Shield tunnel unitary dehumidification air conditioning system with modular coupling

Abstract

This invention discloses a modularly coupled unit-type dehumidification and air conditioning system for tunnel boring machines (TBMs). Arranged as modular units, it allows for flexible selection and combination of one or more modules. Modules are coupled only through connecting pipes, facilitating a flat, miniaturized, and flexible design for TBM air conditioning systems. Furthermore, by simply installing an air handling module in the control area for cooling and dehumidification, the thermal comfort needs of workers can be met, significantly reducing the energy consumption of the air conditioning system. Moreover, by selecting the number of refrigeration modules based on actual cooling capacity requirements, and through the operation of multiple electrically controlled valves, the unit-type dehumidification and air conditioning system can operate in one-to-two, one-to-many, or two-to-many modes. This effectively utilizes the idle evaporator area in each refrigeration module, increasing the evaporation pressure of the refrigeration cycle in a single module, significantly improving cooling capacity and energy efficiency ratio, further reducing system energy consumption.

Description

Technical Field

[0001] This invention relates to the field of air conditioning, cooling, and dehumidification technology for subway tunnel construction environments, and in particular, to a modularly coupled shield tunnel unit-type dehumidification and air conditioning system. Background Technology

[0002] During the excavation of shield tunnels, the heat dissipation from a large amount of equipment and surface moisture create an extremely harsh working environment. Surveys indicate that dry-bulb temperatures in key work areas during shield tunneling can reach 35℃-40℃ or higher, with relative humidity exceeding 90%. Prolonged work in such high-temperature and high-humidity environments leads to low work efficiency, mental fatigue, and health damage for workers, and may even trigger safety accidents. To improve the working environment in shield tunnels, equipping them with air conditioning systems has gradually become a major trend in the shield tunneling industry.

[0003] However, in recent years, the shortcomings of existing tunnel boring machine (TBM) air conditioning systems have gradually become apparent in practical applications, mainly in the following aspects:

[0004] (1) Air conditioning systems consume a lot of energy. The heat dissipation load of heat sources in shield tunnels can usually reach hundreds of kilowatts. Air conditioning systems aimed at cooling the entire tunnel space consume a lot of energy. In reality, construction workers in shield tunnels mainly work in 2-3 areas, and there is no need to cool the entire tunnel space.

[0005] (2) The dehumidification effect of air conditioning is not significant. The existing air conditioning system mainly focuses on cooling and only uses dehumidification as a secondary function, resulting in a damp and cold state in the tunnel space after cooling, with the air humidity still as high as 90% or more. In fact, the human body's thermal comfort is determined by both temperature and humidity. Low temperature and high humidity environment will also make people feel damp and cold.

[0006] (3) High investment costs. Once an existing air conditioning system is installed, it is difficult to adjust, change or supplement the refrigeration equipment. In order to ensure the maximum cooling demand, the installed capacity is often large, and even a separate trailer is required for large equipment. This makes the system application inflexible and the investment cost remains high.

[0007] (4) Condensation heat discharge is difficult. The existing air conditioning system mainly relies on the cooling water system of the tunnel boring machine to discharge condensation heat. During tunnel boring, the air conditioning system's competition for cooling water can easily lead to excessively high oil temperature of the tunnel boring machine and insufficient cooling of the tunnel boring equipment, which seriously affects the tunneling progress.

[0008] The aforementioned drawbacks make it difficult for existing tunnel boring machine (TBM) air conditioning systems to be widely adopted and used in practical engineering projects. Therefore, there is an increasing need for an air conditioning control system that is energy-efficient, low-cost, flexible, and reliable, suitable for the hot and humid environment of subway TBM construction. Summary of the Invention

[0009] This invention provides a modularly coupled shield tunnel unit-type dehumidification and air conditioning system to address the aforementioned shortcomings of existing shield tunnel air conditioning systems.

[0010] According to one aspect of the present invention, a modularly coupled shield tunnel unit-type dehumidification and air conditioning system is provided, comprising:

[0011] An air handling module, located in the control area, is used to cool and dehumidify the environment in the control area.

[0012] Each refrigeration module is connected to each air handling module via a refrigerant supply pipe and a refrigerant return pipe to form a refrigerant circulation pipeline. The low-temperature, low-pressure gaseous refrigerant formed after heat exchange in the air handling module is input to the refrigeration module through the refrigerant return pipe for compression, condensation, heat exchange, and throttling, forming a low-pressure two-phase refrigerant, which is then transported to the air handling module through the refrigerant supply pipe. Adjacent refrigerant supply pipes are interconnected and equipped with electrically controlled valves on the connecting pipes. Adjacent refrigerant return pipes are also interconnected and equipped with electrically controlled valves on the connecting pipes. Each refrigerant supply pipe and refrigerant return pipe is equipped with an electrically controlled valve. By controlling the working state of multiple electrically controlled valves, the unitary dehumidification air conditioning system can switch between multiple operating modes.

