CN213090173U

CN213090173U - Air conditioning system

Info

Publication number: CN213090173U
Application number: CN202021275116.3U
Authority: CN
Inventors: 胡余生; 魏会军; 巩庆霞; 吴健; 罗惠芳; 柯达俊; 邓罡; 麦境治; 尹雪峰
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai; Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
Priority date: 2020-07-02
Filing date: 2020-07-02
Publication date: 2021-04-30
Anticipated expiration: 2030-07-02

Abstract

The utility model provides an air conditioning system. The air conditioning system includes: a compression assembly including a first compression part having a first suction port and a first discharge port and a second compression part having a second suction port and a second discharge port; the first reversing component is used for switching refrigeration and heating of the air conditioning system and is connected with the first air inlet and the first air outlet; the second reversing component is used for switching refrigeration and heating of the air conditioning system and is connected with the second air suction port; the second exhaust port is connected with both the second reversing component and the first air suction port; the first indoor heat exchanger is connected with the first reversing component; the second indoor heat exchanger is connected with the second reversing component; and the outdoor heat exchanger is connected with the first reversing component, the second reversing component, the first indoor heat exchanger and the second indoor heat exchanger. The utility model discloses an air conditioning system has solved the problem that air conditioning system among the prior art can't always be in the running state of economy most.

Description

Air conditioning system

Technical Field

The utility model relates to an air conditioning field particularly, relates to an air conditioning system.

Background

In some areas, the climate is changeable all year round, if the humidity is high in early summer, the traditional fresh air conditioner needs lower evaporation temperature to meet the dehumidification requirement, but the evaporation temperature is reduced once, for a compressor, the pressure ratio is increased, the operation is not economical, the air outlet temperature of an indoor unit is reduced due to the reduction of the evaporation temperature, and the comfort of a human body is reduced; however, in the summer season, the outdoor temperature is high, and the risk that the common single-stage compression system cannot operate due to overhigh exhaust temperature exists; meanwhile, in the early winter, the pressure ratio of the system operation working condition is small, the load is small, but in the severe winter, the outdoor temperature is extremely low, and the pressure ratio of the system operation is large.

When the existing air conditioning system circulation mode realizes refrigeration/heating in regions with changeable climate all the year around, the system can not be ensured to be always in the most economic operation state; even under some severe conditions, the existing air conditioning system cannot operate.

SUMMERY OF THE UTILITY MODEL

The main object of the present invention is to provide an air conditioning system to solve the problem that the air conditioning system in the prior art cannot always be in the most economical operation state.

In order to achieve the above object, the present invention provides an air conditioning system, including: a compression assembly including a first compression part having a first suction port and a first discharge port and a second compression part having a second suction port and a second discharge port; the first reversing component is used for switching refrigeration and heating of the air conditioning system and is connected with the first air inlet and the first air outlet; the second reversing component is used for switching refrigeration and heating of the air conditioning system and is connected with the second air suction port; the second exhaust port is connected with both the second reversing component and the first air suction port; the first end of the first indoor heat exchanger is connected with the first reversing component; the first end of the second indoor heat exchanger is connected with the second reversing component; and the first end of the outdoor heat exchanger is connected with the first reversing component and the second reversing component, and the second end of the outdoor heat exchanger is connected with the second end of the first indoor heat exchanger and the second end of the second indoor heat exchanger.

Furthermore, the first reversing component is provided with a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is communicated with the second valve port or the fourth valve port, and the third valve port is communicated with the fourth valve port or the second valve port; the second valve port is connected with the first air suction port; the fourth valve port is connected with the first exhaust port; the second reversing component is provided with a fifth valve port, a sixth valve port, a seventh valve port and an eighth valve port, the fifth valve port is communicated with the sixth valve port or the eighth valve port, and the seventh valve port is communicated with the eighth valve port or the sixth valve port; the sixth valve port is connected with the second air suction port; the second exhaust port is connected with the eighth valve port and the first intake port; the first end of the first indoor heat exchanger is connected with the first valve port; the first end of the second indoor heat exchanger is connected with the fifth valve port; the first end of the outdoor heat exchanger is connected with the third valve port and the seventh valve port.

Furthermore, the compression component is a compressor which is a double-cylinder compressor, an upper cylinder of the double-cylinder compressor is a first compression part, and a lower cylinder of the double-cylinder compressor is a second compression part; or, the compression assembly comprises two compressors, one compressor is a first compression part, and the other compressor is a second compression part.

Furthermore, the first reversing component is a four-way reversing valve; and/or the second reversing component is a four-way reversing valve.

Further, the air conditioning system further includes: a first end of the first connecting pipe is connected with a first end of the first indoor heat exchanger, and a second end of the first connecting pipe is connected with the first valve port; and a first end of the second connecting pipe is connected with the second valve port, and a second end of the second connecting pipe is connected with the first air suction port.

Further, the air conditioning system further includes: a first end of the third connecting pipe is connected with the first end of the outdoor heat exchanger, and a second end of the third connecting pipe is connected with the third valve port; and a first end of the fourth connecting pipe is connected with the first exhaust port, and a second end of the fourth connecting pipe is connected with the fourth valve port.

Further, the air conditioning system further includes: and a first end of the fifth connecting pipe is connected with the first end of the second indoor heat exchanger, and a second end of the fifth connecting pipe is connected with the fifth valve port.

Further, the air conditioning system further includes: a first end of the sixth connecting pipe is connected with the sixth valve port, and a second end of the sixth connecting pipe is connected with the second air suction port; and a first end of the seventh connecting pipe is connected with the seventh valve port, and a second end of the seventh connecting pipe is connected with the first end of the outdoor heat exchanger.

Further, the air conditioning system further includes: and a first end of the eighth connecting pipe is connected with the eighth valve port, and a second end of the eighth connecting pipe is connected with the second exhaust port.

Further, the air conditioning system further includes: the first end of the first header pipe is connected with the second end of the outdoor heat exchanger; the first end of the first branch pipe is connected with the second end of the first main pipe, and the second end of the first branch pipe is connected with the second end of the first indoor heat exchanger; the first branch pipe is provided with a first throttling mechanism; a first end of the first branch pipe is connected with a first end of the first main pipe, and a second end of the first branch pipe is connected with a second end of the first indoor heat exchanger; the second branch pipe is provided with a second throttling mechanism.

Further, the air conditioning system further includes: a flash evaporator; the first end of the first pipeline is connected with the second end of the outdoor heat exchanger, and the second end of the first pipeline is connected with the flash evaporator; a first end of the second pipeline is connected with the flash evaporator, and a second end of the second pipeline is connected with both a second end of the first indoor heat exchanger and a second end of the second indoor heat exchanger; and the first end of the third pipeline is connected with the flash evaporator, and the second end of the third pipeline is connected with the first air suction port.

Further, a third throttling mechanism is arranged on the first pipeline.

Further, the first end of the first pipeline is connected with the first main pipe, and the second end of the first pipeline is connected with the flash evaporator; the first end of the second pipeline is connected with the flash evaporator, and the second end of the second pipeline is connected with the second end of the first main pipe; the second pipeline is provided with a first control valve; the air conditioning system further includes: the second control valve is arranged on the first main pipe and is positioned on one side, far away from the outdoor heat exchanger, of the first pipeline; a third control valve provided on the first branch pipe; the fourth control valve is arranged on the second branch pipe and is positioned between the second throttling mechanism and the second indoor heat exchanger; a first end of the fourth pipeline is connected with the second end of the first indoor heat exchanger, and a second end of the fourth pipeline is connected with the second branch pipe and is positioned between the second throttling mechanism and the fourth control valve; and a fifth control valve is arranged on the fourth pipeline.

Further, the first end of the third pipeline is connected with the flash evaporator, and the second end of the third pipeline is connected with the first air suction port; and a sixth control valve is arranged on the third pipeline.

