WO2018006569A1 - 空调系统 - Google Patents

空调系统 Download PDF

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Publication number
WO2018006569A1
WO2018006569A1 PCT/CN2016/113735 CN2016113735W WO2018006569A1 WO 2018006569 A1 WO2018006569 A1 WO 2018006569A1 CN 2016113735 W CN2016113735 W CN 2016113735W WO 2018006569 A1 WO2018006569 A1 WO 2018006569A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
conditioning system
air conditioning
valve
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2016/113735
Other languages
English (en)
French (fr)
Inventor
戚文端
曾祥兵
李金波
杨亚新
刘湍顺
陈明瑜
刘燕飞
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.)
Midea Group Co Ltd
GD Midea Air Conditioning Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
Guangdong Midea Refrigeration Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201610539872.4A external-priority patent/CN105972852A/zh
Priority claimed from CN201620723190.4U external-priority patent/CN206291521U/zh
Application filed by Midea Group Co Ltd, Guangdong Midea Refrigeration Equipment Co Ltd filed Critical Midea Group Co Ltd
Publication of WO2018006569A1 publication Critical patent/WO2018006569A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator

Definitions

  • the present invention relates to the field of refrigeration technology, and in particular, to an air conditioning system.
  • the air conditioning refrigeration system does not optimize the circulation design of the gaseous refrigerant before the throttle and enters the evaporator, which causes the gaseous refrigerant to affect the heat exchange performance of the evaporator and increase the compression power consumption of the compressor, thereby affecting the energy efficiency level of the air conditioner.
  • Jet boosting and two-stage compression technology can improve the heating capacity of air conditioning systems at low and ultra-low temperatures, but for air conditioning often used, energy efficiency is very limited.
  • the main object of the present invention is to provide an air conditioning system aimed at improving the energy efficiency of an air conditioning system.
  • an air conditioning system includes a two-cylinder independently compressed compressor, a reversing unit, an outdoor heat exchanger, a first throttling unit, a gas-liquid separator, a second throttling unit, and an indoor a heat exchanger and a first liquid storage tank; wherein the compressor is respectively provided with a first air return port and a second air return port, and the first cylinder connected to the first air return port is connected to the second cylinder port of the second air return port
  • the gas volume ratio ranges from 1% to 10%
  • the reversing unit includes a first valve port to a fourth valve port, the first valve port is in communication with one of the second valve port and the third valve port, the fourth valve port and the second valve port Communicating with the other of the third valve ports, the first valve port is connected to the exhaust port, and the fourth valve port is connected to the first liquid storage tank;
  • the first end of the outdoor heat exchanger is connected to the second valve port, and the first end of the indoor heat exchanger is connected to the third valve port;
  • the gas-liquid separator includes a gas outlet, a first interface and a second interface, the gas outlet is connected to the second air return port, and the first interface is connected to the second end of the outdoor heat exchanger, The second interface is connected to the second end of the indoor heat exchanger, and the first throttle element is connected in series between the first interface and the outdoor heat exchanger, and the second interface and the indoor exchange The second throttle element is connected in series between the heaters;
  • the T2 is an outlet temperature of the indoor heat exchanger in the heating mode
  • T3 is a coil temperature of the outdoor heat exchanger in the heating mode.
  • the value of ⁇ t ranges from -1 ° C to 3 ° C.
  • the degree of refrigerant throttling of the second throttling unit is less than or equal to a degree of refrigerant throttling of the first throttling unit.
  • the first throttle unit comprises any one of a first electronic expansion valve, a first capillary tube, and a first two-way throttle valve.
  • the first throttle unit includes a second capillary connected in series and a first one-way throttle valve, and a cut-off direction of the first one-way throttle valve is a refrigerant from the outdoor heat exchanger to the gas The direction in which the liquid separator flows.
  • the second throttle unit comprises any one of a second electronic expansion valve, a third capillary tube, and a second two-way throttle valve.
  • the second throttle unit comprises a fourth capillary connected in series and a second one-way throttle valve, and a closing direction of the second one-way throttle valve is a refrigerant from the indoor heat exchanger to the gas The direction in which the liquid separator flows.
  • the air conditioning system further includes a refrigerant heat exchanger and a one-way valve disposed on a connecting line of the outdoor heat exchanger and the first throttle unit and arranged in parallel, and the one-way valve is in an air conditioning system It is turned on when running in the heating mode and turned off when it is running in the cooling mode.
  • the air conditioning system further includes a first refrigerant heat exchange unit located on a connecting line of the first throttle unit and the gas-liquid separator.
  • the first refrigerant heat exchange unit is a refrigerant heat exchanger, or the first refrigerant heat exchange unit includes a refrigerant heat exchanger and a check valve disposed in parallel, and the check valve operates on the air conditioning system Turns on during heating mode and turns off when operating in cooling mode.
  • the air conditioning system further includes a second refrigerant heat exchange unit located on a connecting line of the gas-liquid separator and the second throttle unit.
  • the second refrigerant heat exchange unit is a refrigerant heat exchanger, or the second refrigerant heat exchange unit includes a refrigerant heat exchanger and a check valve disposed in parallel, and the check valve operates on the air conditioning system Turns on during heating mode and turns off when operating in cooling mode.
  • the air conditioning system further includes a third refrigerant heat exchange unit located on the connecting line of the gas-liquid separator and the compressor.
  • the third refrigerant heat exchange unit is a refrigerant heat exchanger, or the third refrigerant heat exchange unit includes a refrigerant heat exchanger and a first electromagnetic valve and a second electromagnetic valve, and the first electromagnetic valve and the refrigerant The heat exchangers are connected in series and then arranged in parallel with the second electromagnetic valve.