[0013] Furthermore, it also includes a cooling water buffer tank. The outlet pipe of the cooling water buffer tank is connected to the cooling water inlet of the refrigeration module, and its inlet pipe is connected to the cooling water supply pipe of the tunnel boring machine (TBM). A first electrically controlled valve is installed on the inlet pipe. The cooling water outlet of the refrigeration module is connected to the cooling water return pipe of the TBM through a cooling water return pipe, and an electrically controlled valve is installed at the cooling water outlet of each refrigeration module. The inlet pipe of the cooling water buffer tank is also connected to the cooling water return pipe through a bypass pipe, and a second electrically controlled valve is installed on the bypass pipe. A third electrically controlled valve is also installed on the cooling water return pipe. The third electrically controlled valve is located before the connection point of the bypass pipe. During non-TBM tunneling, the first and third electrically controlled valves are controlled to open, and the second electrically controlled valve is controlled to close, so as to realize the parallel operation of the cooling water. During TBM tunneling, the first and third electrically controlled valves are controlled to close, and the second electrically controlled valve is controlled to open, so as to realize the internal circulation of the cooling water.

[0014] Furthermore, the volume of the cooling water buffer tank is designed based on the following formula:

[0015]

[0016] Where V represents the volume of the cooling water buffer tank. Q represents the redundancy factor, N represents the number of refrigeration modules, and Q represents the redundancy factor. lρ represents the cooling capacity of a single refrigeration module, τ represents the operating time in internal circulation mode, ε represents the coefficient of performance (COP) of the refrigeration module, and ρ and c p ΔT represents the density and specific heat capacity at constant pressure of the cooling water, respectively; n represents the number of internal circulation cycles; and ΔT represents the temperature rise per cycle.

[0017] Furthermore, the air handling module includes a finned tube evaporator, a main centrifugal fan, a condensate tank, a condensate pump, a plate-fin air-to-air heat exchanger, and a secondary centrifugal fan, all housed within the casing. A primary return air inlet and a secondary return air inlet are located on one side of the middle portion of the casing, with the primary return air inlet below the secondary return air inlet. The finned tube evaporator is located in the central region of the casing, with its refrigerant inlet connected to the refrigerant liquid supply pipe and its refrigerant outlet connected to the refrigerant return gas pipe. The condensate tank is located below the finned tube evaporator. The primary return air entering through the primary return air inlet exchanges heat with the low-pressure two-phase refrigerant in the finned tube evaporator. After releasing heat, the primary return air forms near-saturated low-temperature air and a large amount of water... After condensation on the surface of the finned tube evaporator to form condensate, the vapor enters the condensate tank for storage and is discharged by the condensate pump. The main centrifugal fan and the plate-fin air-to-air heat exchanger are located above the finned tube evaporator. The top of the shell has a first air outlet, and the top of the other side has a second air outlet. The secondary centrifugal fan is located at the second air outlet. The main centrifugal fan is used to pressurize the near-saturated low-temperature air and deliver it to the plate-fin air-to-air heat exchanger. The plate-fin air-to-air heat exchanger is also connected to the secondary return air outlet through a pipeline. The low-temperature air exchanges heat with the secondary return air entering from the secondary return air outlet again and is then sent to the control area through the second air outlet. The heat-exchanged secondary return air is then sent to the control area through the first air outlet.

[0018] Furthermore, a liquid level sensor is installed inside the condensate tank, and a flow regulating valve is also installed between the condensate tank and the condensate pump. When the liquid level in the condensate tank reaches a first threshold, the condensate pump is controlled to start, and the flow regulating valve is controlled to adjust to its maximum opening. When the liquid level in the condensate tank drops to a second threshold, the flow regulating valve is controlled to adjust its opening to maintain the liquid level in the condensate tank at the second threshold. When the liquid level in the condensate tank continues to drop to a third threshold, the condensate pump is controlled to shut down, and the flow regulating valve is controlled to reset to its maximum opening.

[0019] Furthermore, return air equalization plates are provided at the primary return air inlet and the secondary return air inlet to ensure that the incoming return air flows evenly and reduces its velocity.

[0020] Furthermore, a condensate collection basin is provided between the finned tube evaporator and the condensate tank, and a filter screen is installed inside the condensate collection basin.

[0021] Furthermore, the refrigeration module includes a compressor, a plate condenser, a dryer filter, an expansion valve, a cooling water pump, a Y-type filter, and a flow switch. The refrigerant inlet of the compressor is connected to the refrigerant return pipe, and the refrigerant outlet is connected to the refrigerant inlet of the plate condenser. The refrigerant outlet of the plate condenser is connected to the dryer filter. One end of the expansion valve is connected to the dryer filter, and the other end is connected to the refrigerant supply pipe. One end of the Y-type filter is connected to the cooling water source, and the other end is connected to the cooling water pump. One end of the flow switch is connected to the cooling water pump, and the other end is connected to the cooling water inlet of the plate condenser. The low-temperature, low-pressure gaseous refrigerant from the air handling module is compressed by the compressor and transformed into a high-temperature, high-pressure gaseous refrigerant. After heat exchange with the cooling water in the plate condenser, it condenses into a high-temperature, high-pressure liquid refrigerant. After passing through the dryer filter and the expansion valve, it is transformed into a low-pressure, two-phase refrigerant and then delivered to the refrigerant supply pipe. The cooled water after heat exchange is then delivered to the cooling water source.