Further, the air conditioning system further includes: a first end of the fifth pipeline is connected with the first connecting pipe, and a second end of the fifth pipeline is connected with the fifth connecting pipe; a seventh control valve is arranged on the fifth pipeline; and the eighth control valve is arranged on the second connecting pipe.

Further, the air conditioning system further includes: a first end of the sixth pipeline is connected with the second exhaust port, and a second end of the sixth pipeline is connected with the first air suction port; a ninth control valve is arranged on the sixth pipeline; and a tenth control valve provided on the eighth connection pipe.

Further, the air conditioning system further includes: a first end of the seventh pipeline is connected with the second air suction port; the first three-way valve is arranged on the second connecting pipe, a first connecting port and a second connecting port of the first three-way valve are both positioned on the second connecting pipe, and a third connecting port of the first three-way valve is connected with a second end of the seventh pipeline; the first connecting port can be selectively communicated with the second connecting port or the third connecting port.

Further, the air conditioning system further includes: an eighth pipeline; the fourth connecting port and the fifth connecting port of the second three-way valve are both positioned on the eighth connecting pipe, and the sixth connecting port of the second three-way valve is connected with the first end of the eighth pipeline; the fourth connecting port can be selectively communicated with the fifth connecting port or the sixth connecting port; the third three-way valve is arranged on the second connecting pipe and is positioned on one side, far away from the first reversing part, of the first three-way valve, a seventh connecting port and an eighth connecting port of the third three-way valve are both positioned on the second connecting pipe, and a ninth connecting port of the third three-way valve is connected with the second end of the eighth pipeline; wherein, the seventh connecting port can be selectively communicated with the eighth connecting port or the ninth connecting port.

Further, the first end of the third pipeline is connected with the flash evaporator, and the second end of the third pipeline is connected with the eighth pipeline.

Furthermore, the first end of the first pipeline is connected with the first branch pipe and is positioned on one side of the first throttling mechanism away from the first main pipe, and the second end of the first pipeline is connected with the flash evaporator; the first pipeline is provided with a first valve; the first end of the second pipeline is connected with the flash evaporator, and the second end of the second pipeline is connected with the second branch pipe and is positioned on one side, far away from the second indoor heat exchanger, of the second throttling mechanism; the air conditioning system further includes: a first end of the ninth pipeline is connected with the second branch pipe and is positioned on one side, close to the second indoor heat exchanger, of the second throttling mechanism; the tenth connecting port and the eleventh connecting port of the fourth three-way valve are both positioned on the first branch pipe, and the twelfth connecting port of the fourth three-way valve is connected with the second end of the ninth pipeline; the tenth connecting port is selectively communicated with the eleventh connecting port or the twelfth connecting port; and the second valve is arranged on the second branch pipe and is positioned on one side of the second pipeline, which is far away from the second throttling mechanism.

Further, when the air conditioning system is in a cooling and dehumidifying mode and is in a rated cooling working condition, the flow rate of the refrigerant flowing through the first indoor heat exchanger is q1, and the flow rate of the refrigerant flowing through the second indoor heat exchanger is q 2; the ratio of q1 to (q1+ q2) ranges from 10% to 30%.

Further, when the air conditioning system is in the cooling and dehumidifying mode and is in the intermediate cooling condition, the flow rate of the refrigerant flowing through the first indoor heat exchanger is q1, the flow rate of the refrigerant flowing through the second indoor heat exchanger is q2, and the ratio of q1 to (q1+ q2) ranges from 1% to 6%.

The air conditioning system of the utility model realizes single-stage and double-stage compression of the refrigerant by arranging the first compression part and the second compression part, and meets the requirements of different operation pressure ratios; the switching between cooling and heating is realized by arranging the first reversing component and the second reversing component; the refrigeration and the initial separation treatment can be realized by arranging the two indoor heat exchangers, and the change of the heat exchange area can also be realized; furthermore, the air conditioning system can realize the switching of five operation modes, including a double-evaporator double-cylinder single-stage operation mode, a double-evaporator double-cylinder double-stage air supplementing mode, a double-condenser double-cylinder double-stage air supplementing mode, a single-condenser double-cylinder double-stage air supplementing mode and a double-condenser double-cylinder single-stage mode, so that the condition that the system is always in the most economical operation state when the refrigeration and heating functions are realized in regions with variable climates is met.

Drawings

The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 shows a schematic view of a first embodiment of an air conditioning system according to the present invention;

FIG. 2 is a schematic diagram illustrating the air conditioning system of FIG. 1 in a cooling and dehumidification mode;

fig. 3 shows a pressure-enthalpy diagram of an air conditioning system according to the present invention in a cooling and dehumidification mode;

FIG. 4 is a graph illustrating the ratio of dehumidification flow path refrigerant flow to total flow rate (q1/(q1+ q2)) versus the energy efficiency ratio (E) for a system at nominal refrigeration conditions;

FIG. 5 is a schematic diagram illustrating the air conditioning system of FIG. 1 in a cooling and mode;

FIG. 6 illustrates a schematic view of the air conditioning system of FIG. 1 in a first heating mode;

FIG. 7 is a schematic diagram illustrating the air conditioning system of FIG. 1 in a second heating mode;

FIG. 8 is a schematic diagram illustrating the air conditioning system of FIG. 1 in a third heating mode;

fig. 9 shows a schematic view of a second embodiment of an air conditioning system according to the invention.

Wherein the figures include the following reference numerals:

10. a compression assembly; 11. a first compression section; 12. a second compression section; 20. an outdoor heat exchanger; 30. a first indoor heat exchanger; 40. a second indoor heat exchanger; 50. a first reversing component; 51. a first valve port; 52. a second valve port; 53. a third valve port; 54. a fourth valve port; 60. a first connecting pipe; 70. a second connecting pipe; 80. a third connecting pipe; 90. a fourth connecting pipe; 100. a second commutation segment; 101. a fifth valve port; 102. a sixth valve port; 103. a seventh valve port; 104. an eighth valve port; 110. a fifth connecting pipe; 120. a sixth connecting pipe; 130. a seventh connecting pipe; 140. an eighth connecting pipe; 150. a first header pipe; 160. a first branch pipe; 170. a second branch pipe; 180. a first throttle mechanism; 190. a second throttling mechanism; 200. a flash evaporator; 210. a first pipeline; 220. a second pipeline; 230. a third pipeline;

240. a third throttling mechanism; 250. a first control valve; 260. a second control valve; 270. a third control valve; 280. a fourth control valve; 290. a fourth pipeline; 300. a fifth control valve; 310. a sixth control valve; 320. a fifth pipeline; 330. a seventh control valve; 340. an eighth control valve; 350. a sixth pipeline; 360. a ninth control valve; 370. a tenth control valve;

380. a seventh pipeline; 390. a first three-way valve; 391. a first connection port; 392. a second connection port; 393. a third connection port; 400. an eighth pipeline; 410. a second three-way valve; 411. a fourth connection port; 412. a fifth connection port; 413. a sixth connection port; 420. a third three-way valve; 421. a seventh connection port; 422. an eighth connection port; 423. a ninth connection port; 430. a first valve; 440. a ninth conduit; 450. a fourth three-way valve; 451. a tenth connection port; 452. an eleventh connection port; 453. a twelfth connecting port; 460. a second valve.

Detailed Description

It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

It should be noted that the following detailed description is exemplary and is intended to provide further explanation of the disclosure. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.

The technical problem that this application was solved: when the air conditioning system circulation mode in the prior art realizes the refrigeration/heating problem in regions with changeable climate all the year around, the system can not be ensured to be always in the most economical operation state.