  • the air conditioning system further includes a second liquid storage irrigation, the second liquid storage irrigation end is connected to the second air return port of the compressor, and the other end is connected to the gas outlet of the gas liquid separator.
  • the 7725-2004 room air conditioner is rated for cooling/heating, intermediate cooling/heating, and maintains energy efficient operation.
  • FIG. 1 is a schematic structural view of a first embodiment of an air conditioning system according to the present invention.
  • FIG. 2 is a schematic structural view of a second embodiment of an air conditioning system according to the present invention.
  • FIG. 3 is a schematic structural view of a third embodiment of an air conditioning system according to the present invention.
  • FIG. 4 is a schematic structural view of a fourth embodiment of an air conditioning system according to the present invention.
  • Figure 5 is a schematic structural view of a fifth embodiment of an air conditioning system according to the present invention.
  • FIG. 6 is a schematic structural view of a sixth embodiment of an air conditioning system according to the present invention.
  • Figure 7 is a schematic structural view of a seventh embodiment of an air conditioning system according to the present invention.
  • Figure 8 is a schematic structural view of an eighth embodiment of an air conditioning system according to the present invention.
  • Figure 9 is a schematic structural view of a ninth embodiment of an air conditioning system according to the present invention.
  • Figure 10 is a schematic structural view of a tenth embodiment of an air conditioning system according to the present invention.
  • Figure 11 is a schematic structural view of an eleventh embodiment of an air conditioning system according to the present invention.
  • Figure 12 is a schematic view showing the structure of a twelfth embodiment of the air conditioning system of the present invention.
  • first, second, and the like in the present invention are used for the purpose of description only, and are not to be construed as indicating or implying their relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the technical solutions between the various embodiments may be combined with each other, but must be based on the realization of those skilled in the art, and when the combination of the technical solutions is contradictory or impossible to implement, it should be considered that the combination of the technical solutions does not exist. It is also within the scope of protection required by the present invention.
  • the invention provides an air conditioning system.
  • an air conditioning system includes: a two-cylinder independent compression compressor 1 that sequentially connects and forms a refrigerant circuit, a reversing unit 2, an outdoor heat exchanger 3, and a first throttling unit. 4.
  • the compressor 1 includes a housing in which a first cylinder 11 and a second cylinder 12 are disposed, and a first liquid storage tank 13 and a second liquid storage tank 14 are disposed outside the housing.
  • the compressor 1 is further provided with an exhaust port communicating with the commutation unit 2, a first air return port communicating with the intake port of the first cylinder 11, and a second communication port communicating with the intake port of the second cylinder 12.
  • the first liquid storage irrigation 13 has one end communicating with the reversing unit 2, and the other end is in communication with the first air return port; the second liquid storage irrigation 14 has one end communicating with the gas outlet of the gas-liquid separator 5, and the other end is in communication with the second return air port. It can be understood that the second liquid storage irrigation 14 can also be omitted.
  • the second liquid storage tank 14 is connected to the second air return port in order to further improve the stability of the air conditioning system.
  • the air conditioner is independently compressed by the first cylinder 11 and the second cylinder 12, and the compressed refrigerant discharged from the first cylinder 11 and the compressed refrigerant discharged from the second cylinder 12 are discharged into the casing 1 and then discharged.
  • the port is discharged.
  • the gas outlet of the gas-liquid separator 5 directly communicates with the gas return port of the compressor 1, and after the refrigerant passing through the first throttle unit 4 passes through the gas-liquid separator 5, the gaseous refrigerant passes through the gas outlet of the gas-liquid separator 5 to the compressor.
  • the second cylinder 12 is cyclically compressed to reduce compression power consumption and improve energy efficiency.
  • the ratio of the exhaust volume ratio of the second cylinder 12 and the first cylinder 11 is in the range of 1% to 10%. Further, the ratio of the exhaust volume ratio of the second cylinder 12 and the first cylinder 11 ranges from 1% to 9%. Preferably, the ratio of the exhaust volume ratio of the second cylinder 12 and the first cylinder 11 ranges from 4% to 9%.
  • the exhaust volume ratio of the second cylinder 12 and the first cylinder 11 may be a parameter such as 4%, 5%, 8%, or 8.5%.
  • the reversing unit 2 is preferably a four-way valve that communicates with the first air return port through the first liquid storage irrigation 13 , and the reversing unit 2 includes a first valve port D to a fourth valve port S, and the first valve port D and the first valve port One of the two valve ports C and the third valve port E communicates, the fourth valve port S communicates with the other of the second valve port C and the third valve port E, the first valve port D and the compressor 1
  • the exhaust ports are connected, and the fourth port S is connected to the first reservoir 13.
  • the first end of the outdoor heat exchanger 3 is connected to the second valve port C, and the first end of the indoor heat exchanger 7 is connected to the third valve port E.
  • the first valve port D communicates with the second valve port C and the third valve port E communicates with the fourth valve port S.
  • the first valve port D It is in communication with the third valve port E and the second valve port C is in communication with the fourth valve port S.
  • the gas-liquid separator 5 includes a gas outlet, a first port and a second port, the gas outlet is connected to the second gas return port, the first port is connected to the second end of the outdoor heat exchanger 3, and the second port is connected to the indoor heat exchanger 7
  • the second end is connected, the first throttle unit 4 is connected in series between the first interface and the outdoor heat exchanger 3, and the second throttle unit 6 is connected in series between the second interface and the indoor heat exchanger 7.
  • the high temperature and high pressure refrigerant discharged from the exhaust port of the compressor 1 is circulated to the outdoor heat exchanger 3 through the first valve port D and the second valve port C for condensation cooling from the outdoor heat exchanger 3
  • the circulating liquid refrigerant is subjected to first-stage throttling and depressurization by the first throttling unit 4, and then circulated from the first interface to the gas-liquid separator 5 for gas-liquid separation, and the separated intermediate pressure gaseous refrigerant is circulated from the gas outlet to the first
  • the two cylinders 12 are compressed.