[0022] Furthermore, it also includes air curtain modules installed at both ends of the control area, which are used to exchange heat with the condensate output by the air handling module to form a vertically distributed low-temperature air curtain at both ends of the control area.

[0023] Furthermore, the air curtain module includes two air curtain machines located at opposite ends of the control area. The centrifugal fans of the air curtain machines are installed at the top. Each air curtain machine is equipped with a cold recovery surface cooler at its air curtain outlet. The cold recovery surface cooler is connected to the condensate outlet of the air handling module. After the low-temperature condensate enters the cold recovery surface cooler, it exchanges heat with the air discharged from the air curtain machine to reduce the air curtain temperature.

[0024] The present invention has the following effects:

[0025] In this invention, the modularly coupled shield tunnel unit-type dehumidification and air conditioning system employs air handling modules and refrigeration modules arranged as modular units. One or more modules can be flexibly selected and combined based on the climate conditions of the application site, shield equipment parameters, number and distribution of workers, and expected goals. When combined, modules are coupled only through connecting pipes, facilitating a flat, miniaturized, and flexible design for the shield tunnel air conditioning system. Furthermore, by installing air handling modules in controlled areas such as long-term work and rest areas for cooling and dehumidification, the thermal comfort needs of workers can be met, significantly reducing energy consumption compared to cooling the entire tunnel space. Moreover, the number of refrigeration modules can be selected based on the actual cooling capacity requirements of the air handling modules. By controlling the operating states of multiple electrically controlled valves in the piping system, the unit-type dehumidification and air conditioning system can operate in one-to-two, one-to-many, or two-to-many modes. This effectively utilizes the idle evaporator area in each refrigeration module, increasing the evaporation pressure of the refrigeration cycle in a single refrigeration module, significantly improving cooling capacity and energy efficiency ratio, further reducing system energy consumption.

[0026] 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

[0027] The accompanying drawings, which form part of this application, 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:

[0028] Figure 1 This is a schematic diagram of the pipeline connection structure of a modularly coupled shield tunnel unit-type dehumidification and air conditioning system according to a preferred embodiment of the present invention.

[0029] Figure 2 This is a schematic diagram of the connection structure in a preferred embodiment of the present invention, in which a solenoid valve group is installed on the pipeline connecting the refrigeration module and the air handling module to switch the operating mode.

[0030] Figure 3 This is a schematic diagram of the structure of the refrigeration module according to a preferred embodiment of the present invention.

[0031] Figure 4 This is a schematic diagram of the air treatment module according to a preferred embodiment of the present invention.

[0032] Figure 5 This is a schematic diagram of the structure of the air curtain module according to a preferred embodiment of the present invention.

[0033] Explanation of reference numerals in the attached figures

[0034] 1. Air handling module; 2. Refrigeration module; 3. Air curtain module; 4. Cooling water buffer tank; 5. Refrigerant supply pipe; 6. Refrigerant return pipe; 100. Shield machine cooling water supply pipe; 200. Shield machine cooling water return pipe; 41. First electrically controlled valve; 42. Second electrically controlled valve; 43. Third electrically controlled valve; 10. First solenoid valve group; 20. Second solenoid valve group; 30. Third solenoid valve group; 11. Finned tube evaporator; 12. Main centrifugal fan; 13. Condensate tank; 14. Condensate pump; 15. Plate-fin air-to-air heat exchanger; 16. Secondary centrifugal fan; 17. Liquid level sensor; 18. Flow regulating valve; 19. Return air distribution plate; 101. Primary return air inlet; 102. Secondary return air inlet; 103. First air supply outlet; 104. Second air supply outlet; 105. Return air filter cotton; 106. Secondary filter; 111. Condensate collection basin; 112. Filter screen; 21. Compressor; 22. Plate condenser; 23. Dryer filter; 24. Expansion valve; 25. Cooling water pump; 26. Y-type filter; 27. Flow switch; 31. Air curtain machine; 32. Cold recovery surface cooler. Detailed Implementation

[0035] 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.

[0036] like Figure 1 As shown, a preferred embodiment of the present invention provides a modularly coupled shield tunnel unit-type dehumidification and air conditioning system, comprising:

[0037] Air handling module 1 is located in the control area and is used to cool and dehumidify the environment in the control area.

