CN219283481U

CN219283481U - Air conditioning system

Info

Publication number: CN219283481U
Application number: CN202320061096.7U
Authority: CN
Inventors: 汤奇雄; 黎辉玲; 邱小洲; 刘群波; 冯君璞; 李鹏
Original assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Current assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2023-01-04
Filing date: 2023-01-04
Publication date: 2023-06-30
Anticipated expiration: 2033-01-04

Abstract

The utility model discloses an air conditioning system which comprises a compressor, a first switching device, a second switching device, an outdoor heat exchanger and a plurality of groups of indoor heat exchange units, wherein at least one group of indoor heat exchange units comprises a first indoor heat exchanger and a second indoor heat exchanger, the compressor is provided with a first exhaust port, a second exhaust port and an air suction port, the first exhaust port, the air suction port and the first end of the first indoor heat exchanger are connected with the first switching device, a first flow path is formed between the first end of the outdoor heat exchanger and the first switching device, the first end of the second exhaust port and the first end of the second indoor heat exchanger are connected with the second switching device, the second switching device is connected with the first flow path, and the second ends of the first indoor heat exchanger and the second indoor heat exchanger are connected with the second end of the outdoor heat exchanger. In the utility model, the first indoor heat exchanger and the second indoor heat exchanger can have different refrigerant pressures, and can realize step heating or more efficient dehumidification and defrosting, thereby improving the energy efficiency of the system.

Description

Air conditioning system

Technical Field

The utility model relates to the technical field of air conditioners, in particular to an air conditioning system.

Background

The multi-tube air conditioning system in the prior art can realize the functions of refrigeration, heating and constant-temperature dehumidification. However, although the conventional air conditioning system can meet the general refrigerating and heating conditions, the capacity is attenuated and the energy efficiency is also deteriorated under the low-temperature heating conditions, and when the outdoor unit is defrosted in the heating dehumidification or cold seasons, the indoor heat exchanger is easy to have large work load and poor energy efficiency.

Disclosure of Invention

The utility model mainly aims to provide an air conditioning system, which aims to improve the energy efficiency of the air conditioning system.

In order to achieve the above object, the present utility model provides an air conditioning system, which includes a compressor, a first switching device, a second switching device, an outdoor heat exchanger, and a plurality of sets of indoor heat exchange units, wherein at least one set of indoor heat exchange units includes a first indoor heat exchanger and a second indoor heat exchanger;

the compressor is provided with a first exhaust port, a second exhaust port and an air suction port;

the first exhaust port, the air suction port, the first end of the first indoor heat exchanger and the first end of the outdoor heat exchanger are connected with the first switching device, a first flow path is formed between the first end of the outdoor heat exchanger and the first switching device, and the second end of the outdoor heat exchanger is connected with the second end of the first indoor heat exchanger;

the second exhaust port and the first end of the second indoor heat exchanger are connected with the second switching device, the second switching device is connected with the first flow path, and the second end of the second indoor heat exchanger is connected with the second end of the outdoor heat exchanger.

In an embodiment, the first switching device is a first reversing valve.

In an embodiment, the second switching device is a second reversing valve, and the second reversing valve is further connected to the air suction port.

In an embodiment, a first one-way valve is arranged between the second reversing valve and the first flow path, and the first one-way valve is arranged to be in one-way conduction from the second reversing valve to the first flow path; or alternatively, the process may be performed,

a first connecting valve is arranged between the second reversing valve and the first flow path.

In an embodiment, a second flow path is formed between the second reversing valve and the first end of the second indoor heat exchanger, and the second flow path is communicated with the first flow path and is provided with a first control valve.

In an embodiment, the second switching device includes a first electromagnetic valve and a second electromagnetic valve that are disposed in parallel, one end of the first electromagnetic valve is connected to the second air outlet, the other end is connected to the first flow path, one end of the second electromagnetic valve is connected to the second air outlet, and the other end is connected to the first end of the second indoor heat exchanger.

In one embodiment, a second control valve is provided between the first solenoid valve and the first flow path.

In an embodiment, a first indoor throttling element is arranged between the second end of the first indoor heat exchanger and the second end of the outdoor heat exchanger, and a second indoor throttling element is arranged between the second end of the second indoor heat exchanger and the second end of the outdoor heat exchanger.

In an embodiment, the second end of the first indoor heat exchanger and the second end of the second indoor heat exchanger are respectively connected with the second end of the outdoor heat exchanger through a main road, an air supplementing module is arranged on the main road, and the air supplementing module is connected with the air suction port through an air supplementing pipeline.

In an embodiment, the air supplementing module comprises a supercooling throttle valve and an economizer, the economizer is arranged on the main road, a bypass pipeline is arranged on the main road and communicated with the main road and the economizer, the supercooling throttle valve is arranged on the bypass pipeline, and the economizer is connected with the air suction port through the air supplementing pipeline.

In an embodiment, the compressor includes mutually independent first compression jar and second compression jar, first compression jar with first gas vent intercommunication, the second compression jar with second gas vent intercommunication, first compression jar with the second compression jar all with the induction port intercommunication, the air supplementing pipeline pass through the air supplementing branch pipe with the second compression jar intercommunication, be equipped with the third solenoid valve on the air supplementing branch pipe, still be equipped with the fourth solenoid valve on the air supplementing branch pipe, the fourth solenoid valve is located the air inlet end of air supplementing branch pipe with between the induction port.

In an embodiment, the first indoor heat exchanger is disposed on a windward side, and the second indoor heat exchanger is disposed on a leeward side.

