WO2025092854A1 - 一种空调系统及其控制方法 - Google Patents

一种空调系统及其控制方法 Download PDF

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Publication number
WO2025092854A1
WO2025092854A1 PCT/CN2024/128656 CN2024128656W WO2025092854A1 WO 2025092854 A1 WO2025092854 A1 WO 2025092854A1 CN 2024128656 W CN2024128656 W CN 2024128656W WO 2025092854 A1 WO2025092854 A1 WO 2025092854A1
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WIPO (PCT)
Prior art keywords
conditioning system
air conditioning
compressor
air
gas booster
Prior art date
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Pending
Application number
PCT/CN2024/128656
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English (en)
French (fr)
Inventor
刘洪�
韩海晓
李海滨
王学军
张学斌
余兴松
于贺
程磊
谷宇
王琪
杨锟
田泽琦
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
China Mobile Communications Group Co Ltd
China Mobile Group Design Institute Co Ltd
Original Assignee
China Mobile Communications Group Co Ltd
China Mobile Group Design Institute Co Ltd
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Publication date
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Publication of WO2025092854A1 publication Critical patent/WO2025092854A1/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
    • H05K7/208—Liquid cooling with phase change
    • H05K7/20827—Liquid cooling with phase change within rooms for removing heat from cabinets, e.g. air conditioning devices
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
    • H05K7/20836—Thermal management, e.g. server temperature control

Definitions

  • the present disclosure relates to the technical field of computer room refrigeration systems, and in particular to an air conditioning system and a control method thereof.
  • the existing system operates the compressor and refrigerant pump for cooling at the same time during the transition season when the outdoor temperature is between 5°C and 25°C, i.e., the mixed mode.
  • the air conditioning system consumes too much energy and has low cooling efficiency, which seriously affects the overall energy efficiency and power utilization efficiency of the computer room throughout the year.
  • the purpose of the present disclosure is to provide an air-conditioning system and a control method thereof, which are used to improve the refrigeration efficiency of the air-conditioning system during transitional seasons, reduce the boost power consumption of the air-conditioning system, and improve the overall energy efficiency and power utilization efficiency of the computer room throughout the year.
  • the present disclosure also provides an air-conditioning system control method, which applies the above-mentioned air-conditioning system.
  • the method includes: determining an excess cooling demand index of the refrigerated space based on the actual temperature of the indoor space at a target position and a preset temperature; determining a target operating mode of the air-conditioning system based on the excess cooling demand index of the refrigerated space and the actual temperature difference between the inside and outside of the refrigerated space; and controlling the air-conditioning system to cool the refrigerated space in the target operating mode.
  • FIG1 shows a schematic structural diagram of an air conditioning system provided in an embodiment of the present disclosure
  • FIG2 shows a flow chart of an air conditioning system control method provided in an embodiment of the present disclosure
  • FIG3a shows a schematic diagram of a refrigerant pump driving mode provided in an embodiment of the present disclosure
  • FIG3 b shows a schematic diagram of a first overclocking mode provided in an embodiment of the present disclosure
  • FIG3c shows a schematic diagram of a hybrid driving mode provided in an embodiment of the present disclosure
  • FIG3 d shows a schematic diagram of a second overclocking mode provided in an embodiment of the present disclosure
  • FIG3e is a schematic diagram showing a driving mode of a gas booster provided in an embodiment of the present disclosure.
  • FIG3f shows a schematic diagram of a compressor driving mode provided in an embodiment of the present disclosure
  • first and second are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as “first” or “second” may explicitly or implicitly include one or more of the features.
  • “multiple” means two or more, unless otherwise clearly and specifically defined.
  • "Several” means one or more, unless otherwise clearly and specifically defined.
  • At least one of a, b or c can mean: a, b, c, the combination of a and b, the combination of a and c, the combination of b and c, or the combination of a, b and c, where a, b, c can be single or multiple.
  • the existing system operates the compressor and the refrigerant pump for refrigeration at the same time during the transition season when the outdoor temperature is between 5°C and 25°C, that is, the hybrid mode.
  • the compressor is still mainly used for refrigeration, and the refrigerant pump plays a role in increasing the circulation pressure, indirectly reducing the energy consumption of the compressor, but the reduction is very limited, and affected by the working characteristics of the compressor under different working conditions, running the hybrid mode under some working conditions will not save energy, but will consume more energy. Therefore, the control strategy of the air-conditioning system in the hybrid mode is too complicated and the final energy-saving effect is not good.
  • the duration of the transition season accounts for at least 40% of the whole year
  • the power consumption and energy efficiency of the air conditioner in the transition season will have a great impact on the operating energy efficiency, power utilization efficiency and power consumption of the data center air-conditioning system throughout the year; the energy-saving effect of the hybrid mode of the current air-conditioning system in the transition season is very limited, and it is difficult to meet the increasingly stringent requirements for power utilization efficiency.
  • FIG. 1 shows a schematic diagram of the structure of the air-conditioning system provided in an embodiment of the present disclosure.
  • the air-conditioning system 100 includes: a gas booster 101, a condenser 102 and an evaporator 103, the outlet of the gas booster 101 is connected to the inlet of the evaporator 103 through the condenser 102, and the outlet of the evaporator 103 is connected to the inlet of the gas booster 101.
  • the liquid reservoir 104 can also be used to connect the inlet of the evaporator 103 and the outlet of the condenser 102.
  • the outlet of the gas booster 101 is connected to the inlet of the evaporator 103 through the condenser 102, and the outlet of the evaporator 103 is connected to the inlet of the gas booster 101.
  • the coolant increases the condensation pressure under the action of the gas booster 101, and enters the condenser 102 from the outlet of the gas booster 101 for heat exchange, and then the coolant enters the inlet of the evaporator 103 to absorb heat from the air.
  • the condensation pressure in the condenser 102 is higher than the evaporation pressure in the evaporator 103, and the condensation temperature is higher than the evaporation temperature, which reduces the probability of the condensation temperature being lower than the evaporation temperature due to the use of the compressor in the prior art solution, and improves the refrigeration efficiency of the air conditioning system. It is found through testing that by using the air conditioning system, the temperature corresponding to the use of the outdoor natural cold source can be increased by at least 5°C, reducing the probability of the temperature corresponding to the use of the outdoor natural cold source being too low, and the length of time for using the outdoor natural cold source throughout the year is increased by more than 10%.
  • the gas booster 101 has the characteristic of low working pressure difference. Therefore, after the gas booster 101 replaces the compressor, the boosting power consumption of the air-conditioning system 100 can be greatly reduced, and the overall energy efficiency and power utilization efficiency of the computer room in the whole year can be improved.
  • the air-conditioning system 100 can use a circulation loop composed of at least a gas booster 101, a condenser 102, a liquid storage device 104 and an evaporator 103 for refrigeration, without the need to select according to extreme high temperature, thereby solving the problems of excessive air-conditioning capacity, excessive quantity, excessive cost, too low air-conditioning load rate in the initial delivery of the data center, and excessive power utilization efficiency.
  • the present invention can realize cooling during the transition season by driving the air-conditioning system through a gas booster, thereby reducing the operating time of the refrigerant pump in the system, reducing the probability of cavitation of the refrigerant pump, and at the same time slowing down the wear rate of the refrigerant pump, thereby extending the service life of the refrigerant pump.