The utility model provides an air conditioning system please refer to fig. 1 to fig. 9, include: a compression unit 10 including a first compression part 11 and a second compression part 12, the first compression part 11 having a first suction port and a first discharge port, the second compression part 12 having a second suction port and a second discharge port; the first reversing component 50 is used for switching between refrigeration and heating of the air conditioning system, and the first reversing component 50 is connected with the first air inlet and the first air outlet; the second reversing component 100 is used for switching between refrigeration and heating of the air conditioning system, and the second reversing component 100 is connected with the second air suction port; the second exhaust port is connected with both the second reversing component 100 and the first intake port; a first indoor heat exchanger 30, a first end of the first indoor heat exchanger 30 being connected to the first direction changing member 50; a second indoor heat exchanger 40, wherein a first end of the second indoor heat exchanger 40 is connected with the second reversing component 100; and a first end of the outdoor heat exchanger 20 is connected to both the first direction changing part 50 and the second direction changing part 100, and a second end of the outdoor heat exchanger 20 is connected to both a second end of the first indoor heat exchanger 30 and a second end of the second indoor heat exchanger 40.

The air conditioning system of the utility model realizes single-stage and double-stage compression of the refrigerant by arranging the first compression part 11 and the second compression part 12, and meets the requirements of different operation pressure ratios; the switching between cooling and heating is realized by arranging the first reversing component 50 and the second reversing component 100; the two indoor heat exchangers are arranged, so that refrigeration and dehumidification can be separately processed, and the change of heat exchange area can be realized; furthermore, the air conditioning system can realize the switching of five operation modes, including a double-evaporator double-cylinder single-stage operation mode, a double-evaporator double-cylinder double-stage air supplementing mode, a double-condenser double-cylinder double-stage air supplementing mode, a single-condenser double-cylinder double-stage air supplementing mode and a double-condenser double-cylinder single-stage mode, so that the condition that the system is always in the most economical operation state when the refrigeration and heating functions are realized in regions with variable climates is met.

In the present embodiment, the first direction changing component 50 has a first valve port 51, a second valve port 52, a third valve port 53 and a fourth valve port 54, the first valve port 51 is communicated with the second valve port 52 or the fourth valve port 54, and the third valve port 53 is communicated with the fourth valve port 54 or the second valve port 52; the second valve port 52 is connected to the first suction port; the fourth port 54 is connected to a first exhaust port; the second direction changing component 100 is provided with a fifth valve port 101, a sixth valve port 102, a seventh valve port 103 and an eighth valve port 104, wherein the fifth valve port 101 is communicated with the sixth valve port 102 or the eighth valve port 104, and the seventh valve port 103 is communicated with the eighth valve port 104 or the sixth valve port 102; the sixth valve port 102 is connected with the second suction port; the second exhaust port is connected with both the eighth valve port 104 and the first intake port; a first end of the first indoor heat exchanger 30 is connected to the first port 51; a first end of the second indoor heat exchanger 40 is connected to the fifth valve port 101; the first end of the outdoor heat exchanger 20 is connected to both the third port 53 and the seventh port 103.

In this embodiment, the compression assembly 10 is a compressor, the compressor is a dual-cylinder compressor, an upper cylinder of the dual-cylinder compressor is a first compression part 11, and a lower cylinder of the dual-cylinder compressor is a second compression part 12; alternatively, the compression assembly 10 includes two compressors, one compressor being the first compression part 11 and the other compressor being the second compression part 12.

In this embodiment, the first direction changing member 50 is a four-way direction changing valve; and/or the second direction changing component 100 is a four-way direction changing valve.

In this embodiment, the air conditioning system further includes: a first connection pipe 60, a first end of the first connection pipe 60 being connected to a first end of the first indoor heat exchanger 30, and a second end of the first connection pipe 60 being connected to the first valve port 51; a third connection pipe 80, a first end of the third connection pipe 80 being connected to the first end of the outdoor heat exchanger 20, and a second end of the third connection pipe 80 being connected to the third valve port 53; a fourth connection pipe 90, a first end of the fourth connection pipe 90 being connected to the first exhaust port, and a second end of the fourth connection pipe 90 being connected to the fourth valve port 54; a fifth connection pipe 110, a first end of the fifth connection pipe 110 being connected to a first end of the second indoor heat exchanger 40, and a second end of the fifth connection pipe 110 being connected to the fifth port 101; a sixth connection pipe 120, a first end of the sixth connection pipe 120 being connected to the sixth port 102, and a second end of the sixth connection pipe 120 being connected to the second suction port; a first end of the seventh connection pipe 130 is connected to the seventh port 103, and a second end of the seventh connection pipe 130 is connected to the first end of the outdoor heat exchanger 20.

In this embodiment, the air conditioning system further includes: a second connection pipe 70, a first end of the second connection pipe 70 being connected to the second valve port 52, and a second end of the second connection pipe 70 being connected to the first suction port.

In this embodiment, the air conditioning system further includes: a first end of the eighth connection pipe 140 is connected to the eighth port 104, and a second end of the eighth connection pipe 140 is connected to the second exhaust port.

In this embodiment, the air conditioning system further includes: a first header pipe 150, a first end of the first header pipe 150 being connected to a second end of the outdoor heat exchanger 20; a first branch pipe 160, a first end of the first branch pipe 160 being connected to the second end of the first header pipe 150, and a second end of the first branch pipe 160 being connected to the second end of the first indoor heat exchanger 30; the first branch pipe 160 is provided with a first throttling mechanism 180; a second branch pipe 170, a first end of the second branch pipe 170 being connected to the second end of the first header pipe 150, and a second end of the second branch pipe 170 being connected to the second end of the second indoor heat exchanger 40; the second branch pipe 170 is provided with a second throttling mechanism 190.

In this embodiment, the air conditioning system further includes: a flash evaporator 200; a first pipe 210, a first end of the first pipe 210 being connected to a second end of the outdoor heat exchanger 20, a second end of the first pipe 210 being connected to the flash evaporator 200; a second pipe 220, a first end of the second pipe 220 is connected with the flash evaporator 200, and a second end of the second pipe 220 is connected with both a second end of the first indoor heat exchanger 30 and a second end of the second indoor heat exchanger 40; a third pipe 230, a first end of the third pipe 230 being connected to the flash evaporator 200, and a second end of the third pipe 230 being connected to the first suction port.

In the first embodiment, the first pipeline 210 is provided with a third throttling mechanism 240.

In the first embodiment, a first end of the first pipe 210 is connected to the first manifold 150, and a second end of the first pipe 210 is connected to the flash evaporator 200; a first end of the second pipe 220 is connected with the flash evaporator 200, and a second end of the second pipe 220 is connected with a second end of the first header pipe 150; the second pipeline 220 is provided with a first control valve 250; the air conditioning system further includes: a second control valve 260 disposed on the first manifold 150 on a side of the first pipe 210 remote from the outdoor heat exchanger 20; a third control valve 270 provided on the first branch pipe 160; a fourth control valve 280 provided on the second branch pipe 170 between the second throttling mechanism 190 and the second indoor heat exchanger 40; a fourth pipe 290, a first end of the fourth pipe 290 being connected to a second end of the first indoor heat exchanger 30, a second end of the fourth pipe 290 being connected to the second branch pipe 170 and being located between the second throttling mechanism 190 and the fourth control valve 280; a fifth control valve 300 is provided on the fourth line 290.

In the first embodiment, a first end of the third pipe 230 is connected to the flash evaporator 200, and a second end of the third pipe 230 is connected to the first suction port; a sixth control valve 310 is provided on the third line 230.

In a first embodiment, the air conditioning system further comprises: a fifth pipeline 320, a first end of the fifth pipeline 320 being connected to the first connection pipe 60, and a second end of the fifth pipeline 320 being connected to the fifth connection pipe 110; a seventh control valve 330 is arranged on the fifth pipeline 320; and an eighth control valve 340 provided on the second connection pipe 70.