In an embodiment, at least one of the indoor heat exchange units further comprises a third indoor heat exchanger, the air conditioning system further comprises a first branch and a second branch, the first end of the third indoor heat exchanger is connected with the first switching device through the first branch, the second end of the third indoor heat exchanger is connected with the second end of the outdoor heat exchanger through the second branch, a fifth electromagnetic valve is arranged on the first branch, and a sixth electromagnetic valve is arranged on the second branch.

In an embodiment, the air suction port comprises a first sub air suction port and a second sub air suction port, a first pipeline is formed between the first reversing valve and the first sub air suction port, a second pipeline is formed between the second reversing valve and the second sub air suction port, and the first pipeline is communicated with the second pipeline.

In an embodiment, a second one-way valve is arranged on the second pipeline, and the second one-way valve is arranged to be in one-way conduction from the second reversing valve to the second sub-air suction port; or alternatively, the process may be performed,

And a second connecting valve is arranged on the second pipeline.

In an embodiment, the second end of the first indoor heat exchanger and the second end of the second indoor heat exchanger are connected with the second end of the outdoor heat exchanger through a main road respectively, and the main road is provided with an air supplementing module, and the air supplementing module is connected with the second pipeline through an air supplementing pipeline.

In an embodiment, the air supplementing module includes a supercooling throttle valve and an economizer, the economizer is disposed on the main road, a bypass pipeline is disposed on the main road, the bypass pipeline is communicated with the main road and the economizer, the supercooling throttle valve is disposed on the bypass pipeline, and the economizer is connected with the second pipeline through the air supplementing pipeline.

In an embodiment, a seventh electromagnetic valve is provided between the first and second pipelines.

The utility model provides an air conditioning system which comprises a compressor, a first switching device, a second switching device, an outdoor heat exchanger and a plurality of groups of indoor heat exchange units, wherein at least one group of indoor heat exchange units comprises a first indoor heat exchanger and a second indoor heat exchanger, the compressor is provided with a first exhaust port, a second exhaust port and an air suction port, the first exhaust port, the air suction port, a first end of the first indoor heat exchanger and a first end of the outdoor heat exchanger are connected with the first switching device, a first flow path is formed between the first end of the outdoor heat exchanger and the first switching device, the first end of the second exhaust port and the first end of the second indoor heat exchanger are connected with the second switching device, the second switching device is connected with the first flow path, and the second ends of the first indoor heat exchanger and the second indoor heat exchanger are connected with the second end of the outdoor heat exchanger. In the embodiment provided by the utility model, the first indoor heat exchanger and the second indoor heat exchanger can have different refrigerant pressures, so that the cascade heating can be realized in a heating mode, the energy efficiency of the system can be improved, the efficient reheating and dehumidification can be realized in a dehumidification or defrosting mode, the temperature fluctuation is small, the human body comfort is improved, and meanwhile, the energy efficiency of the system is higher.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present utility model, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic structural diagram of an embodiment of an air conditioning system according to the present utility model;

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

FIG. 3 is a schematic diagram of the reheat dehumidification mode of the air conditioning system of FIG. 1;

FIG. 4 is a schematic diagram of a hybrid mode of the air conditioning system of FIG. 1;

fig. 5 is a schematic structural diagram of a heating mode of another embodiment of an air conditioning system according to the present utility model;

FIG. 6 is a schematic diagram of the air conditioning system of FIG. 1 with enhanced vapor injection functionality;

fig. 7 is a schematic structural diagram of a heating mode of another embodiment of an air conditioning system according to the present utility model.

Reference numerals illustrate:

the achievement of the objects, functional features and advantages of the present utility model will be further described with reference to the accompanying drawings, in conjunction with the embodiments.

Detailed Description

In the case where a directional instruction is involved in the embodiment of the present utility model, the directional instruction is merely used to explain the relative positional relationship, movement condition, etc. between the components in a specific posture, and if the specific posture is changed, the directional instruction is changed accordingly.

In addition, if there is a description of "first", "second", etc. in the embodiments of the present utility model, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" as it appears throughout is meant to include three side-by-side schemes, for example, "A and/or B", including the A scheme, or the B scheme, or the scheme where A and B meet at the same time.

The utility model provides an air conditioning system, which aims to increase the energy efficiency of the air conditioning system by arranging double exhaust compressors in a refrigerant circulation loop, improve the low-temperature heating capacity and the indoor temperature non-fluctuation capacity during defrosting, and improve the user experience. In the present utility model, the air conditioning system is a multi-tube air conditioning system including an outdoor heat exchanger 30 and a plurality of sets of indoor heat exchange units. The following specifically describes the structure of the air conditioning system.

In the present utility model, as shown in fig. 1 to 5, the air conditioning system includes a compressor, a first switching device 21, a second switching device 22, an outdoor heat exchanger 30, and a plurality of sets of indoor heat exchange units. It should be noted that the number of the indoor heat exchange units is not limited, and may be, for example, two groups, three groups or five groups, etc., and may be specifically set according to the needs of the usage scenario. In addition, the specific forms of the indoor heat exchangers in each group of indoor heat exchange units can also be respectively set according to requirements, and in one embodiment, at least one group of indoor heat exchange units comprises two indoor heat exchangers of the first indoor heat exchanger 31 and the second indoor heat exchanger 32. In another embodiment, at least one of the sets of indoor heat exchange units includes only one indoor heat exchanger of the third indoor heat exchanger 33.

