A liquid twin-rotor compressor and air conditioning system

Abstract

The utility model discloses a liquid double rotor compressor and air conditioning system, wherein liquid double rotor compressor includes compressor body and gas -liquid separation liquid storage jar A, the compressor body includes seal cylinder body, be equipped with upper pump cavity and lower pump cavity in the seal cylinder body, be equipped with upper eccentric rotor in the rotation of upper pump cavity, be equipped with lower eccentric rotor in the rotation of lower pump cavity, the top of seal cylinder body is equipped with liquid outlet B, the side bottom of seal cylinder body is equipped with liquid inlet B, the top of gas -liquid separation liquid storage jar A is equipped with liquid inlet A, the bottom of gas -liquid separation liquid storage jar A is equipped with liquid outlet A, liquid outlet A and liquid inlet B are communicated through liquid -passing pipe. The utility model discloses liquid double rotor compressor and air conditioning system can reduce the risk of fluorine pump cavitation and promote the operation efficiency.

Description

Technical Field

[0001] This utility model relates to the field of data center heat dissipation technology, and in particular to a liquid twin-rotor compressor and air conditioning system. Background Technology

[0002] The rapid development of artificial intelligence and data centers has led to a dramatic increase in server density and energy consumption. Currently, cooling energy consumption has become one of the main sources of energy consumption in data centers, and optimizing its efficiency is crucial for energy conservation and emission reduction. Utilizing natural cooling sources (such as low-temperature air) is a key path to reduce energy consumption, and existing technologies include heat exchange systems and various heat pipe composite air conditioners. However, in areas with abundant natural cooling sources, existing systems have the following shortcomings during use:

[0003] 1. Insufficient subcooling of liquid refrigerant or incomplete gas-liquid separation in the refrigerant pump can exacerbate the risk of cavitation, leading to system performance degradation or even failure.

[0004] 2. The heat pipe and compression refrigeration system operate independently, making it difficult to dynamically and efficiently integrate the utilization of natural cold sources based on outdoor temperature (such as low-temperature periods during day and night / transitional seasons / winter).

[0005] 3. Conventional compressor refrigeration and refrigerant pump energy-saving solutions cannot achieve efficient coupling of the two technologies, resulting in reliance on high-power mechanical compression even when there is sufficient natural cold source, thus limiting the energy-saving effect. Utility Model Content

[0006] In view of this, this utility model proposes a liquid twin-rotor compressor and air conditioning system to reduce the risk of cavitation in the refrigerant pump and improve operating efficiency.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A liquid twin-rotor compressor includes a compressor body and a gas-liquid separation storage tank A. The compressor body includes a sealed cylinder with an upper pump chamber and a lower pump chamber. An upper eccentric rotor rotates in the upper pump chamber, and a lower eccentric rotor rotates in the lower pump chamber. The top of the sealed cylinder has a liquid outlet B, and the bottom side of the sealed cylinder has a liquid inlet B. The top of the gas-liquid separation storage tank A has a liquid inlet A, and the bottom of the gas-liquid separation storage tank A has a liquid outlet A. The liquid outlet A and the liquid inlet B are connected by a liquid passage pipe.

[0009] To better implement the above technical solution, optionally, the liquid passage pipe is a single pipe, with the inlet end of the liquid passage pipe extending into the gas-liquid separation storage tank A through the outlet A, and the outlet end of the liquid passage pipe extending into the sealed cylinder body through the inlet B and communicating with the upper pump chamber and the lower pump chamber respectively.

[0010] Optionally, there are two liquid-passing pipes, with two outlets A and two inlets B. The inlet ends of the two liquid-passing pipes extend into the gas-liquid separation storage tank A through the two outlets A, and the outlet ends of the two liquid-passing pipes are connected to the upper pump chamber and the lower pump chamber through the two inlets B, respectively.

[0011] Optionally, the inlet end of the liquid-conducting pipe is higher than its outlet end.

[0012] Optionally, the inlet end of the liquid inlet pipe extends into the upper part of the gas-liquid separation storage tank A or is flush with the outlet A.

[0013] An air conditioning system includes a liquid twin-rotor compressor as described in any one of the above claims, and further includes a second compressor, a condenser, a gas-liquid separator receiver B, a first one-way valve, an electronic expansion valve, and an evaporator, wherein the second compressor is configured to operate safely under the condition that the compression ratio parameter ξ satisfies 1.2≤ξ.