  • the air conditioning system 100 further includes a compressor 105 connected in parallel with the gas supercharger 101.
  • the outlet of the compressor 105 is condensed.
  • the compressor 102 is connected to the inlet of the evaporator 103 , and the outlet of the evaporator 103 is connected to the inlet of the compressor 105 .
  • another circulation loop may be formed by the compressor 105, the condenser 102, the liquid storage tank 104 and the evaporator 103.
  • the coolant increases the condensation pressure under the action of the compressor 105, and passes from the outlet of the compressor 105 into the condenser 102 for heat exchange, and then the coolant passes into the inlet of the evaporator 103 to absorb heat from the air, thereby achieving the refrigeration purpose of the air conditioning system 100.
  • the air-conditioning system 100 also includes a gas booster 101 connected in parallel with the compressor 105, and the outlet of the gas booster 101 is connected to the inlet of the evaporator 103 through the condenser 102, and the outlet of the evaporator 103 is connected to the inlet of the gas booster 101.
  • the gas booster 101 and the compressor 105 work together, wherein the gas booster 101 can disperse the pressure difference of the compressor 105 in the air-conditioning system, and reduce the probability of the compressor 105 entering an over-compression state due to the influence of the excessive pressure difference, thereby increasing the cooling capacity of the air-conditioning system, and solving the problem of the high-temperature downtime risk caused by insufficient cooling capacity of the air-conditioning in the data center after high temperature outdoors or failure of multiple air conditioners.
  • the condensation pressure of the coolant can be significantly increased, so that the condensation pressure in the condenser 102 is higher than the evaporation pressure in the evaporator 103, and the condensation temperature is higher than the evaporation temperature, reducing the probability of the condensation temperature being lower than the evaporation temperature during the operation of the compressor 105, and improving the refrigeration efficiency of the air-conditioning system 100.
  • the temperature corresponding to the outdoor natural cooling source can be increased by at least 5°C, reducing the probability of the temperature corresponding to the outdoor natural cooling source being too low, and the time of using the outdoor natural cooling source throughout the year is increased by more than 10%.
  • the circuit to be used can be selected according to actual needs, thus solving the problems of excessive capacity, excessive quantity, high cost, too low air conditioning load rate in the initial stage of data center delivery, and too high electricity utilization efficiency caused by selecting air conditioners for extreme high temperatures.
  • the air conditioning system 100 provided in this embodiment further includes a first valve 106 and a second valve 107, wherein the inlet of the compressor 105 is connected to the outlet of the evaporator 103 through the first valve 106; the inlet of the gas booster 101 is connected to the outlet of the evaporator 103 through the second valve 107.
  • the first valve 106 is turned on, and when the gas booster 101 is in operation, the second valve 107 is turned on.
  • the air conditioning system 100 When the air conditioning system 100 is in the compressor driving mode (as shown in FIG. 3f below), the first valve 106 is turned on, so that the compressor 105 is in the working state, and the second valve 107 is turned off, so that the gas booster 101 is in the non-working state. At this time, the refrigerant, driven by the compressor 105, enters the condenser 102, the liquid storage tank 104, and the evaporator 103 in sequence to complete a cycle. When the cycle is completed, the refrigerant enters the compressor 105 from the outlet of the evaporator 103 through the first valve 106 to perform the next cycle. At this time, the air conditioning system 100 can achieve refrigeration only by running the compressor 105.
  • the first valve 106 and the second valve 107 are turned on, so that the compressor 105 and the gas booster 101 are both in the working state.
  • the refrigerant flows through the compressor 105 and the gas booster 101 at the same time, and under their joint action, enters the condenser 102, the liquid storage tank 104, and the evaporator 103 in sequence to complete a cycle.
  • the refrigerant flows from the outlet of the evaporator 103 along the first valve 106 and the second valve 107, and enters the compressor 105 and the gas booster 101 at the same time to perform the next cycle.
  • the air conditioning system 100 When the air conditioning system 100 is in the overclocking driving mode, the outdoor temperature is extremely high, the pressure difference between the condensing pressure and the evaporating pressure in the air conditioning system 100 is too large, and the compressor 105 is affected by the excessive pressure difference and enters an over-compression state, thereby causing the flow of the compressor 105 to drop significantly, causing the refrigeration capacity of the air conditioning system to drop. Therefore, the air conditioning system sets the compressor 105 and the gas booster 101 to be in working state at the same time to reduce the pressure difference between the condensing pressure and the evaporating pressure in the air conditioning system 100, and improve the refrigeration capacity and refrigeration capacity of the air conditioning system 100.
  • the refrigeration capacity under the extremely high temperature condition is increased by more than 20%, avoiding the substantial attenuation of the refrigeration capacity caused by the outdoor high temperature, reducing the specifications and quantity of the air conditioners configured in the data center, and reducing the initial investment cost of the data center air conditioning system.
  • the air conditioning system 100 provided in this embodiment further includes a refrigerant pump 108 and a first bypass valve 109.
  • the outlet of the condenser 102 is connected to the inlet of the evaporator 103 through the refrigerant pump 108, and the inlet of the refrigerant pump 108 is connected to the outlet of the refrigerant pump 108 through the first bypass valve 109.
  • the first bypass valve 109 is turned on.
  • the air conditioning system 100 provided in the embodiment of the present disclosure further includes an expansion valve 110, which is provided at the inlet of the evaporator 103, and is used to control the superheat of the gaseous refrigerant at the outlet of the evaporator 103, thereby controlling the refrigerant flow entering the evaporator 103.
  • an expansion valve 110 which is provided at the inlet of the evaporator 103, and is used to control the superheat of the gaseous refrigerant at the outlet of the evaporator 103, thereby controlling the refrigerant flow entering the evaporator 103.
  • this hybrid drive mode can improve the energy efficiency ratio of the air-conditioning system by more than 40%.
  • the air conditioning system 100 further includes a second bypass valve 111, the outlet of the evaporator 103 is connected to the inlet of the condenser 102 through the second bypass valve 111, the second bypass valve 111 is connected in parallel with the compressor 105 and the gas booster 101, and the second bypass valve 111 is turned on when the air conditioning system is in the overclocking driving mode, at which time the compressor 105 and the gas booster 101 are in working state at the same time, reducing the pressure difference between the condensing pressure and the evaporation pressure in the air conditioning system 100, and improving the refrigeration capacity and refrigeration capacity of the air conditioning system 100.
  • the refrigeration capacity under the extremely high temperature condition is increased by more than 20%, avoiding the substantial attenuation of the refrigeration capacity caused by the high temperature outside, reducing the specifications and quantity of the air conditioners configured in the data center, and reducing the initial investment cost of the air conditioning system of the data center.
  • the present disclosure also provides an air conditioning system control method for controlling the above-mentioned air conditioning system, wherein the air conditioning system also includes a compressor and a refrigerant pump, which can improve the refrigeration efficiency of the air conditioning system during the transition season, meet the refrigeration needs of historical extreme high temperatures with low probability and short duration, and improve the overall energy efficiency and power utilization efficiency of the computer room in the whole year.
