Air conditioning system

Abstract

An air conditioning system (1000), comprising an outdoor unit (100), at least one indoor unit (300), a refrigerant cut-off component (200), and a controller (600). The at least one indoor unit (300) is connected to the outdoor unit (100). The refrigerant cut-off component (200) is disposed between the outdoor unit (100) and the at least one indoor unit (300). The refrigerant cut-off component (200) comprises a first throttling component (210) and a second throttling component (220). The indoor unit (300) comprises an indoor electronic expansion valve (330). The controller (600) is configured to: obtain the temperature change rate of an air-conditioned room where the indoor unit (300) is located, and the degree of deviation of the temperature in the air-conditioned room from a target temperature; determine, on the basis of the temperature change rate and the degree of deviation, a target refrigerant temperature matching a current load of the air-conditioned room; and determine the opening degrees of the indoor electronic expansion valve (330), the first throttling component (210) and the second throttling component (200) on the basis of at least one of the target refrigerant temperature, a preset target superheat degree or a preset target subcooling degree.

Description

Air conditioning system

[0001] This application claims priority to Chinese Patent Application No. 202410521901.9, filed on April 28, 2024, Chinese Patent Application No. 202410521583.6, filed on April 28, 2024, and Chinese Patent Application No. 202420772038.X, filed on April 15, 2024, the contents of which are incorporated herein by reference in their entirety. TECHNICAL FIELD

[0002] The present disclosure relates to the field of air conditioning technology, and in particular, to an air conditioning system. BACKGROUND

[0003] The air conditioning system includes a multi-split air conditioning system, which can adjust the cooling and heating of multiple rooms or areas, and the temperature of different rooms or areas can be independently controlled or combined control. The multi-split air conditioning system is suitable for buildings that require independent temperature control, including multiple rooms or areas, such as office buildings, schools, hotels, and large residences, etc.

[0004] SUMMARY

[0005] The present disclosure aims to at least solve one of the technical problems existing in the related art. To this end, the present disclosure provides an air conditioning system, which aims to solve the problem of over-regulation of indoor units of a multi-split air conditioning system under small load conditions.

[0006] In one aspect, an air conditioning system is provided, which includes an outdoor unit. The outdoor unit includes a compressor and an outdoor heat exchanger. The compressor. The first end of the outdoor heat exchanger is connected to the compressor.

[0007] The air conditioning system further includes at least one indoor unit connected to the outdoor unit, and any one of the at least one indoor unit includes an indoor heat exchanger and an indoor electronic expansion valve. The first end of the indoor heat exchanger is connected to the second end of the outdoor heat exchanger, and the second end of the indoor heat exchanger is connected to the compressor. The indoor electronic expansion valve is arranged at the first end of the indoor heat exchanger and can adjust the flow of refrigerant flowing through the indoor heat exchanger.

[0008] The air conditioning system further includes a refrigerant cutoff component arranged between the outdoor unit and the at least one indoor unit. The refrigerant cutoff component includes a first throttling component and a second throttling component. The first throttling component is arranged between the indoor electronic expansion valve and the second end of the outdoor heat exchanger. The second throttling component is arranged between the second end of the indoor heat exchanger and the compressor.

[0009] The air conditioning system further comprises a controller configured to: acquire a temperature change rate of an air conditioning room where any one of the indoor units is located, and a deviation degree of a temperature of the air conditioning room from a target temperature; determine a target refrigerant temperature matched with a current load of the air conditioning room according to the temperature change rate and the deviation degree; and determine the opening degrees of the indoor electronic expansion valve, the first throttling component and the second throttling component according to at least one of the target refrigerant temperature, a preset target superheat degree or a preset target subcooling degree.

[0010] The air conditioning system according to some embodiments of the present disclosure improves the accuracy of the adjustment of the refrigerant flow and temperature in the indoor unit by arranging the refrigerant cutting component between the indoor unit and the outdoor unit, thereby ensuring that the indoor temperature and humidity can be maintained within a preset range, and solving the over-adjustment problem of the indoor unit under a small load condition.