The compressor has a first discharge port 11, a second discharge port 12, and a suction port 13. The first exhaust port 11 and the second exhaust port 12 of the compressor can independently exhaust air to form two mutually independent flow paths, wherein one flow path flows through the first switching device 21 and then is respectively connected with each indoor heat exchange unit, and the other flow path flows through the second switching device 22 and then is connected with each indoor heat exchange unit. In the present embodiment, the flow path of the first exhaust port 11 is connected to the first indoor heat exchanger 31, and the flow path of the second exhaust port 12 is connected to the second indoor heat exchanger 32. Specifically, referring to fig. 1 to 4, the first exhaust port 11, the air intake port 13, the first end of the first indoor heat exchanger 31, and the first end of the outdoor heat exchanger 30 are connected to the first switching device 21, a first flow path A1 is formed between the first end of the outdoor heat exchanger 30 and the first switching device 21, and the second end of the outdoor heat exchanger 30 is connected to the second end of the first indoor heat exchanger 31. The second exhaust port 12 and the first end of the second indoor heat exchanger 32 are connected to the second switching device 22, the second switching device 22 is connected to the first flow path A1, and the second end of the second indoor heat exchanger 32 is connected to the second end of the outdoor heat exchanger 30.

In this embodiment, the first switching device 21 and the second switching device 22 may be a reversing valve, a solenoid valve group, or a combination of a reversing valve and a solenoid valve group. The air conditioning system is mainly used for switching the flow direction of the refrigerant in the refrigerant circulation loop so as to realize heating, refrigerating, reheating, dehumidifying or defrosting and mixing modes according to actual requirements. In an embodiment, the first switching device 21 and the second switching device 22 are reversing valves, the second switching device 22 is further connected to the air suction port 13, and different refrigerant flow directions are realized through valve position switching, so that in this embodiment, the first switching device 21 and the second switching device 22 are four-way reversing valves for convenience of understanding.

Referring to fig. 1, in the heating mode, the outdoor heat exchanger 30 corresponds to an evaporator, and the first indoor heat exchanger 31 and the second indoor heat exchanger 32 correspond to condensers. The first switching device 21 conducts the first exhaust port 11 and the first end of the first indoor heat exchanger 31 while conducting the first end of the outdoor heat exchanger 30 and the suction port 13; the second switching device 22 turns on the second exhaust port 12 and the first end of the second indoor heat exchanger 32. One air flow discharged from the compressor flows into the first indoor heat exchanger 31 to exchange heat through the discharge port of the first exhaust port 11, the other air flow flows into the second indoor heat exchanger 32 to exchange heat through the discharge port of the second exhaust port, and then the two air flows are converged in the main path B and flow through the outdoor heat exchanger 30 to exchange heat, and return to the air suction port 13 of the compressor from the first switching device 21 through the first flow path A1 so as to perform the next refrigerant circulation, thereby realizing rapid heating of indoor air. In this embodiment, the first heat exchanger and the second heat exchanger may have different refrigerant pressures, so that step heating may be implemented, and energy efficiency of the air conditioning system may be higher.

Referring to fig. 2, in the cooling mode, the outdoor heat exchanger 30 corresponds to a condenser, and the first indoor heat exchanger 31 and the second indoor heat exchanger 32 correspond to an evaporator. The first switching device 21 conducts the first exhaust port 11 and the first end of the outdoor heat exchanger 30 while conducting the first end of the first indoor heat exchanger 31 and the suction port 13; the second switching device 22 communicates the second exhaust port 12 and the first flow path A1, and simultaneously communicates the first end of the second indoor heat exchanger 32 and the suction port 13. One air flow discharged from the compressor is discharged through the first exhaust port 11 and flows into the first flow path A1, the other air flow is discharged through the second exhaust port 12 and flows into the first flow path A1, after being converged and subjected to heat exchange through the outdoor heat exchanger 30, the two air flows are divided into two flow paths, respectively pass through the first indoor heat exchanger 31 and the second outdoor heat exchanger 30 and are subjected to heat exchange, and then respectively flow back into the air suction port 13 of the compressor from the first switching device 21 and the second switching device 22, so that the next refrigerant circulation is performed, and the indoor air rapid refrigerating function is realized.

In a preferred embodiment, a first check valve 41 is disposed between the second reversing valve and the first flow path A1, and the first check valve 41 is disposed to be in unidirectional communication from the second reversing valve to the first flow path A1. In this way, the refrigerant in the first flow path A1 is prevented from flowing to the second switching device 22, and flowing to the second indoor heat exchanger 32 or the second exhaust port 12, which affects the energy efficiency of the air conditioning system. It will be appreciated that in this embodiment, a first connection valve may be further disposed between the second reversing valve and the first flow path A1, where the first connection valve may be a solenoid valve or other valve body, and is configured to directly control the flow direction of the refrigerant between the second reversing valve and the first flow path A1, so as to prevent the refrigerant in the first flow path A1 from flowing to the second switching device 22.