[0038] Refrigeration module 2, each of which is connected to each of the air handling modules 1 via a refrigerant supply pipe 5 and a refrigerant return pipe 6 to form a refrigerant circulation pipeline. The low-temperature, low-pressure gaseous refrigerant formed after heat exchange in the air handling module 1 is input to the refrigeration module 2 via the refrigerant return pipe 6 for compression, condensation, heat exchange, and throttling, forming a low-pressure two-phase refrigerant, which is then transported to the air handling module 1 via the refrigerant supply pipe 5. Adjacent refrigerant supply pipes 5 are interconnected and equipped with electrically controlled valves, as are adjacent refrigerant return pipes 6. Each refrigerant supply pipe 5 and refrigerant return pipe 6 is equipped with an electrically controlled valve. By controlling the operating state of multiple electrically controlled valves, the unitary dehumidification air conditioning system can switch between various operating modes. For example, ... Figure 2As shown, there are two air handling modules 1 and two refrigeration modules 2. A first solenoid valve group 10 is installed on the refrigerant supply pipe 5 and refrigerant return pipe 6 connecting the first refrigeration module 2 and the first air handling module 1. A second solenoid valve group 20 is installed on the refrigerant supply pipe 5 and refrigerant return pipe 6 connecting the second refrigeration module 2 and the second air handling module 1. A third solenoid valve group 30 is installed on the pipe connecting the two refrigerant supply pipes 5 and the pipe connecting the two refrigerant return pipes 6. When the third solenoid valve group 30 is closed and the first solenoid valve group 10 and the second solenoid valve group 20 are opened, the unitary dehumidification air conditioning system adopts a one-to-one operation mode, and each refrigeration module 2 and air handling module 1 achieve independent refrigerant circulation. When the first solenoid valve group 10 and the third solenoid valve group 30 are opened and the second solenoid valve group 20 is closed, the first refrigeration module 2 works and the second refrigeration module 2 does not work. The low-pressure two-phase refrigerant generated by the first refrigeration module 2 is simultaneously diverted to the two air handling modules 1, and the unitary dehumidification air conditioning system adopts a one-to-two operation mode. It is understood that the number of air handling modules 1 and refrigeration modules 2 can be three or more. In this case, by controlling the working state of each solenoid valve group, the unitary dehumidification air conditioning system can also operate in a one-to-many, two-to-many, or many-to-many mode. When the cooling capacity demand is not high, the number of refrigeration modules 2 can be selected according to actual needs, operating in one-to-two, one-to-many, or two-to-many modes. This can effectively utilize the idle evaporator area in each refrigeration module 2, increasing the evaporation pressure of the refrigeration cycle of a single refrigeration module 2, and significantly improving both the cooling capacity and energy efficiency ratio. In addition, the electronically controlled valves in this invention can be solenoid valves or electric valves.

[0039] It is understood that the air handling module 1 and the cooling module 2 are arranged in the form of modular units. One or more modules can be flexibly selected and combined according to the climate conditions of the application site, the parameters of the tunnel boring machine (TBM), the number and distribution of workers, and expected goals. When combined, the modules are coupled only through connecting pipes, facilitating the flattened, miniaturized, and flexible design of the TBM tunnel air conditioning system. Furthermore, by only installing air handling modules 1 in controlled areas such as long-term work and rest areas for cooling and dehumidification, the thermal comfort needs of the workers can be met, significantly reducing the energy consumption of the air conditioning system compared to cooling the entire tunnel space. Moreover, the number of cooling modules 2 can be selected according to the actual cooling capacity requirements of the air handling modules 1. By controlling the operating status of multiple electrically controlled valves in the piping system, the unitary dehumidification air conditioning system can operate in one-to-two, one-to-many, or two-to-many modes. This effectively utilizes the idle evaporator area in each cooling module 2, increasing the evaporation pressure of the cooling cycle in a single cooling module 2, significantly improving the cooling capacity and energy efficiency ratio, and further reducing system energy consumption.

[0040] Optionally, the unit-type dehumidification air conditioning system further includes a cooling water buffer tank 4. The cooling water buffer tank 4 is a pressureless water tank. The outlet pipe of the cooling water buffer tank 4 is connected to the cooling water inlet of the refrigeration module 2, and its inlet pipe is connected to the shield machine cooling water supply pipe 100. A first electrically controlled valve 41 is installed on the inlet pipe. The cooling water outlet of the refrigeration module 2 is connected to the shield machine cooling water return pipe 200 through a cooling water return pipe. An electrically controlled valve is installed at the cooling water outlet of each refrigeration module 2. The inlet pipe of the cooling water buffer tank 4 is also connected to the cooling water return pipe through a bypass pipe. A second electrically controlled valve 42 is installed on the bypass pipe. A third electrically controlled valve 43 is also installed on the cooling water return pipe. The third electrically controlled valve 43 is located before the connection point of the bypass pipe. During non-shield tunneling, the first and third solenoid valves 41 and 43 are opened and the second solenoid valve 42 is closed to achieve parallel operation of cooling water. During shield tunneling, the first and third solenoid valves 41 and 43 are closed and the second solenoid valve 42 is opened to achieve internal circulation of cooling water.