  • the intermediate pressure liquid refrigerant circulated from the second interface of the gas-liquid separator 5 is depressurized by the secondary throttling of the second throttling unit 6 and then circulated to the indoor heat exchanger 7 for heat exchange to reduce the indoor ambient temperature.
  • the refrigerant circulated from the indoor heat exchanger 7 is circulated to the first liquid storage tank 13 through the third valve port E and the fourth valve port S, and the refrigerant circulated from the first liquid storage tank 13 is recirculated into the first cylinder 11 Compress.
  • the high temperature and high pressure refrigerant circulating from the exhaust port of the compressor 1 is circulated through the first valve port D and the third valve port E to the indoor heat exchanger 7 for condensing cooling to rise.
  • the indoor ambient temperature is converted into a liquid refrigerant to be recycled to the second throttling unit 6, and is subjected to primary throttling and depressurization, and then circulated from the second interface to the gas-liquid separator 5 for gas-liquid separation, and the separated intermediate pressure gaseous refrigerant is separated.
  • the gas is circulated from the gas outlet to the second cylinder 12 for compression.
  • the intermediate pressure liquid refrigerant circulated from the first interface of the gas-liquid separator 5 is subjected to secondary throttle reduction of the first throttle unit 4, and then circulated to the outdoor heat exchanger 3 for heat exchange from the outdoor heat exchanger 3
  • the circulated refrigerant is circulated to the first liquid storage tank 13 through the second valve port C and the fourth valve port S, and the refrigerant circulated from the first liquid storage tank 13 is recirculated into the first cylinder 11 for compression.
  • the refrigerants of different pressure states enter the first cylinder 11 and the second cylinder 12, respectively, and the first cylinder 11 and the second cylinder 12 independently complete the compression process, from the first
  • the compressed refrigerant discharged from the cylinder 11 and the compressed refrigerant discharged from the second cylinder 12 are discharged into the casing 10 and discharged from the exhaust port, while the exhaust volume ratio of the second cylinder 12 and the first cylinder 11 is exceeded.
  • the value ranges from 1% to 10%, and the refrigerant having a small flow rate and a high pressure state is discharged into the second cylinder 12 having a small exhaust volume for compression, thereby improving energy efficiency, energy saving and emission reduction.
  • the gas-liquid separator 5 separates a part of the gaseous refrigerant and then discharges it back into the second cylinder 12 for compression.
  • the gas content in the refrigerant flowing into the indoor heat exchanger 7 during cooling is reduced, and the gas content in the refrigerant flowing into the outdoor heat exchanger 3 during heating is reduced, and the indoor heat exchange of the gaseous refrigerant as the evaporator is reduced.
  • the heat exchange performance of the device 7 or the outdoor heat exchanger 3 can improve the heat exchange efficiency and reduce the compression power consumption of the compressor.
  • the 7725-2004 room air conditioner is rated for cooling/heating, intermediate cooling/heating, and maintains energy efficient operation.
  • the air conditioning system operates under rated cooling with a coefficient of performance of 4.23, which is 3.92% higher than the conventional scheme; when operating in intermediate cooling, the coefficient of performance is 5.81, which is 5.07% higher than the conventional scheme; The coefficient of performance is 3.53, which is 4.1% higher than the conventional scheme; when operating in the middle, the coefficient of performance is 5.24, which is 4.2% higher than the conventional scheme. Therefore, the energy efficiency of the air conditioning system operating under the national standard operating conditions has been greatly improved.
  • the first throttle unit 4 of the air conditioning system can be configured in the following manners:
  • the first throttle unit 4 may be a first electronic expansion valve.
  • the opening degree of the first electronic expansion valve can be adjusted, the flow rate of the refrigerant can be arbitrarily adjusted.
  • the first throttle unit 4 can be a separately provided first capillary or a first two-way throttle. In this way, the production cost of the air conditioner can be further saved, and the installation space of the air conditioner can be saved.
  • the first throttle unit 4 may include a second capillary 41 and a first one-way throttle valve 42 connected in series, and the first one-way throttle
  • the cutoff direction of the valve 42 is the direction in which the refrigerant flows from the outdoor heat exchanger 3 to the gas-liquid separator 5. It can be understood that the mounting positions of the second capillary 41 and the first one-way throttle valve 42 in the flow direction of the refrigerant can be interchanged. Compared with the first setting mode, the production cost of the air conditioner can be saved.
  • the first one-way throttle valve 42 acts as a throttling mechanism for the refrigerant, and after the refrigerant exchanges heat from the outdoor heat exchanger 3, passes through the second capillary 41 and the first one-way throttle valve 42. After the throttle is depressurized, it enters the gas-liquid separator 5.
  • the first one-way throttle valve 42 does not throttle the refrigerant, and the liquid refrigerant that has circulated the intermediate pressure from the gas-liquid separator passes through the second capillary 41 for secondary throttling and depressurization. , enter the outdoor heat exchanger 3 to evaporate and cool down.
  • the second throttle unit 6 of the air conditioning system can be configured in the following manners:
  • the second throttle unit 6 can be a second electronic expansion valve.
  • the opening degree of the second electronic expansion valve can be adjusted, the flow rate of the refrigerant can be arbitrarily adjusted.
  • the second throttle unit 6 can be a separately disposed third capillary or a second two-way throttle. In this way, the production cost of the air conditioner can be further saved, and the installation space of the air conditioner can be saved.
