A superimposed composite air conditioning system

Abstract

This utility model provides a superimposed composite air conditioning system, which includes a first-cycle refrigeration system and a second-cycle refrigeration system. The first-cycle refrigeration system is connected to the outer refrigerant channel of the evaporator, and the second-cycle refrigeration system is connected to the inner refrigerant channel of the evaporator. The first-cycle refrigeration system and the second-cycle refrigeration system can switch between multiple operating modes according to the real-time outdoor temperature. By setting up two independent and coordinated refrigeration cycle systems, the air conditioning system can operate in compression refrigeration mode, dual-pump supplemental cooling mode, and refrigerant pump natural cooling mode. Based on real-time monitoring of the outdoor temperature and combined with changes in indoor load demand, the air conditioning system can intelligently switch between the three operating modes, significantly extending the applicable cycle of the natural cooling source and significantly improving energy-saving effect.

Description

Technical Field

[0001] This utility model relates to the technical field of data center temperature control systems, specifically to a superimposed composite air conditioning system. Background Technology

[0002] With the proposal and advancement of information technology projects, the scale and number of data centers have grown rapidly, making them major energy consumers in today's information society. To reduce the energy consumption of data centers, integrated refrigerant pump air conditioning units have gained widespread application. These units utilize refrigerant pump technology, enabling deep utilization of natural cooling sources and achieving high energy efficiency. However, traditional integrated refrigerant pump air conditioning units currently have a short utilization time of outdoor cooling sources; the pure refrigerant pump mode can only be activated when the outdoor real-time temperature is below 10℃. Furthermore, the cooling capacity distribution of the parallel-distributed evaporator coils is uneven, making precise control of the supply air temperature difficult. Therefore, a new solution is needed to address the shortcomings and deficiencies of the existing technology. Utility Model Content

[0003] In order to overcome the shortcomings and deficiencies of the existing technology, this utility model proposes a superimposed composite air conditioning system.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: A superimposed composite air conditioning system, the system comprising a first cycle refrigeration system and a second cycle refrigeration system, wherein, The first refrigeration cycle system includes a first compressor, the discharge port of the first compressor being connected to the inlet of a first condenser, the outlet of the first condenser being connected to the inlet of a first liquid receiver, the outlet of the first liquid receiver being connected to the inlet of a first refrigerant pump, the outlet of the first refrigerant pump being connected to the inlet of a first electronic expansion valve, the outlet of the first electronic expansion valve being connected to the refrigerant passage inlet of an evaporator, and the refrigerant passage outlet of the evaporator being connected to the suction port of the first compressor. The second cycle refrigeration system includes a second compressor. The discharge port of the second compressor is connected to the inlet of a second condenser. The outlet of the second condenser is connected to the inlet of a second liquid receiver. The outlet of the second liquid receiver is connected to the inlet of a second refrigerant pump. The outlet of the second refrigerant pump is connected to the inlet of a second electronic expansion valve. The outlet of the second electronic expansion valve is connected to the inlet of the refrigerant passage of the evaporator. The outlet of the refrigerant passage of the evaporator is connected to the suction port of the second compressor. Its features are: The first circulating refrigeration system is connected to the outer refrigerant channel of the evaporator, and the second circulating refrigeration system is connected to the inner refrigerant channel of the evaporator. The first circulating refrigeration system and the second circulating refrigeration system can switch between multiple operating modes according to the real-time outdoor temperature.

[0005] As a further preferred embodiment of the present invention, a first compressor series check valve is connected in series between the exhaust port of the first compressor and the inlet of the first condenser, and a second compressor series check valve is connected in series between the exhaust port of the second compressor and the inlet of the second condenser.

[0006] As a further preferred embodiment of the present invention, a first compressor parallel check valve is provided in parallel between the exhaust port of the first compressor and the inlet of the first condenser, and a second compressor parallel check valve is provided in parallel between the exhaust port of the second compressor and the inlet of the second condenser.