[0041] It is understandable that in existing air conditioning systems, the air conditioning unit and the tunnel boring machine (TBM) are generally connected in parallel to share cooling water in order to reduce investment and operating costs. However, the cooling water volume of the TBM is primarily for cooling process equipment, and its quantity is insufficient to simultaneously supply the TBM and air conditioning unit during peak load periods. This often leads to insufficient cooling water supply to the TBM, causing the oil temperature to exceed the temperature limit, requiring intermittent shutdowns of tunneling operations and affecting the tunneling progress. To achieve stable and reliable simultaneous operation of the tunnel boring machine (TBM) and cooling modules 2 while sharing cooling water, this invention incorporates a cooling water buffer tank 4 between multiple cooling modules 2 and the TBM cooling water pipelines to store cooling water. Furthermore, a switchable water flow loop cooling water circulation pipeline system is constructed. During non-TBM tunneling operations, when the TBM is not in operation and its cooling water demand is low, the first and third electrically controlled valves 41 and 43 are opened, while the second electrically controlled valve 42 is closed. This switches the water flow loop of the cooling water circulation pipeline system to a parallel loop, allowing cooling water from the TBM cooling water supply pipe 100 to sequentially enter the cooling water supply system. After passing through the cooling buffer tank 4 and the cooling module 2, the cooling water returns to the shield machine's cooling water return pipeline 200. The shared cooling water system between the shield machine and the cooling module 2 operates in parallel mode. However, during shield tunneling, the shield equipment operates continuously, resulting in a high demand for cooling water. If parallel operation is adopted, the cooling water demand of the cooling module 2 will inevitably affect the normal operation of the shield equipment. At this time, the first solenoid valve 41 and the third solenoid valve 43 are closed, and the second solenoid valve 42 is opened, switching the water flow loop of the cooling water circulation pipeline system to an internal circulation loop. The cooling water temporarily circulates internally between the cooling water buffer tank 4 and the cooling module 2. By constructing the above-mentioned pipeline system with switchable water flow loops, the appropriate shared cooling water operation mode can be switched at different times during shield construction, ensuring that the shield equipment and the cooling module 2 can operate synchronously, stably, and reliably.

[0042] It is understandable that the capacity of the cooling water buffer tank 4 needs to be set according to the actual needs of the refrigeration module 2. Theoretically, the larger the volume, the better. However, the larger the volume of the cooling water buffer tank 4, the larger the space it occupies, and it may even require a transfer trailer. This not only increases the initial investment but also hinders the flexible and miniaturized design of the entire unit-type dehumidification system. Preferably, the volume of the cooling water buffer tank 4 is designed based on the following formula:

[0043]

[0044] Where V represents the volume of cooling water buffer tank 4. This represents the redundancy factor, typically taken as 1.2 to 1.3. N represents the number of refrigeration modules 2, and Q... lLet ρ represent the cooling capacity of a single refrigeration module 2, τ represent the operating time in internal circulation mode, ε represent the coefficient of performance (COP) of refrigeration module 2, and ρ and c represent the cooling capacity of a single refrigeration module 2. p Here, ρ represents the density and specific heat capacity at constant pressure of the cooling water, n represents the number of internal circulation cycles (typically 2-3), and ΔT represents the temperature rise per cycle (usually 5°C). The volume of the cooling water buffer tank 4 is calculated by comprehensively considering factors such as the cooling capacity and coefficient of performance of a single refrigeration module 2, the number of internal circulation cycles, the number of refrigeration modules 2, and relevant cooling water parameters. This ensures that the cooling water buffer tank 4 can provide sufficient cooling water for multiple refrigeration modules 2, especially in internal circulation mode, guaranteeing the cooling water supply needs of the refrigeration system. Furthermore, it reduces the volume of the cooling water buffer tank 4, which is beneficial for the flexible and miniaturized design of the unitary dehumidification system.

[0045] Understandable, such as Figure 3 As shown, the refrigeration module 2 specifically includes a compressor 21, a plate condenser 22, a dryer filter 23, an expansion valve 24, a cooling water pump 25, a Y-type filter 26, and a flow switch 27. The refrigerant inlet of the compressor 21 is connected to the refrigerant return pipe 6, and the refrigerant outlet is connected to the refrigerant inlet of the plate condenser 22. The refrigerant outlet of the plate condenser 22 is connected to the dryer filter 23. One end of the expansion valve 24 is connected to the dryer filter 23, and the other end is connected to the refrigerant supply pipe 5. One end of the Y-type filter 26 is connected to the cooling water source, i.e., to the cooling water buffer tank 4, and the other end is connected to the cooling water pump 25. One end of the flow switch 27 is connected to the cooling water pump 25, and the other end is connected to the cooling water inlet of the plate condenser 22. The low-temperature, low-pressure gaseous refrigerant from the air handling module 1 is compressed by the compressor 21 and transformed into a high-temperature, high-pressure gaseous refrigerant. After heat exchange with cooling water in the plate condenser 22, it condenses into a high-temperature, high-pressure liquid refrigerant. After drying by the dryer filter 23 and passing through the expansion valve 24, it transforms into a low-pressure two-phase refrigerant and is then transported to the refrigerant supply pipe 5, and subsequently to the air handling module 1. The cooled water, after heat exchange, is then transported to the cooling water buffer tank 4. The internal structure of the entire refrigeration module 2 is simple, facilitating a flattened design that is well-suited to the limited space constraints within a shield tunnel.