  • the second throttle unit 6 can be a fourth capillary 61 and a second one-way throttle 62 connected in series, and the cut-off direction of the second one-way throttle 62 is from the indoor
  • the heat exchanger flows in the direction of the refrigerant of the gas-liquid separator. It can be understood that the mounting positions of the fourth capillary 61 and the second one-way throttle valve 62 in the flow direction of the refrigerant can be interchanged. In this arrangement, the production cost of the air conditioner can be saved and the flow rate of the refrigerant can be effectively adjusted.
  • the second one-way throttle valve 62 acts as a throttling mechanism for the refrigerant, and after the refrigerant exchanges heat from the indoor heat exchanger 7, passes through the fourth capillary tube 61 and the second one-way throttle valve 62. After the throttle is depressurized, it enters the gas-liquid separator 5.
  • the second one-way throttle valve 62 does not throttle the refrigerant, and the intermediate pressure liquid refrigerant circulating from the gas-liquid separator 5 passes through the fourth capillary 61 for secondary throttling. After that, it enters the indoor heat exchanger 7 to evaporate and cool down.
  • any one of the plurality of installation modes of the first throttle unit 4 may be combined with any of the plurality of installation modes of the second throttle unit 6.
  • the first throttle unit 4 is an electronic expansion valve
  • the second throttle unit 6 is a capillary tube and a one-way throttle. valve.
  • the first throttle unit 4 is a capillary tube and a one-way throttle valve
  • the second throttle unit 6 is an electronic expansion valve. It can be understood that there are multiple combinations of the first throttle unit 4 and the second throttle unit 6, which are not enumerated here.
  • the present invention will also provide a refrigerant heat exchanger at a suitable position of the refrigerant pipeline, through circulating refrigerant, to the air conditioning system.
  • the frequency conversion module performs cooling. details as follows:
  • the unthrottled refrigerant circulating in the outdoor heat exchanger 3 is cooled, in this manner, the outdoor heat exchanger 3 and The refrigerant heat exchanger 8 and the check valve 9 are arranged in parallel on the connecting line of the first throttle unit 4, and the check valve 9 is turned on when the air conditioning system is operating in the heating mode, and is turned off when operating in the cooling mode. That is, in the cooling operation mode, after the heat exchange of the refrigerant from the outdoor heat exchanger 3, the heat exchange of the refrigerant heat exchanger 8 is performed, thereby cooling the frequency conversion module of the outdoor unit to ensure the electronic control board of the outdoor unit in a high temperature environment. safe job.
  • the heating operation mode After the refrigerant exchanges heat from the indoor heat exchanger, and then through the throttling of the second throttle element 6 and the first throttle element 4, the temperature of the refrigerant has dropped a lot, and if heat exchange is performed, The temperature of the refrigerant heat exchanger 8 is too low, and condensed water is easily generated.
  • the refrigerant heat exchanger 8 When the refrigerant heat exchanger 8 is in contact with the inverter module of the outdoor unit, there is a safety hazard. Therefore, the one-way valve 9 is turned on in the heating mode, and does not need to pass through. Refrigerant heat exchange.
  • the refrigerant heat exchange unit is applied to the air conditioning system, and the refrigerant that is circulated by the outdoor heat exchanger 3 and throttled by the first throttle unit 4 is cooled.
  • the air conditioning system can provide the first refrigerant heat exchange unit 15 on the connecting line of the first throttle unit 4 and the gas-liquid separator 5.
  • the air conditioning system may also provide a second refrigerant heat exchange unit 16 on the connecting line of the gas-liquid separator 5 and the second throttle unit 6.
  • the first refrigerant heat exchange unit 15 may be a refrigerant heat exchanger, or the first refrigerant heat exchange unit 15 may include a refrigerant heat exchanger and a check valve arranged in parallel, and the check valve is operated when the air conditioning system is in the heating mode. Turn-on, turn off when operating in the cooling mode; the second refrigerant heat exchange unit 16 may be a refrigerant heat exchanger, or the second refrigerant heat exchange unit 16 may include a refrigerant heat exchanger and a check valve arranged in parallel, and one-way The valve is turned on when the air conditioning system is operating in the heating mode and is turned off when operating in the cooling mode.
  • the refrigerant heat exchange unit is applied to an air conditioning system to cool the gaseous refrigerant separated by the gas-liquid separator 5.
  • the air conditioning system is provided with a third refrigerant heat exchange unit 17 on the connecting line of the gas-liquid separation 5 and the compressor 1.
  • the third refrigerant heat exchange unit 17 may be a refrigerant heat exchanger, or the third refrigerant heat exchange unit 17 may include a refrigerant heat exchanger and a first electromagnetic valve and a second electromagnetic valve, wherein the first electromagnetic valve and the refrigerant heat exchanger After being connected in series, it is placed in parallel with the second solenoid valve.