In a first embodiment, the air conditioning system further comprises: a sixth pipeline 350, a first end of the sixth pipeline 350 being connected to the second exhaust port, and a second end of the sixth pipeline 350 being connected to the first intake port; a ninth control valve 360 is arranged on the sixth pipeline 350; and a tenth control valve 370 provided on the eighth connection pipe 140.

Specifically, a second end of the third pipeline 230 is connected to the second connection pipe 70 and is located on a side of the eighth control valve 340 away from the first direction changing member 50; a first end of the sixth pipe 350 is connected to the eighth connection pipe 140, and a second end of the sixth pipe 350 is connected to the third pipe 230 and is located on a side of the sixth control valve 310 away from the flash evaporator 200.

Optionally, the first control valve 250, the second control valve 260, the third control valve 270, the fourth control valve 280, the fifth control valve 300, the sixth control valve 310, the seventh control valve 330, the eighth control valve 340, the ninth control valve 360, and the tenth control valve 370 are all shut-off valves.

In a second embodiment, the air conditioning system further comprises: a seventh pipe 380, a first end of the seventh pipe 380 being connected to the second suction port; a first three-way valve 390, the first three-way valve 390 being disposed on the second connection pipe 70, the first connection port 391 and the second connection port 392 of the first three-way valve 390 being both located on the second connection pipe 70, and the third connection port 393 of the first three-way valve 390 being connected to the second end of the seventh pipeline 380; wherein, the first connection port 391 can be selectively communicated with the second connection port 392 or the third connection port 393.

In a second embodiment, the air conditioning system further comprises: an eighth conduit 400; a second three-way valve 410, the second three-way valve 410 being disposed on the eighth connection pipe 140, a fourth connection port 411 and a fifth connection port 412 of the second three-way valve 410 being located on the eighth connection pipe 140, and a sixth connection port 413 of the second three-way valve 410 being connected to a first end of the eighth pipeline 400; wherein, the fourth connection port 411 can be selectively communicated with the fifth connection port 412 or the sixth connection port 413; a third three-way valve 420, the third three-way valve 420 being disposed on the second connecting pipe 70 and being located on a side of the first three-way valve 390 away from the first direction changing member 50, a seventh connection port 421 and an eighth connection port 422 of the third three-way valve 420 being located on the second connecting pipe 70, and a ninth connection port 423 of the third three-way valve 420 being connected to a second end of the eighth pipeline 400; the seventh connection port 421 is selectively communicated with the eighth connection port 422 or the ninth connection port 423.

In the second embodiment, a first end of the third pipe 230 is connected to the flash evaporator 200, and a second end of the third pipe 230 is connected to the eighth pipe 400.

In the second embodiment, a first end of the first pipe 210 is connected to the first branch pipe 160 and is located on the side of the first throttling mechanism 180 away from the first main pipe 150, and a second end of the first pipe 210 is connected to the flash evaporator 200; the first pipeline 210 is provided with a first valve 430; a first end of the second pipeline 220 is connected with the flash evaporator 200, and a second end of the second pipeline 220 is connected with the second branch pipe 170 and is positioned on the side of the second throttling mechanism 190 away from the second indoor heat exchanger 40; the air conditioning system further includes: a ninth pipe 440, a first end of the ninth pipe 440 being connected to the second branch pipe 170 and located at a side of the second throttling mechanism 190 adjacent to the second indoor heat exchanger 40; a fourth three-way valve 450, the fourth three-way valve 450 being disposed on the first branch pipe 160, a tenth connection port 451 and an eleventh connection port 452 of the fourth three-way valve 450 being located on the first branch pipe 160, a twelfth connection port 453 of the fourth three-way valve 450 being connected to a second end of the ninth pipeline 440; wherein, the tenth connection port 451 is selectively communicated with the eleventh connection port 452 or the twelfth connection port 453; and a second valve 460 disposed on the second branch pipe 170 and located on a side of the second pipeline 220 away from the second throttling mechanism 190.

Optionally, both the first valve 430 and the second valve 460 are shut-off valves.

In the present embodiment, when the air conditioning system is in the cooling and dehumidifying mode and is in the rated cooling operation mode, the flow rate of the refrigerant flowing through the first indoor heat exchanger 30 is q1, and the flow rate of the refrigerant flowing through the second indoor heat exchanger 40 is q 2; the ratio of q1 to (q1+ q2) ranges from 10% to 30%. Preferably, the ratio of q1 to (q1+ q2) is in the range of 17% to 25%.

In the present embodiment, when the air conditioning system is in the cooling and dehumidifying mode and is in the intermediate cooling operation mode, the flow rate of the refrigerant flowing through the first indoor heat exchanger 30 is q1, the flow rate of the refrigerant flowing through the second indoor heat exchanger 40 is q2, and the ratio of q1 to (q1+ q2) ranges from 1% to 6%. Preferably, the ratio of q1 to (q1+ q2) is in the range of 1.0% to 3.5%.

The humidity is high in early summer, the traditional fresh air conditioner needs lower evaporation temperature to meet the dehumidification requirement, but the evaporation temperature is reduced, the pressure ratio of a compressor is increased, the operation is not economical, the air outlet temperature of an indoor unit is reduced due to the reduction of the evaporation temperature, and the comfort of a human body is reduced; being fit for under this kind of occasion and separately handling cooling and dehumidification, directly realizing two kinds of evaporating temperature of cooling and dehumidification, improved the evaporating temperature who realizes refrigeration function, reduce the pressure ratio for the system efficiency promotes. However, in the midsummer season, the outdoor temperature is high, under the operating condition with a large pressure ratio, the single-stage circulating system with double evaporation temperatures is uneconomical to operate, the energy efficiency of the double-stage compression system is high, and meanwhile, under the operating condition, the operating load is large, the area of the heat exchanger is increased, and the energy efficiency of the system can be improved. Meanwhile, in the early winter, the pressure ratio of the operating condition of the system is small, the load is small, the requirement can be met by adopting a single-stage compression system and a small heat exchanger, but in the severe winter, the outdoor temperature is extremely low, the pressure ratio of the system operation is large, the problems of low volumetric efficiency, overhigh exhaust temperature and the like exist in single-stage compression, and the problems can be well solved by double-stage compression, so that the system is in a high-efficiency operating state. Meanwhile, the operation load is large in severe winter, and the energy efficiency of the system can be improved by increasing the area of the heat exchanger. Therefore, the development of an air conditioning system with a single/double stage switching function and a variable heat exchanger area is urgently needed, so that the system meets the requirements of regions with changeable climate all the year around, and the system is always in the most economical operation state.

The beneficial effect of this application: an air conditioning system device with single/double stage automatic conversion and capable of adjusting the area of a heat exchanger according to the load is provided, namely an air conditioning system with multi-mode operation. The air conditioning system can realize the switching of five operation modes by the switching of the stop valve and the matching of the compression assembly, and can ensure that the system is always in the most economical operation state when the refrigeration/heating function is realized in a region with variable climate.

The air conditioning system realizes the switching of five operation modes by the switching of the stop valve and the matching of the compression assembly, and comprises a double-evaporator double-cylinder single-stage operation mode (namely a refrigeration and dehumidification mode), a double-evaporator double-cylinder double-stage air supply mode (namely a refrigeration mode), a double-condenser double-cylinder double-stage air supply mode (namely a first heating mode), a single-condenser double-cylinder double-stage air supply mode (namely a second heating mode) and a double-condenser double-cylinder single-stage mode (namely a second heating mode).