[0046] Understandable, such as Figure 4As shown, the air handling module 1 includes a finned tube evaporator 11, a main centrifugal fan 12, a condensate tank 13, a condensate pump 14, a plate-fin air-to-air heat exchanger 15, and a secondary centrifugal fan 16, all housed within a casing. A primary return air inlet 101 and a secondary return air inlet 102 are located on one side of the middle portion of the casing, with the primary return air inlet 101 positioned below the secondary return air inlet 102. The finned tube evaporator 11 is located in the central region of the casing, with its refrigerant inlet connected to the refrigerant supply pipe 5 and its refrigerant outlet connected to the refrigerant return gas pipe 6, thereby achieving refrigerant circulation. The condensate tank 13 is located below the finned tube evaporator 11. The primary return air entering from the primary return air inlet 101 exchanges heat with the low-pressure two-phase refrigerant in the finned tube evaporator 11. After absorbing heat, the low-pressure two-phase refrigerant transforms into a low-temperature, low-pressure gaseous refrigerant, which is then transported to the refrigeration module 2 via the refrigerant return pipe 6. After the primary return air releases heat, it forms near-saturated low-temperature air on one hand, and a large amount of water vapor condenses on the surface of the finned tube evaporator 11 to form condensate, which is then stored in the condensate tank 13 and discharged by the condensate pump 14. The main centrifugal fan 12 and the plate-fin air-to-air heat exchanger 15 are located above the finned tube evaporator 11. A first air inlet 103 is located at the top of the casing, and a second air inlet 104 is located on the upper side of the other side. The secondary centrifugal fan 16 is positioned at the second air inlet 104. The main centrifugal fan 12 pressurizes near-saturated low-temperature air and delivers it to the plate-fin air-to-air heat exchanger 15. The plate-fin air-to-air heat exchanger 15 is also connected to a secondary return air inlet 102 via a pipeline. The low-temperature air undergoes further heat exchange with the secondary return air entering from the secondary return air inlet 102 and is then sent to the control area through the second air inlet 104. The heat-exchanged secondary return air is then sent to the control area through the first air inlet 103. The entire air handling module 1 has a compact and simple internal structure, facilitating a flattened design that is well-suited to the limited space constraints within shield tunnels. Furthermore, the first heat exchange is achieved through the finned tube evaporator 11, and the second heat exchange is achieved through the plate-fin air-to-air heat exchanger 15. This two-stage heat exchange process fully utilizes the cooling capacity of the refrigerant. Although the temperature of the low-temperature air increases by 3°C to 5°C after the second heat exchange, its relative humidity can be reduced to 60% to 70%, improving the air environment in the controlled area to a low-temperature, medium-humidity environment, significantly enhancing the dehumidification effect and improving the thermal comfort of the workers. Additionally, the second air outlet 104 is equipped with adjustable blades for easy adjustment of the air outlet angle.

[0047] Optionally, a level sensor 17 is installed in the condensate tank 13, and a flow regulating valve 18 is also installed between the condensate tank 13 and the condensate pump 14. When the liquid level in the condensate tank 13 reaches a first threshold, the condensate pump 14 is turned on, and the flow regulating valve 18 is adjusted to its maximum opening. When the liquid level in the condensate tank 13 drops to a second threshold, the flow regulating valve 18 is adjusted to maintain the liquid level in the condensate tank 13 at the second threshold. When the liquid level in the condensate tank 13 continues to drop to a third threshold, the condensate pump 14 is turned off, and the flow regulating valve 18 is reset to its maximum opening, thereby achieving automatic control of the balance between condensate flow and output. Preferably, a secondary filter 106 is also installed before the flow regulating valve 18 to finely filter the condensate and prevent the condensate pump 14 from being blocked by impurities.

[0048] Optionally, return air distribution plates 19 are provided at the primary return air inlet 101 and the secondary return air inlet 102 to ensure uniform flow and reduced velocity of the incoming return air. This improves the heat exchange effect between the low-pressure two-phase refrigerant and the primary return air, and between the low-temperature air and the secondary return air, fully utilizing the cooling capacity of the refrigerant and resulting in better air cooling performance. Additionally, return air filter cotton 105 is provided at the primary return air inlet 101 and the secondary return air inlet 102 to perform primary filtration of the incoming return air, preventing dust, debris, and other contaminants in the air from affecting the heat exchange performance of the finned tube evaporator 11.

[0049] Optionally, a condensate collection basin 111 is also provided between the finned tube evaporator 11 and the condensate tank 13, and a filter screen 112 is installed in the condensate collection basin 111. The condensate is first collected through the condensate collection basin 111, and then undergoes primary filtration treatment through the filter screen 112 before entering the condensate tank 13 for storage, preventing impurities in the condensate from clogging the condensate pump 14.