Referring to fig. 3, in the reheat dehumidification or defrosting mode, the first indoor heat exchanger 31 corresponds to an evaporator, and the second indoor heat exchanger 32 corresponds to a condenser. The first switching device 21 conducts the first exhaust port 11 and the first end of the outdoor heat exchanger 30 while conducting the first end of the first indoor heat exchanger 31 and the suction port 13; the second switching device 22 turns on the second exhaust port 12 and the first end of the second indoor heat exchanger 32. One air flow discharged from the compressor is discharged through the first exhaust port 11, flows through the outdoor heat exchanger 30 to exchange heat and flows to the second end of the first indoor heat exchanger 31, the other air flow is discharged through the second exhaust port 12, flows through the second indoor heat exchanger 32 to exchange heat and also flows to the second end of the first indoor heat exchanger 31, flows through the first indoor heat exchanger 31 after being combined, flows back to the air suction port 13 of the compressor from the first switching device 21 after exchanging heat, and is circulated for the next refrigerant. It can be appreciated that in this embodiment, the first indoor heat exchanger 31 plays a role in moisture absorption, the second indoor heat exchanger 32 plays a role in heating, and heating is continued, so that when moisture absorption or defrosting is performed, indoor temperature fluctuation is reduced, and human comfort is improved. Meanwhile, since the two exhaust streams of the compressor are mutually independent, the first indoor heat exchanger 31 and the second indoor heat exchanger 32 can have different refrigerant pressures, and the air conditioning system can adjust the refrigerant pressure ratio of the two indoor heat exchangers according to the loads of the two indoor heat exchangers, so that the energy efficiency of the air conditioning system is higher.

In practical application, the first indoor heat exchanger 31 can be arranged on the windward side, the second indoor heat exchanger 32 is arranged on the leeward side, and the air flow cooled and dehumidified by the first indoor heat exchanger 31 can be heated by the second heat exchanger, so that the effect of no fluctuation of defrosting and dehumidifying temperature is achieved, and the purpose of constant-temperature dehumidification and frost removal is achieved.

In a preferred embodiment, a second flow path A2 is formed between the second reversing valve and the first end of the second indoor heat exchanger 32, and the second flow path A2 is communicated with the first flow path A1, and a first control valve 51 is provided. The first control valve 51 may adjust the refrigerant pressure ratio between the first flow path A1 and the second flow path A2 according to the working load conditions of the first indoor heat exchanger 31 and the second indoor heat exchanger 32, so that the air conditioning system achieves a better working condition, and the energy efficiency of the air conditioning system is improved. The specific type of the first control valve 51 is not limited, and may be, for example, a solenoid valve, a proportional valve, a throttle valve, etc., and in an embodiment, the first control valve 51 is an electronic expansion valve.

Referring to fig. 4, the air conditioning system may also implement a hybrid mode. Specifically, taking the operation of the air conditioning system under reheat dehumidification as an example, the outdoor heat exchanger 30 at this time operates as a condenser. In a group of indoor heat exchange units, the flow rate of the first indoor heat exchanger 31 serving as an evaporator is controlled to be zero, and the second indoor heat exchanger 32 serves as a condenser, and the indoor heat exchange units realize a heating function. And the other group of indoor units can control the first indoor heat exchanger 31 to work as an evaporator, and meanwhile, the flow of the second indoor heat exchanger 32 is zero, and the indoor heat exchange units realize a refrigerating function. In still another group of indoor units, the first indoor heat exchanger 31 may be controlled to operate as an evaporator and the second indoor heat exchanger 32 may be controlled to operate as a condenser, the indoor heat exchange units implementing a reheat dehumidification function. The air conditioning system can realize different working modes of different indoor heat exchange units, thereby realizing the integral mixed mode of the air conditioning system. It will be appreciated that the above-described hybrid mode is not limited to the outdoor heat exchanger 30 as a condenser, and the outdoor heat exchanger 30 may also be an evaporator, and the operation mode of each indoor heat exchange unit may also be a cooling or heating mode as needed, thereby realizing the hybrid mode of the air conditioning system.

The flow control manners of the first indoor heat exchanger 31 and the second indoor heat exchanger 32 may be various, in this embodiment, a first indoor throttling element 53 is disposed between the second end of the first indoor heat exchanger 31 and the second end of the outdoor heat exchanger 30, and a second indoor throttling element 54 is disposed between the second end of the second indoor heat exchanger 32 and the second end of the outdoor heat exchanger 30. The first indoor throttling element 53 and the second indoor throttling element 54 are preferably electronic expansion valves, so that in this embodiment, the working modes of the indoor heat exchange units can be controlled by controlling the refrigerant flow rates of the first indoor heat exchanger 31 and the second indoor heat exchanger 32 in the indoor heat exchange units by controlling the first indoor throttling element 53 and the second indoor throttling element 54.

Referring to fig. 5, in another embodiment, the first switching device 21 is a reversing valve, and the second switching device 22 is a solenoid valve set. Optionally, the first switching device 21 is a four-way reversing valve. Specifically, the second switching device 22 includes a first electromagnetic valve 61 and a second electromagnetic valve 62 that are disposed in parallel, one end of the first electromagnetic valve 61 is connected to the second exhaust port 12, the other end is connected to the first flow path A1, one end of the second electromagnetic valve 62 is connected to the second exhaust port 12, and the other end is connected to the first end of the second indoor heat exchanger 32.

Referring to fig. 5, in the heating mode, the outdoor heat exchanger 30 corresponds to an evaporator, and the first indoor heat exchanger 31 and the second indoor heat exchanger 32 correspond to condensers. The first switching device 21 conducts the first exhaust port 11 and the first end of the first indoor heat exchanger 31 while conducting the first end of the outdoor heat exchanger 30 and the suction port 13; the first solenoid valve 61 is closed and the second solenoid valve 62 is opened. One air flow discharged from the compressor flows into the first indoor heat exchanger 31 to exchange heat through the discharge port of the first exhaust port 11, the other air flow flows into the second indoor heat exchanger 32 to exchange heat through the discharge port of the second exhaust port, and then the two air flows are converged in the main path B to flow through the outdoor heat exchanger 30 to exchange heat, and the air flows back to the air suction port 13 of the compressor from the first switching device 21 through the first flow path A1 to perform the next refrigerant circulation, so that the indoor air is quickly heated. In this embodiment, the first heat exchanger and the second heat exchanger may have different refrigerant pressures, so that step heating may be implemented, and energy efficiency of the air conditioning system may be higher.