[0007] As a further preferred embodiment of the present invention, a first refrigerant pump series check valve is connected in series between the outlet of the first refrigerant pump and the inlet of the first electronic expansion valve, and a second refrigerant pump series check valve is connected in series between the outlet of the second refrigerant pump and the inlet of the second electronic expansion valve.

[0008] As a further preferred embodiment of the present invention, a first refrigerant pump parallel check valve is provided in parallel between the outlet of the first refrigerant pump and the inlet of the first electronic expansion valve, and a second refrigerant pump parallel check valve is provided in parallel between the outlet of the second refrigerant pump and the inlet of the second electronic expansion valve.

[0009] As a further preferred embodiment of the present invention, the minimum compression ratio of the first compressor and the second compressor is 1.1.

[0010] As a further preferred embodiment of this utility model, the first condenser and the second condenser adopt a waterless condensation method.

[0011] As a further preferred embodiment of the present invention, the first condenser and the second condenser adopt an evaporative condensation method, and a first evaporative condensation component is provided on one side of the first condenser and a second evaporative condensation component is provided on one side of the second condenser.

[0012] As a further preferred embodiment of the present invention, the air conditioning system can operate in compression refrigeration mode, dual-pump supplemental cooling mode, or refrigerant pump natural cooling mode.

[0013] As a further preferred embodiment of this utility model, When the air conditioning system is operating in compression refrigeration mode: the first compressor series check valve and the second compressor series check valve are closed, and the first compressor parallel check valve and the second compressor parallel check valve are open; the first refrigerant pump series check valve and the second refrigerant pump series check valve are open, and the first refrigerant pump parallel check valve and the second refrigerant pump parallel check valve are closed. When the air conditioning system operates in dual-pump supplemental cooling mode: the first compressor series check valve is open, the second compressor series check valve is closed, the first compressor parallel check valve is closed, and the second compressor parallel check valve is open; the first refrigerant pump series check valve is closed, the second refrigerant pump series check valve is open, the first refrigerant pump parallel check valve is open, and the second refrigerant pump parallel check valve is closed. When the air conditioning system operates in the refrigerant pump natural cooling mode: the series check valve of the first compressor and the series check valve of the second compressor are disconnected, and the parallel check valve of the first compressor and the parallel check valve of the second compressor are closed; the series check valve of the first refrigerant pump and the series check valve of the second refrigerant pump are closed, and the parallel check valve of the first refrigerant pump and the parallel check valve of the second refrigerant pump are disconnected.

[0014] Compared with the prior art, the advantages and positive effects of this utility model include: 1) This utility model provides a superimposed composite air conditioning system. By setting up two independent and coordinated refrigeration cycle systems, the air conditioning system can operate in compression refrigeration mode, dual-pump supplemental cooling mode, and refrigerant pump natural cooling mode. Based on real-time monitoring of outdoor temperature and combined with changes in indoor load demand, the air conditioning system can intelligently switch between the three operating modes. Through the dual-pump supplemental cooling mode, combined with a low compression ratio compressor, the utilization temperature of the natural cold source is increased from below 10°C to below 25°C, which greatly extends the applicable cycle of the natural cold source and significantly improves the energy-saving effect.

[0015] 2) This utility model provides a superimposed composite air conditioning system, which combines with the traditional refrigerant pump air conditioning system. By adopting a superimposed composite air conditioning system, the outer coil of the evaporator is connected to the first refrigeration cycle system, while the inner coil is connected to the second refrigeration cycle system. This breaks the traditional side-by-side distribution pattern. Combined with the electronic expansion valve to adjust the opening degree of the expansion valve or the fan speed in real time, it solves the problems of uneven distribution of cooling capacity of the evaporator coil and difficulty in controlling the accuracy of the air supply temperature.

