WO2016058280A1 - 一种复合式制冷多联空调系统及其控制方法 - Google Patents

一种复合式制冷多联空调系统及其控制方法 Download PDF

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Publication number
WO2016058280A1
WO2016058280A1 PCT/CN2015/000379 CN2015000379W WO2016058280A1 WO 2016058280 A1 WO2016058280 A1 WO 2016058280A1 CN 2015000379 W CN2015000379 W CN 2015000379W WO 2016058280 A1 WO2016058280 A1 WO 2016058280A1
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air
refrigeration
refrigerant
compressor
outdoor
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PCT/CN2015/000379
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English (en)
French (fr)
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王铁军
曾晓程
刘志峰
王景晖
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中国扬子集团滁州扬子空调器有限公司
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Publication of WO2016058280A1 publication Critical patent/WO2016058280A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices

Definitions

  • the invention relates to the technical field of refrigeration and air conditioning, and particularly relates to a composite refrigeration multi-connected air conditioning system capable of maximizing low-cost heat transfer by using a natural cold source and a control method thereof.
  • the rapid development of information industry and digital construction has promoted the number of data rooms and communication base stations, and the scale of construction has grown rapidly.
  • the energy consumption of air conditioners and base stations accounts for 40% to 50% of their total energy consumption.
  • the sensible heat load ratio of the equipment room and base station is large, and continuous cooling operation is required throughout the year.
  • the indoor temperature is set to be higher than the outdoor ambient temperature, especially in the low temperature season or cold area.
  • the conventional data room and communication base station air conditioning system are still It is necessary to continue to operate the refrigeration compressor.
  • the refrigeration system has low working efficiency and is prone to failure. If the indoor and outdoor temperature difference (natural cold source) can be used to transport heat at a low cost or provide cooling for the indoor side, the energy consumption of the air conditioning system will be greatly reduced. Operating costs.
  • China utility model patent ZL200720019537.8 discloses a computer room auxiliary energy-saving refrigeration device.
  • the air conditioner stops working, and the outdoor low-temperature air is directly sent to the indoor for electronic cabinet and other equipment to cool down, and the natural cold source is utilized. , reducing air conditioning energy consumption.
  • the direct use of outdoor low-temperature air for electronic cooling cannot ensure the indoor air quality, and it is impossible to prevent outdoor dust and moisture from entering the room, which may cause damage to electronic equipment such as servers.
  • a utility model patent ZL201020114596.X discloses a natural cold energy heat exchange device for a communication base station, including an air heat exchanger, an indoor fan, an outdoor fan and a box thereof.
  • the outdoor temperature is low
  • the outdoor low-temperature air is introduced, and the indoor air is exchanged with heat
  • the natural cold source is used indirectly to reduce the air temperature in the base station and reduce the energy consumption of the base station.
  • a gas-to-gas heat exchange can ensure the quality of indoor air, a large heat exchange area is required for a machine room object having a large heat load and a high temperature uniformity to overcome the disadvantage of low heat transfer efficiency of the gas-gas heat exchanger.
  • the Chinese invention patent CN201010528027.X discloses an air-cooled heat pipe type computer room air conditioning system, which has two working modes of compression refrigeration and heat pipe circulation refrigeration.
  • the cooling mode works, the first refrigerant in the refrigeration cycle evaporates and absorbs heat in the evaporative condenser, and cools and condenses the second refrigerant; when the outdoor temperature is ⁇ 20 °C, the system is converted into a heat pipe.
  • the circulating cooling mode uses the outdoor low temperature air to cool and condense the second refrigerant, and the compression refrigeration cycle stops working, thereby effectively reducing the annual air conditioning energy consumption.
  • This system makes up for the shortcomings of the first two systems in terms of utilizing outdoor low-temperature air cooling and ensuring indoor air quality, but the two working modes of compression refrigeration and heat pipe circulation refrigeration are switched at a certain temperature point, and the natural cold source of outdoor low-temperature air Not fully utilized; for the implementation of GB/T 19413-2010 In the air conditioning system, since the indoor side set temperature is 24 ° C, the outdoor ambient temperature of the compression refrigeration to the heat pipe circulation refrigeration must be very low, and the utilization rate of the natural cold source is low.
  • Utility model patent ZL01278831.7 discloses an energy-saving refrigeration cycle device with a circulation pump.
  • the use of a circulation pump in the heat pipe circulation system is beneficial to improve the working efficiency of the heat pipe cycle, and also simplifies the installation of the condenser and the liquid storage during the installation of the heat pipe system.
  • the relative position of the evaporator and the evaporator, but ZL01278831.7 is similar to CN201010528027.X in maximizing the utilization of outdoor cold air.
  • the upper limit temperature of the heat pipe cycle must be lower to smoothly connect with the refrigeration cycle.
  • the air conditioning system meets the air conditioning requirements of hundreds of tens of thousands of kW of large data room, and solves the multi-machine parallel connection of the composite refrigeration and air conditioning system.
  • the structural characteristic of the composite refrigeration multi-connected air conditioning system of the present invention is that the multi-connected air conditioning system is provided with two or more outdoor composite refrigeration modules (1) on the outdoor side to constitute a cold source system of the multi-connected air conditioning system, One or more indoor air cooler modules (3) are disposed on the indoor side, and the refrigerant storage and transport unit (2) is connected to the outdoor through the liquid collecting pipe (4), the liquid supply main pipe (5), and the return air main pipe (6).
  • a closed circulation system is formed between the composite refrigeration module (1) and the indoor cooling fan module (3);
  • the outdoor composite refrigeration module (1) is composed of a vapor compression refrigeration cycle of the first refrigerant and a composite refrigeration cycle of the second refrigerant through a heat exchanger (14), and passes through the second refrigerant to the indoor cooling fan module ( 3) conveying the cooling capacity;
  • the vapor compression refrigeration cycle is sequentially set according to the flow direction of the first refrigerant: the compressor (11), the air-cooled condenser (122) in the air-cooled heat exchange assembly (12), and the throttling a mechanism (13) and an evaporation passage (141) in the heat exchanger (14); a high pressure exhaust side of the compressor (11) connected to an inlet of the air-cooled condenser (122), a low pressure suction side and evaporation
  • the outlet of the passage (141) is connected;
  • the compressor (11) is a parallel combination of two compressors (111) and compressors (112) of the same specification;
  • the composite refrigeration cycle has a combined refrigeration working path and steam a compression refrigeration working path;
  • the indoor cooling fan module (3) is composed of an evaporator (31), an evaporating fan (32) and a flow control valve (33), and the outlet branch connecting valves (362) of the indoor cooling fan modules (3) are connected in parallel.
  • the flow control valve (33) is disposed at the At the inlet end of the evaporator (31), the temperature sensing element (35) of the flow control valve (33) is mounted on the wall of the outlet end of the evaporator (31);
  • the flow control valve (33) is a proportional control valve, wherein the temperature sensing element (35) converts a refrigerant temperature signal at an outlet of the evaporator (31) into a pressure signal, and transmits it to a flow control valve (35) through a capillary tube (34) to adjust a flow control valve (33)
  • the degree of opening thereby controlling the amount of liquid supplied to the evaporator (31) and the degree of
  • the refrigerant storage and transport unit (2) includes a liquid reservoir (22) and a liquid pump (21), and an input end of the liquid storage device (22) passes through a liquid collecting pipe (4) and each outdoor composite refrigeration module (1)
  • the outlet branch connecting valve (152) is connected, and the output end of the accumulator (22) passes through the liquid pump (21) and through the liquid supply manifold (5) and the inlet of each indoor cooling fan module (3)
  • the branch connection valve (361) is connected;
  • An overflow pipe (25) is disposed at a top of the accumulator (22), and the overflow pipe (25) is in communication with a return air main pipe (6) through a one-way valve (26), the one-way valve (26) ) is a single-way flow in the flow direction of the accumulator (22) toward the return air main (6).
  • the structural characteristic of the composite refrigeration multi-connected air conditioning system of the present invention is also that: in the air-cooled heat exchange assembly (12), both the air-cooled heat exchanger (121) and the air-cooled condenser (122) adopt parallel flow. a heat exchanger that is juxtaposed parallel to the wind direction, the air-cooled heat exchanger (121) is located on the inlet side, the air-cooled condenser (122) is located on the outlet side, and forms a duct with the fan (123) .
  • the structural characteristic of the composite refrigeration multi-connected air conditioning system of the present invention is also: in the refrigerant storage and delivery unit (2), the liquid pump (21) is a fixed-frequency shielded pump to keep the hydraulic head stable, and the liquid supply manifold (5) a bypass pipe (23) and a bypass valve (24) are disposed between the liquid accumulator (22), and the opening degree of the bypass valve (24) is controlled by the inlet pressure thereof, and the pressure is large, and the opening degree is large, and vice versa. Also.
  • the structural characteristic of the composite refrigeration multi-connected air conditioning system of the present invention is also that the fan (123) is a variable frequency speed control fan.
  • the composite refrigeration multi-connected air conditioning system of the present invention is also characterized in that: the first refrigerant is selected from R410A, R407, R134a, R290 or R32 refrigerant, and the second refrigerant is selected from R134a, R290 or R32 refrigerant.
  • the control method of the composite refrigeration multi-connected air conditioning system of the present invention is characterized in that: the multi-connected air conditioning system is set to be a vapor pressure Two different working modes of refrigeration and composite refrigeration, and have:
  • T h T h -T a
  • T h the measured value of the real-time temperature of the second refrigerant in the return air main pipe (6)
  • T a the measured value of the outdoor ambient temperature
  • A the set value.
  • the working mode of the vapor compression refrigeration means that the cooling capacity of the composite refrigeration multi-connected air conditioning system is all provided by operating vapor compression refrigeration; in the working mode of the vapor compression refrigeration, the outdoor composite refrigeration module is put into operation ( 1) The compressor (11) and the fan (123) are operated, the first solenoid valve (16) is opened, the second solenoid valve (17) is closed, and the second refrigerant is connected to the valve (151) and the first solenoid valve through the inlet branch pipe.