  • FIG2 shows a flow chart of the air conditioning system control method provided in an embodiment of the present disclosure. As shown in FIG2, the air conditioning system control method includes:
  • Step 201 Determine an excess cooling demand index of the refrigerated space based on the actual temperature of the indoor space at the target location and the preset temperature.
  • the air conditioning system operates in a compressor driving mode, a gas booster driving mode, a hybrid driving mode, a refrigerant pump driving mode and an overclocking mode.
  • the cooling deviation of the air-conditioning system is determined; based on the cooling deviation of the air-conditioning system and the allowable cooling temperature fluctuation range of the air-conditioning system, the excess cooling demand index of the refrigerated space is determined.
  • the excess cooling demand index of the refrigerated space CFC (Tc-Ts)/TP, where Tc is the actual temperature of the indoor space at the target location, such as supply air temperature, return air temperature, cold channel temperature, etc.
  • Tc is the actual temperature of the indoor space at the target location, such as supply air temperature, return air temperature, cold channel temperature, etc.
  • the specific location can be adjusted according to actual needs and is not limited here; Ts is the preset temperature of the indoor space at the target location; TP is the allowable temperature fluctuation range.
  • the target operating mode is determined to be the overclocking drive mode; if the excess cooling demand index of the refrigeration space is less than or equal to the preset index, the target operating mode of the air-conditioning system is determined based on the actual temperature difference between the inside and outside of the refrigeration space and the driving mode screening conditions.
  • Step 202 Determine a target operation mode of the air conditioning system based on the excess cooling demand index of the cooling space and the actual temperature difference between the inside and outside of the cooling space.
  • the actual temperature difference between the inside and outside of the refrigerated space Temd Tin-Tout, where Tin is the return air dry bulb temperature of the indoor air conditioning system and Tout is the outdoor air dry bulb temperature.
  • Td is a preset threshold value, corresponding to different operation modes, which can be a first preset threshold value Td1, a second preset threshold value Td2, and a third preset threshold value Td3.
  • Table 1 shows the determination conditions of the target operation mode of the air conditioning system provided in this embodiment.
  • the driving mode screening condition includes at least one of the following:
  • the target operating mode is the hybrid drive mode. If the excess cooling demand index of the refrigeration space is greater than the preset index, the target operating mode is the second overclocking mode.
  • the target operation mode is the gas booster driving mode; if the excess refrigeration demand index of the refrigerated space is less than or equal to the preset index, the target operation mode is the gas booster driving mode.
  • the excess cooling demand index is greater than the preset index, and the target operating mode is the second overclocking mode.
  • the target operation mode is the compressor drive mode. If the excess refrigeration demand index of the refrigeration space is greater than the preset index, the target operation mode is the third overclocking mode.
  • the value range of Td1, Td2, and Td3 is 0°C to 30°C
  • the overclocking modes provided in this embodiment include a first overclocking mode, a second overclocking mode, and a third overclocking mode.
  • the overclocking mode operated varies depending on the actual temperature difference between the inside and outside of the refrigeration space of the air-conditioning system.
  • the target operation mode is the refrigerant pump driving mode, and if the excess cooling demand index CFC of the refrigerated space is greater than the preset index, the target operation mode is the first overclocking mode.
  • the target operating mode is the hybrid drive mode. If the excess cooling demand index CFC of the refrigerated space is greater than the preset index, the target operating mode is the second overclocking mode.
  • the target operating mode is the compressor drive mode. If the excess cooling demand index CFC of the refrigerated space is greater than the preset index, the target operating mode is the third overclocking mode.
  • the preset index of CFC can be set according to actual conditions, for example, 100%, 75%, and is not limited here.
  • Step 203 Control the air conditioning system to cool the refrigeration space in the target operation mode.
  • FIG. 3a shows a schematic diagram of the refrigerant pump drive mode provided in an embodiment of the present disclosure.
  • the air-conditioning system 100 when the air-conditioning system 100 operates in the refrigerant pump drive mode, the refrigerant flows through the condenser 102, the liquid reservoir 104, the refrigerant pump 108, the expansion valve 110 and the evaporator 103 to form a cycle.
  • the first valve 106, the second valve 107 and the second bypass valve 111 are closed, and the first bypass valve 109 is turned on, wherein the expansion valve 110 can be opened to its maximum opening.
  • FIG3b shows a schematic diagram of the first overclocking mode provided in an embodiment of the present disclosure.
  • the air-conditioning system operates in the first overclocking mode, the refrigerant flows through the compressor 105 and the gas booster 101 at the same time and then enters the condenser 102, the liquid reservoir 104, the second bypass valve 111, the expansion valve 110, and the evaporator 103 to form a cycle.
  • the first valve 106, the second valve 107, and the second bypass valve 111 are turned on, and the first bypass valve 109 is turned off, wherein the expansion valve 110 can control its opening according to the superheat of the evaporator.
  • the compressor and the gas booster work simultaneously.
  • the outdoor temperature is low, the refrigerant flow in the air-conditioning system will increase significantly, and the cooling capacity of the air-conditioning system will increase by at least 40% to 50%. This excess cooling capacity can supplement the insufficient cooling capacity of the computer room, avoiding the high-temperature shutdown problem of information and communication technology equipment.
  • Figure 3c shows a schematic diagram of the hybrid drive mode provided in an embodiment of the present disclosure.
  • the air-conditioning system operates in the hybrid drive mode, the refrigerant enters the condenser 102, the liquid storage tank 104, the refrigerant pump 108, the expansion valve 110 and the evaporator 103 after passing through the gas booster 101 to form a cycle.
  • This hybrid drive mode replaces the hybrid mode of the existing technical solution, and utilizes the low working pressure difference of the gas booster to significantly reduce the system boosting power consumption compared to the compressor; the corresponding temperature of the outdoor natural cold source is increased by at least 5°C, and the duration of utilizing the outdoor natural cold source throughout the year is increased by more than 10%; at the same time, because the efficiency of the refrigerant pump is higher than that of the gas booster and the power consumption is lower than that of the gas booster when overcoming the same pressure drop, turning on the refrigerant pump in this mode to overcome part of the system pressure drop can further reduce the working pressure difference of the gas booster, reduce the overall power consumption of the refrigeration system, and improve the system energy efficiency ratio. It can increase the annual energy efficiency ratio of the air-conditioning unit by more than 20%, and the benefits of energy saving and emission reduction are very significant.
  • FIG3d shows a schematic diagram of the second overclocking mode provided in an embodiment of the present disclosure.
  • the refrigerant flows through the compressor 105 and the gas booster 101 at the same time and then enters the condenser 102, the liquid reservoir 104, the second bypass valve 111, the expansion valve 110, and the evaporator 103 to form a cycle.
  • the first valve 106, the second valve 107, and the second bypass valve 111 are turned on, and the first bypass valve 109 is turned off.
  • the compressor and the gas booster work at the same time.
  • the outdoor temperature is lower in this mode, and the refrigerant flow in the air-conditioning system will be significantly larger.
  • the cooling capacity of the air-conditioning system will increase by at least 30% to 40%. This excess cooling capacity can supplement the insufficient cooling capacity of the computer room, avoiding the problem of high-temperature shutdown of information and communication technology equipment.