[0016] 3) This utility model provides a superimposed composite air conditioning system. The first condenser and the second condenser can adopt a waterless condensation method or an evaporative condensation method to reduce the condensation temperature. The condensation method of the condenser can be selected according to local conditions, and the application range is wide. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the logical structure of the air conditioning system proposed in this utility model; Figure 2 This is a schematic diagram of the circulation structure of the air conditioning system proposed in this utility model when it is operating in the compression refrigeration mode. Figure 3This is a schematic diagram of the circulation structure of the air conditioning system proposed in this utility model operating in the dual-pump supplementary cooling mode; Figure 4 This is a schematic diagram of the circulation structure of the air conditioning system proposed in this utility model when operating in the refrigerant pump natural cooling mode; Legend: 1A - First compressor; 2A - First condenser; 3A - First liquid receiver; 4A - First refrigerant pump; 5A - First electronic expansion valve; 6 - Evaporator 1B - Second compressor; 2B - Second condenser; 3B - Second liquid receiver; 4B - Second refrigerant pump; 5B - Second electronic expansion valve; F1A - First compressor series check valve; F1B - Second compressor series check valve; F2A - Parallel check valve for the first compressor; F2B - Parallel check valve for the second compressor; F3A - First refrigerant pump in series with check valve; F3B - Second refrigerant pump in series with check valve; F4A - Parallel check valve for the first refrigerant pump; F4B - Parallel check valve for the second refrigerant pump; 7A - First evaporator-condenser assembly; 7B - Second evaporator-condenser assembly. Detailed Implementation

[0018] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0019] In the description of this utility model, it should be noted that the terms "upper," "lower," "inner," "outer," "front end," "rear end," "both ends," "one end," and "the other end," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0020] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," and "connected," etc., should be interpreted broadly. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0021] [First Embodiment] like Figure 1-4 The image shows a superimposed composite air conditioning system provided in the first embodiment of this utility model. The system includes a first circulating refrigeration system and a second circulating refrigeration system, wherein... The first cycle refrigeration system includes a first compressor 1A. The discharge port of the first compressor 1A is connected to the inlet of the first condenser 2A. The outlet of the first condenser 2A is connected to the inlet of the first liquid receiver 3A. The outlet of the first liquid receiver 3A is connected to the inlet of the first refrigerant pump 4A. The outlet of the first refrigerant pump 4A is connected to the inlet of the first electronic expansion valve 5A. The outlet of the first electronic expansion valve 5A is connected to the refrigerant passage inlet of the evaporator 6. The refrigerant passage outlet of the evaporator 6 is connected to the suction port of the first compressor 1A. The second-cycle refrigeration system includes a second compressor 1B. The discharge port of the second compressor 1B is connected to the inlet of the second condenser 2B. The outlet of the second condenser 2B is connected to the inlet of the second liquid receiver 3B. The outlet of the second liquid receiver 3B is connected to the inlet of the second refrigerant pump 4B. The outlet of the second refrigerant pump 4B is connected to the inlet of the second electronic expansion valve 5B. The outlet of the second electronic expansion valve 5B is connected to the refrigerant passage inlet of the evaporator 6. The refrigerant passage outlet of the evaporator 6 is connected to the suction port of the second compressor 1B. The improvement of this embodiment compared to the prior art is as follows: The first cycle refrigeration system is connected to the outer refrigerant channel of the evaporator 6, and the second cycle refrigeration system is connected to the inner refrigerant channel of the evaporator 6. The first cycle refrigeration system and the second cycle refrigeration system can switch between multiple working modes according to the real-time outdoor temperature. By setting up two independent yet coordinated refrigeration cycle systems, the air conditioning system can operate in three modes: compression refrigeration, dual-pump supplemental cooling, and refrigerant pump natural cooling. Based on real-time monitoring of the outdoor temperature and changes in indoor load demand, the system can intelligently switch between these three modes. In dual-pump supplemental cooling mode, combined with a low-compression-ratio compressor, the natural cooling source utilization temperature is increased from below 10°C to below 25°C, significantly extending the service life of the natural cooling source and improving energy efficiency. Simultaneously, in conjunction with a traditional refrigerant pump air conditioning system, a superimposed composite air conditioning system is adopted. The outer coil of the evaporator is connected to the first refrigeration cycle system, while the inner coil is connected to the second refrigeration cycle system. This breaks the traditional parallel distribution pattern. Combined with an electronic expansion valve that adjusts the expansion valve opening or fan speed in real time, it solves problems such as uneven cooling distribution in the evaporator coils and difficulty in controlling the precise supply air temperature.