  • the adjustment of the cooling capacity is realized by the loading or unloading of the compressor (11), and the control method thereof is:
  • B is the set saturation temperature of the second refrigerant in the accumulator (22)
  • ⁇ B is the control deviation of B
  • T b is the detected value of the real-time saturation temperature of the second refrigerant in the accumulator (22).
  • the working mode of the composite refrigeration means preferentially utilizing the air-cooling heat exchanger (121) to provide the cooling capacity, and the insufficient cooling amount is supplemented by controlling the number of operating units and the operating frequency of the refrigeration compressor (11);
  • the control method is: if the refrigeration compressor (11) is operated on the outdoor side, the fan (123) of all the outdoor composite refrigeration modules (1) in the cold source system runs at a high speed, the first electromagnetic valve (16) is closed, and the second electromagnetic The valve (17) is opened, and the second refrigerant is connected to the valve (151) and the second solenoid valve (17) through the inlet branch pipe, first releasing heat in the air-cooling heat exchanger (121), and then condensing through the heat exchanger (14).
  • the passage (142) is further exothermic, and enters the liquid collecting pipe (4) through the outlet branch connecting valve (152), and then flows into the liquid accumulator (22);
  • control method of loading or unloading the compressor (11) is:
  • the compressor (11) is loaded until one compressor (111) or compressor (112) is put into operation in each outdoor composite refrigeration module (1), and then B+ is still satisfied. ⁇ B ⁇ T b , and then performing the second compressor operation or loading of the second-round outdoor composite refrigeration module (1);
  • the fan (123) When the operating conditions change such that B + ⁇ B ⁇ T b is satisfied, the fan (123) is operated one by one, and if B + ⁇ B ⁇ T b is still satisfied, the fan (123) speed is increased one by one to a high speed.
  • the first-in-first-stop first-rate operation mode is used; for all the compressors (11) in the system, the first-time first-stop first-stop operation is also used. In the mode, the start-stop interval of each compressor (11) is set to 3 to 5 minutes.
  • the invention integrates a new technology of air-cooled phase change refrigeration using vapor compression refrigeration and low-power natural cold source scale application, and performs condition switching and cooling capacity adjustment according to indoor and outdoor temperature difference and indoor heat load condition, and composite refrigeration
  • the application of the cyclic working mode broadens the working temperature zone where the natural cold source is applied, avoids the shortage of natural cold source when the indoor and outdoor temperature difference is small, and must operate the vapor compression refrigeration mode alone, which can maximize the utilization of the natural cold source and achieve low air conditioning units. Cost operation and energy saving purposes.
  • the outdoor side of the multi-connected air conditioning system of the present invention comprises two or more outdoor composite refrigeration modules to form a cold source system of the multi-connected air conditioning system, and the number of outdoor composite refrigeration modules and indoors can be flexibly configured according to the air conditioning design load.
  • the number of cooling fan modules, load matching and air conditioning system capacity is convenient; the outdoor composite refrigeration module adopts double compressors in parallel, the energy adjustment precision of the multi-compressor system is improved, and the area of the condensing heat exchanger is large when the single compressor is working.
  • the refrigeration system has high thermal efficiency; if a compressor fails, the outdoor composite refrigeration module will not be shut down. Even if an outdoor composite refrigeration module fails, it is convenient for quick repair or replacement, and will not be used for data center air conditioning systems. The quality of operation has a large impact and high reliability.
  • the invention designs an air-cooled heat exchanger, an air-cooled condenser and a fan of an outdoor composite refrigeration module into an air-cooled heat exchange assembly. It is beneficial to improve production efficiency and product quality; air-cooled heat exchanger and air-cooled condenser are aluminum microchannel parallel flow structure, which is light in weight, small in volume and high in heat transfer efficiency, which can significantly reduce heat transfer temperature difference and improve system. Thermal efficiency; the two heat exchangers share a fan channel to make the space structure compact, the system layout is beautiful, and the cost is low.
  • the air-cooled condenser is a key component of the vapor compression cycle system. Its function is to cool, condense and supercool the high-temperature and high-pressure refrigerant. It works in the high and medium temperature environment outside, and the heat transfer of the air-cooled condenser in the medium temperature environment. The temperature difference is large and the heat transfer capacity is rich; the air-cooled heat exchanger works only in the environment of medium and low temperature outdoors, and the natural cold source partially replaces or completely replaces the high-power compressor refrigeration, which is a substantial energy saving of the invention.
  • the air-cooled heat exchanger and the air-cooled condenser are respectively disposed on the air inlet side and the air outlet side, and the two work simultaneously only under the condition that the outdoor temperature is moderate, and the air-cooled heat exchanger is disposed on the air inlet side. It not only increases the cooling capacity of the air-cooled heat exchanger, but also improves the efficiency of using the natural cold source.
  • the temperature rise of the air heated by the air-cooled heat exchanger is less than 10 °C, which is efficient for the vapor compression cycle system and improves the reliability of the refrigeration system. Sex has a positive effect.
  • the invention provides a refrigerant storage and conveying unit, and is provided with a large-capacity second refrigerant liquid storage device, which has large heat capacity, can quickly respond to the heat load of the adjusted object, has wide frequency change, good stability, high adjustment precision; liquid pump delivery second
  • the refrigerant is concentrated and cooled in the indoor side, and the power cycle reliability is high, which is not restricted by the installation position; the second refrigerant undergoes phase change heat at the heat release end and the heat absorption section, the heat transfer coefficient is large, the heat exchange efficiency is high, and the heat exchange is performed.
  • the utility model has the advantages of compact structure, avoiding the problem that the heat transfer efficiency of the gas-gas or gas-water heat exchanger is low, the heat exchanger area is large, and the circulation flow is small, the conveying work is small; the liquid pump is forced to circulate, and the liquid supply amount is stable, The flow adjustment is convenient and accurate; the liquid pump head can be optimally matched according to the liquid supply distance, the drop and the system resistance, which is conducive to the precise control of the air conditioning temperature.
  • the composite refrigeration multi-connected air conditioning system of the invention adopts multiple outdoor composite refrigeration modules, and each of the outdoor composite refrigeration modules has two refrigeration compressors, and the refrigeration capacity is precisely adjusted through multiple compressors, which reduces the number of Failure rate and manufacturing cost of the combined air conditioning system.
  • Figure 1 is a block diagram of a composite refrigeration multi-connected air conditioning system of the present invention
  • FIG. 2 is a block diagram of an outdoor composite refrigeration module of the present invention
  • 3a is a schematic front view showing the structure of an air-cooled heat exchanger assembly according to the present invention.
  • Figure 3b is a side view showing the structure of the air-cooled heat exchange assembly of the present invention.
  • FIG. 4 is a block diagram of an indoor cooling fan module of the present invention.
  • FIG. 5 is a schematic diagram of energy regulation planning of a composite refrigeration multi-connected air conditioning system according to the present invention.
  • the structure of the composite refrigeration multi-connected air conditioning system in the present embodiment is set as follows: two or more outdoor composite refrigeration modules 1 are disposed on the outdoor side to form a cold source system of the multi-connected air conditioning system, One or more indoor cooling fan modules 3 are disposed on the indoor side, and the refrigerant storage and conveying unit 2 is connected to the outdoor composite refrigeration module 1 and the indoor cooling fan module 3 through the liquid collecting pipe 4, the liquid supply main pipe 5 and the return air main pipe 6. Form a closed loop system.
  • the vapor-compression refrigeration cycle of the first refrigerant and the composite refrigeration cycle of the second refrigerant are combined by the heat exchanger 14 and are passed through the second refrigerant to the indoors.
  • the cooling fan module 3 delivers the cooling capacity; the vapor compression refrigeration cycle is sequentially arranged according to the flow direction of the first refrigerant: the compressor 11, the air-cooled condenser 122 in the air-cooled heat exchange assembly 12, the throttle mechanism 13, and the heat exchanger
  • the compressor 11 is two compressors of the same specification (111), the parallel combination of the compressor (112);
  • the composite refrigeration cycle has a composite refrigeration working path and a vapor compression refrigeration working path; the composite refrigeration working path is: the second refrigerant is introduced into the inlet branch connection valve 151, in turn The two solenoid valves 17, the air-cooled heat exchanger 121 in the air-cooled heat exchange assembly 12 and the condensation passage 142 in the heat exchanger 14 are led out in the outlet branch connection valve 152; the vapor compression
  • the fan 123 is a shared fan for the air-cooled heat exchanger 121 and the air-cooled condenser 122, and the fan 123 is a variable frequency speed control fan;
  • the first refrigerant is R410A, R407, R134a, R290 or R32 refrigerant, the second refrigerant is R134a, R290 or R32 refrigerant.
  • the indoor cooling fan module 3 is composed of an evaporator 31, an evaporating fan 32, and a flow control valve 33.
  • the outlet branch connecting valve 362 of each indoor cooling fan module 3 is connected in parallel to the return air main pipe 6, And connected to the inlet branch connection valve 151 of each outdoor composite refrigeration module 1 through the return air header 6; the flow control valve 33 is disposed at the inlet end of the evaporator 31, and the temperature sensing element 35 of the flow control valve 33 is mounted on the evaporator 31.
  • the outlet end is on the pipe wall.
  • the flow control valve 33 is a proportional control valve, and the temperature sensing element 35 converts the refrigerant temperature signal at the outlet of the evaporator 31 into a pressure signal, and transmits it to the flow control valve 35 through the capillary 34, and adjusts the opening degree of the flow control valve 33, thereby controlling evaporation.
  • the refrigerant storage and transport unit 2 in this embodiment includes a liquid reservoir 22 and a liquid pump 21, and the liquid storage device 22 is transported.
