Control methods for compressed air air conditioning systems

Abstract

This invention relates to the field of heat exchange technology, specifically providing a control method for a compressed air air conditioning system, aiming to solve the problems of low heat exchange efficiency and high overall energy consumption in existing compressed air air conditioning systems. To this end, the compressed air air conditioning system of this invention includes a recirculating cooler, a centrifuge, a first indirect evaporative cooler, a compression-expansion unit, a second indirect evaporative cooler, a bypass branch, and a refrigerant circulation loop. The recirculating cooler includes a first recirculating cooling pipe and a second recirculating cooling pipe. The bypass branch can directly introduce air cooled by the first indirect evaporative cooler into the room to improve cooling efficiency and reduce cooling energy consumption. The refrigerant circulation loop can selectively operate to achieve further cooling. The control method of this invention includes: acquiring the outdoor ambient temperature; and controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature to ensure that the compressed air air conditioning system always maintains a high-efficiency operating state, thereby effectively reducing energy consumption.

Description

Technical Field

[0001] This invention belongs to the field of heat exchange technology, specifically providing a control method for a compressed air air conditioning system. Background Technology

[0002] From the perspective of air conditioning technology, it is well known that the various refrigerants used in humanity's pursuit of cooling have caused serious damage to the Earth's ozone layer. New environmentally friendly refrigerants, to varying degrees, have problems such as flammability, explosiveness, toxicity, potential greenhouse effect, and high cost. Therefore, the Kigali Amendment, the EU's F-Gas regulation, and my country's refrigerant substitution scheme all require the use of more environmentally friendly refrigerants.

[0003] In recent years, technicians have gradually discovered that air, as a ubiquitous gas, possesses numerous advantages such as being non-toxic, odorless, easy to collect, and environmentally friendly. As an excellent environmentally friendly refrigerant, air offers a series of environmental and cost advantages. First, air is readily available and ubiquitous. From a production perspective, it eliminates the procurement, transportation, and storage costs of traditional refrigerants, and reduces cumbersome processes such as vacuuming and refrigerant charging, thus lowering overall production costs. Second, air is non-toxic, odorless, environmentally friendly, leak-proof, and requires simple operation and maintenance of air conditioning systems, saving significant maintenance costs. Of course, while air-based cooling has many advantages, its inherently poor cooling performance is undeniable. Due to this characteristic, existing air conditioning systems using air for heat exchange have low heat exchange efficiency and high overall energy consumption.

[0004] Accordingly, there is a need in the field for a new control method for compressed air air conditioning systems to solve the above problems. Summary of the Invention

[0005] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problems of low heat exchange efficiency and high overall energy consumption of existing compressed air air conditioning systems.

[0006] This invention provides a control method for a compressed air air conditioning system. The compressed air air conditioning system includes a recirculating cooler, a centrifuge, a first indirect evaporative cooler, a compressor-expander integrated unit, a second indirect evaporative cooler, a bypass branch, and a refrigerant circulation loop. The recirculating cooler includes a first recirculating pipe and a second recirculating pipe, which are capable of heat exchange. The inlet end of the first recirculating pipe is connected to the indoor unit, and the outlet end of the first recirculating pipe is connected to the inlet end of the centrifuge. The outlet end of the centrifuge is connected to the inlet end of the first indirect evaporative cooler, and the outlet end of the first indirect evaporative cooler is connected to the inlet of the compressor-expander integrated unit. A first control valve is provided between the outlet end of the first indirect evaporative cooler and the inlet of the compressor-expander integrated unit. The exhaust port of the compression end of the integrated compressor-expansion unit is connected to the inlet end of the second indirect evaporative cooler. The exhaust port of the second indirect evaporative cooler is connected to the inlet end of the second return cooling pipe. The exhaust port of the second return cooling pipe is connected to the inlet port of the expansion end of the integrated compressor-expansion unit. One end of the bypass branch is connected between the first indirect evaporative cooler and the first control valve. The other end of the bypass branch is connected to the exhaust port of the expansion end of the integrated compressor-expansion unit. A second control valve is provided on the bypass branch. A compressor, a condenser, a throttling component, and an evaporator are sequentially arranged on the refrigerant circulation loop. The evaporator is located at the exhaust port of the expansion end of the integrated compressor-expansion unit and downstream of the bypass branch. The exhaust port of the expansion end of the integrated compressor-expansion unit is connected to the indoor unit.

[0007] The control method includes:

[0008] Obtain the outdoor ambient temperature;

[0009] The compressed air air conditioning system is controlled to operate in the appropriate mode based on the outdoor ambient temperature.

[0010] In the preferred embodiment of the above control method, the step of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature" includes:

[0011] If the outdoor ambient temperature is lower than the first preset outdoor ambient temperature, the compressed air air conditioning system is controlled to operate in natural ventilation cooling mode.

[0012] In a preferred embodiment of the above control method, the control method further includes:

[0013] When the compressed air air conditioning system is operating in natural ventilation cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained.

[0014] If the current supply air temperature is greater than the target supply air temperature and the current power of the supply air fan of the compressed air air conditioning system has reached its maximum power, then the compressed air air conditioning system is controlled to operate in air cooling mode.

[0015] In a preferred embodiment of the above control method, the control method further includes:

[0016] When the compressed air air conditioning system is operating in air cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained again.

[0017] If the current supply air temperature is still greater than the target supply air temperature and the current power of the compressed air air conditioning system's supply fan has reached its maximum power, then the compressed air air conditioning system is controlled to operate in the first hybrid cooling mode.

[0018] In the preferred embodiment of the above control method, the step of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature" further includes:

[0019] If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature, then the outdoor ambient humidity is further obtained;

[0020] The compressed air air conditioning system is controlled to operate in the appropriate mode based on the outdoor ambient temperature and humidity.

[0021] In the preferred embodiment of the above control method, the step of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature and the outdoor ambient humidity" includes:

[0022] If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in compressor cooling mode.