[0022] like Figure 1 As shown, a first compressor series check valve F1A is connected in series between the discharge port of the first compressor 1A and the inlet of the first condenser 2A; a second compressor series check valve F1B is connected in series between the discharge port of the second compressor 1B and the inlet of the second condenser 2B; a first compressor parallel check valve F2A is connected in parallel between the discharge port of the first compressor 1A and the inlet of the first condenser 2A; and a second compressor parallel check valve F2B is connected in parallel between the discharge port of the second compressor 1B and the inlet of the second condenser 2B. By controlling the opening and closing of the first compressor series check valve F1A and the first compressor parallel check valve F2A, the participation of the first compressor 1A in the working circuit of the first cycle refrigeration system can be controlled. Similarly, by controlling the second compressor series check valve F1B and the second compressor parallel check valve F2B, the participation of the second compressor 1B in the working circuit of the second cycle refrigeration system can be controlled.

[0023] Similarly, such as Figure 1As shown, a first refrigerant pump series check valve F3A is connected in series between the outlet of the first refrigerant pump 4A and the inlet of the first electronic expansion valve 5A; a second refrigerant pump series check valve F3B is connected in series between the outlet of the second refrigerant pump 4B and the inlet of the second electronic expansion valve 5B; a first refrigerant pump parallel check valve F4A is connected in parallel between the outlet of the first refrigerant pump 4A and the inlet of the first electronic expansion valve 5A; a second refrigerant pump parallel check valve F4B is connected in parallel between the outlet of the second refrigerant pump 4B and the inlet of the second electronic expansion valve 5B. By controlling the opening and closing of the first refrigerant pump series check valve F3A and the first refrigerant pump parallel check valve F4A, the participation of the first refrigerant pump 4A in the working circuit of the first circulating refrigeration system can be controlled. Similarly, by controlling the opening and closing of the second refrigerant pump series check valve F3B and the second refrigerant pump parallel check valve F4B, the participation of the second refrigerant pump 4B in the working circuit of the second circulating refrigeration system can be controlled.

[0024] Based on this, in this embodiment, the minimum compression ratio of the first compressor 1A and the second compressor 1B is 1.1. By using a low compression ratio compressor, the utilization temperature range of the natural cold source can be effectively increased, the applicable cycle of the natural cold source can be greatly extended, and the energy-saving effect can be significantly improved.

[0025] In this embodiment, the first condenser 2A and the second condenser 2B can adopt either anhydrous condensation or evaporative condensation. A first evaporative condensation component 7A is provided on one side of the first condenser 2A, and a second evaporative condensation component 7B is provided on one side of the second condenser 2B. The first evaporative condensation component 7A and the second evaporative condensation component 7B are preferably spray components to achieve a spray cooling effect on the corresponding condensers by spraying water, thereby reducing the condensation temperature. The condensation method of the condenser can be selected according to local conditions, and the applicability is wide.