  • the inlet end is connected to the outlet branch connection valve 152 of each outdoor composite refrigeration module 1 through the liquid collection tube 4, and the output end of the liquid storage unit 22 passes through the liquid pump 21 and passes through the liquid supply main pipe 5 and each indoor cooling fan module 3.
  • the inlet branch connection valve 361 is connected; an overflow pipe 25 is provided at the top of the accumulator 22, and the overflow pipe 25 communicates with the return air main pipe 6 through the check valve 26, and the check valve 26 is oriented toward the accumulator 22.
  • the flow direction of the return air main pipe 6 is unidirectional.
  • the refrigerant storage and conveying unit is arranged, and the second refrigerant storage device with larger capacity is arranged, and the heat storage capacity is large, the thermal inertia is large, and the heat load of the adjusted object can be quickly responded to frequently, the wide variation, the stability of the liquid supply temperature is good, and the air conditioning is good.
  • the temperature accuracy is high; the second refrigerant conveyed by the liquid pump is concentrated circulation cooling on the indoor side, the power cycle reliability is high, and is not restricted by the installation position; the second refrigerant undergoes phase change heat at the heat release end and the heat absorption end, and the heat transfer coefficient
  • the corresponding structural settings also include:
  • the air-cooling heat exchanger 121 and the air-cooling condenser 122 both adopt a parallel flow heat exchanger and are juxtaposed in parallel with the wind direction, and the wind
  • the cold heat exchanger 121 is located on the air inlet side
  • the air-cooled condenser 122 is located on the air outlet side, and forms a duct with the fan 123.
  • the arrows in Fig. 3a indicate the wind direction.
  • the air-cooled condenser 122 is a key component of the vapor compression cycle system. It functions as a refrigerant that cools, condenses, and subcools high-temperature and high-pressure refrigerants.
  • the air cooling heat exchanger 121 and the air cooling condenser 122 are respectively disposed on the air inlet side and the air outlet side, and both work simultaneously under the condition that the outdoor temperature is medium temperature, and the air cooling heat exchanger 121 is disposed in the air inlet.
  • the cooling capacity of the air-cooled heat exchanger 121 is increased, and the efficiency of utilizing the natural cold source is improved, and the temperature rise of the air heated by the air-cooling heat exchanger 121 is less than 10 ° C, and the steam compression cycle system is efficiently operated and improved.
  • the reliability of the refrigeration system has a positive effect.
  • the air-cooled heat exchanger 121, the air-cooled condenser 122 and the fan 123 of the outdoor composite refrigeration module 1 are designed as air-cooled heat exchange assemblies, which are beneficial to improve production efficiency and product quality; air-cooled heat exchanger 121, air-cooled
  • the condenser 122 adopts an aluminum microchannel parallel flow structure, which is light in weight, small in volume, high in heat transfer efficiency, can obviously reduce heat transfer temperature difference and improve system thermal efficiency; the two heat exchangers share one fan channel to make the space structure compact, and the system Beautiful layout and low cost.
  • the liquid pump 21 is a fixed frequency shield pump to keep the hydraulic head stable, and a bypass pipe 23 and a bypass valve are provided between the liquid supply manifold 5 and the accumulator 22.
  • the opening degree of the bypass valve 24 is controlled by its inlet pressure, and the pressure is large, and the opening degree is large, and vice versa.
  • the purpose is to bypass the excess second refrigerant to the accumulator 22 when the indoor side thermal load is small and the flow control valve 33 has a small opening degree, thereby keeping the evaporating pressure of the indoor cooling fan module 3 relatively stable.
  • the control method of the composite refrigeration multi-connected air conditioning system in this embodiment is: setting the multi-connected air conditioning system into two different working modes of vapor compression refrigeration and composite refrigeration, and having:
  • Th is the measured value of the real-time temperature of the second refrigerant in the return air main pipe 6
  • T a is a measured value of the outdoor ambient temperature
  • A is a set value.
  • the working mode of the vapor compression refrigeration means that the cooling capacity of the composite refrigeration multi-connected air conditioning system is all provided by the operation of the vapor compression refrigeration, as shown in the A2-A3 segment of FIG. 5, and the number of the refrigeration compressors 11 is controlled.
  • the adjusted cooling capacity is matched with the heat load of the air conditioner; in the working mode of the vapor compression refrigeration, the compressor 11 and the fan 123 in the outdoor composite refrigeration module 1 that is put into operation operate, the first electromagnetic valve 16 is opened, and the second The solenoid valve 17 is closed, and the second refrigerant is connected to the first solenoid valve 16 through the inlet branch pipe, and is exchanged with the first refrigerant in the evaporation passage 141 in the condensation passage 142 of the heat exchanger 14, and the second refrigerant is condensed by heat.
  • the accumulator 22 After passing through the outlet branch connecting valve 152 and the collecting tube 4, the accumulator 22 is entered; for an outdoor composite refrigerating module 1, the fan of the outdoor combined refrigerating module 1 is only when both compressors 11 are stopped. 123 stops running, and the first solenoid valve 16 and the second solenoid valve 17 are closed;
  • the adjustment of the cooling capacity is realized by loading or unloading of the compressor 11, and the control method thereof is:
  • B is the set saturation temperature of the second refrigerant in the accumulator 22
  • ⁇ B is the control deviation of B
  • T b is the real-time temperature detection value of the second refrigerant in the accumulator 22
  • B and ⁇ B are set values. It can be set according to air conditioning object and temperature control accuracy requirements, which is convenient for users to use and debug.
  • the working mode of the composite refrigeration means that the air cooling heat exchanger (121) is preferentially used to provide the cooling capacity, and the insufficient cooling amount is supplemented by controlling the number and frequency of the running of the refrigeration compressor 11, as shown in the A1-A2 segment of Fig. 5, M point
  • the air-cooling heat exchanger 121 provides a cooling capacity of Q 2
  • the operating compressor 11 provides a cooling capacity Q 1 as a supplement; the composite cooling is controlled by: if the outdoor cooling compressor 11 is operated, all the outdoor cooling source systems
  • the fan 123 of the compound refrigeration module 1 runs at a high speed to maximize the utilization of the natural cold source.
  • the first solenoid valve 16 is closed, the second solenoid valve 17 is opened, and the second refrigerant is connected to the valve 151 and the second solenoid valve 17 through the inlet branch pipe.
  • the air-cooled heat exchanger 121 releases heat, and then further exotherms through the condensation passage 142 of the heat exchanger 14, passes through the outlet branch connecting valve 152, enters the collecting pipe 4, and then flows into the accumulator 22.
  • control method for loading or unloading the compressor 11 is:
  • the compressor 11 is loaded until one compressor 11 is put into operation in each outdoor composite refrigeration module 1, and if it still satisfies B+ ⁇ B ⁇ T b , then the second round outdoor The second compressor 11 of the composite refrigeration module 1 is loaded.
  • T b ⁇ B - ⁇ B the compressor 11 is deloaded until only one compressor 11 in each outdoor composite refrigeration module 1 is operated, and then if T b ⁇ B - ⁇ B is still satisfied, then the second round reduction is performed. Load until all the compressors 11 of the outdoor composite refrigeration module 1 are stopped.
  • the composite cooling multiple In the working mode of the combined refrigeration, when the indoor side heat load is lower than the cooling amount provided by the air-cooling heat exchanger 121, all the compressors 11 stop working, as shown in the A0-A1 segment of Fig. 5, the composite cooling multiple The air conditioning system operates in the most energy-saving working state that fully utilizes the natural cooling source. In order to ensure the liquid supply temperature and the air conditioning temperature accuracy, the cooling capacity generated by the air-cooling heat exchanger 121 is adjusted according to the following rules:
  • the fan 123 When the operating conditions change such that B + ⁇ B ⁇ T b is satisfied, the fan 123 is operated one by one, and if B + ⁇ B ⁇ T b is still satisfied, the speed of the fan 123 is increased one by one to a high speed until the compressor 11 starts operating.
  • the abscissa is the outdoor ambient temperature
  • the ordinate is the energy, including: air conditioning rated heat load, compressor cooling capacity, air cooling capacity and air conditioning energy consumption.
  • the A2-A3 section is the compressor refrigeration, the compressor plus load and load regulates the cooling capacity
  • the A1-A2 section is the composite refrigeration, the air-cooled full load operation, the compressor plus load and load adjustment cooling capacity
  • A0-A1 section the compressor stops Work, adjust the fan speed to adjust the air-cooled cooling capacity
  • the total energy consumption of the air conditioner changes, such as the bottom line segment, from high temperature to low temperature, respectively, W1, W2, W3, W4, W5.
  • the heat load of the equipment room is constant in the wide temperature range; the output cooling capacity of the vapor compression refrigeration and the air cooling refrigeration increases with the decrease of the ambient temperature in the operation interval, and energy adjustment is required to make the heat load to the engine room.
  • the A3-A2 section is the vapor compression refrigeration mode working area.
  • the cooling capacity of the composite refrigeration multi-connected air conditioning system is provided by the operation of vapor compression refrigeration. By controlling the number of compressors 11 and the frequency to adjust the cooling output, the corresponding energy consumption changes. From W1 to W2; A1-A2 is the composite refrigeration zone in the transitional season.
  • the air-cooled heat exchanger 121 maximizes the full-load operation and uses the natural cold source to control the number of compressors 11 and the frequency-regulated cooling output. From W3 to W4, since the air-cooling cycle works effectively reduces the energy consumption of the compressor 11, W2>W3; the A1-A0 segment is a low temperature season, and the engine room thermal load is lower than that provided by the air-cooled heat exchanger (121).
  • Cooling capacity all compressors 11 stop working, the combined cooling multi-connected air conditioning system operates in the most energy-saving working state that fully utilizes the natural cold source, and controls the speed of the fan 123 or the number of running to adjust the cooling capacity provided by the air-cooled heat exchanger 121
  • Single vapor compression refrigeration then increased to W1 to W6, energy consumption not only in A3-A0 air conditioning energy consumption changes throughout the operating temperature region, while also increasing the risk of failure low temperature vapor compression refrigeration system running.