The outdoor heat exchanger 30 corresponds to a condenser, and the first indoor heat exchanger 31 corresponds to an evaporator, which is not shown in the drawing in the cooling mode. The first switching device 21 conducts the first exhaust port 11 and the first end of the outdoor heat exchanger 30 while conducting the first end of the first indoor heat exchanger 31 and the suction port 13; the first solenoid valve 61 is opened and the second solenoid valve 62 is closed. The air flow discharged from the compressor is discharged through the first exhaust port 11 and flows into the first flow path A1, the other air flow is discharged through the second exhaust port 12, flows into the first flow path A1 through the first electromagnetic valve 61, is mixed, exchanges heat through the outdoor heat exchanger 30, and flows back into the air suction port 13 of the compressor through the first indoor heat exchanger 31 after exchanging heat through the first switching device 21, so that the next refrigerant cycle is performed, and the indoor air rapid cooling function is realized.

Not shown in the drawings in the reheat dehumidification or defrosting mode, the first indoor heat exchanger 31 corresponds to an evaporator, and the second indoor heat exchanger 32 corresponds to a condenser. The first switching device 21 conducts the first exhaust port 11 and the first end of the outdoor heat exchanger 30 while conducting the first end of the first indoor heat exchanger 31 and the suction port 13; the second solenoid valve 62 is opened. One air flow discharged from the compressor is discharged through the first exhaust port 11, flows through the outdoor heat exchanger 30 to exchange heat and flows to the second end of the first indoor heat exchanger 31, the other air flow is discharged through the second exhaust port 12, flows through the second indoor heat exchanger 32 to exchange heat and also flows to the second end of the first indoor heat exchanger 31, flows through the first indoor heat exchanger 31 after being combined, flows back to the air suction port 13 of the compressor from the first switching device 21 after exchanging heat, and is circulated for the next refrigerant. It can be appreciated that in this embodiment, the first indoor heat exchanger 31 plays a role in moisture absorption, the second indoor heat exchanger 32 plays a role in heating, and heating is continued, so that when moisture absorption or defrosting is performed, indoor temperature fluctuation is reduced, and human comfort is improved. Meanwhile, since the two exhaust streams of the compressor are mutually independent, the first indoor heat exchanger 31 and the second indoor heat exchanger 32 can have different refrigerant pressures, and the air conditioning system can adjust the refrigerant pressure ratio of the two indoor heat exchangers according to the loads of the two indoor heat exchangers, so that the energy efficiency of the air conditioning system is higher.

In a preferred embodiment, a second control valve 52 is provided between the first solenoid valve 61 and the first flow path A1. In the reheat dehumidification mode, the first solenoid valve 61 and the second solenoid valve 62 are both opened, and the second control valve 52 can adjust the refrigerant pressure ratio between the first flow path A1 and the second flow path A2 according to the working load conditions of the first indoor heat exchanger 31 and the second indoor heat exchanger 32, so that the air conditioning system achieves a better working condition, and the energy efficiency of the air conditioning system is improved. The specific type of the second control valve 52 is not limited, and may be, for example, a solenoid valve, a proportional valve, a throttle valve, etc., and in one embodiment, the second control valve 52 is an electronic expansion valve.

The air conditioning system described above may also implement a hybrid mode. Specifically, taking the operation of the air conditioning system under reheat dehumidification as an example, the outdoor heat exchanger 30 at this time operates as a condenser. In a group of indoor heat exchange units, the flow rate of the first indoor heat exchanger 31 serving as an evaporator is controlled to be zero, and the second indoor heat exchanger 32 serves as a condenser, and the indoor heat exchange units realize a heating function. And the other group of indoor units can control the first indoor heat exchanger 31 to work as an evaporator, and meanwhile, the flow of the second indoor heat exchanger 32 is zero, and the indoor heat exchange units realize a refrigerating function. In still another group of indoor units, the first indoor heat exchanger 31 may be controlled to operate as an evaporator and the second indoor heat exchanger 32 may be controlled to operate as a condenser, the indoor heat exchange units implementing a reheat dehumidification function. The air conditioning system can realize different working modes of different indoor heat exchange units, thereby realizing the integral mixed mode of the air conditioning system. It will be appreciated that the above-described hybrid mode is not limited to the outdoor heat exchanger 30 as a condenser, and the outdoor heat exchanger 30 may also be an evaporator, and the operation mode of each indoor heat exchange unit may also be a cooling or heating mode as needed, thereby realizing the hybrid mode of the air conditioning system.

On the basis of the above embodiment, please continue to refer to fig. 1 to 5, at least one of the plurality of sets of indoor heat exchange units includes an indoor heat exchanger, the indoor heat exchanger is a third indoor heat exchanger 33, the air conditioning system further includes a first branch D1 and a second branch D2, the first end of the third indoor heat exchanger 33 is connected to the first switching device 21 through the first branch D1, the second end of the third indoor heat exchanger 33 is connected to the second switching device 22 through the second branch D2, the second end of the third indoor heat exchanger 33 is connected to the second end of the outdoor heat exchanger 30, a fifth electromagnetic valve 65 is disposed on the first branch D1, and a sixth electromagnetic valve 66 is disposed on the second branch D2. In this embodiment, the indoor heat exchange unit may implement a cooling or heating function.