[0026] In this embodiment, as Figure 2-4 As shown, the air conditioning system can operate in compression refrigeration mode, dual-pump supplemental cooling mode, or refrigerant pump natural cooling mode, and the corresponding one-way valve operating conditions in each mode meet the following requirements: When the air conditioning system is operating in compression refrigeration mode: the first compressor series check valve F1A and the second compressor series check valve F1B are closed, and the first compressor parallel check valve F2A and the second compressor parallel check valve F2B are open; the first refrigerant pump series check valve F3A and the second refrigerant pump series check valve F3B are open, and the first refrigerant pump parallel check valve F4A and the second refrigerant pump parallel check valve F4B are closed. When the air conditioning system operates in dual-pump supplemental cooling mode: the first compressor series check valve F1A is open, the second compressor series check valve F1B is closed, the first compressor parallel check valve F2A is closed, and the second compressor parallel check valve F2B is open; the first refrigerant pump series check valve F3A is closed, the second refrigerant pump series check valve F3B is open, the first refrigerant pump parallel check valve F4A is open, and the second refrigerant pump parallel check valve F4B is closed. When the air conditioning system is operating in the refrigerant pump natural cooling mode: the first compressor series check valve F1A and the second compressor series check valve F1B are open, and the first compressor parallel check valve F2A and the second compressor parallel check valve F2B are closed; the first refrigerant pump series check valve F3A and the second refrigerant pump series check valve F3B are closed, and the first refrigerant pump parallel check valve F4A and the second refrigerant pump parallel check valve F4B are open.

[0027] A schematic diagram of the cyclic structure of the compression refrigeration working mode is shown below. Figure 2 As shown: When there is no natural cold source available outdoors, i.e., when the real-time outdoor temperature T > the first threshold temperature T1 (or, if the condenser uses evaporative condensation, when the outdoor wet-bulb temperature TW > T1), the unit operates entirely in compression refrigeration mode. The systems connected to both the inner and outer evaporators operate in compressor mode. At this time, the first refrigerant pump 4A and the second refrigerant pump 4B are shut down. The first refrigeration cycle system consists of a first compressor 1A, a first compressor series check valve F1A, a first condenser 2A, a first liquid receiver 3A, a first refrigerant pump parallel check valve F4A, a first electronic expansion valve 5A, and the outer layer of an evaporator 6. The second refrigeration cycle system consists of a second compressor 1B, a second compressor series check valve F1B, a second condenser 2B, a second liquid receiver 3B, a second refrigerant pump parallel check valve F4B, a second electronic expansion valve 5B, and the inner layer of the evaporator 6. The first and second refrigeration cycles work together to provide cooling for the data center.

[0028] A schematic diagram of the circulation structure in the dual-pump cooling operation mode is shown below. Figure 3 As shown: When there is a certain degree of natural cold source available outdoors, i.e., the second threshold temperature T2 < outdoor real-time temperature T ≤ first threshold temperature T1 (if the condenser uses evaporative condensation, then the second threshold temperature T2 < outdoor wet-bulb temperature TW ≤ first threshold temperature T1), the system operates in dual-pump supplemental cooling mode for data center heat dissipation. At this time: The first cycle refrigeration system consists of a first compressor connected in parallel with a one-way valve F2A, a first condenser 2A, a first liquid receiver 3A, a first refrigerant pump 4A, a first electronic expansion valve 5A, and the outer layer of an evaporator 6, forming a precooling cycle unit. The second-cycle refrigeration system consists of a second compressor 1B, a second compressor series check valve F1B, a second condenser 2B, a second liquid receiver 3B, a second refrigerant pump parallel check valve F4B, a second electronic expansion valve 5B, and the inner layer of the evaporator 6, forming a supplementary cooling cycle unit. The first and second cycle refrigeration systems lower the return air temperature to the target value to provide cooling for the data center. Due to the availability of a natural cold source, the first refrigerant pump 4A operates in refrigerant pump mode to pre-cool the indoor return air. Compared to the compressor, the refrigerant pump has lower power consumption and higher energy efficiency. The second compressor 1B operates in gas pump mode to compensate for the temperature difference with the outside temperature, achieving condensation. The compressor operates at a low compression ratio, resulting in high energy efficiency.