[0014] The outlet of the evaporator is connected in series with the second compressor, the first one-way valve, the condenser, the gas-liquid separator receiver B, the liquid twin-rotor compressor, the electronic expansion valve, and the liquid inlet of the evaporator to form a composite refrigeration mode.

[0015] Furthermore, it also includes a second one-way valve, which is connected in parallel with the first one-way valve and the second compressor. The gas outlet of the evaporator is connected in series with the second one-way valve, the condenser, the gas-liquid separator receiver B, the liquid twin-rotor compressor, the electronic expansion valve, and the liquid inlet of the evaporator to form a refrigerant pump refrigeration mode.

[0016] Furthermore, it also includes a third one-way valve, which is connected in parallel with the liquid twin-rotor compressor. The outlet of the evaporator is connected in series with the second compressor, the first one-way valve, the condenser, the gas-liquid separator receiver B, the third one-way valve, the electronic expansion valve, and the liquid inlet of the evaporator to form a compression refrigeration mode.

[0017] Furthermore, there is at least one second compressor, and when there are multiple second compressors, the multiple second compressors are connected in series or in parallel.

[0018] The beneficial effects of this utility model are:

[0019] This utility model discloses a liquid twin-rotor compressor and an air conditioning system. The liquid twin-rotor compressor combines the advantages of traditional rotor compressors and refrigerant pumps, providing stable low-frequency operation and adaptability to small-displacement scenarios. It also offers more precise flow regulation and lower energy consumption. Furthermore, in the refrigerant pump assembly of the air conditioning system, the combination structure of the gas-liquid separation storage tank A and the small storage tank in the compressor body achieves double subcooling and gas-liquid separation, reducing the risk of refrigerant pump cavitation. It maintains performance without degradation under high-drop, long-piping conditions, and the small storage tank is fully filled with liquid refrigerant. Compared to traditional refrigerant pump air conditioning systems, the refrigerant pump air conditioning system equipped with a liquid twin-rotor compressor requires a lower refrigerant charge. It overcomes the technical defects of centrifugal refrigerant pumps, such as minimum flow limit, high control difficulty, and weak anti-cavitation capability, as well as gear refrigerant pumps, such as large gear wear and large performance degradation at high head.

[0020] This utility model discloses a liquid twin-rotor compressor and air conditioning system. The liquid twin-rotor compressor can be installed in multi-split air conditioning systems, precision refrigerant pump air conditioning systems for computer rooms, integrated refrigerant pump air conditioning systems, phase change multi-split air conditioning systems, etc. In the combined cooling mode and refrigerant pump cooling mode, the liquid twin-rotor compressor participates in the system operation, which can effectively improve the unit's operating efficiency, fully realize the efficient utilization of day and night temperature differences, transitional seasons and low-grade outdoor natural cold sources in winter, thereby reducing the unit's operating power consumption and improving energy-saving performance. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the first structure of a liquid twin-rotor compressor according to Embodiment 1 of this utility model;

[0022] Figure 2 This is a schematic diagram of the second structure of a liquid twin-rotor compressor according to Embodiment 1 of this utility model;

[0023] Figure 3 This is a schematic diagram of an air conditioning system according to Embodiment 2 of this utility model;

[0024] Figure 4 yes Figure 3 A schematic diagram of the central air conditioning system in compression refrigeration mode;

[0025] Figure 5 yes Figure 3 A schematic diagram of the central air conditioning system in a combined cooling mode;

[0026] Figure 6 yes Figure 3 A schematic diagram of a central air conditioning system in refrigerant pump cooling mode;

[0027] Figure Labels

[0028] Liquid twin-rotor compressor 10, sealed cylinder 11, upper pump chamber 111, lower pump chamber 112, upper eccentric rotor 113, lower eccentric rotor 114, liquid inlet B115, liquid outlet B116, gas-liquid separation storage tank A12, liquid inlet A121, liquid outlet A122, liquid passage pipe 13, second compressor 30, condenser 40, gas-liquid separation storage tank B50, electronic expansion valve 60, evaporator 70, first check valve 81, second check valve 82, second check valve 83. Detailed Implementation

[0029] The technical solution of this utility model will be described in detail below with reference to the accompanying drawings and specific embodiments. Identical components are indicated by the same reference numerals.