  • the first-in-first-stop first-time rotation operation mode is used; All the compressors 11 in the system are also operated by the first-on-first-stop first-rate operation mode to improve the average life of the composite refrigeration multi-connected air-conditioning system and the utilization rate of key components; the start-stop interval of each compressor 11 is preset. The time is 3 to 5 minutes.
  • two liquid pumps 21 are usually required to be configured to form a wheeled operation with one standby to ensure system operation reliability.
  • the closed server cabinet has a set air supply temperature of 22 ° C and a return air temperature of 33 ° C.
  • the difference between the second refrigerant temperature in the return air header 6 and the outdoor ambient temperature is ⁇ T a , and the set value of A is 2. If ⁇ T a ⁇ 2, the vapor compression refrigeration operation mode is operated; if ⁇ T a ⁇ 2, the composite refrigeration is operated. Operating mode.
  • the air conditioning system when the outdoor air temperature is >20 °C, the air conditioning system operates in the vapor compression refrigeration zone; when the outdoor air temperature is ⁇ 20 °C, the air conditioning system can operate in the composite refrigeration working zone; since the computer system usually has a working load of 40 to 60% Scope, the operating rule of the composite refrigeration working area is: full-load operation air cooling to maximize the utilization of the natural cold source chamber, when the cooling capacity generated by the air-cooling heat exchanger 121 is greater than or equal to the heat load, the compressor 11 stops working.
  • the air conditioning system fully utilizes the natural cold source to achieve low energy consumption operation of the air conditioning system.
  • the cold source system of the air conditioning unit operates in a vapor compression refrigeration mode, and the control method thereof is: the compressor 11 of the composite refrigeration module 1 that is not put into operation, the fan 123, the first solenoid valve 16, and the first The two solenoid valves 17 are all in a closed state; the compressor 11 and the fan 123 of the composite refrigeration module 1 that is put into operation are operated, the first electromagnetic valve 16 is opened, the second electromagnetic valve 17 is closed, and the second refrigerant is connected to the valve 151 through the inlet branch pipe.
  • the first solenoid valve 16 exchanges heat with the first refrigerant in the evaporation passage 141 in the condensation passage 142 of the heat exchanger 14, and the second refrigerant releases heat and condenses, and passes through the outlet branch pipe connecting valve 152 to enter the liquid collection pipe 4, and then Flow into the reservoir 22.
  • the saturation temperature and deviation of the second refrigerant in the accumulator 22 are set to 18 ° C ⁇ 1 ° C, T b is the real-time saturation temperature of the second refrigerant in the accumulator 22, and the loading, deloading and energy adjustment of the compressor 11 are performed.
  • the control method is:
  • the cold source system of the air conditioning unit operates in the composite cooling mode.
  • the control rules are: priority to operate air cooling, maximizing the use of natural cooling sources, and insufficient cooling is supplemented by running compressor refrigeration.
  • the refrigeration compressor 11 If the refrigeration compressor 11 is operated on the outdoor side, the fan 123 of all the composite refrigeration modules 1 in the cold source system is operated at full load, the first electromagnetic valve 16 is closed, the second electromagnetic valve 17 is opened, and the second refrigerant is connected to the valve through the inlet branch pipe. 151.
  • the second electromagnetic valve 17 first releases heat in the air-cooling heat exchanger 121, and then further releases heat through the condensation passage 142 of the heat exchanger 14, passes through the outlet branch pipe connecting valve 152, enters the liquid collection pipe 4, and then flows into the storage tube. Liquidizer 22.
  • the control method of the load, load shedding and energy adjustment of the compressor 11 is: if 17 ° C ⁇ T b ⁇ 19 ° C is satisfied, the same is maintained; °C ⁇ T b , the compressor 11 is loaded until one compressor 11 is put into operation in each composite refrigeration module 1, and then the second compressor 11 of the second-stage composite refrigeration module 1 is loaded; if T is satisfied b ⁇ 17 ° C, the compressor 11 is deloaded until only one compressor 11 in each of the composite refrigeration modules 1 is operated, and then the second round of load shedding is performed until all the compressors 11 of the composite refrigeration module 1 are stopped.