[0023] If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in the second hybrid cooling mode.

[0024] In the preferred embodiment of the above control method, the step of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature and the outdoor ambient humidity" further includes:

[0025] If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in air cooling mode.

[0026] If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in indirect evaporative cooling mode.

[0027] In a preferred embodiment of the above control method, the control method further includes:

[0028] When the compressed air air conditioning system is operating in air cooling mode, the exhaust temperature of the expansion end of the integrated compressor and expander and the current power of the air supply fan of the compressed air air conditioning system are obtained.

[0029] If the exhaust temperature at the expansion end of the integrated compressor-expander is greater than the preset exhaust temperature and the current power of the blower of the compressed air air conditioning system has reached the maximum power, then the compressed air air conditioning system is controlled to operate in the first mixed cooling mode.

[0030] In a preferred embodiment of the above control method, the control method further includes:

[0031] When the compressed air air conditioning system is operating in indirect evaporative cooling mode, the current supply air temperature and the current power of the spray system of the first indirect evaporative cooler are obtained.

[0032] If the current supply air temperature is greater than the target supply air temperature and the current power of the spray system of the first indirect evaporative cooler has reached its maximum power, then the compressed air air conditioning system is controlled to operate in the third hybrid cooling mode.

[0033] In a preferred embodiment of the above control method, the control method further includes:

[0034] When the compressed air air conditioning system is operating in the third hybrid cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained again.

[0035] If the current supply air temperature is greater than the target supply air temperature and the current power of the supply air fan of the compressed air air conditioning system has reached its maximum power, then the compressed air air conditioning system is controlled to operate in the fourth hybrid cooling mode.

[0036] With the above technical solution adopted, the compressed air air conditioning system of the present invention includes a recirculating cooler, a centrifuge, a first indirect evaporative cooler, a compression-expansion integrated machine, a second indirect evaporative cooler, a bypass branch, and a refrigerant circulation loop. The recirculating cooler includes a first recirculating pipe and a second recirculating pipe, which are capable of heat exchange. The inlet end of the first recirculating pipe is connected to the indoor unit, and the outlet end of the first recirculating pipe is connected to the inlet end of the centrifuge. The outlet end of the centrifuge is connected to the inlet end of the first indirect evaporative cooler, and the outlet end of the first indirect evaporative cooler is connected to the inlet of the compression end of the compression-expansion integrated machine. A first control valve is provided between the outlet end of the first indirect evaporative cooler and the inlet of the compression end of the compression-expansion integrated machine. The exhaust port of the compression end of the integrated compressor-expansion unit is connected to the inlet end of the second indirect evaporative cooler. The exhaust port of the second indirect evaporative cooler is connected to the inlet end of the second return cooling pipe. The exhaust port of the second return cooling pipe is connected to the inlet port of the expansion end of the integrated compressor-expansion unit. One end of the bypass branch is connected between the first indirect evaporative cooler and the first control valve. The other end of the bypass branch is connected to the exhaust port of the expansion end of the integrated compressor-expansion unit. A second control valve is provided on the bypass branch. A compressor, a condenser, a throttling component, and an evaporator are sequentially arranged on the refrigerant circulation loop. The evaporator is located at the exhaust port of the expansion end of the integrated compressor-expansion unit and downstream of the bypass branch. The exhaust port of the expansion end of the integrated compressor-expansion unit is connected to the indoor unit. Based on the above structural configuration, firstly, this invention utilizes air as a refrigerant for heat exchange to achieve green cooling. Air is non-toxic, harmless, and environmentally friendly, and its resources are abundant and easy to obtain, saving on procurement, transportation, and storage costs. Using air as a refrigerant also eliminates the need for the system to maintain a vacuum state, preventing leaks and effectively reducing production and maintenance costs. Secondly, this invention further enhances heat exchange efficiency and reduces energy consumption by adding a recirculating cooler at the primary compression inlet and secondary cooling outlet. Furthermore, the integrated compression-expansion unit recovers expansion work as secondary compression input work, further reducing energy consumption. Additionally, the overall structure of this invention is simple, easy to assemble, and has low production costs. Moreover, the compressed air air conditioning system of this invention employs a two-stage compression and two-stage heat dissipation method to maximize the heat exchange efficiency of the compressed air air conditioning system. Based on the above structural configuration, the control method of this invention includes: acquiring the outdoor ambient temperature and controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature, so that the compressed air air conditioning system can always maintain a high-efficiency operating state, thereby minimizing energy consumption. Attached Figure Description

[0037] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

[0038] Figure 1 This is a schematic diagram of the overall structure of the compressed air air conditioning system of the present invention;

[0039] Figure 2 This is a schematic diagram of the internal structure of the integrated compression and expansion machine of the present invention;

[0040] Figure 3 This is a flowchart of the main steps of the control method of the present invention;

[0041] Figure 4 This is a flowchart illustrating the specific steps of the first preferred embodiment of the present invention;

[0042] Figure 5 This is a flowchart illustrating the specific steps of the second preferred embodiment of the present invention;

[0043] Figure 6 This is a flowchart illustrating the specific steps of the third preferred embodiment of the present invention;

[0044] Figure label:

[0045] 11. Cooler; 111. First cooler piping; 112. Second cooler piping;

[0046] 12. Centrifuge;

[0047] 13. First indirect evaporative cooler; 131. First shell; 132. First spray component; 133. First water pump;

[0048] 14. Compression and expansion integrated machine; 141. Compression impeller; 142. Expansion impeller; 143. Connecting shaft;

[0049] 15. Second indirect evaporative cooler; 151. Second shell; 152. Second spray assembly; 153. Second water pump;

[0050] 16. First control valve;

[0051] 17. Bypass branch; 171. Second control valve;

[0052] 18. Refrigerant circulation loop; 181. Compressor; 182. Condenser; 183. Throttling component; 184. Evaporator;

[0053] 101. Computer Room. Detailed Implementation

[0054] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the invention and are not intended to limit the scope of protection of the invention. Those skilled in the art can make adjustments as needed to adapt to specific applications. For example, although the compressed air air conditioning system in this preferred embodiment is used to cool a computer room, this is clearly not limiting; that is, the present invention does not impose any restrictions on the specific application scenario of the compressed air air conditioning system, and those skilled in the art can select one according to actual usage requirements. Such changes regarding specific application scenarios do not deviate from the basic principles of the present invention and should fall within the scope of protection of the present invention.