[0030] Example 1

[0031] Please see Figure 1 and Figure 2 This utility model discloses a liquid twin-rotor compressor 10, which includes a compressor body 10 and a gas-liquid separation storage tank A12.

[0032] The compressor body 10 includes a sealed cylinder 11, which contains an upper pump chamber 111 and a lower pump chamber 112. An upper eccentric rotor 113 is rotatably mounted in the upper pump chamber 111, and a lower eccentric rotor 114 is rotatably mounted in the lower pump chamber 112. The upper eccentric rotor 113 and the lower eccentric rotor 114 are symmetrically placed to reduce vibration during operation. The top of the sealed cylinder 11 has a liquid outlet B116, and the bottom side of the sealed cylinder 11 has a liquid inlet B115. The top of the gas-liquid separation storage tank A12 has a liquid inlet A121, and the bottom of the gas-liquid separation storage tank A12 has a liquid outlet A122. The liquid outlet A122 and the liquid inlet B115 are connected by a liquid pipe 13.

[0033] In one embodiment of this utility model, the liquid passage pipe 13 is a single pipe. The liquid inlet end of the liquid passage pipe 13 extends into the gas-liquid separation storage tank A12 through the liquid outlet A122, and the liquid outlet end of the liquid passage pipe 13 extends into the sealed cylinder 11 through the liquid inlet B115 and is connected to the upper pump chamber 111 and the lower pump chamber 112 respectively.

[0034] In one embodiment of this utility model, there are two liquid passage pipes 13, with two liquid outlets A122 and two liquid inlets B115. The liquid inlet ends of the two liquid passage pipes 13 extend into the gas-liquid separation storage tank A12 through the two liquid outlets A122, and the liquid outlet ends of the two liquid passage pipes 13 are connected to the upper pump chamber 111 and the lower pump chamber 112 through the two liquid inlets B115, respectively.

[0035] In this embodiment of the invention, the inlet end of the liquid-conducting pipe 13 is higher than its outlet end.

[0036] In this embodiment of the utility model, the inlet end of the liquid inlet pipe 13 extends into the upper part of the gas-liquid separation storage tank A12 or is flush with the outlet A122.

[0037] The liquid twin-rotor compressor 10 of this invention has a liquid inlet B115 connected to a gas-liquid separation storage tank A12. The gas-liquid separation storage tank A12 is always kept full of liquid, which reduces the risk of cavitation of the refrigerant pump while achieving subcooling and gas-liquid separation. In addition, there is no performance degradation under high drop and long piping conditions. Compared with traditional refrigerant pump air conditioning systems, it can significantly reduce the amount of refrigerant charged into the system.

[0038] Example 2

[0039] like Figures 3 to 6 As shown, this utility model discloses an air conditioning system, including a second compressor 30, a condenser 40, a gas-liquid separator receiver B50, an electronic expansion valve 60, an evaporator 70, a first one-way valve 81, a second one-way valve 82, a third one-way valve 83, and the liquid twin-rotor compressor 10 in Embodiment 1. The second compressor 30 is configured to operate safely under the condition that the compression ratio parameter ξ satisfies 1.2≤ξ. The condenser 40 can be an air-cooled condenser, a water-cooled condenser, or an indirect evaporative cooling / condensing condenser. The electronic expansion valve 60 has a wide-range flow rate adjustment function.

[0040] In this configuration, the outlet of the evaporator 70 is connected in series with the second compressor 30, the first one-way valve 81, the condenser 40, the gas-liquid separator receiver B50, the liquid twin-rotor compressor 10, the electronic expansion valve 60, and the liquid inlet of the evaporator 70 to form a composite refrigeration mode.

[0041] The second one-way valve 82 is connected in parallel with the first one-way valve 81 and the second compressor 30. The gas outlet of the evaporator 70 is connected in series with the second one-way valve 82, the condenser 40, the gas-liquid separator receiver B50, the liquid twin-rotor compressor 10, the electronic expansion valve 60 and the liquid inlet of the evaporator 70 to form a refrigerant pump refrigeration mode.

[0042] The third one-way valve 83 is connected in parallel with the twin-rotor compressor 10. The outlet of the evaporator 70 is connected in series with the second compressor 30, the first one-way valve 81, the condenser 40, the gas-liquid separator receiver B50, the third one-way valve 83, the electronic expansion valve 60, and the liquid inlet of the evaporator 70 to form a compression refrigeration mode.