  • FIG3e shows a schematic diagram of the gas booster driving mode provided in this embodiment.
  • the air-conditioning system operates in the gas booster driving mode, After passing through the gas booster 101, the refrigerant enters the condenser 102, the liquid storage tank 104, the second bypass valve 111, the expansion valve 110 and the evaporator 103 to form a cycle.
  • the second valve 107 and the second bypass valve 111 are turned on, and the first valve 106 and the first bypass valve 109 are turned off.
  • the low working pressure difference characteristic of the gas booster is adopted, which can greatly reduce the system boosting power consumption compared with the compressor, and can save more than 20% of energy consumption compared with the hybrid mode in the prior art solution.
  • Figure 3f shows a schematic diagram of the compressor drive mode provided in an embodiment of the present disclosure. As shown in Figure 3f, when the air-conditioning system operates in the compressor drive mode, the refrigerant enters the condenser 102, the liquid reservoir 104, the second bypass valve 111, the expansion valve 110 and the evaporator 103 after passing through the compressor 105 to complete a cycle.
  • the air-conditioning system can achieve air conditioning refrigeration without running other devices.
  • FIG. 3g shows a schematic diagram of the third overclocking mode provided in an embodiment of the present disclosure.
  • the air-conditioning system operates in the third overclocking mode, the refrigerant flows through the compressor 105 and the gas booster 101 at the same time and then enters the condenser 102, the liquid storage tank 104, the second bypass valve 111, the expansion valve 110, and the evaporator 103 to form a cycle.
  • the first valve 106, the second valve 107, and the second bypass valve 111 are turned on, and the first bypass valve 109 is turned off.
  • the compressor and the gas booster work at the same time, the refrigerant flow in the air-conditioning system will increase significantly, and the cooling capacity of the air-conditioning system will increase by at least 20% to 30%. This part of the excess cooling capacity can supplement the insufficient cooling capacity of the computer room, avoiding the high temperature shutdown problem of information and communication technology equipment.

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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
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  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

一种空调系统及其控制方法，涉及机房制冷系统技术领域，以解决过渡季节时空调系统的能耗过高，制冷效率低，严重影响机房全年维度下的整体能效和电能利用效率的问题。该空调系统包括气体增压器（101）、冷凝器（102）和蒸发器（103），气体增压器（101）的出口通过冷凝器（102）与蒸发器（103）的入口连接，蒸发器（103）的出口与所述气体增压器（101）的入口连接。该空调系统及其控制方法用于对空间进行制冷。

Description

一种空调系统及其控制方法
相关申请的交叉引用
本公开基于申请号为202311443652.8、申请日为2023年11月01日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本公开作为参考。
技术领域
本公开涉及机房制冷系统技术领域，尤其涉及一种空调系统及其控制方法。
背景技术
随着制冷技术的发展，系统简单、传热路径短、耗水量小的制冷剂系统重新成为了数据中心空调系统的首选技术。带有制冷剂泵的空调系统虽然是降低机房能耗的有效解决方案，但现有系统仍有其自身的局限性。
现有系统在室外温度为5℃～25℃的温度区间内的过渡季节时，同时运行压缩机及制冷剂泵制冷，即混合模式。此时，空调系统能耗过高，制冷效率低，严重影响机房全年维度下的整体能效和电能利用效率。
发明内容
本公开的目的在于提供一种空调系统及其控制方法，用于提高过渡季节时空调系统的制冷效率，降低空调系统的增压功耗，提高机房全年维度下的整体能效和电能利用效率。