Referring to fig. 1, 3 and 5, in the heating mode or the reheat dehumidification mode of the air conditioning system, the fifth electromagnetic valve 65 is closed, the sixth electromagnetic valve 66 is opened, the air flow discharged from the second air outlet 12 flows to the second branch D2 through the second switching device 22, flows to the main circuit B after exchanging heat with the third indoor heat exchanger 33, flows back to the air inlet 13 of the compressor through the first switching device 21 after exchanging heat with the outdoor heat exchanger 30. At this time, the fifth electromagnetic valve 65 is opened, the sixth electromagnetic valve 66 is closed, the third indoor heat exchanger 33 can realize the cooling mode, and the air conditioning system is switched to the mixing mode. Referring to fig. 2, in the cooling mode of the air conditioning system, the fifth electromagnetic valve 65 is closed, the sixth electromagnetic valve 66 is opened, and the air flow discharged from the first air outlet 11 flows through the outdoor heat exchanger 30 to exchange heat, flows through the third indoor heat exchanger 33 to exchange heat, and flows through the second branch D2 to return to the air inlet 13 of the compressor through the second switching device 22. At this time, the fifth electromagnetic valve 65 is opened, the sixth electromagnetic valve 66 is closed, the heating mode of the third indoor heat exchanger 33 can be realized, and the air conditioning system is switched to the hybrid mode.

The air conditioning system further comprises an air supplementing module, and the air supplementing module is connected with the compressor. By arranging the air supplementing module to supplement air and increase enthalpy of the compressor, it can be understood that the air supplementing and increase enthalpy is used under the condition of low-temperature heating, namely by introducing a medium-pressure air flow during low-temperature heating, the air suction of the compressor is improved, the efficiency of the compressor is improved, the system capacity during low-temperature heating is further improved, and the low-temperature heating quantity is improved. Specifically, referring to fig. 1 to 6, the second end of the first indoor heat exchanger 31 and the second end of the second indoor heat exchanger 32 are respectively connected to the second end of the outdoor heat exchanger 30 through a main path B, and an air supplementing module is disposed on the main path B and is connected to the air suction port 13 through an air supplementing pipeline C. In this embodiment, the air make-up module may be implemented in the form of an economizer 71 or in the form of a flash tank to achieve air make-up and enthalpy increase for the high temperature gas during heating or defrosting.

In a preferred embodiment, referring to fig. 3, the air supplementing module includes a supercooling throttle valve 72 and an economizer 71, the economizer 71 is disposed on the main path B, a bypass line is disposed on the main path B, the bypass line communicates the main path B with the economizer 71, the supercooling throttle valve 72 is disposed on the bypass line, and the economizer 71 is connected with the air intake port 13 through the air supplementing line C. In the thermal dehumidification mode, the heating load is smaller, the refrigeration load is larger, at the moment, the supercooling throttle valve 72 is opened, the economizer 71 operates, the economizer 71 comprises two groups of heat exchange pipelines, a part of the refrigerant flowing out of the outdoor heat exchanger 30 is throttled by the supercooling throttle valve 72 and is further cooled in a heat expansion mode, the temperature of the other part of the refrigerant is reduced, the other part of the refrigerant is supercooled, the stabilized supercooled liquid enters the first indoor heat exchanger 31 for refrigeration, and therefore the supercooling degree of the refrigerant entering the first indoor heat exchanger 31 is increased, and the refrigeration load is reduced. Meanwhile, the gaseous refrigerant reenters the compressor through the air supplementing pipeline C to be continuously compressed and enters the circulation, so that the capacity and the efficiency of the system are improved.

Preferably, referring to fig. 6, the compressor includes a first compression cylinder 101 and a second compression cylinder 102 that are independent from each other, the first compression cylinder 101 is communicated with the first exhaust port 11, the second compression cylinder 102 is communicated with the second exhaust port 12, the first compression cylinder 101 and the second compression cylinder 102 are both communicated with the air suction port 13, the air supplementing pipeline C is communicated with the second compression cylinder 102 through an air supplementing branch pipe C1, a third electromagnetic valve 63 is disposed on the air supplementing branch pipe C1, a fourth electromagnetic valve 64 is further disposed on the air supplementing pipeline C, and the fourth electromagnetic valve 64 is located between an air inlet end of the air supplementing branch pipe C1 and the air suction port 13. In this way, when only the supercooling degree needs to be increased, the fourth solenoid valve 64 may be opened, and the third solenoid valve 63 may be closed. And when the air supplementing enthalpy is needed, the third electromagnetic valve 63 can be opened to close the fourth electromagnetic valve 64, so that the air supplementing module directly supplements air to the second compression cylinder 102 through the air supplementing branch pipe C1, the energy efficiency of the compressor is improved, and the low-temperature heating capacity of the air conditioning system is improved.

In an embodiment, referring to fig. 7, the compressor may also be a dual-cylinder dual-suction dual-row compressor, the suction port 13 includes a first sub-suction port 131 and a second sub-suction port 132, the first switching device 21 is a first reversing valve, the second switching device 22 is a second reversing valve, a first pipeline E1 is formed between the first reversing valve and the first sub-suction port 131, a second pipeline E2 is formed between the second reversing valve and the second sub-suction port 132, and the first pipeline E1 is communicated with the second pipeline E2. In this embodiment, the first sub-air intake port 131 and the second sub-air intake port 132 are independently air-returned, the first air exhaust port 11 and the second air exhaust port 12 are independently air-exhausted, and the two compression cylinders are utilized to work simultaneously, so that the air intake capacity and the air exhaust capacity of the compressor are increased, the compression capacity of the compressor 10 is improved, and the energy efficiency of the air conditioning system can be improved.