Further, in the refrigeration and dehumidification mode of the air conditioning system, the percentage range of the refrigerant flow q2 of the dehumidification flow path to the total flow (q1+ q2) when the air conditioning system obtains the optimal energy efficiency ratio under different operation conditions is specified, for example, under the rated refrigeration condition, when the ratio range of q2 to (q1+ q2) is between 10% and 30%, the system has the better energy efficiency ratio, the operation is more economical (see fig. 4), and when the ratio is in the range of 17% to 25%, the energy efficiency ratio is optimal; under the intermediate refrigeration working condition, the system has a better energy efficiency ratio when the ratio of q2 to (q1+ q2) ranges from 1.0% to 6%, and has the best energy efficiency ratio when the ratio ranges from 1.0% to 3.5%.

In a first embodiment, the air conditioning system includes a compression assembly, three heat exchangers, two four-way reversing valves, three throttling mechanisms, and ten shut-off valves. The compression component can be a multi-cylinder compressor capable of realizing single-stage and double-stage switching or a plurality of compressors. The heat exchangers are two indoor side heat exchangers and one outdoor side heat exchanger; the four-way reversing valve is responsible for switching between refrigeration and heating; the throttling mechanism is responsible for throttling the high pressure to the medium pressure or throttling the high pressure from the medium pressure to the low pressure; the stop valve and the compression assembly are matched to realize the switching of multiple operation modes.

The utility model also provides an air conditioning system's control method, please refer to fig. 1 to fig. 9, is applied to the air conditioning system in the above-mentioned embodiment, and air conditioning system's control method includes: controlling the air conditioning system to enter a refrigeration and dehumidification mode; the cooling and dehumidifying mode includes: a first compression part 11 of a compression assembly 10 of the air conditioning system compresses the refrigerant discharged from a first indoor heat exchanger 30 of the air conditioning system, and then the refrigerant enters an outdoor heat exchanger 20 of the air conditioning system; the second compression unit 12 of the compression unit 10 compresses the refrigerant discharged from the second indoor heat exchanger 40 of the air conditioning system, and then causes the refrigerant to enter the outdoor heat exchanger 20; part of the refrigerant flowing out of the outdoor heat exchanger 20 passes through the first indoor heat exchanger 30 to dehumidify the indoor air, and part of the refrigerant flowing out of the outdoor heat exchanger 20 passes through the second indoor heat exchanger 40 to refrigerate the indoor air; or, controlling the air conditioning system to enter a refrigeration mode; the cooling mode includes: the second compression unit 12 performs first-stage compression on the refrigerant discharged from the first indoor heat exchanger 30 and the refrigerant of the second indoor heat exchanger 40, and then the refrigerant enters the first compression unit 11 to perform second-stage compression; the refrigerant discharged from the first compression part 11 passes through the outdoor heat exchanger 20 and then enters the first indoor heat exchanger 30 and the second indoor heat exchanger 40 respectively to exchange heat with indoor air; or, controlling the air conditioning system to enter a first heating mode; the first heating mode includes: the second compression unit 12 performs first-stage compression on the refrigerant discharged from the outdoor heat exchanger 20, and then the refrigerant enters the first compression unit 11 to perform second-stage compression; the refrigerant discharged from the first compression part 11 enters the outdoor heat exchanger 20 after passing through the first indoor heat exchanger 30 and the second indoor heat exchanger 40 to exchange heat with indoor air; or, controlling the air conditioning system to enter a second heating mode; the second heating mode includes: the second compression unit 12 performs first-stage compression on the refrigerant discharged from the outdoor heat exchanger 20, and then the refrigerant enters the first compression unit 11 to perform second-stage compression; the refrigerant discharged from the first compression part 11 exchanges heat with indoor air through the first indoor heat exchanger 30, and then flows into the outdoor heat exchanger 20; or, controlling the air conditioning system to enter a third heating mode; the third heating mode includes: the first compression part 11 compresses a part of the refrigerant discharged from the outdoor heat exchanger 20, and then the refrigerant enters the first indoor heat exchanger 30 to exchange heat with indoor air; the second compression part 12 compresses a part of the refrigerant discharged from the outdoor heat exchanger 20, and then the refrigerant enters the second indoor heat exchanger 40 to exchange heat with indoor air; the refrigerants discharged from the first and second indoor heat exchangers 30 and 40 flow into the outdoor heat exchanger 20.

As shown in fig. 1, the air conditioning system can meet the requirement of a region with changeable climate all the year around by single/double stage automatic conversion and adjusting the area of the heat exchanger according to the load, and the system is always in the most economical operation state. The present application takes a twin-cylinder compressor as an example for introduction.

In a first embodiment, as shown in fig. 2, the cooling and dehumidification mode includes: the first valve port 51 and the second valve port 52 of the first reversing component 50 for controlling the air conditioning system are communicated, and the fourth valve port 54 and the third valve port 53 of the first reversing component 50 are controlled to be communicated; the fifth valve port 101 and the sixth valve port 102 of the second direction changing component 100 of the control air conditioning system are communicated, and the seventh valve port 103 and the eighth valve port 104 of the second direction changing component 100 are controlled to be communicated; the second, third, fourth, eighth and

tenth control valves

260, 270, 280, 340 and 370 controlling the air conditioning system are opened, and the first, fifth, sixth, seventh and

ninth control valves

250, 300, 310, 330 and 360 controlling the air conditioning system are closed.

Specifically, the air conditioning system is in a refrigeration and dehumidification mode, double evaporation temperatures can be realized, the compressor is in a double-cylinder single-stage operation mode, the first indoor heat exchanger 30 realizes a lower evaporation temperature, the second indoor heat exchanger 40 realizes a higher evaporation temperature, the first indoor heat exchanger 30 with the lower evaporation temperature bears latent heat load and mainly realizes a dehumidification function, the second indoor heat exchanger 40 with the higher evaporation temperature bears sensible heat load and mainly realizes a refrigeration function, and the efficiency of the system with a small pressure ratio can be remarkably improved due to the fact that the air side of the second indoor heat exchanger 40 is subjected to small enthalpy difference heat exchange. Wherein, the refrigerant in the second indoor heat exchanger 40 passes through the second reversing component 100 and is absorbed by the lower cylinder of the compressor, as shown in fig. 3, the pressure of the refrigerant is P2, the temperature of the refrigerant is T2, and the refrigerant is compressed in the lower cylinder into the refrigerant with the pressure of P4 and the temperature of T4; the refrigerant in the first indoor heat exchanger 30 is absorbed by the upper cylinder of the compressor through the first direction changing part 50, has a pressure of P1 and a temperature of T1 (wherein, T2> T1), and is compressed into the refrigerant with a pressure of P4 and a temperature of T3. The refrigerant flow q2 with the pressure of P2 and the temperature of T2 is greater than the refrigerant flow q1 with the pressure of P1 and the temperature of T1, when the air-conditioning system under different operation conditions obtains the optimal energy efficiency ratio, the percentage range of the refrigerant flow q1 of the dehumidification flow path to the total flow (q1+ q2) is different, for example, under the rated refrigeration condition, the ratio range of q1 to (q1+ q2) is 10% -30%, the system has the optimal energy efficiency ratio and is more economical to operate (see FIG. 4), when the ratio range is 17% -25%, the air-conditioning system has the optimal energy efficiency ratio, and under the intermediate refrigeration condition, when the ratio range of q1 to (q1+ q2) is 1% -6%, the air-conditioning system has the optimal energy efficiency ratio, and when the ratio is 1.0% -3.5%, the system has the optimal energy efficiency ratio. A refrigerant with pressure of P4 and temperature of T3 and a refrigerant with pressure of P4 and temperature of T3 enter a condenser (i.e., the outdoor heat exchanger 20) through the second reversing component 100 and the first reversing component 50, are condensed and cooled by the condenser to form a high-temperature and high-pressure liquid refrigerant, then the refrigerant passing through the second control valve 260 is divided into two paths, one path of the refrigerant is throttled by the second throttling mechanism 190 to form a refrigerant with pressure of P6 and temperature of T6 and then enters the second indoor heat exchanger 40, absorbs heat and evaporates to form a refrigerant with pressure of P2 and temperature of T2, and then the refrigerant is sucked away by the lower cylinder of the compressor; the other path of refrigerant is throttled and reduced into refrigerant with pressure of P7 and temperature of T7 through the first throttling mechanism 180, enters the first indoor heat exchanger 30 which is responsible for the dehumidification function, absorbs heat and evaporates into refrigerant with pressure of P1 and temperature of T1, and then is sucked away by the upper cylinder of the compressor, so that the whole system circulation process is completed. When the circulation form is used in early summer with high humidity, refrigeration and dehumidification can be separately processed, two evaporation temperatures of refrigeration and dehumidification are directly realized, the evaporation temperature of realizing the refrigeration function is improved, the pressure ratio is reduced, and the energy efficiency of the system is improved.