[0043] In the embodiments of this utility model, there is at least one second compressor 30. When there are multiple second compressors 30, the multiple second compressors 30 are connected in series or in parallel, and each second compressor 30 has an exhaust port and a return port.

[0044] like Figure 4As shown, when there is no available natural cold source in the outdoor environment (i.e., T > T1), the air conditioning system operates in compression refrigeration mode. At this time, the liquid dual-rotor compressor 10 is turned off, and the second compressor 30 is turned on. The second compressor 30, the first one-way valve 81, the gas-liquid separator receiver B50, the second one-way valve 82, the electronic expansion valve 60, and the evaporator 70 constitute the compression refrigeration mode to provide cooling capacity for the data center. Since there is no available natural cold source, when the outdoor natural cold source is unavailable, the difference between the outdoor temperature and the target condensing temperature can only be compensated by the pressure compensation mechanism of the second compressor 30 to drive the refrigerant to complete the condensation process. The condensed refrigerant is transported to the evaporator 70 through the system pipeline to exchange heat with the heat load of the data center, thereby realizing the cooling function of the data center.

[0045] Specifically, in a data center air conditioning system, if the return air temperature at the data center air conditioning terminal is controlled at 24℃, the supply air temperature is 12-15℃, and the evaporation temperature is approximately 8-10℃: If the outdoor condenser 40 is an air-cooled condenser, when the outdoor temperature is higher than 20℃, the unit operates in compression refrigeration mode (if the outdoor temperature is 35℃ at this time, the condensing temperature is approximately 45-48℃). After the refrigerant is condensed and cooled in the condenser 40, it enters the gas-liquid separator B50 for storage, and is throttled and depressurized through the electronic expansion valve 60, becoming a low-temperature, low-pressure gas-liquid mixture of refrigerant, ultimately cooling the return air temperature from 24℃ to 12-15℃. If the condenser 40 uses water cooling or indirect evaporative cooling, the outdoor wet-bulb temperature is used as the switching indicator.

[0046] like Figure 5 As shown, when a certain degree of natural cold source is available outdoors (i.e., T2 < T ≤ T1), the air conditioning system operates in a composite cooling mode: the second compressor 30 and the liquid twin-rotor compressor 10 are simultaneously turned on. The second compressor 30, the first one-way valve 81, the condenser 40, the gas-liquid separator receiver B50, the liquid twin-rotor compressor 10, the electronic expansion valve 60, and the evaporator 70 constitute the composite cooling mode, providing cooling capacity for the data center. When a usable natural cold source is available, the system uses the second compressor 30 to implement a small pressure compensation for the temperature difference with the outside, driving the refrigerant to complete the condensation process. Under this condition, the second compressor 30 operates in a low compression ratio mode, resulting in better energy efficiency. However, the low compression ratio operation mode may lead to insufficient system pressure difference, causing problems such as obstructed lubricating oil return and motor cooling failure. Therefore, it is necessary to coordinately start the liquid twin-rotor compressor 10 to implement pressure difference compensation control to maintain the system pressure difference to meet design requirements and ensure the overall safe and stable operation. The condensed refrigerant is transported to the evaporator 70 through the system pipeline, where it exchanges heat with the data center's heat load, ultimately achieving the data center's cooling function.

[0047] Specifically, in a data center air conditioning system, if the return air temperature at the data center air conditioning terminal is controlled at 24°C, the supply air temperature is 12-15°C, and the evaporation temperature is approximately 8-10°C. If the outdoor condenser 40 uses an air-cooled condenser, when the outdoor temperature is below 20°C but above 5°C (e.g., the outdoor temperature is 15°C), the unit operates in a composite cooling mode: due to the availability of a certain natural cold source, the condensation temperature is relatively low (approximately 25-28°C). After the refrigerant is condensed and cooled by the condenser 40, it enters the gas-liquid separator receiver B50 for storage. Combined with the gas-liquid separator receiver B50 of the liquid twin-rotor compressor 10, secondary subcooling and gas-liquid separation can be achieved, reducing the risk of cavitation in the refrigerant pump, and there is no performance degradation under high drop and long piping conditions. Once the liquid refrigerant has completely filled the gas-liquid separator receiver B50, the charging can be stopped (the refrigerant charge is reduced). Subsequently, the liquid twin-rotor compressor 10 performs pressure compensation to ensure normal oil return and motor cooling of the second compressor 30, and transfers the refrigerant to the evaporator 70 for data center cooling. If the condenser 40 uses water cooling or indirect evaporative cooling, the outdoor wet-bulb temperature will be used as the switching indicator.