  • first throttling element 4 the second throttling element 6, and the refrigerant heat exchange structure is not limited to the structure shown in the drawings, and may be according to different requirements in practical applications. A combination of structures is formed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

一种空调系统（100），包括依次连通并形成冷媒回路的双缸独立压缩的压缩机（1）、换向单元（2）、室外换热器（3）、第一节流单元（4）、气液分离器（5）、第二节流单元（6）、室内换热器（7），压缩机（1）分别设置有第一回气口和第二回气口，换向单元（2）通过第一储液罐（13）与第一回气口连通，气液分离器（5）的气体出口与第二回气口连通，第一节流元件（4）和第二节流元件（6）的冷媒节流程度的设置使得气液分离器（5）的气体出口温度Tm＝（T2+T3）/2+△t，△t的取值范围为-2℃～4℃，其中，T2为制冷模式下室内换热器（7）的盘管温度，T3为制冷模式下室外换热器（3）的出口温度。

Description

空调系统
技术领域
本发明涉及制冷技术领域，特别涉及一种空调系统。
背景技术
目前的空调制冷系统没有对节流后并进入蒸发器前的气态制冷剂进行优化循环设计，导致气态制冷剂影响蒸发器换热性能，并且增加压缩机压缩功耗，从而影响到空调器能效水平。喷气增焓和双级压缩技术可以提高空调系统在低温和超低温下的制热能力水平，但对于空调经常使用的工况，能效提升非常有限。
发明内容
本发明的主要目的是提供一种空调系统，旨在提高空调系统的能效。
为实现上述目的，本发明提出的一种空调系统，包括双缸独立压缩的压缩机、换向单元、室外换热器、第一节流单元、气液分离器、第二节流单元、室内换热器和第一储液灌；其中，所述压缩机分别设置有第一回气口和第二回气口，第一回气口连接的第一气缸与第二回气口连接的第二气缸的排气容积比值范围为1%~10%；
所述换向单元包括第一阀口至第四阀口，所述第一阀口与第二阀口和第三阀口中的其中一个连通，所述第四阀口与所述第二阀口和所述第三阀口中的另一个连通，所述第一阀口与所述排气口相连，所述第四阀口与所述第一储液罐相连；
所述室外换热器的第一端与所述第二阀口相连，所述室内换热器的第一端与所述第三阀口相连；
所述气液分离器包括气体出口、第一接口和第二接口，所述气体出口与所述第二回气口相连，所述第一接口与所述室外换热器的第二端相连，所述第二接口与所述室内换热器的第二端相连，所述第一接口和所述室外换热器之间串联所述第一节流元件，所述第二接口和所述室内换热器之间串联所述第二节流元件；
所述空调系统中，所述第一节流元件和第二节流元件的冷媒节流程度的设置使得所述气液分离器的气体出口温度Tm= （T2+ T3）/2+△t，△t的取值范围为-2℃~4℃；其中，T2为制冷模式下室内换热器的盘管温度，T3为制冷模式下室外换热器的出口温度。
优选地，所述T2为制热模式下室内换热器的出口温度，T3为制热模式下室外换热器的盘管温度。
优选地，所述△t的取值范围为-1℃~3℃。
优选地，所述第二节流单元的冷媒节流程度小于或等于所述第一节流单元的冷媒节流程度。
优选地，所述第一节流单元包括第一电子膨胀阀、第一毛细管、第一双向节流阀的任意一个。
优选地，所述第一节流单元包括串接的第二毛细管和第一单向节流阀，且所述第一单向节流阀的截止方向为冷媒自室外换热器向所述气液分离器流动的方向。
优选地，所述第二节流单元包括第二电子膨胀阀、第三毛细管、第二双向节流阀的任意一个。
优选地，所述第二节流单元包括串接的第四毛细管和第二单向节流阀，且第二单向节流阀的截止方向为冷媒自所述室内换热器向所述气液分离器流动的方向。
优选地，所述空调系统还包括位于所述室外换热器与所述第一节流单元的连接管路上且并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
优选地，所述空调系统还包括位于所述第一节流单元与所述气液分离器的连接管路上的第一冷媒换热单元。
优选地，所述第一冷媒换热单元为冷媒换热器，或者所述第一冷媒换热单元包括并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
优选地，所述空调系统还包括位于所述气液分离器与所述第二节流单元的连接管路上的第二冷媒换热单元。
优选地，所述第二冷媒换热单元为冷媒换热器，或者所述第二冷媒换热单元包括并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
优选地，所述空调系统还包括位于所述气液分离器与所述压缩机的连接管路上的第三冷媒换热单元。
优选地，所述第三冷媒换热单元为冷媒换热器，或者所述第三冷媒换热单元包括冷媒换热器和第一电磁阀、第二电磁阀，所述第一电磁阀与冷媒换热器串联后再与所述第二电磁阀并联设置。
优选地，所述空调系统还包括第二储液灌，所述第二储液灌一端与所述压缩机的第二回气口连接，另一端与所述气液分离器的气体出口连接。
本发明的空调系统，在压缩机、室外换热器、室内换热器一定的情况下，依据Tm= （T2+ T3）/2+△t，对第一节流单元和第二节流单元的冷媒节流程度进行设置，可以使得该设计的空调系统运行在GB/T 7725-2004房间空气调节器中的额定制冷/制热、中间制冷/制热下，保持高能效运行。
附图说明
为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本发明空调系统第一实施例的结构示意图；
图2为本发明空调系统第二实施例的结构示意图；
图3为本发明空调系统第三实施例的结构示意图；
图4为本发明空调系统第四实施例的结构示意图；
图5为本发明空调系统第五实施例的结构示意图；
图6为本发明空调系统第六实施例的结构示意图；