  • the energy regulation rule is : If T b ⁇ 17 ° C is satisfied, the rotation speed of the fan 123 is reduced one by one according to the setting procedure, and if T b ⁇ 17 ° C is still satisfied, the operation of the fan 123 is stopped one by one;
  • the composite refrigeration multi-connected air conditioning system When the composite refrigeration multi-connected air conditioning system is operated in the composite cooling mode, after some or all of the fans 123 are shut down, when the outdoor ambient temperature rises, or the indoor side heat load increases, or both conditions occur simultaneously, if 19 ° C is satisfied ⁇ T b , the fan 123 is operated, and if 19 ° C ⁇ T b is still satisfied, the rotation speed of the fan 123 is increased one by one to a high speed, and if 19 ° C ⁇ T b is still satisfied, the startup compressor 11 is insufficient in replenishing capacity.
  • the first-in-first-stop first-time rotation operation mode is adopted; for all the compressors 11 in the system, the first-time first-stop first-stop rotation operation mode is also used.
  • the present invention is applied to an air-conditioning object such as a machine room having an indoor side set temperature of 27 ° C or 24 ° C, and the set saturation temperature T b of the second refrigerant in the accumulator 22 can be appropriately adjusted to satisfy the air supply air supply temperature and the cooling capacity. Under the required conditions, the use of outdoor low-temperature air as a natural cold source is maximized to achieve low-carbon operation of the air-conditioning system and high quality of indoor air.

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Abstract

一种复合式制冷多联空调系统及其控制方法，其特征是多联空调系统的室外侧设置两个或两个以上的室外复合式制冷模块（1）构成多联空调的冷源系统，室外复合式制冷模块（1）由第一冷媒的蒸汽压缩制冷循环回路与第二冷媒循环回路复合构成，在室内侧设置一个或一个以上的室内冷风机模块（3），第二冷媒的储存输送单元（2）通过集液管（4）、供液总管（5）和回气总管（6）连接在室外复合式制冷模块（1）与室内冷风机模块（3）之间构成闭式循环系统。该空调系统根据空调对象的设计热负荷配置室内、外的模块数，精确调节制冷量，满足各类全天候运行的数据机房和电子设备的热控需求；可最大化利用冬季和过渡季节室内外的正温差低成本排热，实现空调系统节能。

Description

一种复合式制冷多联空调系统及其控制方法 技术领域
本发明涉及制冷空调技术领域，具体涉及一种能够最大化利用自然冷源低成本输送热量的复合式制冷多联空调系统及其控制方法。
背景技术
信息产业和数字化建设的快速发展，推动了数据机房、通讯基站的数量，建设规模快速增长，据统计机房、基站空调的能耗占其总能耗的40％～50％。机房、基站的显热负荷比大，一年四季需连续制冷运行，在室内侧设定温度高于室外环境温度的季节，尤其在低温季节或寒冷地区，常规的数据机房和通讯基站空调系统仍需继续运行制冷压缩机，制冷系统工作效率低而且易发生故障，若能利用室内外温差(自然冷源)低成本输送热量或为室内侧提供冷量，将大大减小空调系统的能耗和运行成本。
利用室外低温空气为室内侧提供冷量的方法已得到业内学者和工程技术人员的关注，并以不同的形式展开工程技术研究与应用，如目前采用的新风系统，此外还有不同形式的气-气、气-水热交换系统，以及应用热管技术的复合型空调。
中国实用新型专利ZL200720019537.8中公开了一种机房辅助节能制冷装置，当室外空气温度较低时，空调停止工作，直接将室外低温空气送至室内用于电子柜等设备降温，利用自然冷源，减少空调能耗。但这种直接利用室外低温空气用于电子冷却由于不能确保室内空气品质，无法杜绝室外的灰尘、水分等进入室内，易对服务器等电子设备造成损害。
中国实用新型专利ZL201020114596.X中公开了一种用于通信基站的自然冷能热交换装置，包括空气换热器、室内风机、室外风机及其箱体。当室外温度较低时，将室外低温空气引入，与室内空气进行热交换，间接利用自然冷源降低基站内空气温度，减少基站能耗。此种气-气热交换虽然能够保证室内空气的品质，但对于热负荷大和温度均匀度要求高的机房对象，需要庞大的换热面积以克服气-气热交换器传热效率低的弊端。
中国发明专利CN201010528027.X中公开了一种风冷式热管型机房空调系统，该系统具有压缩式制冷和热管循环制冷两种工作模式。当室外温度≥20℃时制冷模式工作，参与制冷循环的第一制冷工质在蒸发冷凝器中蒸发吸热，冷却和冷凝第二制冷工质；当室外温度＜20℃时，系统转换为热管循环制冷模式，利用室外低温空气对第二制冷工质进行冷却和冷凝，压缩式制冷循环停止工作，从而有效减少全年空调能耗。此系统在利用室外低温空气冷量和确保室内空气品质方面弥补了前两种系统的不足，但压缩式制冷和热管循环制冷两种工作模式在某一温度点切换，室外低温空气的自然冷源没得到充分利用；对于执行GB/T 19413-2010 的空调系统，由于室内侧设定温度为24℃，压缩式制冷转换到热管循环制冷的室外环境温度必定很低，自然冷源的利用率低。
实用新型专利ZL01278831.7公开了一种带循环泵的节能型制冷循环装置，在热管循环系统中使用循环泵有利于提高热管循环的工作效率，也简化了热管系统安装时对冷凝器、储液器和蒸发器相对位置的要求，但ZL01278831.7在最大化利用室外低温空气的冷量方面的不足与CN201010528027.X类似，即热管循环工作的上限温度必须较低才能与制冷循环平稳衔接。
大数据、云计算等信息化技术发展的推动，大型数据机房面积已发展到数千～数十万平方米，单位面积热流密度从5kW/m2增长到超级计算机系统的35kW/m2之多，产生了对更大功率的高效空调系统及其更灵活的组合和控制方式的需要。
发明内容
为避免机房空调系统在低温季节仍需要运行蒸气压缩制冷所产生的高能耗及可靠性等不足，满足大型数据机房数百～数万kW容量的空调需求，并解决复合式制冷空调系统多机并联技术及制冷量调节与能量控制等问题，最大化地利用自然冷源，实现复合空调产品规模化、高效率生产和应用，本发明提供了一种复合式制冷多联空调系统及其控制方法。
本发明为解决技术问题采用如下技术方案：
本发明复合式制冷多联空调系统的结构特点是：所述多联空调系统是在室外侧设置两个或两个以上的室外复合式制冷模块(1)构成多联空调系统的冷源系统，在室内侧设置一个或一个以上的室内冷风机模块(3)，冷媒储存输送单元(2)通过集液管(4)、供液总管(5)以及回气总管(6)连接在所述室外复合式制冷模块(1)与室内冷风机模块(3)之间构成闭式循环系统；
所述室外复合式制冷模块(1)由第一冷媒的蒸气压缩制冷循环回路与第二冷媒的复合制冷循环回路通过换热器(14)复合构成，并通过第二冷媒向室内冷风机模块(3)输送冷量；所述蒸气压缩制冷循环回路按第一冷媒的流向依次设置为：压缩机(11)、风冷换热总成(12)中的风冷冷凝器(122)、节流机构(13)以及换热器(14)中的蒸发通道(141)；所述压缩机(11)的高压排气侧与风冷冷凝器(122)的入口相连接、低压吸气侧与蒸发通道(141)的出口相连接；所述压缩机(11)为两台同规格的压缩机(111)、压缩机(112)的并联组合；所述复合制冷循环回路具有复合制冷工作路径和蒸气压缩制冷工作路径；所述复合制冷工作路径是：第二冷媒在进口支管连接阀(151)中导入，依次经第二电磁阀(17)、风冷换热总成(12)中的风冷换热器(121)和换热器(14)中的冷凝通道(142)，并在出液支管连接阀(152)中导出；所述蒸气压缩制冷工作路径是：第二冷媒在所述进口支管连接阀(151)中 导入，依次经第一电磁阀(16)和换热器(14)中的冷凝通道(142)后在所述出口支管连接阀(152)中导出；所述换热器(14)采用板式换热器或壳管式冷凝蒸发器；在所述风冷换热总成(12)中，设置风机(123)是为所述风冷换热器(121)和所述风冷冷凝器(122)的共用风机；
所述室内冷风机模块(3)是由蒸发器(31)、蒸发风机(32)和流量控制阀(33)构成，各室内冷风机模块(3)的出口支路连接阀(362)并联连接至回气总管(6)，并通过所述回气总管(6)与各室外复合式制冷模块(1)的进口支管连接阀(151)相连接；所述流量控制阀(33)设置在所述蒸发器(31)的入口端，所述流量控制阀(33)的感温元件(35)安装在所述蒸发器(31)的出口端的管壁上；所述流量控制阀(33)为比例调节阀，所述感温元件(35)将蒸发器(31)出口的冷媒温度信号转换为压力信号，并通过毛细管(34)传递至流量控制阀(35)，调节流量控制阀(33)的开度，从而控制蒸发器(31)的供液量及其出口的过热度；