[0055] It should be noted that in the description of this invention, terms such as "upper," "lower," "left," and "right," indicating directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are used solely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. Furthermore, the terms "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0056] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "connected" should be interpreted broadly. For example, they can refer to a direct connection, an indirect connection through an intermediate medium, or a connection within two elements. Those skilled in the art can understand the specific meaning of these terms in this invention according to the specific circumstances. Although the steps of the control method of this invention are described in a specific order in this application, this order is not restrictive. Those skilled in the art can perform the steps in different orders without departing from the basic principles of this invention.

[0057] First refer to Figure 1 This figure is a schematic diagram of the overall structure of the compressed air air conditioning system of the present invention. Figure 1As shown, the arrows indicate the direction of medium flow. The compressed air air conditioning system of the present invention includes a recirculating cooler 11, a centrifuge 12, a first indirect evaporative cooler 13, a compression-expansion integrated unit 14, a second indirect evaporative cooler 15, and a first control valve 16. The recirculating cooler 11 includes a first recirculating pipe 111 and a second recirculating pipe 112, which are capable of heat exchange. As a preferred configuration, the first recirculating pipe 111 is U-shaped, and the second recirculating pipe 112 is L-shaped. A portion of the second recirculating pipe 112 is located between two parallel pipes of the first recirculating pipe 111 to effectively improve heat exchange efficiency. Of course, this configuration is only a preferred configuration; technicians can also customize the specific structure and positional relationship of the first recirculating pipe 111 and the second recirculating pipe 112 according to actual usage requirements, as long as heat exchange is possible. In addition, the inlet of the first return cooling pipe 111 is connected to the machine room 101, the outlet of the first return cooling pipe 111 is connected to the inlet of the centrifuge 12, the outlet of the centrifuge 12 is connected to the inlet of the first indirect evaporative cooler 13, and the outlet of the first indirect evaporative cooler 13 is connected to the compression end of the integrated compression-expansion machine 14 (i.e., Figure 1 The air inlet of the first indirect evaporator 13 is connected to the air inlet of the compression end of the integrated compressor-expansion unit 14, and the first control valve 16 is located between the exhaust end of the first indirect evaporator 13 and the air inlet of the compression end of the integrated compressor-expansion unit 14. The exhaust end of the compression end of the integrated compressor-expansion unit 14 is connected to the air inlet of the second indirect evaporator 15, and the exhaust end of the second indirect evaporator 15 is connected to the air inlet of the second return cooling pipe 112. The exhaust end of the second return cooling pipe 112 is connected to the air inlet of the expansion end of the integrated compressor-expansion unit 14 (i.e., the left end of the compression end of the integrated compressor-expansion unit 14). Figure 1 The air inlet of the compressor-expander unit 14 is connected to the air inlet at the right end of the compressor-expander unit 14, and the exhaust port of the expansion end of the compressor-expander unit 14 is connected to the machine room 101. A blower (not shown in the figure) is also provided at the connection between the exhaust port of the expansion end of the compressor-expander unit 14 and the machine room 101 to better supply air to the machine room 101. Of course, the specific location of the blower is not limited, as long as it can achieve the air supply effect.

[0058] It should be noted that the present invention does not impose any restrictions on the specific types of each component, and those skilled in the art can set them according to actual usage requirements; for example, the types of the first indirect evaporative cooler 13 and the second indirect evaporative cooler 15 can be the same or different, which is not restrictive.

[0059] Next, refer to Figure 2 This figure is a schematic diagram of the internal structure of the integrated compression and expansion machine of the present invention. Figure 2As shown, in a preferred embodiment, the integrated compressor-expander 14 includes a compression impeller 141, an expansion impeller 142, and a connecting shaft 143 for connecting the compression impeller 141 and the expansion impeller 142. This coaxial arrangement allows the expansion work acquired by the expansion impeller 142 to be effectively transferred to the compression impeller 141 for work recovery, thereby effectively reducing energy consumption. Preferably, the integrated compressor-expander 14 of this invention employs a centrifugal compressor and a centrifugal expander to provide a large air volume, effectively adapting to the requirements of high air volume and low pressure ratio applications, thus effectively improving its working efficiency. It should be noted that the above arrangement is only a preferred structural arrangement; technicians can also customize the specific structure of the integrated compressor-expander 14 according to actual usage requirements, as long as the integrated compressor-expander 14 can achieve the compression and expansion effect.

[0060] Based on the above structural configuration, when the compressed air air conditioning system of the present invention operates in air cooling mode, the compressed air air conditioning system can draw ambient temperature air from the machine room 101. The ambient temperature air is heated by the first return cooling pipe 111 of the return cooler 11 and then enters the centrifuge 12 for primary compression to obtain high temperature and high pressure air. It is then discharged into the first indirect evaporative cooler 13. After the high temperature and high pressure air is cooled by the first indirect evaporative cooler 13, it enters the compression end of the integrated compressor-expansion machine 14 for secondary compression to obtain higher pressure and high temperature air. It is then discharged into the second indirect evaporative cooler 15. After the high temperature and high pressure air is cooled by the second indirect evaporative cooler 15, it enters the second return cooling pipe 112 of the return cooler 11 to exchange heat with the ambient temperature air from the machine room 101 in the first return cooling pipe 111, thereby further cooling down the air. It then enters the expansion end of the integrated compressor-expansion machine 14 to be throttled into low temperature and normal pressure air, and then discharged into the machine room 101, thereby cooling down the machine room 101.