图7为本发明空调系统第七实施例的结构示意图；
图8为本发明空调系统第八实施例的结构示意图；
图9为本发明空调系统第九实施例的结构示意图；
图10为本发明空调系统第十实施例的结构示意图；
图11为本发明空调系统第十一实施例的结构示意图；
图12为本发明空调系统第十二实施例的结构示意图。
本发明目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明的一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
需要说明，本发明实施例中所有方向性指示（诸如上、下、左、右、前、后……）仅用于解释在某一特定姿态（如附图所示）下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，在本发明中涉及“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其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至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本发明要求的保护范围之内。
本发明提出一种空调系统。
请参照图1和图2，本发明所提供的空调系统，包括：依次连通并形成冷媒回路的双缸独立压缩的压缩机1、换向单元2、室外换热器3、第一节流单元4、气液分离器5、第二节流单元6、室内换热器7。其中压缩机1包括壳体，该壳体内设有第一气缸11和第二气缸12，壳体外设有第一储液罐13和第二储液罐14。压缩机1壳体上还设有与换向单元2连通的排气口、与第一气缸11的吸气口连通的第一回气口，以及与第二气缸12的吸气口连通的第二回气口。第一储液灌13一端与换向单元2连通，另一端与第一回气口连通；第二储液灌14一端与气液分离器5的气体出口连通，另一端与第二回气口连通。可以理解的是，该第二储液灌14也可以省略。在第二回气口连通有第二储液罐14是为了进一步提高空调系统的稳定性。
本空调通过第一气缸11和第二气缸12的独立压缩，从第一气缸11排出的压缩后的冷媒和从第二气缸12排出的压缩后的冷媒分别排入到壳体1内然后从排气口排出。另外，气液分离器5的气体出口直接连通压缩机1的回气口，经过第一节流单元4的冷媒通过气液分离器5后，气态冷媒经过气液分离器5的气体出口到压缩机的第二气缸12循环压缩，降低压缩功耗，提升能效。
具体地，上述第二气缸12和第一气缸11的排气容积比值的取值范围为1%~10%。进一步地，第二气缸12和第一气缸11的排气容积比值的取值范围为1%~9%，优选地，第二气缸12和第一气缸11的排气容积比值的取值范围为4%~9%。例如第二气缸12和第一气缸11的排气容积比值可以为4%、5%、8%或8.5%等参数。
上述换向单元2优选为四通阀，其通过第一储液灌13与第一回气口连通，换向单元2包括第一阀口D至第四阀口S，第一阀口D与第二阀口C和第三阀口E中的其中一个连通，第四阀口S与第二阀口C和所述第三阀口E中的另一个连通，第一阀口D与压缩机1的排气口相连，第四阀口S与第一储液罐13相连。室外换热器3的第一端与第二阀口C相连，室内换热器7的第一端与第三阀口E相连。具体地，当冷暖型空调器100制冷时，第一阀口D与第二阀口C连通且第三阀口E与第四阀口S连通，当空调系统制热时，第一阀口D与第三阀口E连通且第二阀口C与第四阀口S连通。
气液分离器5包括气体出口、第一接口和第二接口，气体出口与第二回气口相连，第一接口与室外换热器3的第二端相连，第二接口与室内换热器7的第二端相连，第一接口和室外换热器3之间串联第一节流单元4，第二接口和室内换热器7之间串联第二节流单元6。
本实施例第一节流元件4和第二节流元件6的冷媒节流程度的设置使得气液分离器5的气体出口温度Tm= （T2+ T3）/2+△t，△t的取值范围为-2℃~4℃；其中，制冷模式下时，T2为室内换热器的盘管温度，T3为室外换热器的出口温度。制热模式下时，所述T2为室内换热器的出口温度，T3为室外换热器的盘管温度。进一步地，△t的取值范围也可以为-1℃~3℃。例如△t可以为0.5℃、1.8℃等参数。
当空调系统100制冷时，从压缩机1的排气口排出的高温高压冷媒通过第一阀口D和第二阀口C循环到室外换热器3中进行冷凝冷却，从室外换热器3循环出的液态冷媒经过第一节流单元4的一级节流降压后从第一接口循环到气液分离器5中进行气液分离，分离出来的中间压力气态冷媒从气体出口循环到第二气缸12内进行压缩。
从气液分离器5的第二接口循环出的中间压力液态冷媒经过第二节流单元6的二级节流降压后循环到室内换热器7内进行换热以降低室内环境温度，从室内换热器7循环出的冷媒通过第三阀口E和第四阀口S循环到第一储液罐13中，从第一储液罐13循环出的冷媒再循环到第一气缸11内进行压缩。
当冷暖型空调器100制热时，从压缩机1的排气口循环出的高温高压冷媒通过第一阀口D和第三阀口E循环到室内换热器7中进行冷凝冷却以升高室内环境温度，变成液态冷媒再循环到第二节流单元6，经过一级节流降压后从第二接口循环到气液分离器5中进行气液分离，分离出来的中间压力气态冷媒从气体出口循环到第二气缸12内进行压缩。
从气液分离器5的第一接口循环出的中间压力液态冷媒经过第一节流单元4的二级节流降压后循环到室外换热器3内进行换热，从室外换热器3循环出的冷媒通过第二阀口C和第四阀口S循环到第一储液罐13中，从第一储液罐13循环出的冷媒再循环到第一气缸11内进行压缩。
由此分析可知，在冷暖型空调器100运行时，不同压力状态的冷媒分别进入到第一气缸11和第二气缸12内，第一气缸11和第二气缸12独立完成压缩过程，从第一气缸11排出的压缩后的冷媒和从第二气缸12排出的压缩后的冷媒排到壳体10内混合后从排气口排出，同时由于第二气缸12和第一气缸11的排气容积比值的取值范围为1%~10%，流量较少且压力状态较高的冷媒排入到排气容积较小的第二气缸12内进行压缩，从而可以提高能效，节能减排。