为了实现上述目的，本公开提供一种空调系统，包括：一种空调系统，包括：气体增压器、冷凝器和蒸发器，所述气体增压器的出口通过所述冷凝器与所述蒸发器的入口连接，所述蒸发器的出口与所述气体增压器的入口连接。
与现有技术相比，本公开提供的空调系统中包括气体增压器、冷凝器和蒸发器，其中气体增压器的出口通过冷凝器与所述蒸发器的入口连接，蒸发器的出口与气体增压器的入口连接，冷却剂在气体增压器的作用下提高冷凝压力，并从气体增压器的出口通入冷凝器进行热量交换，随后冷却剂通入蒸发器的入口以将吸收空气中的热量。在此过程中，使得冷凝器中的冷凝压力高于蒸发器中的蒸发压力、冷凝温度高于蒸发温度，减少了现有技术方案中由于使用压缩机导致冷凝温度低于蒸发温度的发生几率，提高了空调系统的制冷效率，经过检测发现，通过使用该空调系统，使得冷凝器中的冷凝压力高于蒸发器中的蒸发压力，从而将利用室外自然冷源对应温度提升至少5℃以上，降低了利用室外自然冷源对应温度过低的几率，全年利用室外自然冷源的时长提升10％以上。
另外，现有技术的混合模式中至少使用了压缩机，而气体增压器具有低工作压差特点，因此将气体增压器替代压缩机后，可大幅度降低空调系统增压功耗，提高机房全年维度下的整体能效和电能利用效率。在此基础上，在过渡季节时，空调系统能够使用至少由气体增压器、冷凝器和蒸发器构成的回路进行制冷，无需按极端高温选型，解决了空调容量过大、数量过多、成本过高、数据中心交付初期空调负载率过低、电能利用效率过高问题。
本公开还提供一种空调系统控制方法，应用上述的空调系统，该方法包括：基于所述室内空间在目标位置的实际温度和预设温度，确定所述制冷空间的超额制冷需求指标；基于所述制冷空间的超额制冷需求指标和所述制冷空间的内外实际温度差异，确定所述空调系统的目标运行模式；控制所述空调系统在所述目标运行模式对所述制冷空间进行制冷。
与现有技术相比，本公开提供的一种空调系统控制方法的有益效果与上述的空调系统的有益效果相同，此处不做赘述。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本公开的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1示出了本公开实施例中提供的空调系统的结构示意图；
图2示出了本公开实施例中提供的空调系统控制方法的流程图；
图3a示出了本公开实施例中提供的制冷剂泵驱动模式的示意图；
图3b示出了本公开实施例中提供的第一超频模式的示意图；
图3c示出了本公开实施例中提供的混合驱动模式的示意图；
图3d示出了本公开实施例中提供的第二超频模式的示意图；
图3e示出了本公开实施例中提供的气体增压器驱动模式的示意图；
图3f示出了本公开实施例中提供的压缩机驱动模式的示意图；
图3g示出了本公开实施例中提供的第三超频模式的示意图。
具体实施方式
为了使本公开所要解决的技术问题、技术方案及有益效果更加清楚明白，以下结合附图及实施例，对本公开进行进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本公开，并不用于限定本公开。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本公开的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。“若干”的含义是一个或一个以上，除非另有明确具体的限定。
在本公开的描述中，需要理解的是，术语“上”、“下”、“前”、“后”、“左”、“右”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本公开和简化描述，而不是指示或暗示所指的器件或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本公开的限制。
需要说明的是，本公开中，“示例性的”或者“例如”等词用于表示作例子、例证或说明。本公开中被描述为“示例性的”或者“例如”的任何实施例或设计方案不应被解释为比其他实施例或设计方案更优选或更具优势。确切而言，使用“示例性的”或者“例如”等词旨在以具体方式呈现相关概念。
本公开中，“至少一个”是指一个或者多个，“多个”是指两个或两个以上。“和/或”，描述关联对象的关联关系，表示可以存在三种关系，例如，A和/或B，可以表示：单独存在A，同时存在A和B，单独存在B的情况，其中A，B可以是单数或者复数。字符“/”一般表示前后关联对象是一种“或”的关系。“以下至少一项(个)”或其类似表达，是指的这些项中的任意组合，包括单项(个)或复数项(个)的任意组合。例如，a，b或c中的至少一项(个)，可以表示：a，b，c，a和b的结合，a和c的结合，b和c的结合，或a、b和c的结合，其中a，b，c可以是单个，也可以是多个。
现有系统在室外温度为5℃～25℃的温度区间内的过渡季节时，同时运行压缩机及制冷剂泵制冷，即混合模式。对于混合模式，该模式依然主要利用压缩机进行制冷，制冷剂泵起到增加循环压力的作用，间接降低压缩机能耗，但降低幅度非常有限，且受到压缩机在不同工况下的工作特性的影响，部分工况下运行混合模式不会节能、反而会更加耗能，因此也造成空调系统在混合模式下的控制策略过于复杂且最终节能效果不佳。同时，由于过渡季节的时长在全年占比达到至少40％以上，因此过渡季节下空调的功耗和能效会对数据中心空调系统全年的运行能效、电能利用效率和耗电量带来很大影响；当前空调系统在过渡季节运行的混合模式节能效果非常有限，难以满足日益严格的电能利用效率要求。
不仅如此，空调按极端高温选型则会带来容量过大、数量过多、成本过高、数据中心交付初期空调负载率过低、电能利用效率过高等问题。
针对上述问题，本公开提供一种空调系统，用于提高过渡季节时空调系统的制冷效率，降低空调系统的增压功耗，提高机房全年维度下的整体能效和电能利用效率。图1示出了本公开实施例中提供的空调系统的结构示意图。如图1所示，该空调系统100包括：气体增压器101、冷凝器102和蒸发器103，气体增压器101的出口通过冷凝器102与蒸发器103的入口连接，蒸发器103的出口与气体增压器101的入口连接。应理解，为了调节制冷剂的循环量，还可以利用储液器104连通蒸发器103的入口和冷凝器102的出口。
在实际应用中，气体增压器101的出口通过冷凝器102与蒸发器103的入口连接，蒸发器103的出口与气体增压器101的入口连接，冷却剂在气体增压器101的作用下提高冷凝压力，并从气体增压器101的出口通入冷凝器102进行热量交换，随后冷却剂通入蒸发器103的入口以吸收空气中的热量。在此过程中，使得冷凝器102中的冷凝压力高于蒸发器103中的蒸发压力、冷凝温度高于蒸发温度，减少了现有技术方案中由于使用压缩机导致冷凝温度低于蒸发温度的发生几率，提高了空调系统的制冷效率，经过检测发现，通过使用该空调系统，可将利用室外自然冷源对应温度提升至少5℃以上，降低了利用室外自然冷源对应温度过低的几率，全年利用室外自然冷源的时长提升10％以上。
另外，现有技术的混合模式中至少使用了压缩机，而气体增压器101具有低工作压差特点，因此将气体增压器101替代压缩机后，可大幅度降低空调系统100的增压功耗，提高机房全年维度下的整体能效和电能利用效率。在此基础上，在过渡季节时，空调系统100能够使用至少由气体增压器101、冷凝器102、储液器104和蒸发器103构成的循环回路进行制冷，无需按极端高温选型，从而解决了空调容量过大、数量过多、成本过高、数据中心交付初期空调负载率过低、电能利用效率过高等问题。