[0061] Furthermore, as a preferred configuration, taking the specific structure of the first indirect evaporative cooler 13 as an example, the first indirect evaporative cooler 13 includes a first housing 131 and a first spray system. A first cooling chamber (not shown in the figure) is formed in the first housing 131. Of course, the present invention does not impose any restrictions on the specific shape of the first cooling chamber. The pipes of the compressed air air conditioning system pass through the first cooling chamber, allowing external air to enter the first cooling chamber so that the air introduced into the first indirect evaporative cooler 13 through the centrifuge 12 can exchange heat with the external air in the first cooling chamber through the pipes to achieve cooling. It should be noted that although the first housing 131 in this preferred embodiment is a quadrangular prism, this is not limiting. Those skilled in the art can set the specific shape of the first housing 131 according to actual usage requirements. In addition, the first spray system can spray water into the first cooling chamber to further cool the air. Specifically, the first spray system includes a first spray component 132 and a first water pump 133. The first spray component 132 has an elongated structure and is equipped with multiple nozzles. The first water pump 133 supplies water to the first spray component 132, and the water in the first spray component 132 is sprayed into the first cooling chamber through the multiple nozzles to further enhance the cooling effect. Furthermore, the second indirect evaporative cooler 15 includes a second housing 151 and a second spray system. A second cooling chamber is formed in the second housing 151. The second spray system includes a second spray component 152 and a second water pump 153, and its specific structure is the same as that of the first indirect evaporative cooler 13, so it will not be described again here. It should be noted that the present invention does not impose any limitations on the specific structure of the first indirect evaporative cooler 13 and the second indirect evaporative cooler 15. Those skilled in the art can set it according to actual usage requirements, as long as it includes a spray system capable of spray cooling.

[0062] Based on the above structural configuration, when the external ambient temperature is low, the cooling capacity of the first indirect evaporative cooler 13 and the second indirect evaporative cooler 15 is sufficient to meet the heat dissipation requirements. In this case, there is no need to activate the spray system, thus effectively saving energy. However, when the external ambient temperature is high, the cooling capacity of the first indirect evaporative cooler 13 and the second indirect evaporative cooler 15 is insufficient to meet the heat dissipation requirements. In this case, at least one of the spray systems is activated to effectively improve the cooling effect. In other words, based on the spray system configuration, the compressed air air conditioning system can still effectively guarantee the cooling effect when the external ambient temperature is high.

[0063] Continue reading Figure 1 ,like Figure 1As shown, the compressed air air conditioning system also includes a bypass branch 17. The left end of the bypass branch 17 is connected between the first indirect evaporative cooler 13 and the first control valve 16, and the right end of the bypass branch 17 is connected to the exhaust port of the expansion end of the integrated compressor-expander 14. It should be noted that the present invention does not impose any restrictions on the specific connection positions of the two ends of the bypass branch 17; those skilled in the art can set them according to actual usage requirements. For example, the right end of the bypass branch 17 can be directly connected to the exhaust port of the expansion end of the integrated compressor-expander 14, or it can be connected to an exhaust branch connected to the exhaust port of the expansion end of the integrated compressor-expander 14; these are not limiting factors. Furthermore, a second control valve 171 is provided on the bypass branch 17 to control the connection state of the bypass branch 17. It should be noted that the present invention does not impose any restrictions on the specific type of the second control valve 171; those skilled in the art can set it according to actual usage requirements, as long as it can control the connection state of the bypass branch 17. Preferably, the second control valve 171 is an electronic expansion valve.

[0064] Furthermore, the compressed air air conditioning system of the present invention also includes a refrigerant circulation loop 18. A compressor 181, a condenser 182, a throttling component 183, and an evaporator 184 are sequentially arranged on the refrigerant circulation loop 18. The evaporator 184 is located at the exhaust port of the expansion end of the integrated compressor-expansion unit 14 and downstream of the bypass branch 17. This means that air flowing through the bypass branch can also exchange heat through the evaporator 184. When the refrigerant circulation loop 18 is operating, the evaporator 184 can further cool the air about to enter the machine room 101. Of course, those skilled in the art can adjust the specific structure of the refrigerant circulation loop 18 according to actual usage requirements, as long as the evaporator 184 can cool the air about to enter the machine room 101.

[0065] Based on the above structural configuration, the compressed air air conditioning system of the present invention can operate in the following eight working modes:

[0066] 1. Natural ventilation cooling mode: When running this mode, the second control valve 171 is opened, the two spray systems and the first control valve 16 are closed, and the refrigerant circulation loop 18 is not running. The centrifuge 12 sends the air in the machine room 101 into the first indirect evaporative cooler 13 for cooling and then sends it back to the machine room 101 directly through the second control valve 171.

[0067] 2. Air cooling mode: When running this mode, the first control valve 16 is opened, the two spray systems and the second control valve 171 are closed, and the refrigerant circulation loop 18 is not running. The air is sent back to the machine room 101 after two stages of compression, two stages of heat dissipation and expansion cooling.

[0068] 3. Indirect Evaporation Mode: When operating in this mode, the first spray system and the second control valve 171 are opened, the second spray system and the first control valve 16 are closed, and the refrigerant circulation loop 18 is not running. The centrifuge 12 sends the air in the machine room 101 into the first indirect evaporative cooler 13 for spray cooling and then sends it back to the machine room 101 directly through the second control valve 171.

[0069] 4. Compressor refrigeration mode: When running this mode, open the second control valve 171, close the two spray systems and the first control valve 16, and run the refrigerant circulation loop 18. The centrifuge 12 first sends the air in the machine room 101 into the first indirect evaporator 13 for cooling, then enters the evaporator 184 through the second control valve 171 for further cooling, and finally sends it back to the machine room 101.