同时通过在室外换热器3和室内换热器7之间设有气液分离器5，从而气液分离器5将一部分气态冷媒分离出来后排回到第二气缸12内进行压缩，由此降低了制冷时流入到室内换热器7的冷媒中的气体含量，以及降低了制热时流入到室外换热器3的冷媒中的气体含量，减少了气态冷媒对作为蒸发器的室内换热器7或者室外换热器3的换热性能的影响，从而可以提高换热效率，降低压缩机压缩功耗。
本发明的空调系统，在压缩机、室外换热器、室内换热器一定的情况下，依据Tm=（T2+ T3）/2+△t，对第一节流单元4和第二节流单元6的冷媒节流程度进行设置，可以使得该设计的空调系统运行在GB/T 7725-2004房间空气调节器中的额定制冷/制热、中间制冷/制热下，保持高能效运行。
下表中是依据Tm=（T2+ T3）/2+△t对本空调系统中第一节流单元4和第二节流单元6的冷媒节流程度进行设置后，对本空调系统运行在额定制冷/制热、中间制冷/制热下的空调能效情况。
项目 额定制冷 中间制冷 额定制热 中间制热
技术方案 常规方案 本发明技术 常规技术 本发明技术 常规技术 本发明技术 常规技术 本发明技术
能力 3400.4 3434.4 1650 1699 4280 4408 2193 2226
功率 828.3 811.7 299 293 1263 1250 436 425
性能系数 4.11 4.23 5.52 5.81 3.39 3.53 5.03 5.24
性能系数提升比例 3.92% 5.07% 4.1% 4.2%
由上可知，本空调系统运行在额定制冷下，性能系数为4.23，相比常规方案提升3.92%；运行在中间制冷时，性能系数为5.81，相比常规方案提升5.07%；运行在额定制热时，性能系数为3.53，相比常规方案提升4.1%；运行在中间制热时，性能系数为5.24，相比常规方案提升4.2%。因此，本空调系统运行在国标运行工况下的能效得到了很大的提高。
具体地，本空调系统的第一节流单元4可为以下几种设置方式：
请参照图1至图3，在第一设置方式中，第一节流单元4可为第一电子膨胀阀。在此种设置方式下，由于第一电子膨胀阀的开度可调节，因此冷媒的流量可任意调节。
在第二设置方式中，第一节流单元4可为单独设置的第一毛细管或者第一双向节流阀。在此种设置方式下，可进一步节约空调的生产成本，并节约空调的安装空间。
请参照图4和图5，在第三设置方式中，第一节流单元4可包括相串接的第二毛细管41和第一单向节流阀42，且所述第一单向节流阀42的截止方向为冷媒自室外换热器3向所述气液分离器5流动的方向。可以理解的，第二毛细管41和第一单向节流阀42的在冷媒的流动方向上的安装位置可以互换。相比第一种设置方式下，可节约空调的生产成本。本空调系统运行制冷模式下，第一单向节流阀42对冷媒起节流作用，则冷媒自室外换热器3换热后，经过第二毛细管41和第一单向节流阀42的节流降压后，进入气液分离器5。本空调运行制热模式时，第一单向节流阀42对冷媒不起节流作用，从气液分离器循环出中间压力的液态冷媒只经过第二毛细管41进行二次节流降压后，进入室外换热器3蒸发降温。
具体地，本空调系统的第二节流单元6可为以下几种设置方式：
在第一设置方式中，第二节流单元6可为第二电子膨胀阀。在此种设置方式下，由于第二电子膨胀阀的开度可调节，因此冷媒的流量可任意调节。
在第二设置方式中，第二节流单元6可为单独设置的第三毛细管或者第二双向节流阀。在此种设置方式下，可进一步节约空调的生产成本，并节约空调的安装空间。
在第三设置方式中，第二节流单元6可为相串接的第四毛细管61和第二单向节流阀62，且第二单向节流阀62的截止方向为自所述室内换热器向所述气液分离器的冷媒流动方向。可以理解的，第四毛细管61和第二单向节流阀62的在冷媒的流动方向上的安装位置可以互换。在此种设置方式下，可节约空调的生产成本并且对冷媒的流量进行有效调节。本空调系统运行制热模式下，第二单向节流阀62对冷媒起节流作用，则冷媒自室内换热器7换热后，经过第四毛细管61和第二单向节流阀62的节流降压后，进入气液分离器5。本空调运行制冷模式时，第二单向节流阀62对冷媒不起节流作用，从气液分离器5循环出的中间压力的液态冷媒只经过第四毛细管61进行二次节流降压后，进入室内换热器7蒸发降温。
需要说明的是，本实施例的空调系统，第一节流单元4的多种设置方式中的任意一种可与第二节流单元6的多种设置方式中任意一种进行结合。如在第一节流单元4与第二节流单元6的一种结合方式中，第一节流单元4为电子膨胀阀，第二节流单元6为相串接的毛细管和单向节流阀。在另一种结合方式中，第一节流单元4为毛细管和单向节流阀，第二节流单元6为电子膨胀阀。可以理解地，第一节流单元4和第二节流单元6存在多种结合方式，在此不再一一列举。
本空调系统在上述制冷和制热过程中，为了实现高温工况下，空调系统正常可靠运行，本发明还将在冷媒管路的合适位置设置冷媒换热器，通过循环冷媒，对空调系统的变频模块进行降温。具体如下：
请参照图6，在一种方案中，冷媒换热器应用空调系统中，对室外换热器3循环出的未经节流的冷媒进行降温处理，在此方式下，室外换热器3与第一节流单元4的连接管路上且并联设置有冷媒换热器8和单向阀9，且单向阀9在空调系统运行于制热模式时导通，在运行于制冷模式时截止。即制冷运行模式时，冷媒自室外换热器3换热后，经过冷媒换热器8的换热，从而对室外机的变频模块进行降温处理，保证高温环境下，室外机的电控板的安全工作。制热运行模式时，冷媒自室内换热器换热后，依次经过第二节流元件6和第一节流元件4的节流后，冷媒温度已经下降很多，若再进行换热，则会造成冷媒换热器8的温度过低，容易产生冷凝水，在冷媒换热器8与室外机的变频模块接触时会存在安全隐患，故而制热模式下单向阀9导通，不需要经过冷媒换热。
请结合参照图7和图8，在另一种方案中，冷媒换热单元应用于空调系统中，对室外换热器3循环出的并经过第一节流单元4节流的冷媒进行降温处理，在此方式下，本空调系统可在第一节流单元4与气液分离器5的连接管路上设置第一冷媒换热单元15。请结合参照图9和图10，本空调系统也可在气液分离器5与第二节流单元6的连接管路上设置第二冷媒换热单元16。其中第一冷媒换热单元15可为冷媒换热器，或者第一冷媒换热单元15可包括并联设置的冷媒换热器和单向阀，且单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止；第二冷媒换热单元16可为冷媒换热器，或者第二冷媒换热单元16可包括并联设置的冷媒换热器和单向阀，且单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