[0029] For example, when the data center IT load is controlled at 90%, the air conditioner terminal return air temperature is 38℃, and the outdoor real-time temperature is 20℃, there is a certain amount of natural cold source available outdoors. The first refrigerant pump 4A starts, operating in refrigerant pump mode to pre-cool the indoor return air, providing approximately 40% of the cooling capacity. The second compressor 1B starts, operating in gas pump mode for pressurization and supplemental cooling, providing approximately 60% of the cooling capacity. The total cooling capacity provided by the outer refrigerant pump pre-cooling system and the inner compressor supplemental cooling system exceeds the cooling load required by the data center IT. At this point, the system can stably operate in dual-pump supplemental cooling mode.

[0030] A schematic diagram of the circulation structure of a refrigerant pump in natural cooling mode is shown below. Figure 4 As shown: When the outdoor natural cooling source is sufficient, i.e., when the real-time outdoor temperature T ≤ the second threshold temperature T2, the system operates in the refrigerant pump natural cooling mode for data center heat dissipation. At this time: The first cycle refrigeration system consists of a first compressor connected in parallel with a one-way valve F2A, a first condenser 2A, a first liquid receiver 3A, a first refrigerant pump 4A, a first refrigerant pump connected in series with a one-way valve F3A, a first electronic expansion valve 5A, and an outer layer of an evaporator 6, forming a refrigerant pump circulation unit. The second-cycle refrigeration system consists of a second compressor in parallel with a one-way valve F2B, a second condenser 2B, a second liquid receiver 3B, a second refrigerant pump 4B, a second refrigerant pump in series with a one-way valve F3B, a second electronic expansion valve 5B, and the inner layer of the evaporator 6, forming a refrigerant pump circulation unit. The first and second cycle refrigeration systems lower the return air temperature to the target value to provide cooling for the data center. Since the natural cold source is sufficient at this time, the compressor does not need to run, and the refrigerant pump power is much lower than that of the compressor, thus achieving significant energy and power savings.

[0031] For example, when the data center IT load is controlled at 90%, the air conditioner terminal return air temperature is 38℃, and the outdoor real-time temperature is 10℃, there is sufficient natural cold source outdoors. The first refrigerant pump 4A starts, operating in refrigerant pump mode to pre-cool the indoor return air, and the second refrigerant pump 4B starts, operating in refrigerant pump mode to supplement the cooling of the indoor return air. Each of the two circulation systems provides approximately 50% of the cooling capacity. The total cooling capacity provided by the outer refrigerant pump pre-cooling system and the inner refrigerant pump supplementary cooling system exceeds the cooling load required by the data center IT. At this point, the system can stably operate in the refrigerant pump natural cooling mode.

[0032] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A superimposed composite air conditioning system, the system comprising a first-cycle refrigeration system and a second-cycle refrigeration system, wherein, The first refrigeration cycle system includes a first compressor (1A), the exhaust port of the first compressor (1A) is connected to the inlet of the first condenser (2A), the outlet of the first condenser (2A) is connected to the inlet of the first liquid receiver (3A), the outlet of the first liquid receiver (3A) is connected to the inlet of the first refrigerant pump (4A), the outlet of the first refrigerant pump (4A) is connected to the inlet of the first electronic expansion valve (5A), the outlet of the first electronic expansion valve (5A) is connected to the refrigerant passage inlet of the evaporator (6), and the refrigerant passage outlet of the evaporator (6) is connected to the suction port of the first compressor (1A). The second refrigeration cycle includes a second compressor (1B), the exhaust port of which is connected to the inlet of a second condenser (2B), the outlet of which is connected to the inlet of a second liquid receiver (3B), the outlet of which is connected to the inlet of a second refrigerant pump (4B), the outlet of which is connected to the inlet of a second electronic expansion valve (5B), the outlet of which is connected to the refrigerant passage inlet of an evaporator (6), and the refrigerant passage outlet of the evaporator (6) is connected to the suction port of the second compressor (1B). Its features are: The first circulating refrigeration system is connected to the outer refrigerant channel of the evaporator (6), and the second circulating refrigeration system is connected to the inner refrigerant channel of the evaporator (6). The first circulating refrigeration system and the second circulating refrigeration system can switch between multiple working modes according to the real-time outdoor temperature.