所述冷媒储存输送单元(2)包括储液器(22)和液泵(21)，所述储液器(22)的输入端通过集液管(4)与各室外复合式制冷模块(1)中的出液支管连接阀(152)相连接，所述储液器(22)的输出端通过液泵(21)并经供液总管(5)与各室内冷风机模块(3)的进口支路连接阀(361)相连接；
在所述储液器(22)的顶部设有溢气管(25)，所述溢气管(25)通过单向阀(26)与回气总管(6)相连通，所述单向阀(26)是以储液器(22)朝向回气总管(6)的流动方向单向导通。
本发明复合式制冷多联空调系统的结构特点也在于：在所述的风冷换热总成(12)中，风冷换热器(121)和风冷冷凝器(122)均采用平行流换热器，并迎着风向平行并列，所述风冷换热器(121)位于入风侧、风冷冷凝器(122)位于出风侧，且与所述风机(123)构成一个风道。
本发明复合式制冷多联空调系统的结构特点也在于：在所述冷媒储存输送单元(2)中，液泵(21)为定频屏蔽泵以保持供液压头稳定，在供液总管(5)与储液器(22)之间设置旁通管(23)及旁通阀(24)，所述旁通阀(24)的开度受其入口压力控制，压力大则开度大，反之亦然。
本发明复合式制冷多联空调系统的结构特点也在于：所述风机(123)为变频调速风机。
本发明复合式制冷多联空调系统的结构特点也在于：所述第一冷媒选用R410A、R407、R134a、R290或R32制冷剂，所述第二冷媒选用R134a、R290或R32制冷剂。
本发明复合式制冷多联空调系统的控制方法的特点是：设置所述多联空调系统为蒸气压 缩制冷和复合制冷的两种不同工作模式，并有：
在ΔTa＜A的工况下，运行蒸气压缩制冷的工作模式；
在ΔTa≥A的工况下，运行复合制冷的工作模式；
其中：ΔTa＝Th-Ta，Th为回气总管(6)中第二冷媒实时温度的测量值，Ta为室外环境温度的测量值，A为设定值。
本发明复合式制冷多联空调系统的控制方法的特点还在于：
所述蒸气压缩制冷的工作模式是指：复合式制冷多联空调系统的冷量全部由运行蒸气压缩制冷所提供；在所述蒸气压缩制冷的工作模式下，投入运行的室外复合式制冷模块(1)中的压缩机(11)和风机(123)运行、第一电磁阀(16)开启、第二电磁阀(17)关闭，第二冷媒通过进口支管连接阀(151)和第一电磁阀(16)，在换热器(14)的冷凝通道(142)中与蒸发通道(141)内的第一冷媒进行热交换，第二冷媒放热冷凝后经过出液支管连接阀(152)和集液管(4)进入储液器(22)；对于某个室外复合式制冷模块(1)，只有在压缩机(11)均停止工作时，该室外复合式制冷模块(1)的风机(123)才停止运行，并且第一电磁阀(16)和第二电磁阀(17)关闭；
制冷量的调节通过压缩机(11)的加载或减载来实现，其控制方法是：
若满足B-ΔB≤Tb≤B+ΔB，维持压缩机(11)运行状态不变；
若满足B+ΔB＜Tb，压缩机(11)加载；
若满足Tb＜B-ΔB，压缩机(11)减载；
其中：B为储液器(22)内第二冷媒的设定饱和温度，ΔB为B的控制偏差，Tb为储液器(22)内第二冷媒的实时饱和温度的检测值。
本发明复合式制冷多联空调系统的控制方法的特点还在于：
所述复合制冷的工作模式是指：优先利用风冷换热器(121)提供冷量，不足的冷量通过控制制冷压缩机(11)的运行台数和运行频率进行补充；所述复合制冷的控制方式是：若室外侧有制冷压缩机(11)运行，则冷源系统中所有室外复合式制冷模块(1)的风机(123)高速运行，第一电磁阀(16)关闭、第二电磁阀(17)开启，第二冷媒通过进口支管连接阀(151)、第二电磁阀(17)，首先在风冷换热器(121)中放热，然后通过换热器(14)的冷凝通道(142)进一步放热，经出液支管连接阀(152)进入集液管(4)，再流入储液器(22)；
在所述复合式制冷的工作模式下，压缩机(11)的加载或减载的控制方法是：
若满足B-ΔB≤Tb≤B+ΔB，维持压缩机(11)运行状态不变；
若满足B+ΔB＜Tb，压缩机(11)加载，直至每个室外复合制冷模块(1)中都有一个压 缩机(111)或压缩机(112)投入工作，之后若是仍然满足B+ΔB＜Tb，再进行第二轮室外复合制冷模块(1)的第二个压缩机工作或加载；
若满足Tb＜B-ΔB，压缩机(11)减载，直至每个室外复合制冷模块(1)中仅有一个压缩机(111)或压缩机(112)工作，之后若是仍然满足Tb＜B-ΔB，再进行第二轮减载，直至所有室外复合制冷模块(1)的压缩机(11)全部停止工作。
本发明复合式制冷多联空调系统的控制方法的特点还在于：
在复合制冷的工作模式下，当室内侧热负荷低于由风冷换热器(121)所提供的冷量时，所有压缩机(11)停止工作；按如下规则调节制冷量：
若满足B-ΔB≤Tb≤B+ΔB，维持风机(123)运行状态不变；
若满足Tb＜B-ΔB，逐个降低风机(123)的转速，之后若是仍然满足Tb＜B-ΔB，则逐个停止风机(123)的运行；
当工况发生变化使得满足B+ΔB＜Tb时，逐个运行风机(123)，之后若是仍然满足B+ΔB＜Tb，则逐个提高风机(123)转速至高速。
本发明复合式制冷多联空调系统的控制方法的特点还在于：
对于所述系统中所有室外复合式制冷模块(1)，采用先开则先停的轮值运行方式进行工作；对于所述系统中所有压缩机(11)，同样采用先开则先停的轮值运行方式进行工作，设置各压缩机(11)的启停间隔时间为3～5分钟。
与已有技术相比，本发明有益效果体现在：
1、本发明集成应用了蒸气压缩式制冷和低功耗自然冷源规模化应用的风冷相变制冷新技术，根据室内外温差和室内热负荷状况进行工况切换和制冷量调节，复合制冷循环工作模式的应用拓宽了应用自然冷源的工作温区，避免了室内外温差较小时自然冷源不足而必须单一运行蒸气压缩制冷工作模式，可实现最大化利用自然冷源，达到空调机组低成本运行和节能的目的。
2、本发明多联空调系统的室外侧由两个或两个以上的室外复合式制冷模块构成多联空调系统的冷源系统，可根据空调设计负荷灵活配置室外复合式制冷模块的数量和室内冷风机模块的数量，负荷匹配和空调系统增容方便；室外复合式制冷模块采用双压缩机并联设置，多压缩机系统的能量调节精度提高，在单压缩机工作时冷凝换热器面积大，制冷系统热效率高；如遇某个压缩机故障，不至于该室外复合式制冷模块故障停机，即使某个室外复合式制冷模块发生故障，也便于快速维修或更换，不会对数据中心空调系统的运行质量有大的影响，可靠性高。
3、本发明将室外复合式制冷模块的风冷换热器、风冷冷凝器和风机设计成风冷换热总成， 有益于提高生产效率和产品质量；风冷换热器、风冷冷凝器为铝质微通道平行流结构，其质轻、体积小，传热效率高，可明显减小传热温差、提高系统热效率；两个换热器共用一个风机通道使得空间结构紧凑，系统布局美观，造价低。
4、风冷冷凝器是蒸气压缩循环系统的关键部件，功能是冷却、冷凝和过冷高温高压的制冷剂，在室外为高、中温的环境下工作，中温环境下风冷冷凝器的传热温差大、传热能力富裕；风冷换热器仅在室外为中、低温的环境下才工作，利用自然冷源部分替代或完全替代高功耗的压缩机制冷，是本发明产生大幅度节能效果的关键；将风冷换热器与风冷冷凝器分别设置在入风侧和出风侧，两者仅在室外为中温的条件下同时工作，风冷换热器设置在入风侧，既增大了风冷换热器的制冷量，提高了利用自然冷源的效率，经风冷换热器加热的空气温升小于10℃，对蒸气压缩循环系统高效运行和提高制冷系统的可靠性有积极的效果。
5、本发明设置冷媒储存输送单元，配置大容量第二冷媒储液器，热容量大，可快速响应被调对象热负荷频繁、宽幅变化，稳定性好，调节精度高；液泵输送第二冷媒为室内侧集中循环供冷，动力循环可靠性高，不受安装位置限制；第二冷媒在放热端和吸热段进行相变换热，传热系数大、换热效率高，换热器结构紧凑，避免了采用气-气或气-水换热器传热效率低，换热器面积庞大的问题，而且循环流量小，输送功小；采用液泵强制循环，供液量稳定，流量调节便捷、精确；液泵压头可根据供液距离、落差及系统阻力进行最佳匹配，利于空调温度的精密控制。
6、本发明复合式制冷多联空调系统采用多个室外复合式制冷模块，每个室外复合式制冷模块中都有两个制冷压缩机，通过多台压缩机进行制冷量精确调节，降低了多联空调系统的故障率和制造成本。
附图说明
图1为本发明复合式制冷多联空调系统方框图；
图2为本发明中室外复合式制冷模块方框图；
图3a为本发明中风冷换热总成主视结构示意图；
图3b为本发明中风冷换热总成侧视结构示意图；
图4为本发明中室内冷风机模块方框图；
图5为本发明复合式制冷多联空调系统能量调节规划示意图；
图中标号：1室外复合式制冷模块，2冷媒储存输送单元，3室内冷风机模块，4集液管，5供液总管，6回气总管，11压缩机，12风冷换热总成，121风冷换热器，122风冷冷凝器，123风机，13节流机构，14换热器，141蒸发通道，142冷凝通道，151进口支管连接阀，152 出液支管连接阀，16第一电磁阀，17第二电磁阀，21液泵，22储液器，23旁通管，24旁通阀，25溢气管，26单向阀，31蒸发器，32蒸发风机，33流量控制阀，34毛细管，35感温元件，361进口支路连接阀，362出口支路连接阀。
具体实施方式
参见图1和图2，本实施例中复合式制冷多联空调系统的结构设置为：在室外侧设置两个或两个以上的室外复合式制冷模块1构成多联空调系统的冷源系统，在室内侧设置一个或一个以上的室内冷风机模块3，冷媒储存输送单元2通过集液管4、供液总管5和回气总管6连接在室外复合式制冷模块1与室内冷风机模块3之间构成闭式循环系统。
如图2所示，本实施例中室外复合式制冷模块1由第一冷媒的蒸气压缩制冷循环回路与第二冷媒的复合制冷循环回路通过换热器14复合构成，并通过第二冷媒向室内冷风机模块3输送冷量；蒸气压缩制冷循环回路按第一冷媒的流向依次设置为：压缩机11、风冷换热总成12中的风冷冷凝器122、节流机构13以及换热器14中的蒸发通道141；压缩机11的高压排气侧与风冷冷凝器122的入口相连接、低压吸气侧与蒸发通道141的出口相连接；压缩机11为两台同规格的压缩机(111)、压缩机(112)的并联组合；复合制冷循环回路具有复合制冷工作路径和蒸气压缩制冷工作路径；复合制冷工作路径是：第二冷媒在进口支管连接阀151中导入，依次经第二电磁阀17、风冷换热总成12中的风冷换热器121和换热器14中的冷凝通道142，并在出液支管连接阀152中导出；蒸气压缩制冷工作路径是：第二冷媒在进口支管连接阀151中导入，依次经第一电磁阀16和换热器14中的冷凝通道142后在出口支管连接阀152中导出；换热器14是采用板式换热器或者壳管式冷凝蒸发器；在风冷换热总成12中，设置风机123是为风冷换热器121和风冷冷凝器122的共用风机，风机123为变频调速风机；第一冷媒选用R410A、R407、R134a、R290或R32制冷剂，第二冷媒选用R134a、R290或R32制冷剂。