请参照图11和图12，在其他方案中，冷媒换热单元应用于空调系统中，对气液分离器5分离出的气态冷媒进行降温处理。在此种方式下，空调系统于气液分离5与压缩机1的连接管路上设置有第三冷媒换热单元17。第三冷媒换热单元17可为冷媒换热器，或者第三冷媒换热单元17可包括冷媒换热器和第一电磁阀、第二电磁阀，其中，第一电磁阀与冷媒换热器串联后再与第二电磁阀并联设置。
需要说明的是，上述第一节流元件4、第二节流元件6和冷媒换热结构的组合方式并不仅限于附图中所示出的结构，在实际应用过程中，可以根据不同的需求而形成各结构的组合。
以上所述仅为本发明的优选实施例，并非因此限制本发明的专利范围，凡是在本发明的发明构思下，利用本发明说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本发明的专利保护范围内。

Claims (16)

  1. 一种空调系统，其特征在于，包括双缸独立压缩的压缩机、换向单元、室外换热器、第一节流单元、气液分离器、第二节流单元、室内换热器和第一储液灌；其中，所述压缩机分别设置有第一回气口和第二回气口，第一回气口连接的第一气缸与第二回气口连接的第二气缸的排气容积比值范围为1%~10%；
    所述换向单元包括第一阀口至第四阀口，所述第一阀口与第二阀口和第三阀口中的其中一个连通，所述第四阀口与所述第二阀口和所述第三阀口中的另一个连通，所述第一阀口与所述排气口相连，所述第四阀口与所述第一储液罐相连；
    所述室外换热器的第一端与所述第二阀口相连，所述室内换热器的第一端与所述第三阀口相连；
    所述气液分离器包括气体出口、第一接口和第二接口，所述气体出口与所述第二回气口相连，所述第一接口与所述室外换热器的第二端相连，所述第二接口与所述室内换热器的第二端相连，所述第一接口和所述室外换热器之间串联所述第一节流元件，所述第二接口和所述室内换热器之间串联所述第二节流元件；
    所述空调系统中，所述第一节流元件和第二节流元件的冷媒节流程度的设置使得所述气液分离器的气体出口温度Tm= （T2+ T3）/2+△t，△t的取值范围为-2℃~4℃；其中，T2为制冷模式下室内换热器的盘管温度，T3为制冷模式下室外换热器的出口温度。
  2. 如权利要求1所述的空调系统，其特征在于，所述T2还为制热模式下室内换热器的出口温度，T3还为制热模式下室外换热器的盘管温度。
  3. 如权利要求1或2所述的空调系统，其特征在于，所述△t的取值范围为-1℃~3℃。
  4. 如权利要求1或2所述的空调系统，其特征在于，所述第二节流单元的冷媒节流程度小于或等于所述第一节流单元的冷媒节流程度。
  5. 如权利要求1所述的空调系统，其特征在于，所述第一节流单元包括第一电子膨胀阀、第一毛细管、第一双向节流阀的任意一个。
  6. 如权利要求1所述的空调系统，其特征在于，所述第一节流单元包括串接的第二毛细管和第一单向节流阀，且所述第一单向节流阀的截止方向为冷媒自所述室外换热器向所述气液分离器流动的方向。
  7. 如权利要求1或5、6所述的空调系统，其特征在于，所述第二节流单元包括第二电子膨胀阀、第三毛细管、第二双向节流阀的任意一个。
  8. 如权利要求1或5、6所述的空调系统，其特征在于，所述第二节流单元包括串接的第四毛细管和第二单向节流阀，且第二单向节流阀的截止方向为冷媒自所述室内换热器向所述气液分离器的流动的方向。
  9. 如权利要求1所述的空调系统，其特征在于，所述空调系统还包括位于所述室外换热器与所述第一节流单元的连接管路上且并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
  10. 如权利要求1所述的空调系统，其特征在于，所述空调系统还包括位于所述第一节流单元与所述气液分离器的连接管路上的第一冷媒换热单元。
  11. 如权利要求10所述的空调系统，其特征在于，所述第一冷媒换热单元为冷媒换热器，或者所述第一冷媒换热单元包括并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
  12. 如权利要求1或10、11所述的空调系统，其特征在于，所述空调系统还包括： 位于所述气液分离器与所述第二节流单元的连接管路上的第二冷媒换热单元。
  13. 如权利要求12所述的空调系统，其特征在于，所述第二冷媒换热单元为冷媒换热器，或者所述第二冷媒换热单元包括并联设置的冷媒换热器和单向阀，且所述单向阀在空调系统运行于制热模式时导通，在运行于制冷模式时截止。
  14. 如权利要求1所述的空调系统，其特征在于，所述空调系统还包括位于所述气液分离器与所述压缩机的连接管路上的第三冷媒换热单元。
  15. 如权利要求14所述的空调系统，其特征在于，所述第三冷媒换热单元为冷媒换热器，或者所述第三冷媒换热单元包括冷媒换热器和第一电磁阀、第二电磁阀，所述第一电磁阀与冷媒换热器串联后再与所述第二电磁阀并联设置。
  16. 如权利要求1所述的空调系统，其特征在于，所述空调系统还包括第二储液灌，所述第二储液灌一端与所述压缩机的第二回气口连接，另一端与所述气液分离器的气体出口连接。
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CN113357721A (zh) * 2020-03-06 2021-09-07 青岛海信日立空调系统有限公司 热泵机组
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CN112229098B (zh) * 2020-11-18 2024-04-26 珠海格力电器股份有限公司 热泵系统及其控制方法、控制装置、制冷设备和存储介质
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