当现有技术的混合模式中使用了制冷剂泵时，而本公开通过在空调系统中通过气体增压器驱动即可在实现过渡季节时进行制冷，从而减少了系统中制冷剂泵的运行时间，降低了制冷剂泵发生气蚀的概率，同时减缓了制冷剂泵的磨损速度，延长了制冷剂泵的工作寿命。
如图1所示，空调系统100还包括与气体增压器101并联的压缩机105，压缩机105的出口通过冷凝 器102与蒸发器103的入口连接，蒸发器103的出口与压缩机105的入口连接。
示例性的，在室外温度25℃以上时，可以由压缩机105、冷凝器102、储液器104和蒸发器103构成另一个循环回路。例如：在室外温度为26℃时，冷却剂在压缩机105的作用下提高冷凝压力，并从压缩机105的出口通入冷凝器102进行热量交换，随后冷却剂通入蒸发器103的入口以吸收空气中的热量，从而实现空调系统100的制冷目的。
在实际应用中，当室外温度为极端高温时，如40℃，空调系统100内冷凝压力与蒸发压力的压差过大，压缩机105受过大的压差影响会进入过压缩状态，从而造成压缩机105的流量大幅度下降，使得空调系统的制冷能力下降，空调系统的制冷量也会随之大幅度衰减，由此会带来数据中心内空调制冷量不足、信息通信技术设备的高温宕机风险。为了降低上述现象的发生几率，本公开提供的空调系统100中还包括与压缩机105并联的气体增压器101，气体增压器101的出口通过冷凝器102与蒸发器103的入口连接，蒸发器103的出口与气体增压器101的入口连接。在上述由压缩机105、气体增压器101、冷凝器102、储液器104和蒸发器103构成的循环回路中，气体增压器101和压缩机105共同工作，其中，气体增压器101能够分散空调系统中压缩机105受到的压差，降低了压缩机105受过大的压差影响而进入过压缩状态的几率，从而能够提高空调系统的制冷量，解决了室外高温或多台空调故障后，数据中心内空调制冷量不足带来的高温宕机风险的问题。此外，通过气体增压器101和压缩机105共同工作，能够显著提高冷却剂的冷凝压力，使得冷凝器102中的冷凝压力高于蒸发器103中的蒸发压力、冷凝温度高于蒸发温度，减少了压缩机105运行过程中冷凝温度低于蒸发温度的发生几率，提高了空调系统100的制冷效率。经过检测发现，通过使用该空调系统，可将利用室外自然冷源对应温度提升至少5℃以上，降低了利用室外自然冷源对应温度过低的几率，全年利用室外自然冷源的时长提升10％以上。
在实际应用中，可以根据实际需求选择使用的回路，从而解决了空调按极端高温选型带来的容量过大、数量过多、成本过高、数据中心交付初期空调负载率过低、电能利用效率过高等问题。
如图1所示，本实施例中提供的空调系统100还包括第一阀门106和第二阀门107，其中，压缩机105的入口通过第一阀门106与蒸发器103的出口连接；气体增压器101的入口通过第二阀门107与蒸发器103的出口连接。当压缩机105处在工作状态，第一阀门106导通，当气体增压器101处在工作状态，第二阀门107导通。
当空调系统100处在压缩机驱动模式(如下文图3f所示)，导通第一阀门106，使得压缩机105处在工作状态，关断第二阀门107，使得气体增压器101处在非工作状态，此时，制冷剂在压缩机105的驱动下，依次进入冷凝器102、储液罐104、蒸发器103中，以完成一个循环。当该循环结束后，制冷剂从蒸发器103的出口经第一阀门106进入压缩机105中，以进行下一个循环。此时，空调系统100仅需压缩机105运行就能实现制冷。
当空调系统100处在超频驱动模式，导通第一阀门106和第二阀门107，使得压缩机105和气体增压器101均处在工作状态，此时，制冷剂同时流经压缩机105和气体增压器101，并在其共同作用下，依次进入冷凝器102、储液罐104、蒸发器103中，以完成一个循环。当该循环结束后，制冷剂从蒸发器103的出口沿着第一阀门106和第二阀门107，同时进入压缩机105和气体增压器101，以进行下一个循环。当空调系统100处在超频驱动模式时，室外温度为极端高温，空调系统100内冷凝压力与蒸发压力的压差过大，压缩机105受过大的压差影响会进入过压缩状态，从而造成压缩机105的流量大幅度下降，使得空调系统的制冷能力下降，因此空调系统设置压缩机105和气体增压器101同时处在工作状态，以降低空调系统100内冷凝压力与蒸发压力的压差，提高空调系统100的制冷能力和制冷量。经检测，当空调系统100处在超频驱动模式时，极端高温工况下的制冷量提升20％以上，避免了因室外高温带来的制冷量大幅度衰减，减小了数据中心配置空调的规格和数量，降低了数据中心空调系统的初投资成本。
如图1所示，本实施例中提供的空调系统100还包括制冷剂泵108和第一旁通阀门109，冷凝器102的出口通过制冷剂泵108与蒸发器103的入口连接，制冷剂泵108的入口通过第一旁通阀门109与制冷剂泵108的出口连接，当空调系统处在制冷剂泵驱动模式(如下文图3a所示)，第一旁通阀门109导通。在实际应用中，在本公开实施例中提供的空调系统100中还包括膨胀阀门110，该膨胀阀门110设在蒸发器103的入口处，用于控制蒸发器103出口处气态的制冷剂的过热度，进而控制进入蒸发器103的制冷剂流量。
当室外温度为35℃时，空调系统100处在制冷剂泵驱动模式，可以由制冷剂泵108、蒸发器103、第一旁通阀门111、冷凝器102和储液器104构成一个循环回路。例如：在室外温度为25℃以上时，冷却剂进入冷凝器102、储液器104，在制冷剂泵108的驱动下经过蒸发器103流经导通的第一旁通阀门111，从而实现空调系统100的制冷目的。
当室外温度为5℃～25℃时，空调系统100处在混合驱动模式(如下文图3c所示)，可以由制冷剂泵108、蒸发器103、气体增压器101、冷凝器102和储液器104构成循环回路。例如：在室外温度为25℃时，关断第一阀门106，导通第二阀门107，关断第一旁通阀门109，使得压缩机105处在非工作状态， 气体增压器101和制冷剂泵108处在工作状态，此时，冷却剂在气体增压器101的驱动下，依次进入冷凝器102、储液器104，并在制冷剂泵108的驱动下经过蒸发器103，并重新流入气体增压器101的入口，从而实现空调系统100的制冷目的。在混合驱动模式中，采用气体增压器101的增压作用使得冷凝器102中的冷凝压力高于蒸发器103中的蒸发压力、冷凝温度高于蒸发温度，从而避免了现有技术方案中冷凝温度低于蒸发温度、利用室外自然冷源对应温度过低的问题，可将利用室外自然冷源对应温度提升至少5℃以上，全年利用室外自然冷源的时长提升10％以上。同时，由于克服相同压降时，制冷剂泵108的效率高于气体增压器101，功耗低于气体增压器101，因此该模式下开启制冷剂泵108能够克服一部分系统压降，可进一步降低气体增压器101的工作压差，减小空调系统整体功耗，提升系统能效比，相对现有技术方案中的混合模式，该混合驱动模式可提升空调系统能效比40％以上。
当室外温度为20℃～35℃时，空调系统100处在压缩机驱动模式，第一旁通阀门109关断，此时，空调系统100仅需压缩机105运行就能实现制冷。
如图1所示，空调系统100还包括第二旁通阀门111，蒸发器103的出口通过第二旁通阀门111与冷凝器102的入口连接，第二旁通阀门111分别与压缩机105和气体增压器101并联，第二旁通阀门111在空调系统处在超频驱动模式时导通，此时压缩机105和气体增压器101同时处在工作状态，降低了空调系统100内冷凝压力与蒸发压力的压差，提高了空调系统100的制冷能力和制冷量。经检测，当空调系统100处在超频驱动模式时，极端高温工况下的制冷量提升20％以上，避免了因室外高温带来的制冷量大幅度衰减，减小了数据中心配置空调的规格和数量，降低了数据中心空调系统的初投资成本。