参见图4，本实施例中室内冷风机模块3是由蒸发器31、蒸发风机32和流量控制阀33构成，各室内冷风机模块3的出口支路连接阀362并联连接至回气总管6，并通过回气总管6与各室外复合式制冷模块1的进口支管连接阀151相连接；流量控制阀33设置在蒸发器31的入口端，流量控制阀33的感温元件35安装在蒸发器31的出口端的管壁上。流量控制阀33为比例调节阀，感温元件35将蒸发器31出口的冷媒温度信号转换为压力信号，并通过毛细管34传递至流量控制阀35，调节流量控制阀33的开度，从而控制蒸发器31的供液量及其出口的过热度。
如图1所示，本实施例中冷媒储存输送单元2包括储液器22和液泵21，储液器22的输 入端通过集液管4与各室外复合式制冷模块1中的出液支管连接阀152相连接，储液器22的输出端通过液泵21并经供液总管5与各室内冷风机模块3的进口支路连接阀361相连接；在储液器22的顶部设有溢气管25，溢气管25通过单向阀26与回气总管6相连通，单向阀26是以储液器22朝向回气总管6的流动方向单向导通。设置冷媒储存输送单元，配置较大容量的第二冷媒储液器，储液热容量大则热惯性大，可快速响应被调对象热负荷频繁、宽幅变化，供液温度的稳定性好，空调温度精度高；液泵输送第二冷媒为室内侧集中循环供冷，动力循环可靠性高，不受安装位置限制；第二冷媒在放热端和吸热端进行相变换热，传热系数大、换热效率高，换热器体积小、结构紧凑，循环流量小，输送功小；采用液泵强制循环，供液量稳定，流量调节便捷、精确；液泵压头可根据供液距离、落差及系统阻力进行最佳匹配，利于空调温度的精密控制。
具体实施中，相应的结构设置也包括：
如图2、图3a和图3b所示，在风冷换热总成12中，风冷换热器121和风冷冷凝器122均采用平行流换热器，并迎着风向平行并列，风冷换热器121位于入风侧、风冷冷凝器122位于出风侧，且与风机123构成一个风道，图3a中各箭头所示为风向。风冷冷凝器122是蒸气压缩循环系统的关键部件，功能是冷却、冷凝和过冷高温高压的制冷剂，在室外为高、中温的环境下工作，中温环境下风冷冷凝器的传热温差大、传热能力富裕；风冷换热器121在室外为中、低温的环境下工作，利用自然冷源部分替代或完全替代高功耗的压缩机11制冷，是本发明产生大幅度节能效果的关键；将风冷换热器121与风冷冷凝器122分别设置在入风侧和出风侧，两者仅在室外为中温的条件下同时工作，风冷换热器121设置在入风侧，既增大了风冷换热器121的制冷量，提高了利用自然冷源的效率，经风冷换热器121加热的空气温升小于10℃，对蒸气压缩循环系统高效运行和提高制冷系统的可靠性有积极的效果。将室外复合式制冷模块1的风冷换热器121、风冷冷凝器122和风机123设计成风冷换热总成，有益于提高生产效率和产品质量；风冷换热器121、风冷冷凝器122采用铝质微通道平行流结构，质轻、体积小，传热效率高，可明显减小传热温差、提高系统热效率；两个换热器共用一个风机通道使得空间结构紧凑，系统布局美观，造价低。
如图1所示，在冷媒储存输送单元2中，液泵21为定频屏蔽泵以保持供液压头稳定，在供液总管5与储液器22之间设置旁通管23及旁通阀24，旁通阀24的开度受其入口压力控制，压力大则开度大，反之亦然。其目的是：当室内侧热负荷较小、流量控制阀33开度较小时，将多余的第二冷媒旁通至储液器22，保持室内冷风机模块3的蒸发压力相对稳定。
本实施例中复合式制冷多联空调系统的控制方法是：设置多联空调系统为蒸气压缩制冷和复合制冷的两种不同工作模式，并有：
在ΔTa＜A的工况下，运行蒸气压缩制冷的工作模式；
在ΔTa≥A的工况下，运行复合制冷的工作模式；
其中：ΔTa＝Th-Ta，Th为回气总管6中第二冷媒实时温度的测量值，Ta为室外环境温度的测量值，A为设定值。
具体实施中，蒸气压缩制冷的工作模式是指：复合式制冷多联空调系统的冷量全部由运行蒸气压缩制冷所提供，如图5的A2-A3段，通过控制制冷压缩机11的运行台数和频率，调节制冷量与空调热负荷相匹配；在蒸气压缩制冷的工作模式下，投入运行的室外复合式制冷模块1中的压缩机11和风机123运行、第一电磁阀16开启、第二电磁阀17关闭，第二冷媒通过进口支管连接阀151和第一电磁阀16，在换热器14的冷凝通道142中与蒸发通道141内的第一冷媒进行热交换，第二冷媒放热冷凝后经过出液支管连接阀152和集液管4进入储液器22；对于某个室外复合式制冷模块1，只有在两台压缩机11均停止工作时，该室外复合式制冷模块1的风机123才停止运行，并且第一电磁阀16和第二电磁阀17关闭；
制冷量的调节通过压缩机11的加载或减载来实现，其控制方法是：
若满足B-ΔB≤Tb≤B+ΔB，维持压缩机11运行状态不变；
若满足B+ΔB＜Tb，压缩机11加载；
若满足Tb＜B-ΔB，压缩机11减载；
其中：B为储液器22内第二冷媒的设定饱和温度，ΔB为B的控制偏差，Tb为储液器22内第二冷媒的实时温度检测值，B和ΔB均为设定值，可根据空调对象及温控精度要求设定，方便用户使用和调试。
复合制冷的工作模式是指：优先利用风冷换热器(121)提供冷量，不足冷量通过控制制冷压缩机11的运行台数和频率进行补充，如图5的A1-A2段，M点风冷换热器121提供的冷量为Q2，运行压缩机11提供制冷量Q1作为补充；复合制冷的控制方式是：若室外侧有制冷压缩机11运行，则冷源系统中所有室外复合式制冷模块1的风机123高速运行，最大化利用自然冷源，第一电磁阀16关闭、第二电磁阀17开启，第二冷媒通过进口支管连接阀151、第二电磁阀17，首先在风冷换热器121中放热，然后通过换热器14的冷凝通道142进一步放热，经出液支管连接阀152进入集液管4，再流入储液器22。
在复合式制冷的工作模式下，压缩机11的加载或减载的控制方法是：
若满足B-ΔB≤Tb≤B+ΔB，维持压缩机11运行状态不变。
若满足B+ΔB＜Tb，压缩机11加载，直至每个室外复合制冷模块1中都有一个压缩机11投入工作后，之后若是仍然满足B+ΔB＜Tb，再进行第二轮室外复合制冷模块1的第二个压缩机11加载。
若满足Tb＜B-ΔB，压缩机11减载，直至每个室外复合制冷模块1中仅有一个压缩机11工作后，之后若是仍然满足Tb＜B-ΔB，再进行第二轮减载，直至所有室外复合制冷模块1的压缩机11全部停止工作。
在复合制冷的工作模式下，当室内侧热负荷低于由风冷换热器121所提供的冷量时，所有压缩机11停止工作，如图5的A0-A1段，复合式制冷多联空调系统运行在完全利用自然冷源的最节能工作状态，为了保证供液温度和空调温度精度，以如下规则调节风冷换热器121所产生的制冷量：
若满足B-ΔB≤Tb≤B+ΔB，维持风机123运行状态不变。
若满足Tb＜B-ΔB，逐个降低风机123的转速，之后若是仍然满足Tb＜B-ΔB，则逐个停止风冷电机123的运行。
当工况发生变化使得满足B+ΔB＜Tb时，逐个运行风机123，之后若是仍然满足B+ΔB＜Tb，则逐个提高风机123转速至高速，直至压缩机11开始工作。
图5中横坐标为室外环境温度，纵坐标为能量，包括：空调额定热负荷，压缩机制冷量，风冷制冷量和空调能耗。其中A2-A3段为压缩机制冷，压缩机加减载调节制冷量；A1-A2段为复合制冷，风冷满负荷运行，压缩机加减载调节制冷量；A0-A1段，压缩机停止工作，调节风机速度调节风冷的制冷量；在各段中，空调总能耗的变化如最底部线段，从高温至低温，分别是W1、W2、W3、W4、W5。
如图5所示，机房热负荷在宽温区不变；蒸气压缩制冷和风冷制冷的输出制冷量在运行区间随着环温的下降而增大，需要进行能量调节使之与机房热负荷相匹配。A3-A2段为蒸气压缩制冷模式工作区，复合式制冷多联空调系统的冷量全部由运行蒸气压缩制冷来提供，通过控制压缩机11运行台数和频率调节制冷量输出，对应的能耗变化从W1至W2；A1-A2段为过渡季节的复合制冷区，风冷换热器121满负荷运行最大化利用自然冷源，控制压缩机11运行台数和频率调节制冷量输出，对应能耗变化从W3至W4，由于风冷循环工作有效地减少了压缩机11的能耗，W2＞W3；A1-A0段为低温季节，机房热负荷低于由风冷换热器(121)所提供的冷量，所有压缩机11停止工作，复合式制冷多联空调系统运行在完全利用自然冷源的最节能工作状态，控制风机123速度或运行个数调节风冷换热器121所提供的制冷量，对应能耗变化从W4至W5；在宽温区内，复合式制冷多联空调系统的总能耗随着环温的下降逐渐减小，自然冷源的使用大幅降低了系统的总能耗，如采用单一的蒸气压缩制冷，则在整个运行温区A3-A0空调能耗变化为W1至W6，不仅能耗增加，同时还增加蒸气压缩制冷系统运行在低温环境的故障风险。
对于系统中所有室外复合式制冷模块1，采用先开则先停的轮值运行方式进行工作；对 于系统中所有压缩机11，同样采用先开则先停的轮值运行方式进行工作，提高复合式制冷多联空调系统的平均寿命和关键部件的利用率；预先设置各压缩机11的启停间隔时间为3～5分钟。实际运行中，在冷媒储存输送单元2中，通常需要配置两台液泵21，以便形成一用一备的轮值运行，保证系统运行可靠性。
以一台实际运行的高性能计算机系统的空调为实施例，闭式服务器机柜的设定送风温度为22℃、回风温度为33℃。
回气总管6中第二冷媒温度与室外环境温度的差值为ΔTa，A的设定值为2，若ΔTa＜2，运行蒸气压缩制冷工作模式；若ΔTa≥2，运行复合制冷工作模式。
可以预测：当室外空气温度＞20℃时，空调系统运行在蒸气压缩制冷区；室外空气温度≤20℃时，空调系统可以运行在复合制冷工作区；由于计算机系统通常工作负荷在40～60％范围，复合制冷工作区的运行规则是：满负荷运行风冷以实现最大化利用自然冷源室，当风冷换热器121所产生的制冷量大于或等于热负荷时，压缩机11停止工作，空调系统完全利用自然冷源，实现空调系统低能耗运行。
当ΔTa＜2时，空调机组的冷源系统运行在蒸气压缩制冷工作模式，其控制方法是：没投入运行的复合式制冷模块1的压缩机11、风机123、第一电磁阀16、第二电磁阀17均处于关闭状态；投入运行的复合式制冷模块1的压缩机11和风机123运行、第一电磁阀16开、第二电磁阀17关，第二冷媒通过进口支管连接阀151、第一电磁阀16，在换热器14的冷凝通道142中与蒸发通道141内的第一冷媒进行热交换，第二冷媒放热冷凝，经出液支管连接阀152进入集液管4，再流入储液器22。
设定储液器22内第二冷媒的饱和温度及偏差为18℃±1℃，Tb为储液器22内第二冷媒的实时饱和温度，压缩机11的加、减载及能量调节的控制方法是：
若满足17℃≤Tb≤19℃，维持压缩机11运行状态不变；若满足19℃＜Tb，压缩机11加载；若满足Tb＜17℃，压缩机11减载。
当ΔTa≥2时，空调机组的冷源系统运行在复合制冷工作模式，其控制规则是：优先运行风冷，最大化利用自然冷源，不足冷量由运行压缩机制冷予以补充。
若室外侧有制冷压缩机11运行，则冷源系统中所有复合式制冷模块1的风机123满负荷运行，第一电磁阀16关、第二电磁阀17开，第二冷媒通过进口支管连接阀151、第二电磁阀17，首先在风冷换热器121中放热，然后通过换热器14的冷凝通道142进一步放热、经出液支管连接阀152进入集液管4，再流入储液器22。