[0070] 5. First Mixed Cooling Mode: When running this mode, the first control valve 16 is opened, the two spray systems and the second control valve 171 are closed, and the refrigerant circulation loop 18 is running. After two stages of compression, two stages of heat dissipation and expansion cooling, the air enters the evaporator 184 for further cooling and is finally sent back to the machine room 101.

[0071] 6. Second hybrid cooling mode: When operating this mode, the first spray system and the second control valve 171 are opened, the second spray system and the first control valve 16 are closed, and the refrigerant circulation loop 18 is running. After the centrifuge 12 sends the air in the machine room 101 into the first indirect evaporator 13 for spray cooling, it then enters the evaporator 184 through the second control valve 171 for further cooling, and finally sends it back to the machine room 101.

[0072] 7. Third hybrid cooling mode: When running this mode, the first control valve 16 and the two spray systems are opened, the second control valve 171 is closed, and the refrigerant circulation loop 18 is not running. The air is sent back to the machine room 101 after passing through two stages of compression, two stages of spray heat dissipation and expansion cooling.

[0073] 8. Fourth Hybrid Cooling Mode: When running this mode, the first control valve 16 and the two spray systems are opened, the second control valve 171 is closed, and the refrigerant circulation loop 18 is running. After two stages of compression, two stages of spray heat dissipation and expansion cooling, the air enters the evaporator 184 for further cooling and is finally sent back to the machine room 101.

[0074] Based on the above eight operating modes, the compressed air air conditioning system of the present invention can select the corresponding operating mode according to actual needs, so as to reduce energy consumption while maximizing the cooling effect of the compressed air air conditioning system.

[0075] Furthermore, the compressed air air conditioning system of the present invention also includes multiple temperature sensors and a controller. The controller is capable of acquiring detection data from the multiple temperature sensors and controlling the operating status of the compressed air air conditioning system. For example, it can control the operating mode of the compressed air air conditioning system, control the connection status of each bypass branch, and control the operating power of the compressor, the blower, and the spray system. Of course, those skilled in the art will understand that the present invention does not impose any limitations on the specific structure and model of the controller, and the controller can be either the original controller of the compressed air air conditioning system or a controller specifically designed to execute the control method of the present invention. Those skilled in the art can customize the structure and model of the controller according to actual usage requirements.

[0076] Based on the above structural configuration, the control method of the present invention includes: acquiring the outdoor ambient temperature; and controlling the compressed air air conditioning system to operate in a corresponding mode according to the outdoor ambient temperature. It should be noted that the present invention does not impose any limitations on its specific control method; those skilled in the art can set it according to actual usage requirements. For example, control can be performed by comparing the outdoor ambient temperature with a preset value; or, for example, control can be performed based on the temperature range of the outdoor ambient temperature. These are not limiting factors.

[0077] See next Figure 3 This diagram is a flowchart of the main steps of the control method of the present invention. Figure 3 As shown, based on the compressed air air conditioning system described in the above preferred embodiment, the control method of the present invention mainly includes the following steps:

[0078] S11: Obtain indoor temperature;

[0079] S12: Determine if the indoor temperature is greater than the target indoor temperature; if yes, proceed to step S13; if no, proceed to step S11 again.

[0080] S13: Start the compressed air air conditioning system;

[0081] S14: Obtain the outdoor ambient temperature;

[0082] S15: Determine whether the outdoor ambient temperature is lower than the first preset outdoor ambient temperature; if yes, proceed to step S16; if no, proceed to step S17.

[0083] S16: Controls the compressed air air conditioning system to operate in natural ventilation cooling mode;

[0084] S17: Obtain outdoor ambient humidity;

[0085] S18: Determine whether the outdoor ambient temperature is lower than the second preset outdoor ambient temperature; if yes, proceed to step S19; if no, proceed to step S22.

[0086] S19: Determine whether the outdoor ambient humidity is lower than the preset outdoor ambient humidity; if yes, proceed to step S20; if no, proceed to step S21.

[0087] S20: Controls the compressed air air conditioning system to operate in the second hybrid cooling mode;

[0088] S21: Controls the operation of the compressed air air conditioning system in compressor cooling mode;

[0089] S22: Determine whether the outdoor ambient humidity is lower than the preset outdoor ambient humidity; if yes, proceed to step S23; if no, proceed to step S24.

[0090] S23: Controls the operation of the compressed air air conditioning system in indirect evaporative cooling mode;

[0091] S24: Controls the compressed air air conditioning system to operate in air cooling mode.

[0092] First, in steps S11 to S13, the controller acquires the indoor temperature (i.e., the temperature in the machine room 101) to control the on / off state of the compressed air conditioning system accordingly. Specifically, the compressed air conditioning system is turned on when the indoor temperature is greater than the target indoor temperature. Of course, this invention does not impose any restrictions on the target indoor temperature; it can be user-set or automatically set by the system. More preferably, during the operation of the compressed air conditioning system, if the indoor temperature is less than or equal to the target indoor temperature, the compressed air conditioning system is automatically turned off.

[0093] Next, in steps S14 to S17, when the compressed air air conditioning system is turned on, the controller acquires the outdoor ambient temperature (the acquisition method is not limited) to control the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature. Specifically, if the outdoor ambient temperature is lower than the first preset outdoor ambient temperature, the controller controls the compressed air air conditioning system to operate in natural ventilation cooling mode, so as to maximize energy saving while ensuring cooling effect. Simultaneously, if the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature, the controller further acquires the outdoor ambient humidity, so as to control the operation mode of the compressed air air conditioning system according to both the outdoor ambient temperature and the outdoor ambient humidity, thereby effectively improving the accuracy of the judgment. It should be noted that the present invention does not impose any restrictions on the specific value of the first preset outdoor ambient temperature; those skilled in the art can set it according to actual usage needs. Preferably, the first preset outdoor ambient temperature is set to 10°C.