In a first embodiment, as shown in fig. 5, the cooling mode includes: the first valve port 51 and the second valve port 52 of the first reversing component 50 for controlling the air conditioning system are communicated, and the fourth valve port 54 and the third valve port 53 of the first reversing component 50 are controlled to be communicated; the fifth valve port 101 and the sixth valve port 102 of the second direction changing component 100 of the control air conditioning system are communicated, and the seventh valve port 103 and the eighth valve port 104 of the second direction changing component 100 are controlled to be communicated; the second, third, eighth and

tenth control valves

260, 270, 340 and 370 of the air conditioning system are controlled to be closed, and the first, fourth, fifth, sixth, seventh and

ninth control valves

250, 280, 300, 310, 330 and 360 of the air conditioning system are controlled to be opened.

Specifically, the air conditioning system is in a refrigeration mode, the compressor is in a two-cylinder two-stage air make-up operation mode, the refrigerant in the second indoor heat exchanger 40 and the refrigerant in the first indoor heat exchanger 30 are sucked by the lower cylinder of the compressor through the second reversing component 100, the refrigerant at the refrigerant pressure of P1 and the refrigerant at the temperature of T1 is compressed in the lower cylinder into a medium-pressure refrigerant with the pressure of P2 and the temperature of T2, and the medium-pressure refrigerant is mixed with the gas refrigerant separated from the flash evaporator, enters the upper cylinder for high-pressure stage compression, is further compressed to a condensation pressure Pk through the high-pressure stage, and then enters the condenser (i.e., the outdoor heat exchanger 20) through the first reversing component 50 for cooling, condensation and supercooling. The cooled liquid refrigerant is throttled and decompressed into medium-pressure refrigerant by the third throttling mechanism 240 and then enters the flash evaporator, gas separated from the flash evaporator is used as intermediate air supplement to be mixed with the refrigerant with the pressure of P2 and the temperature of T2 by the sixth control valve 310 and then enters the upper cylinder for high-pressure stage compression, so that high-pressure stage suction is cooled, the high-pressure stage compression process is optimized, and the exhaust temperature is reduced; the liquid separated from the flash evaporator is throttled and depressurized by the second throttling mechanism 190 to be a low-temperature and low-pressure refrigerant, and then enters the first indoor heat exchanger 30 and the second indoor heat exchanger 40 through the fifth control valve 300 and the fourth control valve 280 to absorb heat and evaporate to be a low-temperature and low-pressure gaseous refrigerant, and then is sucked and compressed by the lower cylinder, so that the whole system cycle process is completed. In the midsummer season, the outdoor temperature is higher, the pressure ratio is large, the load is high, the pressure ratio can be decomposed by the double-stage compression mode, the volume efficiency is improved, and the exhaust temperature is reduced; meanwhile, the load is large, and the circulating device is provided with two indoor evaporators, so that the system can obtain higher energy efficiency.

In the first embodiment, as shown in fig. 6, the first heating mode includes: the first valve port 51 and the fourth valve port 54 of the first reversing component 50 for controlling the air conditioning system are communicated, and the second valve port 52 and the third valve port 53 of the first reversing component 50 are controlled to be communicated; the fifth valve port 101 and the eighth valve port 104 of the second direction changing component 100 of the control air conditioning system are communicated, and the sixth valve port 102 and the seventh valve port 103 of the second direction changing component 100 are controlled to be communicated; the second, third, eighth and

tenth control valves

ninth control valves

Specifically, the air conditioning system is in a first heating mode, the compressor is in a two-cylinder two-stage operation mode, the low-temperature and low-pressure refrigerant in the evaporator (i.e., the outdoor heat exchanger 20) is absorbed by the lower cylinder of the compressor through the second reversing component 100, the refrigerant has a pressure of P1 and a temperature of T1, is compressed in the lower cylinder into a medium-pressure refrigerant with a pressure of P2 and a temperature of T2, is mixed with the gas refrigerant separated from the flash evaporator through the ninth control valve 360 and enters the upper cylinder for high-pressure stage compression, is further compressed to a condensation pressure Pk at the high pressure stage, is divided into two paths through the first reversing component 50, one path is cooled, condensed and subcooled in the first indoor heat exchanger 30, the other path enters the second indoor heat exchanger 40 through the seventh control valve 330 for cooling, condensing and subcooling, and the heat exchange areas of the two condensers (i.e., the first indoor heat exchanger 30 and the second indoor heat exchanger 40) are increased, The heat dissipation efficiency is improved, the operation load is large in winter, and the energy efficiency of the system can be improved. The cooled liquid refrigerant passes through the fifth control valve 300 and the fourth control valve 280, is throttled and decompressed into a medium-pressure refrigerant by the second throttling mechanism 190, then enters the flash evaporator through the first control valve 250, the gas separated from the flash evaporator is used as intermediate air supplement, is compressed with the refrigerant with the pressure of P2 and the temperature of T2 through the sixth control valve 310, then directly enters the high-pressure stage compression after being mixed with the refrigerant with the lower cylinder, the high-pressure stage compression process is optimized, the compression power consumption of the high-pressure stage is reduced, the liquid separated from the flash evaporator is throttled and decompressed into a low-temperature and low-pressure refrigerant through the third throttling mechanism 240, then enters the evaporator to absorb heat and evaporate into a low-temperature and low-pressure gaseous refrigerant, and then enters the lower cylinder to be compressed, and the whole system circulation process is. In severe winter, the system operation pressure ratio is large, the load is large, the pressure ratio can be reduced by the double-cylinder double-stage air supply operation mode of the double-condenser, the area of the indoor heat exchanger (condenser) is increased, and the system energy efficiency is greatly improved.

In the first embodiment, as shown in fig. 7, the second heating mode includes: the first valve port 51 and the fourth valve port 54 of the first reversing component 50 for controlling the air conditioning system are communicated, and the second valve port 52 and the third valve port 53 of the first reversing component 50 are controlled to be communicated; the fifth valve port 101 and the eighth valve port 104 of the second direction changing component 100 of the control air conditioning system are communicated, and the sixth valve port 102 and the seventh valve port 103 of the second direction changing component 100 are controlled to be communicated; the second, third, fourth, fifth, seventh, eighth and

tenth control valves

260, 270, 280, 300, 330, 340 and 370 of the air conditioning system are controlled to be closed, and the first, sixth and

ninth control valves

250, 310 and 360 of the air conditioning system are controlled to be opened.

Specifically, the air conditioning system is in the second heating mode, the system flow path is substantially the same as the flow path shown in fig. 6, and the main difference is that the second indoor heat exchanger 40 in the system does not participate in the circulation and only the first indoor heat exchanger 30 participates in the system circulation by closing the fourth control valve 280 and the seventh control valve 330, which is advantageous in that the energy saving effect of the system operation is significant at the time of low load operation and the energy efficiency ratio is relatively high.

