104) to regulate the outlet pressure, making the pressure of the low-temperature and low-pressure gas G4 equal to the pressure of the high-temperature and low-pressure gas G1, and realizing isobaric heat absorption.