本公开还提供一种空调系统控制方法，用于对上述的空调系统进行控制，其中，所述空调系统还包括压缩机和制冷剂泵，能够提高过渡季节时空调系统的制冷效率，满足低概率、短时间出现的历史极端高温下的制冷需求，提高机房全年维度下的整体能效和电能利用效率。图2示出了本公开实施例中提供的空调系统控制方法的流程图，如图2所示，该空调系统控制方法包括：
步骤201：基于室内空间在目标位置的实际温度和预设温度，确定制冷空间的超额制冷需求指标。
示例性的，根据不同的室内、室外工况，该空调系统相应运行于压缩机驱动模式、气体增压器驱动模式、混合驱动模式、制冷剂泵驱动模式和超频模式。
具体来说，当基于室内空间在目标位置的实际温度和预设温度，确定空调系统的制冷偏差；基于空调系统的制冷偏差和空调系统的允许制冷温度波动范围，确定制冷空间的超额制冷需求指标。
制冷空间的超额制冷需求指标CFC＝(Tc-Ts)/TP，Tc为室内空间在目标位置的实际温度，例如：送风温度、回风温度、冷通道温度等，具体位置可根据实际需求进行调整，在此不作限定；Ts为室内空间在目标位置的预设温度；TP为允许的温度波动范围。
其中，若制冷空间的超额制冷需求指标大于预设指标，确定目标运行模式为超频驱动模式；若制冷空间的超额制冷需求指标小于或等于预设指标，基于制冷空间的内外实际温度差异和驱动模式筛选条件，确定空调系统的目标运行模式。
步骤202：基于制冷空间的超额制冷需求指标和制冷空间的内外实际温度差异，确定空调系统的目标运行模式。
示例性的，制冷空间的内外实际温度差异Temd＝Tin-Tout，Tin为室内空调系统回风干球温度，Tout为室外空气干球温度。Td为预设阈值，对应不同的运行模式，可取为第一预设阈值Td1、第二预设阈值Td2、第三预设阈值Td3。
表1示出了本实施例中提供的空调系统的目标运行模式的判定条件。
表1
由上可知，当空调系统中包含制冷剂泵时，驱动模式筛选条件包括以下至少一种：
当空调系统的制冷空间的内外实际温度差异小于第一预设阈值Td1时，目标运行模式为制冷剂泵驱动模式，若制冷空间的超额制冷需求指标大于预设指标，目标运行模式为第一超频模式。
当空调系统的制冷空间的内外实际温度差异大于第一预设阈值Td1，且小于第二预设阈值Td2，目标运行模式为混合驱动模式，若制冷空间的超额制冷需求指标大于预设指标，目标运行模式为第二超频模式。
当空调系统的制冷空间的内外实际温度差异大于第二预设阈值Td2，且小于第三预设阈值Td3，若制冷空间的超额制冷需求指标小于或等于预设指标，目标运行模式为气体增压器驱动模式；若制冷空间的 超额制冷需求指标大于预设指标，目标运行模式为第二超频模式。
当空调系统的制冷空间的内外实际温度差异大于第三预设阈值Td3，目标运行模式为压缩机驱动模式，若制冷空间的超额制冷需求指标大于预设指标，目标运行模式为第三超频模式。
示例性的，该Td1、Td2、Td3的取值范围为0℃～30℃，且本实施例中提供的超频模式包括第一超频模式、第二超频模式和第三超频模式，根据空调系统的制冷空间的内外实际温度差异不同，所运行的超频模式也随之不同。
例如：当设置第一预设阈值Td1为0℃，第二预设阈值Td2为20℃，第三预设阈值Td3为30℃。若制冷空间的内外实际温度差异小于0℃时，目标运行模式为制冷剂泵驱动模式，若制冷空间的超额制冷需求指标CFC大于预设指标，目标运行模式为第一超频模式。
当空调系统的制冷空间的内外实际温度差异大于0℃，且小于20℃，目标运行模式为混合驱动模式，若制冷空间的超额制冷需求指标CFC大于预设指标，目标运行模式为第二超频模式。
当空调系统的制冷空间的内外实际温度差异大于30℃，目标运行模式为压缩机驱动模式，若制冷空间的超额制冷需求指标CFC大于预设指标，目标运行模式为第三超频模式。
应理解，CFC的预设指标可以根据实际情况进行设定，例如：100％、75％，在此不作限定。
当室外温度过高造成空调制冷量衰减过大或空调故障数量过多时，均会造成数据中心内制冷量不足，室内温度过高、以及CFC大于预设指标；因此通过该条件即可判定空调系统的目标运行模式的是否为超频模式。
步骤203：控制空调系统在目标运行模式对制冷空间进行制冷。
示例性的，若制冷空间的内外实际温度差异小于第一预设阈值，且超额制冷需求指标小于或等于预设指标时，空调系统运行于制冷剂泵驱动模式。图3a示出了本公开实施例中提供的制冷剂泵驱动模式的示意图。如图3a所示，空调系统100运行于制冷剂泵驱动模式时，制冷剂流经冷凝器102、储液器104、制冷剂泵108、膨胀阀门110和蒸发器103，以构成循环。在该制冷剂泵驱动模式下，关断第一阀门106、第二阀门107和第二旁通阀门111，导通第一旁通阀门109，其中，膨胀阀门110可打开至其最大开度。
示例性的，若制冷空间的内外实际温度差异小于第一预设阈值，且超额制冷需求指标大于预设指标时，空调系统运行于第一超频模式。图3b示出了本公开实施例中提供的第一超频模式的示意图。如图3b所示，空调系统运行于第一超频模式时，制冷剂同时流经压缩机105和气体增压器101后进入冷凝器102、储液器104、第二旁通阀111、膨胀阀门110、蒸发器103，以构成循环。在该第一超频模式下，导通第一阀门106、第二阀门107和第二旁通阀门111，关断第一旁通阀门109，其中，膨胀阀门110可根据蒸发器的过热度控制其开度。在该第一超频模式下，压缩机和气体增压器同时工作，该第一超频模式下室外温度较低，空调系统内的制冷剂流量会大幅度增加，空调系统的制冷量则会至少增加40％～50％，此部分多余的制冷量即可补充机房制冷量不足，避免了信息通信技术设备的高温宕机问题出现。
示例性的，若空调系统的制冷空间的内外实际温度差异大于第一预设阈值，小于第二预设阈值，且超额制冷需求指标小于或等于预设指标时，空调系统运行于混合驱动模式。图3c示出了本公开实施例中提供的混合驱动模式的示意图。如图3c所示，空调系统运行于混合驱动模式时，制冷剂经气体增压器101后进入冷凝器102、储液器104、制冷剂泵108、膨胀阀门110和蒸发器103，以构成循环。在该混合驱动模式下，导通第二阀门107，关断第一阀门106和第二旁通阀门111。该混合驱动模式代替现有技术方案的混合模式，利用气体增压器的低工作压差特点，相对于压缩机可大幅度降低系统增压功耗；将利用室外自然冷源对应温度提升至少5℃以上，全年利用室外自然冷源的时长提升10％以上；同时，由于克服相同压降时，制冷剂泵的效率高于气体增压器，功耗低于气体增压器，因此该模式下开启制冷剂泵克服一部分系统压降，可进一步降低气体增压器的工作压差，减小制冷系统整体功耗，提升系统能效比，可提升空调机组全年能效比20％以上，节能减排收益非常显著。
示例性的，空调系统的制冷空间的内外实际温度差异大于第一预设阈值且小于第二预设阈值，或空调系统的制冷空间的内外实际温度差异大于第二预设阈值且小于第三预设阈值时，对应的超额制冷需求指标大于预设指标，空调系统运行于第二超频模式。图3d示出了本公开实施例中提供的第二超频模式的示意图。如图3d所示，空调系统运行于第二超频模式时，制冷剂同时流经压缩机105和气体增压器101后进入冷凝器102、储液器104、第二旁通阀111、膨胀阀门110、蒸发器103，以构成循环。在该第二超频模式下，导通第一阀门106、第二阀门107和第二旁通阀门111，关断第一旁通阀门109。在该模式下，压缩机和气体增压器同时工作，相比压驱超频模式(也即第三超频模式)，该模式下室外温度较低，空调系统内的制冷剂流量会大幅度更大，空调系统的制冷量则会至少增加30％～40％，此部分多余的制冷量即可补充机房制冷量不足，避免了信息通信技术设备的高温宕机问题出现。