In the first embodiment, as shown in fig. 8, the third heating mode includes: the first valve port 51 and the fourth valve port 54 of the first reversing component 50 for controlling the air conditioning system are communicated, and the second valve port 52 and the third valve port 53 of the first reversing component 50 are controlled to be communicated; the fifth valve port 101 and the eighth valve port 104 of the second direction changing component 100 of the control air conditioning system are communicated, and the sixth valve port 102 and the seventh valve port 103 of the second direction changing component 100 are controlled to be communicated; the second, third, fourth, fifth, seventh, eighth and

tenth control valves

260, 270, 280, 300, 330, 340 and 370 of the air conditioning system are controlled to be opened, and the first, sixth and

ninth control valves

250, 310 and 360 of the air conditioning system are controlled to be closed.

Specifically, the cycle forms shown in fig. 6 and 7 achieve higher system energy efficiency when used in severe winter, but the outdoor temperature is slightly higher than that in severe winter in the early winter season, but the air conditioner is still required to be turned on for heating, and the pressure ratio is relatively small, so that the two-stage compression cycle form is not economical, and the single-stage compression system is more advantageous.

Specifically, the air conditioning system is in a third heating mode, the compressor is in a double-cylinder single-stage operation mode, the low-temperature and low-pressure refrigerant from the evaporator is divided into two paths, one path of the low-temperature and low-pressure refrigerant enters the lower cylinder of the compressor through the second reversing component 100, is compressed into high-temperature and high-pressure refrigerant, then flows through the tenth control valve 370 and the second reversing component 100, enters the second indoor heat exchanger 40 to be cooled, condensed and supercooled, the other path of the low-temperature and low-pressure refrigerant enters the upper cylinder of the compressor through the first reversing component 50, is compressed into high-pressure refrigerant in the lower cylinder, and then enters the first indoor heat exchanger 30 through the first reversing. The cooled liquid refrigerant passes through the fourth control valve 280 and the fifth control valve 300 respectively, is throttled and depressurized to low-pressure refrigerant by the second throttling mechanism 190, then enters the evaporator (i.e., the outdoor heat exchanger 20) through the second control valve 260, is evaporated and absorbs heat, and thus the whole system cycle process is completed.

In the second embodiment, as shown in fig. 9, the operation mode of the air conditioning system is the same as that of the first embodiment, that is, five operation mode switching can be realized, and the system is always in an efficient operation state when used in a climate-changeable region all the year around. The device in this embodiment includes a compression assembly, three heat exchangers, two four-way reversing valves, three-way valves, two throttle valves, and two stop valves. The compression assembly can be a multi-cylinder compressor capable of realizing single-stage and double-stage switching, or a plurality of compressors, the heat exchangers are two indoor side heat exchangers, one outdoor side heat exchanger and a four-way reversing valve are responsible for refrigeration and heating switching, the throttling mechanism is responsible for throttling high pressure to medium pressure or throttling from medium pressure to low pressure, and the stop valve, the three-way valve and the compression assembly are matched to realize multi-mode switching.

From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects:

the air conditioning system of the utility model realizes single-stage and double-stage compression of the refrigerant by arranging the first compression part 11 and the second compression part 12, and meets the requirements of different operation pressure ratios; the switching between cooling and heating is realized by arranging the first reversing component 50 and the second reversing component 100; the refrigeration and the initial separation treatment can be realized by arranging the two indoor heat exchangers, and the change of the heat exchange area can also be realized; furthermore, the air conditioning system can realize the switching of five operation modes, including a double-evaporator double-cylinder single-stage operation mode, a double-evaporator double-cylinder double-stage air supplementing mode, a double-condenser double-cylinder double-stage air supplementing mode, a single-condenser double-cylinder double-stage air supplementing mode and a double-condenser double-cylinder single-stage mode, so that the condition that the system is always in the most economical operation state when the refrigeration and heating functions are realized in regions with variable climates is met.

It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.

Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. An air conditioning system, comprising:

a compression assembly (10) including a first compression part (11) and a second compression part (12), the first compression part (11) having a first suction port and a first discharge port, the second compression part (12) having a second suction port and a second discharge port;

the first reversing component (50) is used for switching between cooling and heating of the air conditioning system, and the first reversing component (50) is connected with the first air inlet and the first air outlet;

the second reversing component (100) is used for switching between cooling and heating of the air conditioning system, and the second reversing component (100) is connected with the second air suction port; the second exhaust port is connected with both the second reversing component (100) and the first air inlet;

a first indoor heat exchanger (30), wherein a first end of the first indoor heat exchanger (30) is connected with the first reversing component (50);

a second indoor heat exchanger (40), wherein a first end of the second indoor heat exchanger (40) is connected with the second reversing component (100);

and a first end of the outdoor heat exchanger (20) is connected with both the first reversing component (50) and the second reversing component (100), and a second end of the outdoor heat exchanger (20) is connected with both a second end of the first indoor heat exchanger (30) and a second end of the second indoor heat exchanger (40).

2. The air conditioning system of claim 1, wherein the first direction changing member (50) has a first valve port (51), a second valve port (52), a third valve port (53), and a fourth valve port (54), the first valve port (51) communicating with the second valve port (52) or the fourth valve port (54), the third valve port (53) communicating with the fourth valve port (54) or the second valve port (52); the second valve port (52) is connected with the first air inlet; the fourth valve port (54) is connected with the first exhaust port;

the second direction changing component (100) is provided with a fifth valve port (101), a sixth valve port (102), a seventh valve port (103) and an eighth valve port (104), the fifth valve port (101) is communicated with the sixth valve port (102) or the eighth valve port (104), and the seventh valve port (103) is communicated with the eighth valve port (104) or the sixth valve port (102); the sixth valve port (102) is connected with the second suction port; the second exhaust port is connected to both the eighth valve port (104) and the first intake port;

a first end of the first indoor heat exchanger (30) is connected with the first valve port (51);

a first end of the second indoor heat exchanger (40) is connected with the fifth valve port (101);

the first end of the outdoor heat exchanger (20) is connected with the third valve port (53) and the seventh valve port (103).

3. Air conditioning system according to claim 1, characterized in that the compression assembly (10) is a compressor, the compressor is a twin-cylinder compressor, the upper cylinder of which is the first compression part (11) and the lower cylinder of which is the second compression part (12); or, the compression assembly (10) comprises two compressors, one of which is the first compression part (11) and the other of which is the second compression part (12).

4. The air conditioning system of claim 1, wherein the first reversing component (50) is a four-way reversing valve; and/or the second reversing component (100) is a four-way reversing valve.

5. The air conditioning system of claim 2, further comprising:

a first connection pipe (60), a first end of the first connection pipe (60) being connected to a first end of the first indoor heat exchanger (30), a second end of the first connection pipe (60) being connected to the first valve port (51);

a second connection pipe (70), a first end of the second connection pipe (70) being connected to the second valve port (52), and a second end of the second connection pipe (70) being connected to the first suction port.

6. The air conditioning system of claim 2, further comprising:

a third connection pipe (80), a first end of the third connection pipe (80) being connected to a first end of the outdoor heat exchanger (20), a second end of the third connection pipe (80) being connected to the third valve port (53);

a fourth connection pipe (90), a first end of the fourth connection pipe (90) being connected to the first exhaust port, and a second end of the fourth connection pipe (90) being connected to the fourth valve port (54).

7. The air conditioning system of claim 5, further comprising:

a fifth connection pipe (110), a first end of the fifth connection pipe (110) being connected to a first end of the second indoor heat exchanger (40), and a second end of the fifth connection pipe (110) being connected to the fifth valve port (101).