在复合式制冷多联空调系统运行在复合制冷工作模式时，压缩机11的加、减载及能量调节的控制方法是：若满足17℃≤Tb≤19℃，维持不变；若满足19℃＜Tb，压缩机11加载，直至 每个复合制冷模块1中都有一个压缩机11投入工作后，再进行第二轮复合制冷模块1的第二个压缩机11的加载；若满足Tb＜17℃，压缩机11减载，直至每个复合制冷模块1中仅有一个压缩机11工作后，再进行第二轮减载，直至所有复合制冷模块1的压缩机11全部停止工作。
复合式制冷多联空调系统运行在复合制冷工作模式时，当室外环境温度较低、或室内侧热负荷较小、或两种情况同时出现，制冷压缩机11全部停机后，能量调节的规则是：若满足Tb＜17℃，按设定程序逐个降低风机123的转速，若仍满足Tb＜17℃，则逐个停止风机123的运行；
复合式制冷多联空调系统运行在复合制冷工作模式时，在部分或全部风机123停机后，当室外环境温度回升、或室内侧热负荷增大、或两种情况同时出现，若满足19℃＜Tb，运行风机123，若仍满足19℃＜Tb，则逐个提高风机123的转速至高速，若仍满足19℃＜Tb，启动压缩机11补充制冷量不足。
运行中，对于系统中所有室外复合式制冷模块1，采用先开则先停的轮值运行方式进行工作；对于系统中所有压缩机11，同样采用先开则先停的轮值运行方式进行工作。
本发明用于室内侧设定温度为27℃或24℃的机房等空调对象，其储液器22内第二冷媒的设定饱和温度Tb可适当调整，在满足空调送风温度和制冷量要求的条件下，最大化利用室外低温空气作为自然冷源，实现空调系统的低碳运行和室内空气的高品质。

Claims (10)

  1. 一种复合式制冷多联空调系统，其特征是：所述多联空调系统的室外侧设置两个或两个以上的室外复合式制冷模块(1)构成多联空调的冷源系统，在室内侧设置一个或一个以上的室内冷风机模块(3)，第二冷媒的储存输送单元(2)通过集液管(4)、供液总管(5)以及回气总管(6)连接在所述室外复合式制冷模块(1)与室内冷风机模块(3)之间构成闭式循环系统；
    所述室外复合式制冷模块(1)由第一冷媒的蒸气压缩制冷循环回路与第二冷媒的复合制冷循环回路通过换热器(14)复合构成，并通过第二冷媒向室内冷风机模块(3)输送冷量；所述蒸气压缩制冷循环回路按第一冷媒的流向依次设置为：压缩机(11)、风冷换热总成(12)中的风冷冷凝器(122)、节流机构(13)以及换热器(14)中的蒸发通道(141)；所述压缩机(11)的高压排气侧与风冷冷凝器(122)的入口相连接、低压吸气侧与所述蒸发通道(141)的出口相连接；所述压缩机(11)为两台同规格的压缩机(111)、压缩机(112)的并联组合；所述复合制冷循环回路具有复合制冷工作路径和蒸气压缩制冷工作路径；所述复合制冷工作路径是：第二冷媒在进口支管连接阀(151)中导入，依次经第二电磁阀(17)、风冷换热总成(12)中的风冷换热器(121)和换热器(14)中的冷凝通道(142)，并在出液支管连接阀(152)中导出；所述蒸气压缩制冷工作路径是：第二冷媒在所述进口支管连接阀(151)中导入，依次经第一电磁阀(16)和换热器(14)中的冷凝通道(142)后在所述出口支管连接阀(152)中导出；所述换热器(14)采用板式换热器或壳管式冷凝蒸发器；在所述风冷换热总成(12)中，设置风机(123)是为所述风冷换热器(121)和所述风冷冷凝器(122)的共用风机；
    所述室内冷风机模块(3)是由蒸发器(31)、蒸发风机(32)和流量控制阀(33)构成，各室内冷风机模块(3)的出口支路连接阀(362)并联连接至回气总管(6)，并通过所述回气总管(6)与各室外复合式制冷模块(1)的进口支管连接阀(151)相连接；所述流量控制阀(33)设置在所述蒸发器(31)的入口端，所述流量控制阀(33)的感温元件(35)安装在所述蒸发器(31)的出口端的管壁上；所述流量控制阀(33)为比例调节阀，所述感温元件(35)将蒸发器(31)出口的冷媒温度信号转换为压力信号，并通过毛细管(34)传递至流量控制阀(35)，调节流量控制阀(33)的开度，从而控制蒸发器(31)的供液量及其出口的过热度；
    所述冷媒储存输送单元(2)包括储液器(22)和液泵(21)，所述储液器(22)的输入端通过集液管(4)与各室外复合式制冷模块(1)中的出液支管连接阀(152)相连接，所述储液器(22)的输出端通过液泵(21)并经供液总管(5)与各室内冷风机模块(3)的进口支路连接阀(361)相连接；
    在所述储液器(22)的项部设有溢气管(25)，所述溢气管(25)通过单向阀(26)与回气总管(6)相连通，所述单向阀(26)是以储液器(22)朝向回气总管(6)的流动方向单向导通。
  2. 根据权利要求1所述的复合式制冷多联空调系统，其特征是：在所述的风冷换热总成(12)中，风冷换热器(121)和风冷冷凝器(122)均采用平行流换热器，并迎着风向平行并列，所述风冷换热器(121)位于入风侧、风冷冷凝器(122)位于出风侧，且与所述风机(123)构成一个风道。
  3. 根据权利要求1所述的复合式制冷多联空调系统，其特征是：在所述冷媒储存输送单元(2)中，液泵(21)为屏蔽泵，在供液总管(5)与储液器(22)之间设置旁通管(23)及旁通阀(24)，所述旁通阀(24)的开度受其入口压力控制，压力大则开度大，反之亦然。
  4. 根据权利要求1所述的复合式制冷多联空调系统，其特征是：所述风机(123)为变频调速风机。
  5. 根据权利要求1所述的复合式制冷多联空调系统，其特征是：所述第一冷媒选用R410A、R407、R134a、R290或R32制冷剂，所述第二冷媒选用R134a、R290或R32制冷剂。
  6. 根据权利要求1所述的复合式制冷多联空调系统的控制方法，其特征是：设置所述多联空调系统为蒸气压缩制冷和复合制冷的两种不同工作模式，并有：
    在ΔTa＜A的工况下，运行蒸气压缩制冷的工作模式；
    在ΔTa≥A的工况下，运行复合制冷的工作模式；
    其中：ΔTa＝Th-Ta，Th为回气总管(6)中第二冷媒实时温度的测量值，Ta为室外环境温度的测量值，A为设定值。
  7. 根据权利要求6所述的复合式制冷多联空调系统的控制方法，其特征是：
    所述蒸气压缩制冷的工作模式是指：复合式制冷多联空调系统的冷量全部由运行蒸气压缩制冷所提供；在所述蒸气压缩制冷的工作模式下，投入运行的室外复合式制冷模块(1)中的压缩机(11)和风机(123)运行、第一电磁阀(16)开启、第二电磁阀(17)关闭，第二冷媒通过进口支管连接阀(151)和第一电磁阀(16)，在换热器(14)的冷凝通道(142)中与蒸发通道(141)内的第一冷媒进行热交换，第二冷媒放热冷凝后经过出液支管连接阀(152)和集液管(4)进入储液器(22)；对于某个室外复合式制冷模块(1)，只有在两台压缩机(111)和压缩机(112)均停止工作时，该室外复合式制冷模块(1)的风机(123)才停止运行，并且第一电磁阀(16)和第二电磁阀(17)关闭；
    制冷量的调节通过控制室外复合式制冷模块(1)中压缩机(11)的加载或减载来实现， 其控制方法是：
    若满足B-ΔB≤Tb≤B+ΔB，维持压缩机(11)的运行状态不变；
    若满足B+ΔB＜Tb，压缩机(11)加载；
    若满足Tb＜B-ΔB，压缩机(11)减载；
    其中：B为储液器(22)内第二冷媒的设定饱和温度，ΔB为B的控制偏差，Tb为储液器(22)内第二冷媒的实时饱和温度的检测值。
  8. 根据权利要求6所述的复合式制冷多联空调系统的控制方法，其特征是：
    所述复合制冷的工作模式是指：优先利用风冷换热器(121)提供冷量，不足冷量通过控制制冷压缩机(11)的输出制冷量进行补充；所述复合制冷的控制方式是：若室外侧有制冷压缩机(11)运行，则冷源系统中所有室外复合式制冷模块(1)的风机(123)高速运行，第一电磁阀(16)关闭、第二电磁阀(17)开启，第二冷媒通过进口支管连接阀(151)、第二电磁阀(17)，首先在风冷换热器(121)中放热，然后通过换热器(14)的冷凝通道(142)进一步放热，经出液支管连接阀(152)进入集液管(4)，再流入储液器(22)；
    在所述复合式制冷的工作模式下，压缩机(11)的加载或减载的控制方法是：
    若满足B-ΔB≤Tb≤B+ΔB，维持压缩机(11)运行状态不变；
    若满足B+ΔB＜Tb，压缩机(11)加载，直至每个室外复合制冷模块(1)中都有一个压缩机(111)或压缩机(112)投入工作，之后若是仍然满足B+ΔB＜Tb，再进行第二轮室外复合制冷模块(1)的第二个压缩机工作或加载；
    若满足Tb＜B-ΔB，压缩机(11)减载，直至每个室外复合制冷模块(1)中仅有一个压缩机(111)或压缩机(112)工作，之后若是仍然满足Tb＜B-ΔB，再进行第二轮减载，直至所有室外复合制冷模块(1)的压缩机(11)全部停止工作。
  9. 根据权利要求6或8所述的复合式制冷多联空调系统的控制方法，其特征是：
    在复合制冷的工作模式下，当室内侧热负荷低于由风冷换热器(121)所提供的冷量时，所有压缩机(11)停止工作；按如下规则调节制冷量：
    若满足B-ΔB≤Tb≤B+ΔB，维持风机(123)运行数量和速度不变；
    若满足Tb＜B-ΔB，逐个降低风机(123)的转速，直至逐个停止风机(123)的运行；
    当工况发生变化使得满足B+ΔB＜Tb时，逐个运行风机(123)，直至逐个提高风机(123)转速至高速。
  10. 根据权利要求6所述的复合式制冷多联空调系统的控制方法，其特征是：对于所述系统中所有室外复合式制冷模块(1)，采用先开则先停的轮值运行方式进行工作；对于所述系统中所有压缩机(11)，同样采用先开则先停的轮值运行方式进行工作，设置各制冷压缩机 的启停间隔时间为3～5分钟。
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CN107062668B (zh) * 2017-03-09 2022-06-07 深圳市艾特网能技术有限公司 制冷循环系统及其制冷方法
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CN108050625B (zh) * 2017-12-12 2024-02-27 广东申菱环境系统股份有限公司 一种用于数据机房的联合冷却空调系统
CN108184322A (zh) * 2018-01-22 2018-06-19 南京佳力图机房环境技术股份有限公司 基于热管的vrv机房一体化散热系统及其控制方法
CN108184322B (zh) * 2018-01-22 2023-08-29 南京佳力图机房环境技术股份有限公司 基于热管的vrv机房一体化散热系统及其控制方法
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CN109631410A (zh) * 2019-01-25 2019-04-16 中国建筑科学研究院有限公司 一种复合式制冷系统
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