[0094] Finally, in steps S18 to S24, the controller can further compare the outdoor ambient temperature with the second preset outdoor ambient temperature and compare the outdoor ambient humidity with the preset outdoor ambient humidity, so as to control the compressed air air conditioning system to operate in the corresponding mode. Specifically, 1. If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in compressor cooling mode; 2. If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in second hybrid cooling mode; 3. If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in air cooling mode; 4. If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate indirect evaporative cooling mode. It should be noted that the present invention does not impose any restrictions on the specific values ​​of the second preset outdoor ambient temperature and the preset outdoor ambient humidity. Technicians can set them according to actual usage requirements. Preferably, the second preset outdoor ambient temperature is set to 20°C, and the preset outdoor ambient humidity is the saturation humidity corresponding to the exhaust temperature of the compression end of the integrated compression and expansion machine 14.

[0095] See below. Figure 4This figure is a flowchart illustrating the specific steps of the first preferred embodiment of the present invention. Figure 4 As shown, based on the compressed air air conditioning system described in the above preferred embodiment, the first preferred embodiment of the control method of the present invention specifically includes 20 steps as shown in the figure. According to the main step flowchart of the present invention, when the outdoor ambient temperature is lower than the first preset outdoor ambient temperature, the controller will control the compressed air air conditioning system to operate in natural ventilation cooling mode. Based on this, when the compressed air air conditioning system is operating in natural ventilation cooling mode, step S101 and subsequent steps are executed.

[0096] In steps S101 to S105, the controller can acquire the current supply air temperature of the compressed air air conditioning system, and adjust the operating power of the supply air fan accordingly based on the acquired current supply air temperature, thereby effectively improving heat exchange efficiency. It should be noted that the present invention does not impose any restrictions on the specific method of acquiring the target supply air temperature. For example, it can be set by the user or automatically set by the system according to other control logic; preferably, the target supply air temperature is set to 15℃. As a preferred control method, direct comparison is used for corresponding control to effectively improve control efficiency. Specifically, if the current supply air temperature is equal to the target supply air temperature, the operating power of the supply air fan is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the current supply air temperature is less than the target supply air temperature, the operating power of the supply air fan is reduced to achieve energy saving.

[0097] Further, if the current supply air temperature is greater than the target supply air temperature, then step S106 is executed, i.e., the current power of the supply air fan is obtained. In steps S107 to S109, if the current power of the supply air fan has not reached the maximum power that the supply air fan can operate at, then the operating power of the supply air fan can be increased; if the current power of the supply air fan has reached the maximum power that the supply air fan can operate at, then the compressed air air conditioning system is controlled to operate in air cooling mode in order to effectively ensure the cooling effect.

[0098] When the compressed air air conditioning system is operating in air cooling mode, the operating power of the supply air fan can be automatically adjusted according to other control logic. After running for a period of time, the controller can obtain the current supply air temperature again, so as to adjust the operating power of the supply air fan accordingly based on the newly obtained current supply air temperature, thereby effectively improving heat exchange efficiency. As a preferred control method, in steps S111 to S114, if the newly obtained current supply air temperature is equal to the target supply air temperature, the operating power of the supply air fan is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the newly obtained current supply air temperature is less than the target supply air temperature, the operating power of the supply air fan is reduced, so as to achieve the effect of saving energy consumption.

[0099] Furthermore, if the current supply air temperature is again greater than the target supply air temperature, then step S115 is executed, that is, the current power of the supply air fan is again obtained. In steps S116 to S118, if the current power of the supply air fan is not the maximum power that the supply air fan can operate at, then the operating power of the supply air fan is increased; if the current power of the supply air fan has reached the maximum power that the supply air fan can operate at, then the compressed air air conditioning system is controlled to operate in the first hybrid cooling mode in order to effectively ensure the cooling effect.

[0100] When the compressed air air conditioning system is operating in the first hybrid cooling mode, after the compressed air air conditioning system has been running for a period of time, the controller acquires the current supply air temperature again, so as to control the operating power of the compressor 181 accordingly based on the newly acquired current supply air temperature. As a preferred control method, if the newly acquired current supply air temperature is equal to the target supply air temperature, the operating power of the compressor 181 is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the newly acquired current supply air temperature is less than the target supply air temperature, the operating power of the compressor 181 is reduced, so as to achieve the effect of saving energy; if the newly acquired current supply air temperature is greater than the target supply air temperature, the operating power of the compressor 181 is increased, so as to effectively ensure the cooling effect.

[0101] See below. Figure 5 This figure is a flowchart illustrating the specific steps of the second preferred embodiment of the present invention. Figure 5As shown, based on the compressed air air conditioning system described in the above preferred embodiment, the second preferred embodiment of the control method of the present invention specifically includes 15 steps as shown in the figure. According to the main step flowchart of the present invention, when the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, the controller will control the compressed air air conditioning system to operate in air cooling mode. Based on this, when the compressed air air conditioning system is operating in air cooling mode, step S201 and subsequent steps are executed.

[0102] Specifically, in steps S201 to S205, the controller can obtain the exhaust temperature of the expansion end of the integrated compression and expansion unit 14, so as to adjust the operating power of the blower according to the obtained exhaust temperature, thereby improving the heat exchange efficiency. It should be noted that the present invention does not impose any restrictions on the specific value of the preset exhaust temperature; preferably, the preset exhaust temperature is set to 15°C. As a preferred control method, direct comparison is used for corresponding control to effectively improve control efficiency. Specifically, if the exhaust temperature is equal to the preset exhaust temperature, the operating power of the blower is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the exhaust temperature is less than the preset exhaust temperature, the operating power of the blower is reduced to achieve energy saving.

[0103] Further, if the exhaust temperature is greater than the preset exhaust temperature, then step S206 is executed, that is, the controller obtains the current power of the air supply fan. In steps S207 to S209, if the current power of the air supply fan has not reached the maximum power that the air supply fan can operate at, then the operating power of the air supply fan can be increased; while if the current power of the air supply fan has reached the maximum power that the air supply fan can operate at, then the controller controls the compressed air air conditioning system to operate in the first hybrid cooling mode in order to effectively ensure the cooling effect.