8. The air conditioning system of claim 2, further comprising:

a sixth connection pipe (120), a first end of the sixth connection pipe (120) being connected to the sixth valve port (102), and a second end of the sixth connection pipe (120) being connected to the second suction port;

a seventh connection pipe (130), a first end of the seventh connection pipe (130) being connected to the seventh valve port (103), and a second end of the seventh connection pipe (130) being connected to the first end of the outdoor heat exchanger (20).

9. The air conditioning system of claim 5, further comprising:

an eighth connection pipe (140), a first end of the eighth connection pipe (140) being connected to the eighth valve port (104), and a second end of the eighth connection pipe (140) being connected to the second exhaust port.

10. The air conditioning system of claim 9, further comprising:

a first manifold (150), a first end of the first manifold (150) being connected to a second end of the outdoor heat exchanger (20);

a first branch pipe (160), a first end of the first branch pipe (160) being connected with a second end of the first header pipe (150), a second end of the first branch pipe (160) being connected with a second end of the first indoor heat exchanger (30); a first throttling mechanism (180) is arranged on the first branch pipe (160);

a second branch pipe (170), a first end of the second branch pipe (170) being connected with a second end of the first header pipe (150), a second end of the second branch pipe (170) being connected with a second end of the second indoor heat exchanger (40); and a second throttling mechanism (190) is arranged on the second branch pipe (170).

11. The air conditioning system of claim 10, further comprising:

a flash evaporator (200);

a first pipe (210), a first end of the first pipe (210) is connected with a second end of the outdoor heat exchanger (20), and a second end of the first pipe (210) is connected with the flash evaporator (200);

a second pipe (220), a first end of the second pipe (220) being connected with the flash evaporator (200), a second end of the second pipe (220) being connected with both a second end of the first indoor heat exchanger (30) and a second end of the second indoor heat exchanger (40);

a third pipe (230), a first end of the third pipe (230) being connected to the flash evaporator (200), a second end of the third pipe (230) being connected to the first suction port.

12. Air conditioning system according to claim 11, characterized in that a third throttling mechanism (240) is provided on the first line (210).

13. Air conditioning system according to claim 11, wherein a first end of the first pipe (210) is connected to the first header pipe (150), and a second end of the first pipe (210) is connected to the flash evaporator (200);

a first end of the second pipe (220) is connected with the flash evaporator (200), and a second end of the second pipe (220) is connected with a second end of the first header pipe (150); a first control valve (250) is arranged on the second pipeline (220);

the air conditioning system further includes:

a second control valve (260) disposed on the first manifold (150) on a side of the first pipe (210) remote from the outdoor heat exchanger (20);

a third control valve (270) provided on the first branch pipe (160);

a fourth control valve (280) provided on the second branch pipe (170) between the second throttling mechanism (190) and the second indoor heat exchanger (40);

a fourth pipe (290), a first end of the fourth pipe (290) being connected with a second end of the first indoor heat exchanger (30), a second end of the fourth pipe (290) being connected with the second branch pipe (170) and being located between the second throttling mechanism (190) and the fourth control valve (280); a fifth control valve (300) is arranged on the fourth pipeline (290).

14. The air conditioning system of claim 11, wherein a first end of the third pipe (230) is connected to the flash evaporator (200), and a second end of the third pipe (230) is connected to the first suction port; a sixth control valve (310) is arranged on the third pipeline (230).

15. The air conditioning system of claim 7, further comprising:

a fifth pipeline (320), a first end of the fifth pipeline (320) being connected to the first connection pipe (60), a second end of the fifth pipeline (320) being connected to the fifth connection pipe (110); a seventh control valve (330) is arranged on the fifth pipeline (320);

an eighth control valve (340) provided on the second connection pipe (70).

16. The air conditioning system of claim 9, further comprising:

a sixth pipeline (350), a first end of the sixth pipeline (350) being connected to the second exhaust port, a second end of the sixth pipeline (350) being connected to the first intake port; a ninth control valve (360) is arranged on the sixth pipeline (350);

a tenth control valve (370) provided on the eighth connection pipe (140).

17. The air conditioning system of claim 11, further comprising:

a seventh pipe (380), a first end of the seventh pipe (380) being connected to the second suction port;

a first three-way valve (390), wherein the first three-way valve (390) is disposed on the second connecting pipe (70), the first connecting port (391) and the second connecting port (392) of the first three-way valve (390) are both located on the second connecting pipe (70), and the third connecting port (393) of the first three-way valve (390) is connected with the second end of the seventh pipeline (380); wherein, the first connecting port (391) can be selectively communicated with the second connecting port (392) or the third connecting port (393).

18. The air conditioning system of claim 17, further comprising:

an eighth conduit (400);

a second three-way valve (410), wherein the second three-way valve (410) is arranged on the eighth connecting pipe (140), a fourth connecting port (411) and a fifth connecting port (412) of the second three-way valve (410) are both positioned on the eighth connecting pipe (140), and a sixth connecting port (413) of the second three-way valve (410) is connected with a first end of the eighth pipeline (400); wherein the fourth connection port (411) is selectively communicated with the fifth connection port (412) or the sixth connection port (413);

a third three-way valve (420), wherein the third three-way valve (420) is arranged on the second connecting pipe (70) and is positioned on one side of the first three-way valve (390) far away from the first reversing component (50), a seventh connecting port (421) and an eighth connecting port (422) of the third three-way valve (420) are both positioned on the second connecting pipe (70), and a ninth connecting port (423) of the third three-way valve (420) is connected with the second end of the eighth pipeline (400); wherein the seventh connection port (421) is selectively communicated with the eighth connection port (422) or the ninth connection port (423).

19. Air conditioning system according to claim 18, wherein a first end of the third pipe (230) is connected to the flash evaporator (200) and a second end of the third pipe (230) is connected to the eighth pipe (400).

20. The air conditioning system of claim 11, wherein a first end of the first pipe (210) is connected to the first branch pipe (160) and is located on a side of the first throttling mechanism (180) away from the first header pipe (150), and a second end of the first pipe (210) is connected to the flash evaporator (200); a first valve (430) is arranged on the first pipeline (210);

a first end of the second pipeline (220) is connected with the flash evaporator (200), and a second end of the second pipeline (220) is connected with the second branch pipe (170) and is positioned on the side of the second throttling mechanism (190) far away from the second indoor heat exchanger (40);

the air conditioning system further includes:

a ninth pipeline (440), a first end of the ninth pipeline (440) is connected with the second branch pipe (170) and is positioned at one side of the second throttling mechanism (190) close to the second indoor heat exchanger (40);

a fourth three-way valve (450), the fourth three-way valve (450) being disposed on the first branch pipe (160), a tenth connection port (451) and an eleventh connection port (452) of the fourth three-way valve (450) being located on the first branch pipe (160), a twelfth connection port (453) of the fourth three-way valve (450) being connected to a second end of the ninth pipeline (440); wherein the tenth connection port (451) is selectively communicated with the eleventh connection port (452) or the twelfth connection port (453);

and the second valve (460) is arranged on the second branch pipe (170) and is positioned on the side, away from the second throttling mechanism (190), of the second pipeline (220).

21. The air conditioning system as claimed in claim 1, wherein when the air conditioning system is in a cooling and dehumidifying mode and in a rated cooling operation, a flow rate of the refrigerant passing through the first indoor heat exchanger (30) is q1, and a flow rate of the refrigerant passing through the second indoor heat exchanger (40) is q 2; the ratio of q1 to (q1+ q2) ranges from 10% to 30%.

22. The air conditioning system of claim 1, wherein when the air conditioning system is in the cooling and dehumidification mode and in the intermediate cooling condition, the flow rate of the refrigerant flowing through the first indoor heat exchanger (30) is q1, the flow rate of the refrigerant flowing through the second indoor heat exchanger (40) is q2, and the ratio of q1 to (q1+ q2) is in the range of 1% -6%.