2. The superimposed composite air conditioning system according to claim 1, characterized in that: A first compressor series check valve (F1A) is connected in series between the exhaust port of the first compressor (1A) and the inlet of the first condenser (2A), and a second compressor series check valve (F1B) is connected in series between the exhaust port of the second compressor (1B) and the inlet of the second condenser (2B).

3. The superimposed composite air conditioning system according to claim 2, characterized in that: A first compressor parallel check valve (F2A) is provided in parallel between the exhaust port of the first compressor (1A) and the inlet of the first condenser (2A), and a second compressor parallel check valve (F2B) is provided in parallel between the exhaust port of the second compressor (1B) and the inlet of the second condenser (2B).

4. A superimposed composite air conditioning system according to claim 3, characterized in that: A first refrigerant pump series check valve (F3A) is connected in series between the outlet of the first refrigerant pump (4A) and the inlet of the first electronic expansion valve (5A), and a second refrigerant pump series check valve (F3B) is connected in series between the outlet of the second refrigerant pump (4B) and the inlet of the second electronic expansion valve (5B).

5. A superimposed composite air conditioning system according to claim 4, characterized in that: A first refrigerant pump parallel check valve (F4A) is connected in parallel between the outlet of the first refrigerant pump (4A) and the inlet of the first electronic expansion valve (5A), and a second refrigerant pump parallel check valve (F4B) is connected in parallel between the outlet of the second refrigerant pump (4B) and the inlet of the second electronic expansion valve (5B).

6. A superimposed composite air conditioning system according to claim 1, characterized in that: The minimum compression ratio of the first compressor (1A) and the second compressor (1B) is 1.

1.

7. A superimposed composite air conditioning system according to claim 1, characterized in that: The first condenser (2A) and the second condenser (2B) adopt a waterless condensation method.

8. A superimposed composite air conditioning system according to claim 1, characterized in that: The first condenser (2A) and the second condenser (2B) adopt the evaporation and condensation method, and a first evaporation and condensation component (7A) is provided on one side of the first condenser (2A) and a second evaporation and condensation component (7B) is provided on one side of the second condenser (2B).

9. A superimposed composite air conditioning system according to claim 5, characterized in that: The air conditioning system can operate in compression refrigeration mode, dual-pump supplemental cooling mode, or refrigerant pump natural cooling mode.

10. A superimposed composite air conditioning system according to claim 9, characterized in that: When the air conditioning system operates in compression refrigeration mode: the first compressor series check valve (F1A) and the second compressor series check valve (F1B) are closed, and the first compressor parallel check valve (F2A) and the second compressor parallel check valve (F2B) are open; the first refrigerant pump series check valve (F3A) and the second refrigerant pump series check valve (F3B) are open, and the first refrigerant pump parallel check valve (F4A) and the second refrigerant pump parallel check valve (F4B) are closed. When the air conditioning system operates in dual-pump supplemental cooling mode: the first compressor series check valve (F1A) is open, the second compressor series check valve (F1B) is closed, the first compressor parallel check valve (F2A) is closed, and the second compressor parallel check valve (F2B) is open; the first refrigerant pump series check valve (F3A) is closed, the second refrigerant pump series check valve (F3B) is open, the first refrigerant pump parallel check valve (F4A) is open, and the second refrigerant pump parallel check valve (F4B) is closed. When the air conditioning system operates in the refrigerant pump natural cooling mode: the first compressor series check valve (F1A) and the second compressor series check valve (F1B) are open, and the first compressor parallel check valve (F2A) and the second compressor parallel check valve (F2B) are closed; the first refrigerant pump series check valve (F3A) and the second refrigerant pump series check valve (F3B) are closed, and the first refrigerant pump parallel check valve (F4A) and the second refrigerant pump parallel check valve (F4B) are open.

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