[0050] Optionally, the unit-type dehumidification air conditioning system further includes air curtain modules 3 installed at both ends of the control area, used to exchange heat with the condensate output by the air handling module 1 to form a vertically distributed low-temperature air curtain at both ends of the control area. By setting air curtain modules 3 at both ends of the control area to form a double-stage air curtain barrier, the airflow between the control area and the non-control area is strictly controlled, ensuring the stability of the low-temperature and humid environment in the control area, and further reducing the energy consumption of the air conditioning system.

[0051] Specifically, such as Figure 5As shown, the air curtain module 3 includes two air curtain machines 31 located at opposite ends of the control area. The centrifugal fans of each air curtain machine 31 are positioned at the top to prevent the intake end from being affected by mud splashes during construction. Each air curtain machine 31 has a cold recovery surface cooler 32 at its outlet. This cold recovery surface cooler 32 is connected to the condensate outlet of the air handling module 1. Low-temperature condensate enters the cold recovery surface cooler 32 and exchanges heat with the air discharged from the air curtain machine 31 to reduce the air curtain temperature, lowering the outlet air temperature by 1°C to 2°C. By using the cold recovery surface cooler 32 at the air curtain outlet of the air curtain machine 31 to recover and reuse the condensate from the air handling module 1, and to cool the outlet air, cold energy recovery is achieved, further reducing the overall system energy consumption. Furthermore, the height of the air curtain is related to the diameter of the shield tunnel, with its bottom 0.6m to 0.8m from the tunnel bottom and its top 1m to 1.5m from the tunnel top, ensuring that the barrier layer formed by the air curtain has a certain axial ventilation capacity at both the top and bottom.

[0052] 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 modularly coupled shield tunnel unit-type dehumidification and air conditioning system, characterized in that, include: An air handling module (1) is installed in the control area and is used to cool and dehumidify the environment in the control area. The refrigeration module (2) is connected to each air handling module (1) through a refrigerant supply pipe (5) and a refrigerant return pipe (6) to form a refrigerant circulation pipeline. The low-temperature and low-pressure gaseous refrigerant formed after heat exchange in the air handling module (1) is input to the refrigeration module (2) through the refrigerant return pipe (6) for compression, condensation heat exchange and throttling, forming a low-pressure two-phase refrigerant and being transported to the air handling module (1) through the refrigerant supply pipe (5). Adjacent refrigerant supply pipes (5) are interconnected and an electric control valve is installed on the connecting pipe. Adjacent refrigerant return pipes (6) are interconnected and an electric control valve is installed on the connecting pipe. Each refrigerant supply pipe (5) and refrigerant return pipe (6) is equipped with an electric control valve. By controlling the working state of multiple electric control valves, the unit dehumidification air conditioning system can switch between multiple operating modes. It also includes a cooling water buffer tank (4), the outlet pipe of which is connected to the cooling water inlet of the refrigeration module (2), and its inlet pipe is connected to the shield machine cooling water supply pipe (100), and a first electrically controlled valve (41) is installed on the inlet pipe. The cooling water outlet of the refrigeration module (2) is connected to the shield machine cooling water return pipe (200) through the cooling water return pipe, and an electrically controlled valve is installed at the cooling water outlet of each refrigeration module (2). The inlet pipe of the cooling water buffer tank (4) is also connected to the cooling water return pipe via a bypass pipe. A second electrically controlled valve (42) is installed on the bypass pipeline, and a third electrically controlled valve (43) is installed on the cooling water return pipe. The third electrically controlled valve (43) is located before the connection point of the bypass pipeline. During non-shield tunneling, the first electrically controlled valve (41) and the third electrically controlled valve (43) are opened and the second electrically controlled valve (42) is closed to realize the parallel operation of cooling water. During shield tunneling, the first electrically controlled valve (41) and the third electrically controlled valve (43) are closed and the second electrically controlled valve (42) is opened to realize the internal circulation of cooling water. The volume of the cooling water buffer tank (4) is designed based on the following formula: ； in, This indicates the volume of the cooling water buffer tank (4). This represents the redundancy factor, where N represents the number of refrigeration modules (2). This indicates the cooling capacity of a single refrigeration module (2). This indicates the runtime of the inner loop mode. This indicates the coefficient of performance (COP) of the refrigeration module (2). and Let represent the density and specific heat capacity at constant pressure of the cooling water, respectively, and n represent the number of internal circulation cycles. This indicates the temperature rise during a single cycle.