[0104] When the compressed air air conditioning system is operating in the first hybrid cooling mode, after the compressed air air conditioning system has been running for a period of time, the controller obtains the current supply air temperature so as to control the operating power of the compressor 181 accordingly. As a preferred control method, in steps S211 to S215, if the current supply air temperature is equal to the target supply air temperature, the operating power of the compressor 181 is not adjusted so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the current supply air temperature is less than the target supply air temperature, the operating power of the compressor 181 is reduced to achieve the effect of saving energy; if the current supply air temperature is greater than the target supply air temperature, the operating power of the compressor 181 is increased to effectively ensure the cooling effect.

[0105] See last for reference. Figure 6 This figure is a flowchart illustrating the specific steps of the third preferred embodiment of the present invention. Figure 6 As shown, based on the compressed air air conditioning system described in the above preferred embodiment, the third preferred embodiment of the control method of the present invention specifically includes 20 steps as shown in the figure. According to the main step flowchart of the present invention, when the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, the controller controls the compressed air air conditioning system to operate in indirect evaporative cooling mode. Based on this, when the compressed air air conditioning system is operating in indirect evaporative cooling mode, step S301 and subsequent steps are executed.

[0106] In steps S301 to S305, the controller can obtain the current supply air temperature of the compressed air air conditioning system, and adjust the operating power of the first spray system of the first indirect evaporative cooler 13 accordingly based on the obtained current supply air temperature, thereby effectively improving heat exchange efficiency. As a preferred control method, corresponding control is performed directly by comparison to effectively improve control efficiency. Specifically, if the current supply air temperature is equal to the target supply air temperature, the operating power of the first spray system is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the current supply air temperature is less than the target supply air temperature, the operating power of the first spray system is reduced to achieve energy saving.

[0107] Further, if the current supply air temperature is greater than the target supply air temperature, then step S306 is executed, i.e., the current power of the first spray system is obtained. In steps S307 to S309, if the current power of the first spray system has not reached the maximum power that the first spray system can operate at, then the operating power of the first spray system can be increased; it should be noted that the operating power of the first spray system can be represented by the power of the first water pump 133, or it can be represented by other means, which are not limiting, as long as it can represent the cooling capacity of the first spray system. If the current power of the first spray system has reached the maximum power that the first spray system can operate at, then the compressed air air conditioning system is controlled to operate in the third hybrid cooling mode in order to effectively ensure the cooling effect.

[0108] When the compressed air air conditioning system is operating in the third hybrid cooling mode, after running for a period of time, the controller can obtain the current supply air temperature again, so as to adjust the operating power of the supply air fan accordingly based on the newly obtained current supply air temperature, thereby effectively improving the heat exchange efficiency. As a preferred control method, in steps S311 to S314, if the newly obtained current supply air temperature is equal to the target supply air temperature, the operating power of the supply air fan is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the newly obtained current supply air temperature is less than the target supply air temperature, the operating power of the supply air fan is reduced, so as to achieve the effect of saving energy consumption.

[0109] Furthermore, if the current supply air temperature is again greater than the target supply air temperature, then step S315 is executed, that is, the controller obtains the current power of the supply air fan. In steps S316 to S318, if the current power of the supply air fan has not reached the maximum power that the supply air fan can operate at, then the operating power of the supply air fan can be increased; while if the current power of the supply air fan has reached the maximum power that the supply air fan can operate at, then the compressed air air conditioning system is controlled to operate in the fourth hybrid cooling mode in order to effectively ensure the cooling effect.

[0110] When the compressed air air conditioning system is operating in the fourth hybrid cooling mode, after the compressed air air conditioning system has been running for a period of time, the controller acquires the current supply air temperature again, so as to control the operating power of the compressor 181 accordingly based on the newly acquired current supply air temperature. As a preferred control method, if the newly acquired current supply air temperature is equal to the target supply air temperature, the operating power of the compressor 181 is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the newly acquired current supply air temperature is less than the target supply air temperature, the operating power of the compressor 181 is reduced, so as to achieve the effect of saving energy; if the newly acquired current supply air temperature is greater than the target supply air temperature, the operating power of the compressor 181 is increased, so as to effectively ensure the cooling effect.

[0111] Furthermore, in this preferred embodiment, based on the main steps flowchart of the present invention, when the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, the controller controls the compressed air air conditioning system to operate in compressor cooling mode; when the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, the controller controls the compressed air air conditioning system to operate in a second hybrid cooling mode. During the operation of the compressed air air conditioning system in the above two modes, the controller can obtain the current supply air temperature so as to control the operating power of the compressor 181 accordingly based on the obtained current supply air temperature. As a preferred control method, if the current supply air temperature is equal to the target supply air temperature, the operating power of the compressor 181 is not adjusted, so as to effectively maintain the cooling effect while ensuring cooling efficiency; if the current supply air temperature is less than the target supply air temperature, the operating power of the compressor 181 is reduced to save energy; if the current supply air temperature is greater than the target supply air temperature, the operating power of the compressor 181 is increased to effectively ensure the cooling effect.