As shown in fig. 7, in the heating mode, the first switching device 21 turns on the first exhaust port 11 and the first indoor heat exchanger 31 while turning on the outdoor heat exchanger 30 and the first pipe E1; the second switching device 22 turns on the second exhaust port 12 and the second indoor heat exchanger 32. The refrigerant discharged from the first exhaust port 11 exchanges heat through the first indoor heat exchanger 31, the refrigerant discharged from the second exhaust port 12 exchanges heat through the second indoor heat exchanger 32, and the two streams flow through the outdoor heat exchanger 30 through the main path B after converging, flow into the first pipeline E1 through the first switching device 21, and flow back to the first sub-suction port 131 and the second sub-suction port 132 through the first pipeline E1 and the second pipeline E2. The first switching device 21 is not shown in the drawing in the cooling mode, and is configured to conduct the first exhaust port 11 and the outdoor heat exchanger 30, and conduct the first indoor heat exchanger 31 and the first pipe E1, and the second switching device 22 is configured to conduct the second exhaust port 12 and the outdoor heat exchanger 30, and conduct the second indoor heat exchanger 32 and the second pipe E2. The refrigerant discharged from the first exhaust port 11 exchanges heat with the outdoor heat exchanger 30, flows through the first indoor heat exchanger 31 to exchange heat, and flows back to the first sub-suction port 131 through the first switching device 21, and the refrigerant discharged from the second exhaust port 12 exchanges heat with the outdoor heat exchanger 30, flows through the second indoor heat exchanger 32 to exchange heat, and flows back to the second sub-suction port 132 through the second switching device 22. The first switching device 21 is not shown in the drawings in the reheat dehumidification mode, and is used for conducting the first exhaust port 11 and the outdoor heat exchanger 30, simultaneously conducting the first indoor heat exchanger 31 and the first pipeline E1, and the second switching device 22 is used for conducting the second exhaust port 12 and the second indoor heat exchanger 32. The refrigerant discharged from the first exhaust port 11 flows to the second end of the first indoor heat exchanger 31 after exchanging heat with the outdoor heat exchanger 30, and the other refrigerant flows to the second end of the first indoor heat exchanger 31 after exchanging heat with the second indoor heat exchanger 32, and the two flows are converged and then flow through the first indoor heat exchanger 31 to exchange heat, and flow back to the first sub-air suction port 131 and the second sub-air suction port 132 through the first switching device 21.

On the basis of the above embodiment, the second pipe E2 is provided with a second one-way valve 42, and the second one-way valve 42 is set to be in one-way conduction from the second reversing valve to the second sub-air suction port 132. So as to prevent the refrigerant from flowing in series in the heating or reheating and dehumidifying mode. It can be understood that a second connection valve may be directly disposed on the second pipeline E2, where the second connection valve may be an electromagnetic valve or other valve body, so as to control the flow direction of the refrigerant in the second pipeline E2, and prevent the refrigerant from flowing in series in the heating or reheating and dehumidifying modes.

In a preferred embodiment, the air conditioning system further includes a gas supplementing module, and the gas supplementing module is configured to supplement gas and increase enthalpy for the compressor, so that it can be understood that the gas supplementing and enthalpy increasing module is used in a low-temperature heating situation, that is, by introducing a medium-pressure air flow during low-temperature heating, the gas suction of the compressor is improved, the efficiency of the compressor is improved, the system capacity during low-temperature heating is further improved, and the low-temperature heating quantity is improved. Specifically, referring to fig. 7, the second end of the first indoor heat exchanger 31 and the second end of the second indoor heat exchanger 32 are connected to the second end of the outdoor heat exchanger 30 through a main path B, and an air supplementing module is disposed on the main path B and connected to the second pipeline E2 through an air supplementing pipeline C. In this embodiment, the air make-up module may be implemented in the form of an economizer 71 or in the form of a flash tank to achieve air make-up and enthalpy increase for the high temperature gas during heating or defrosting.

In a preferred embodiment, referring to fig. 7, the air supplementing module includes a supercooling throttle valve 72 and an economizer 71, the economizer 71 is disposed on the main line B, a bypass line is disposed on the main line B, the bypass line communicates the main line B with the economizer 71, the supercooling throttle valve 72 is disposed on the bypass line, and the economizer 71 is connected with the second line E2 through the air supplementing line C. In the thermal dehumidification mode, the heating load is smaller, the refrigeration load is larger, at the moment, the supercooling throttle valve 72 is opened, the economizer 71 operates, the economizer 71 comprises two groups of heat exchange pipelines, a part of the refrigerant flowing out of the outdoor heat exchanger 30 is throttled by the supercooling throttle valve 72 and is further cooled in a heat expansion mode, the temperature of the other part of the refrigerant is reduced, the other part of the refrigerant is supercooled, the stabilized supercooled liquid enters the first indoor heat exchanger 31 for refrigeration, and therefore the supercooling degree of the refrigerant entering the first indoor heat exchanger 31 is increased, and the refrigeration load is reduced. Simultaneously, the gaseous refrigerant enters the compressor through the first sub-air suction port 131 and the second sub-air suction port 132 again through the air supplementing pipeline C to be continuously compressed, and enters the circulation, so that the capacity and the efficiency of the system are improved.