2. The modularly coupled shield tunnel unit-type dehumidification and air conditioning system as described in claim 1, characterized in that, The air handling module (1) includes a finned tube evaporator (11), a main centrifugal fan (12), a condensate tank (13), a condensate pump (14), a plate-fin air-to-air heat exchanger (15), and a secondary centrifugal fan (16) disposed within the housing. A primary return air inlet (101) and a secondary return air inlet (102) are provided on one side of the middle part of the housing. The primary return air inlet (101) is located below the secondary return air inlet (102). The finned tube evaporator (11) is located in the middle region of the housing. Its refrigerant inlet is connected to the refrigerant liquid supply pipe (5), and its refrigerant outlet is connected to the refrigerant return gas pipe (6). The condensate tank (13) is located below the finned tube evaporator (11). The primary return air entering from the primary return air inlet (101) exchanges heat with the low-pressure two-phase refrigerant in the finned tube evaporator (11). After the primary return air releases heat, it forms near-saturated low-temperature air on the one hand, and a large amount of water vapor in the other hand... After condensation forms on the surface of the finned tube evaporator (11), the condensate enters the condensate tank (13) for storage and is discharged by the condensate pump (14). The main centrifugal fan (12) and the plate-fin air-to-air heat exchanger (15) are located above the finned tube evaporator (11). A first air outlet (103) is provided on the top of the shell, and a second air outlet (104) is provided on the top of the other side. The secondary centrifugal fan (16) is located at the second air outlet (104). At 04), the main centrifugal fan (12) is used to pressurize the near-saturated low-temperature air and deliver it to the plate-fin air-to-air heat exchanger (15). The plate-fin air-to-air heat exchanger (15) is also connected to the secondary return air inlet (102) through a pipeline. The low-temperature air and the secondary return air entering from the secondary return air inlet (102) exchange heat again and are then sent to the control area through the second air outlet (104). The heat-exchanged secondary return air is sent to the control area through the first air outlet (103).

3. The modularly coupled shield tunnel unit-type dehumidification and air conditioning system as described in claim 2, characterized in that, A liquid level sensor (17) is installed inside the condensate tank (13). A flow regulating valve (18) is also installed between the condensate tank (13) and the condensate pump (14). When the liquid level in the condensate tank (13) is detected to reach the first threshold, the condensate pump (14) is controlled to turn on, and the flow regulating valve (18) is controlled to adjust to the maximum opening. When the liquid level in the condensate tank (13) is detected to drop to the second threshold, the flow regulating valve (18) is controlled to adjust the opening to keep the liquid level in the condensate tank (13) at the second threshold. When the liquid level in the condensate tank (13) is detected to continue to drop to the third threshold, the condensate pump (14) is controlled to turn off, and the flow regulating valve (18) is controlled to reset to the maximum opening.

4. The modularly coupled shield tunnel unitary dehumidification and air conditioning system of claim 2, wherein, Return air equalization plates (19) are provided at the primary return air inlet (101) and the secondary return air inlet (102) to make the incoming return air flow evenly and reduce the flow velocity.

5. The modularly coupled shield tunnel unit-type dehumidification and air conditioning system as described in claim 2, characterized in that, A condensate collection basin (111) is also provided between the finned tube evaporator (11) and the condensate tank (13), and a filter screen (112) is provided inside the condensate collection basin (111).

6. The modularly coupled shield tunnel unitary dehumidification and air conditioning system of claim 1, wherein, The refrigeration module (2) includes a compressor (21), a plate condenser (22), a filter dryer (23), an expansion valve (24), a cooling water pump (25), a Y-type filter (26), and a flow switch (27). The refrigerant inlet of the compressor (21) is connected to the refrigerant return pipe (6), and the refrigerant outlet is connected to the refrigerant inlet of the plate condenser (22). The refrigerant outlet of the plate condenser (22) is connected to the filter dryer (23). One end of the expansion valve (24) is connected to the filter dryer (23), and the other end is connected to the refrigerant supply pipe (5). The Y-type filter (25) is connected to the filter dryer (26), and the flow switch (27). One end of the flow switch (27) is connected to the cooling water source, and the other end is connected to the cooling water pump (25). One end of the flow switch (27) is connected to the cooling water pump (25), and the other end is connected to the cooling water inlet of the plate condenser (22). The low-temperature and low-pressure gaseous refrigerant from the air handling module (1) is compressed by the compressor (21) and transformed into a high-temperature and high-pressure gaseous refrigerant. After exchanging heat with the cooling water in the plate condenser (22), it is condensed into a high-temperature and high-pressure liquid refrigerant. After passing through the dryer filter (23) and the expansion valve (24), it is transformed into a low-pressure two-phase refrigerant and then transported to the refrigerant supply pipe (5). The cooling water after heat exchange is then transported to the cooling water source.

7. The modularly coupled shield tunnel unitary dehumidification and air conditioning system of claim 1, wherein, It also includes air curtain modules (3) set at both ends of the control area, which are used to exchange heat with the condensate output by the air handling module (1) to form a low-temperature air curtain that is vertically distributed at both ends of the control area.

8. The modularly coupled shield tunnel unitary dehumidification and air conditioning system of claim 7, wherein, The air curtain module (3) includes two air curtain machines (31) located at both ends of the control area. The centrifugal fan of the air curtain machine (31) is installed at the top. Each air curtain machine (31) is equipped with a cold recovery surface cooler (32) at the air curtain outlet. The cold recovery surface cooler (32) is connected to the condensate outlet of the air handling module (1). After the low temperature condensate enters the cold recovery surface cooler (32), it exchanges heat with the air discharged by the air curtain machine (31) to reduce the air curtain temperature.

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