[0112] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A control method for a compressed air air conditioning system, characterized in that, The compressed air air conditioning system includes a recirculating cooler, a centrifuge, a first indirect evaporative cooler, a compressor-expander unit, a second indirect evaporative cooler, a bypass branch, and a refrigerant circulation loop. The recirculating cooler includes a first recirculating cooler pipe and a second recirculating cooler pipe, which are capable of heat exchange. The inlet of the first recirculating cooler pipe is connected to the indoor unit, and the outlet of the first recirculating cooler pipe is connected to the inlet of the centrifuge. The outlet of the centrifuge is connected to the inlet of the first indirect evaporative cooler, and the outlet of the first indirect evaporative cooler is connected to the inlet of the compressor-expander unit. A first control valve is provided between the outlet of the first indirect evaporative cooler and the inlet of the compressor-expander unit. The exhaust port of the compressor end is connected to the inlet end of the second indirect evaporative cooler. The exhaust port of the second indirect evaporative cooler is connected to the inlet end of the second return cooling pipe. The exhaust port of the second return cooling pipe is connected to the inlet port of the expansion end of the integrated compressor-expansion unit. One end of the bypass branch is connected between the first indirect evaporative cooler and the first control valve. The other end of the bypass branch is connected to the exhaust port of the expansion end of the integrated compressor-expansion unit. A second control valve is provided on the bypass branch. A compressor, a condenser, a throttling component, and an evaporator are sequentially arranged on the refrigerant circulation loop. The evaporator is located at the exhaust port of the expansion end of the integrated compressor-expansion unit and downstream of the bypass branch. The exhaust port of the expansion end of the integrated compressor-expansion unit is connected to the indoor unit. The control method includes: Obtain the outdoor ambient temperature; Based on the outdoor ambient temperature, the compressed air air conditioning system is controlled to operate in a corresponding mode; the steps include: if the outdoor ambient temperature is greater than or equal to a first preset outdoor ambient temperature, then the outdoor ambient humidity is further acquired; based on the outdoor ambient temperature and the outdoor ambient humidity, the compressed air air conditioning system is controlled to operate in a corresponding mode; the steps include: If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in compressor cooling mode. If the outdoor ambient temperature is greater than or equal to the first preset outdoor ambient temperature and less than the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in the second hybrid cooling mode. The second hybrid refrigeration mode involves opening the spray system and the second control valve of the first indirect evaporative cooler, closing the spray system and the first control valve of the second indirect evaporative cooler, and operating the refrigerant circulation loop. The compressor refrigeration mode is characterized by opening the second control valve, closing the spray system of the first indirect evaporator, closing the spray system of the second indirect evaporator, and operating the first control valve, while the refrigerant circulation loop is running.

2. The control method according to claim 1, characterized in that, The steps of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature" include: If the outdoor ambient temperature is lower than the first preset outdoor ambient temperature, the compressed air air conditioning system is controlled to operate in natural ventilation cooling mode.

3. The control method according to claim 2, characterized in that, The control method further includes: When the compressed air air conditioning system is operating in natural ventilation cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained. If the current supply air temperature is greater than the target supply air temperature and the current power of the compressed air air conditioning system's supply fan has reached its maximum power, then the compressed air air conditioning system is controlled to operate in air cooling mode. The air cooling mode involves opening the first control valve, closing the spray system of the first indirect evaporative cooler, closing the spray system of the second indirect evaporative cooler, and closing the second control valve, while the refrigerant circulation loop is not running.

4. The control method according to claim 3, characterized in that, The control method further includes: When the compressed air air conditioning system is operating in air cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained again. If the current supply air temperature is still greater than the target supply air temperature and the current power of the compressed air air conditioning system's supply fan has reached its maximum power, then the compressed air air conditioning system is controlled to operate in the first hybrid cooling mode. In the first hybrid refrigeration mode, the first control valve is opened, the spray system of the first indirect evaporative cooler is closed, the spray system of the second indirect evaporative cooler and the second control valve are closed, and the refrigerant circulation loop is running.

5. The control method according to claim 1, characterized in that, The step of "controlling the operation mode of the compressed air air conditioning system according to the outdoor ambient temperature and the outdoor ambient humidity" further includes: If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is greater than or equal to the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in air cooling mode. If the outdoor ambient temperature is greater than or equal to the second preset outdoor ambient temperature, and the outdoor ambient humidity is less than the preset outdoor ambient humidity, then the compressed air air conditioning system is controlled to operate in indirect evaporative cooling mode. The indirect evaporative cooling mode involves opening the spray system and the second control valve of the first indirect evaporative cooler, closing the spray system and the first control valve of the second indirect evaporative cooler, and not operating the refrigerant circulation loop.

6. The control method according to claim 5, characterized in that, The control method further includes: When the compressed air air conditioning system is operating in air cooling mode, the exhaust temperature of the expansion end of the integrated compressor and expander and the current power of the air supply fan of the compressed air air conditioning system are obtained. If the exhaust temperature at the expansion end of the integrated compressor-expander is greater than the preset exhaust temperature and the current power of the blower of the compressed air air conditioning system has reached the maximum power, then the compressed air air conditioning system is controlled to operate in the first hybrid cooling mode. In the first hybrid refrigeration mode, the first control valve is opened, the spray system of the first indirect evaporative cooler is closed, the spray system of the second indirect evaporative cooler and the second control valve are closed, and the refrigerant circulation loop is running.

7. The control method according to claim 5, characterized in that, The control method further includes: When the compressed air air conditioning system is operating in indirect evaporative cooling mode, the current supply air temperature and the current power of the spray system of the first indirect evaporative cooler are obtained. If the current supply air temperature is greater than the target supply air temperature and the current power of the spray system of the first indirect evaporative cooler has reached the maximum power, then control the compressed air air conditioning system to operate in the third hybrid cooling mode. The third hybrid refrigeration mode is as follows: the first control valve and the spray system of the first indirect evaporator are opened, the spray system of the second indirect evaporator is opened, the second control valve is closed, and the refrigerant circulation loop is not running.

8. The control method according to claim 7, characterized in that, The control method further includes: When the compressed air air conditioning system is operating in the third hybrid cooling mode, the current supply air temperature and the current power of the supply air fan of the compressed air air conditioning system are obtained again. If the current supply air temperature is greater than the target supply air temperature and the current power of the supply air fan of the compressed air air conditioning system has reached the maximum power, then control the compressed air air conditioning system to operate in the fourth hybrid cooling mode. The fourth hybrid refrigeration mode is as follows: the first control valve and the spray system of the first indirect evaporator are opened, the spray system of the second indirect evaporator is opened, the second control valve is closed, and the refrigerant circulation loop is running.

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