[0048] like Figure 6 As shown, when there is sufficient outdoor natural cold source (T≤T2), the air conditioning system operates in refrigerant pump cooling mode. At this time, the second compressor 30 is off, and the liquid twin-rotor compressor 10 is on. The second one-way valve 82, condenser 40, gas-liquid separator receiver B50, liquid twin-rotor compressor 10, electronic expansion valve 60, and evaporator 70 constitute the refrigerant pump cooling mode. The condensed refrigerant is transported to the evaporator 70 through the system piping to exchange heat with the data center's heat load, thus achieving the data center's cooling function. Because the system does not need to start the second compressor 30 to participate in the cooling cycle when the natural cold source is sufficient, and the input power of the liquid twin-rotor compressor 10 is significantly lower than that of the second compressor 30, the overall system energy consumption can be greatly reduced, thereby achieving energy-saving and power-saving effects.

[0049] Specifically, in a data center air conditioning system, if the return air temperature at the data center air conditioning terminal is controlled at 24℃, the supply air temperature is 12-15℃, and the evaporation temperature is approximately 8-10℃, and the outdoor condenser 40 uses an air-cooled condenser, then when the outdoor temperature is below 5℃, the refrigerant pump cooling mode is activated. For example, if the outdoor temperature is 5℃, since there is sufficient natural cold source, the second compressor 30 is shut down. Under the force of the liquid twin-rotor compressor 10, the gaseous refrigerant that has absorbed heat after evaporation in the evaporator 70 enters the condenser 40 for condensation and heat dissipation, with a condensation temperature of approximately 12-10℃. At 5℃, the refrigerant condenses and cools before entering the gas-liquid separator receiver B50 for storage. Combined with the gas-liquid separator receiver B50 of the liquid twin-rotor compressor 10, secondary subcooling and gas-liquid separation are achieved, which can reduce the risk of cavitation of the fluorine pump and ensure no performance degradation under high drop and long piping conditions. At the same time, the liquid refrigerant only needs to completely fill the gas-liquid separator receiver A12, reducing the refrigerant charge. The refrigerant is then pressurized and compensated by the liquid twin-rotor compressor 10, and then enters the electronic expansion valve 60 for throttling and depressurization, becoming a low-temperature, low-pressure gas-liquid mixture of refrigerant, which is then transferred to the evaporator 70 to cool the data center.

[0050] This utility model discloses a liquid twin-rotor compressor and an air conditioning system. The liquid twin-rotor compressor 10 combines the advantages of traditional rotor compressors and refrigerant pumps, providing stable low-frequency operation and adaptability to small-displacement scenarios. It also offers more precise flow regulation and lower energy consumption. Furthermore, in the refrigerant pump assembly of the air conditioning system, the gas-liquid separation storage tank A12 is combined with the small storage tank in the compressor body. This achieves double subcooling and gas-liquid separation, reducing the risk of refrigerant pump cavitation. Performance remains unaffected under high-drop, long-piping conditions, and the small storage tank is fully filled with liquid refrigerant. Compared to traditional refrigerant pump air conditioning systems, the refrigerant pump air conditioning system equipped with the liquid twin-rotor compressor 10 requires a lower refrigerant charge. This overcomes the technical defects of centrifugal refrigerant pumps, such as minimum flow limit, high control difficulty, and weak cavitation resistance, as well as gear refrigerant pumps, such as large gear wear and significant performance degradation at high head.

[0051] This utility model discloses a liquid twin-rotor compressor and air conditioning system. The liquid twin-rotor compressor 10 can be installed in multi-split air conditioning systems, precision refrigerant pump air conditioning systems for computer rooms, integrated refrigerant pump air conditioning systems, phase change multi-split air conditioning systems, etc. In the combined cooling mode and refrigerant pump cooling mode, the liquid twin-rotor compressor 10 participates in the system operation, which can effectively improve the unit's operating efficiency, fully realize the efficient utilization of day and night temperature differences, transitional seasons and low-grade outdoor natural cold sources in winter, thereby reducing the unit's operating power consumption and improving energy-saving performance.