Preferably, with continued reference to fig. 7, a seventh electromagnetic valve 67 is disposed between the first pipeline E1 and the second pipeline E2. In this way, when only the supercooling degree needs to be increased, the seventh electromagnetic valve 67 may be opened. And when the air supplementing and enthalpy increasing are needed, the seventh electromagnetic valve 67 is closed, so that the air supplementing module directly supplements air to the second compression cylinder 102 through the second pipeline E2, the energy efficiency of the compressor is improved, and the low-temperature heating capacity of the air conditioning system is improved.

The foregoing description is only of the preferred embodiments of the present utility model and is not intended to limit the scope of the utility model, and all equivalent structural changes made by the description of the present utility model and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the utility model.

Claims

1. An air conditioning system is characterized by comprising a compressor, a first switching device, a second switching device, an outdoor heat exchanger and a plurality of groups of indoor heat exchange units, wherein at least one group of the indoor heat exchange units comprises a first indoor heat exchanger and a second indoor heat exchanger;

2. The air conditioning system of claim 1, wherein the first switching device is a first reversing valve.

3. The air conditioning system of claim 2, wherein said second switching means is a second reversing valve, said second reversing valve further connected to said suction port.

4. The air conditioning system according to claim 3, wherein a first check valve is provided between the second reversing valve and the first flow path, the first check valve being provided to be in one-way conduction from the second reversing valve to the first flow path; or alternatively, the process may be performed,

5. An air conditioning system as set forth in claim 3 wherein a second flow path is formed between said second reversing valve and the first end of said second indoor heat exchanger, said second flow path being in communication with said first flow path and being provided with a first control valve.

6. The air conditioning system according to claim 2, wherein the second switching device includes a first solenoid valve and a second solenoid valve which are disposed in parallel, one end of the first solenoid valve is connected to the second air outlet, the other end is connected to the first flow path, one end of the second solenoid valve is connected to the second air outlet, and the other end is connected to the first end of the second indoor heat exchanger.

7. The air conditioning system as set forth in claim 6, wherein a second control valve is provided between said first solenoid valve and said first flow path.

8. The air conditioning system according to any of claims 1 to 7, wherein a first indoor restriction is provided between the second end of the first indoor heat exchanger and the second end of the outdoor heat exchanger, and a second indoor restriction is provided between the second end of the second indoor heat exchanger and the second end of the outdoor heat exchanger.

9. The air conditioning system according to any of claims 1 to 7, wherein the second end of the first indoor heat exchanger and the second end of the second indoor heat exchanger are connected to the second end of the outdoor heat exchanger through a main line, respectively, on which an air supplementing module is provided, and the air supplementing module is connected to the air intake port through an air supplementing line.

10. The air conditioning system as set forth in claim 9, wherein said air-supplementing module includes a supercooling throttle and an economizer, said economizer being provided in said main passage, said main passage being provided with a bypass passage communicating said main passage with said economizer, said supercooling throttle being provided in said bypass passage, said economizer being connected to said air-intake port through said air-supplementing passage.

11. The air conditioning system of claim 10, wherein the compressor includes a first compression cylinder and a second compression cylinder that are independent of each other, the first compression cylinder is in communication with the first exhaust port, the second compression cylinder is in communication with the second exhaust port, the first compression cylinder and the second compression cylinder are both in communication with the intake port, the air supply line is in communication with the second compression cylinder through an air supply branch pipe, a third solenoid valve is provided on the air supply branch pipe, a fourth solenoid valve is further provided on the air supply line, and the fourth solenoid valve is located between an intake end of the air supply branch pipe and the intake port.

12. The air conditioning system according to any of claims 1 to 7, wherein the first indoor heat exchanger is provided on a windward side and the second indoor heat exchanger is provided on a leeward side.

13. The air conditioning system according to any of claims 1 to 7, wherein at least one of the plurality of sets of indoor heat exchange units includes a third indoor heat exchanger, the air conditioning system further includes a first branch and a second branch, a first end of the third indoor heat exchanger is connected to the first switching device through the first branch, a second end of the third indoor heat exchanger is connected to the second end of the outdoor heat exchanger through the second branch, a fifth electromagnetic valve is provided on the first branch, and a sixth electromagnetic valve is provided on the second branch.

14. The air conditioning system according to any one of claims 3 to 5, wherein the suction port includes a first sub-suction port and a second sub-suction port, a first pipe is formed between the first reversing valve and the first sub-suction port, a second pipe is formed between the second reversing valve and the second sub-suction port, and communication is made between the first pipe and the second pipe.

15. The air conditioning system according to claim 14, wherein a second check valve is provided on the second pipe, and the second check valve is configured to be unidirectional-connected from the second reversing valve to the second sub-suction port; or alternatively, the process may be performed,

and a second connecting valve is arranged on the second pipeline.

16. The air conditioning system of claim 14, wherein the second end of the first indoor heat exchanger and the second end of the second indoor heat exchanger are connected to the second end of the outdoor heat exchanger through a main line, respectively, and an air-supplementing module is disposed on the main line and connected to the second line through an air-supplementing line.

17. The air conditioning system as set forth in claim 16, wherein said air make-up module includes a subcooling throttle and an economizer, said economizer being disposed on said main circuit, said main circuit being provided with a bypass line communicating said main circuit with said economizer, said subcooling throttle being disposed on said bypass line, said economizer being connected to said second line through said air make-up line.

18. The air conditioning system according to claim 17, wherein a seventh solenoid valve is disposed between the first and second lines.