示例性的，若空调系统的制冷空间的内外实际温度差异大于第二预设阈值且小于第三预设阈值，制冷空间的超额制冷需求指标小于或等于预设指标，空调系统运行于气体增压器驱动模式。图3e示出了本实施例中提供的气体增压器驱动模式的示意图。如图3e所示，空调系统运行于气体增压器驱动模式时， 制冷剂经气体增压器101后进入冷凝器102、储液器104、第二旁通阀111、膨胀阀门110和蒸发器103，以构成循环。该模式下，导通第二阀门107和第二旁通阀门111，关断第一阀门106和第一旁通阀门109。该模式工作于过渡季节且室外温度相对较高时，采用气体增压器的低工作压差特点，相对于压缩机可大幅度降低系统增压功耗，较现有技术方案中的混合模式可节约20％以上能耗。
示例性的，若空调系统的制冷空间的内外实际温度差异大于第三预设阈值，超额制冷需求指标小于或等于预设指标，空调系统运行于压缩机驱动模式。图3f示出了本公开实施例中提供的压缩机驱动模式的示意图。如图3f所示，空调系统运行于压缩机驱动模式时，制冷剂经压缩机105后进入冷凝器102、储液器104、第二旁通阀111、膨胀阀门110和蒸发器103，以完成一个循环，该模式下，导通第一阀门106和第二旁通阀门111，关断第一旁通阀门109和第二阀门107，由压缩机105进行制冷。在该模式下，空调系统无需运行其他器件即可实现空调的制冷。
示例性的，若空调系统的制冷空间的内外实际温度差异大于第三预设阈值，超额制冷需求指标大于预设指标，空调系统运行于第三超频模式。图3g示出了本公开实施例中提供的第三超频模式的示意图。如图3g所示，空调系统运行于第三超频模式时，制冷剂同时流经压缩机105和气体增压器101后进入冷凝器102、储液器104、第二旁通阀111、膨胀阀门110、蒸发器103，以构成循环。在该第三超频模式下，导通第一阀门106、第二阀门107和第二旁通阀门111，关断第一旁通阀门109。该模式下，压缩机和气体增压器同时工作，空调系统内的制冷剂流量会大幅度增大，空调系统的制冷量则会至少增加20％～30％，此部分多余的制冷量即可补充机房制冷量不足，避免了信息通信技术设备的高温宕机问题出现。
以上所述，仅为本公开的具体实施方式，显而易见的，在不脱离本公开的精神和范围的情况下，可对其进行各种修改和组合。相应地，本说明书和附图仅仅是所附权利要求所界定的本公开的示例性说明，且视为已覆盖本公开范围内的任意和所有修改、变化、组合或等同物。显然，本领域的技术人员可以对本公开进行各种改动和变型而不脱离本公开的精神和范围。这样，倘若本公开的这些修改和变型属于本公开权利要求及其等同技术的范围之内，则本公开的意图包括这些改动和变型在内。任何熟悉本技术领域的技术人员在本公开揭露的技术范围内，可轻易想到变化或替换，都应涵盖在本公开的保护范围之内。因此，本公开的保护范围应以所述权利要求的保护范围为准。

Claims (13)

  1. 一种空调系统，包括：气体增压器、冷凝器和蒸发器，所述气体增压器的出口通过所述冷凝器与所述蒸发器的入口连接，所述蒸发器的出口与所述气体增压器的入口连接。
  2. 根据权利要求1所述的空调系统，其中，所述空调系统还包括与所述气体增压器并联的压缩机，所述压缩机的出口通过所述冷凝器与所述蒸发器的入口连接，所述蒸发器的出口还与所述压缩机的入口连接。
  3. 根据权利要求2所述的空调系统，其中，当所述压缩机处在工作状态，以及所述气体增压器处在非工作状态时，所述空调系统处在压缩机驱动模式；
    当所述压缩机和所述气体增压器均处在工作状态时，所述空调系统处在超频驱动模式。
  4. 根据权利要求2所述的空调系统，其中，所述空调系统还包括制冷剂泵和第一旁通阀门；
    所述冷凝器的出口通过所述制冷剂泵与所述蒸发器的入口连接，所述制冷剂泵的入口通过所述第一旁通阀门间接地与所述制冷剂泵的出口连接，当所述空调系统处在制冷剂泵驱动模式时，所述制冷剂泵处在工作状态，且所述第一旁通阀门导通。
  5. 根据权利要求4所述的空调系统，其中，当所述空调系统处在气体增压器驱动模式时，所述压缩机处在非工作状态，所述气体增压器处在工作状态，且所述第一旁通阀门关断。
  6. 根据权利要求4所述的空调系统，其中，当所述空调系统处在混合驱动模式时，所述压缩机处在非工作状态，所述气体增压器和所述制冷剂泵处在工作状态，且所述第一旁通阀门关断。
  7. 根据权利要求4所述的空调系统，其中，当所述空调系统处在压缩机驱动模式时，所述第一旁通阀门关断。
  8. 根据权利要求7所述的空调系统，其中，所述空调系统还包括第二旁通阀门，所述蒸发器的出口通过所述第二旁通阀门与所述冷凝器的入口连接，所述第二旁通阀门分别与所述压缩机和所述气体增压器并联，所述第二旁通阀门在所述空调系统处在超频驱动模式时导通。
  9. 根据权利要求2～8任一项所述的空调系统，其中，所述空调系统还包括第一阀门和第二阀门，所述压缩机的入口通过所述第一阀门与所述蒸发器的出口连接；所述气体增压器的入口通过所述第二阀门与所述蒸发器的出口连接；
    当所述压缩机处在工作状态时，所述第一阀门导通，当所述气体增压器处在工作状态时，所述第二阀门导通。
  10. 一种空调系统控制方法，用于对权利要求1～9任一项所述的空调系统进行控制，其中，所述空调系统还包括压缩机和制冷剂泵，所述方法包括：
    基于室内空间在目标位置的实际温度和预设温度，确定所述制冷空间的超额制冷需求指标；
    基于所述制冷空间的超额制冷需求指标和所述制冷空间的内外实际温度差异，确定所述空调系统的目标运行模式；
    控制所述空调系统在所述目标运行模式对所述制冷空间进行制冷。
  11. 根据权利要求10所述的空调系统控制方法，还包括：
    当基于所述室内空间在目标位置的实际温度和预设温度，确定所述空调系统的制冷偏差；
    基于所述空调系统的制冷偏差和所述空调系统的允许制冷温度波动范围，确定所述制冷空间的超额制冷需求指标。
  12. 根据权利要求10所述的空调系统控制方法，其中，
    所述基于所述制冷空间的超额制冷需求指标和所述制冷空间的内外实际温度差异，确定所述空调系统的目标运行模式包括：
    若所述制冷空间的超额制冷需求指标大于预设指标，确定所述目标运行模式为超频驱动模式；
    若所述制冷空间的超额制冷需求指标小于或等于预设指标，基于所述制冷空间的内外实际温度差异，确定所述空调系统的目标运行模式。
  13. 根据权利要求10所述的空调系统控制方法，其中，当所述空调系统包括：制冷剂泵时，确定所述空调系统的目标运行模式包括：
    当所述空调系统的制冷空间的内外实际温度差异小于第一预设阈值时，确定所述目标运行模式为制冷剂泵驱动模式，在所述制冷剂泵驱动模式中，所述制冷剂泵处于工作状态，所述压缩机和所述气体增压器均处于非工作状态；
    当所述空调系统的制冷空间的内外实际温度差异大于第一预设阈值，且小于第二预设阈值，确定所述目标运行模式为混合驱动模式，在所述混合驱动模式中，所述制冷剂泵和所述气体增压器均处于工作状态，所述压缩机处于非工作状态；
    当所述空调系统的制冷空间的内外实际温度差异大于第二预设阈值，且小于第三预设阈值时，若所述制冷空间的超额制冷需求指标小于或等于预设指标，确定所述目标运行模式为气体增压器驱动模式， 在所述气体增压器驱动模式中，所述气体增压器处于工作状态，所述制冷剂和所述压缩机均处于非工作状态；
    当所述空调系统的制冷空间的内外实际温度差异大于第三预设阈值时，确定所述目标运行模式为压缩机驱动模式，在所述压缩机驱动模式中，所述压缩机处于工作状态，所述制冷剂和所述气体增压器均处于非工作状态。
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