[0052] The technical solution of this utility model has been described in detail above with reference to specific embodiments. The specific embodiments described are used to help understand the concept of this utility model. Derivations and modifications made by those skilled in the art based on the specific embodiments of this utility model also fall within the protection scope of this utility model.

Claims

1. A liquid twin-rotor compressor (10), comprising a compressor body, the compressor body including a sealed cylinder (11), the sealed cylinder (11) having an upper pump chamber (111) and a lower pump chamber (112), an upper eccentric rotor (113) rotatably disposed in the upper pump chamber (111), a lower eccentric rotor (114) rotatably disposed in the lower pump chamber (112), a liquid outlet B (116) being provided at the top of the sealed cylinder (11), and a liquid inlet B (115) being provided at the bottom side of the sealed cylinder (11), characterized in that: It also includes a gas-liquid separation storage tank A (12), which has an inlet A (121) at the top and an outlet A (122) at the bottom. The outlet A (122) and the inlet B (115) are connected by a liquid pipe (13).

2. The liquid twin-rotor compressor (10) according to claim 1, characterized in that: The liquid inlet pipe (13) is a single pipe. The inlet end of the liquid inlet pipe (13) extends into the gas-liquid separation storage tank A (12) through the outlet port A (122). The outlet end of the liquid inlet pipe (13) extends into the sealed cylinder (11) through the inlet port B (115) and is connected to the upper pump chamber (111) and the lower pump chamber (112) respectively.

3. The liquid twin-rotor compressor (10) according to claim 1, characterized in that: There are two liquid-passing pipes (13), and there are two liquid outlets A (122) and two liquid inlets B (115). The liquid inlet of the two liquid-passing pipes (13) extends into the gas-liquid separation storage tank A (12) through the two liquid outlets A (122) respectively. The liquid outlet of the two liquid-passing pipes (13) is connected to the upper pump chamber (111) and the lower pump chamber (112) through the two liquid inlets B (115) respectively.

4. The liquid twin-rotor compressor (10) according to claim 1, characterized in that: The inlet end of the liquid-passing pipe (13) is higher than its outlet end.

5. The liquid twin-rotor compressor (10) according to claim 4, characterized in that: The inlet end of the liquid inlet pipe (13) extends into the upper part of the gas-liquid separation storage tank A (12) or is flush with the outlet A (122).

6. An air conditioning system, characterized in that: The liquid twin-rotor compressor (10) according to any one of claims 1 to 5 further includes a second compressor (30), a condenser (40), a gas-liquid separator receiver B (50), a first check valve (81), an electronic expansion valve (60), and an evaporator (70), wherein the second compressor (30) is configured to operate safely under the condition that the compression ratio parameter ξ satisfies 1.2≤ξ; The outlet of the evaporator (70) is connected in series with the second compressor (30), the first one-way valve (81), the condenser (40), the gas-liquid separator receiver B (50), the liquid twin-rotor compressor (10), the electronic expansion valve (60), and the liquid inlet of the evaporator (70) to form a composite refrigeration mode.

7. The air conditioning system according to claim 6, characterized in that: It also includes a second one-way valve (82), which is connected in parallel with the first one-way valve (81) and the second compressor (30). The outlet of the evaporator (70) is connected in series with the second one-way valve (82), the condenser (40), the gas-liquid separator receiver B (50), the liquid twin-rotor compressor (10), the electronic expansion valve (60), and the liquid inlet of the evaporator (70) to form a fluorine pump refrigeration mode.

8. The air conditioning system according to claim 7, characterized in that: It also includes a third one-way valve (83), which is connected in parallel with the liquid twin-rotor compressor (10). The outlet of the evaporator (70) is connected in series with the second compressor (30), the first one-way valve (81), the condenser (40), the gas-liquid separator receiver B (50), the third one-way valve (83), the electronic expansion valve (60), and the liquid inlet of the evaporator (70) to form a compression refrigeration mode.

9. The air conditioning system according to claim 6, characterized in that: There is at least one second compressor (30). When there are multiple second compressors (30), the multiple second compressors (30) are connected in series or in parallel.

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