[0011] In another aspect, an air conditioning system is provided, comprising an outdoor unit, an air-cooled assembly, a water module, a first gas pipe, a liquid pipe, a second gas pipe, a first branch, a second branch, a first regulating valve and a second regulating valve.

[0012] The outdoor unit comprises a compressor and an outdoor heat exchanger. The compressor. A first end of the outdoor heat exchanger is connected to the compressor. The air-cooled assembly is connected to the outdoor unit.

[0013] The air-cooled assembly comprises an air-cooled assembly heat exchanger, which comprises a first sub-air-cooled assembly heat exchanger and a second sub-air-cooled assembly heat exchanger. A first end of the first sub-air-cooled assembly heat exchanger is connected to the compressor, and a second end of the first sub-air-cooled assembly heat exchanger is connected to a second end of the outdoor heat exchanger. A first end of the second sub-air-cooled assembly heat exchanger is connected to the compressor, and a second end of the second sub-air-cooled assembly heat exchanger is connected to the second end of the outdoor heat exchanger.

[0014] The water module is connected to the outdoor unit. The water module comprises a water module heat exchanger.

[0015] A first end of the first gas pipe is connected to the first end of the first sub-air-cooled assembly heat exchanger, a second end of the first gas pipe is connected to the compressor, and the first gas pipe can transport gaseous refrigerant.

[0016] A first end of the liquid pipe is connected to the second end of the first sub-air-cooled assembly heat exchanger and the second end of the second sub-air-cooled assembly heat exchanger, and a second end of the liquid pipe is connected to the second end of the outdoor heat exchanger.

[0017] A first end of the second gas pipe is connected to the first end of the second sub-air-cooled assembly heat exchanger, and a second end of the second gas pipe is connected to the compressor.

[0018] The outdoor unit and the air-cooled assembly are connected through the first gas pipe, the liquid pipe and the second gas pipe.

[0019] The first end of the first branch is communicated with the second gas pipe, and the second end of the first branch is communicated with the first end of the water module heat exchanger.

[0020] The first end of the second branch is communicated with the second end of the water module heat exchanger, and the second end of the second branch is communicated with the second end of the outdoor heat exchanger.

[0021] The water module is connected with the outdoor unit through the first branch and the second branch. The first regulating valve is arranged in the first gas pipe, and the second regulating valve is arranged in the second gas pipe.

[0022] The air conditioning system further comprises a controller configured to: under the condition that the water module is in heating operation and the discharge pressure of the compressor is outside a preset discharge pressure range, adjust the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve from a preset opening degree until the discharge pressure of the compressor is within the preset discharge pressure range.

[0023] According to some embodiments of the present disclosure, an air conditioning system, the air-cooled assembly and the outdoor unit in the air conditioning system are connected through a first gas pipe, a second gas pipe and a liquid pipe. The air conditioning system adjusts the flow of refrigerant entering the water module by arranging a first gas pipe regulating valve on the first gas pipe, arranging a second gas pipe regulating valve on the second gas pipe, and adjusting the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve to make part of the refrigerant enter the air-cooled assembly. In this way, the air conditioning system avoids excessive or insufficient refrigerant entering the water module, so that the temperature of the water module can be kept within a preset range, and the discharge pressure of the compressor can be kept within a preset discharge pressure range, thereby ensuring stable operation of the air conditioning system.

[0024] In another aspect, an air conditioning system is provided, comprising an outdoor unit, an air-cooled assembly, a first gas pipe, a liquid pipe and a water module.

[0025] The outdoor unit comprises a compressor and an outdoor heat exchanger. The air-cooled assembly is connected with the outdoor unit, and the air-cooled assembly comprises an air-cooled assembly heat exchanger. The outdoor unit and the air-cooled assembly are connected through the first gas pipe and the liquid pipe. The water module is connected with the outdoor unit.

[0026] The first end of the first gas pipe is communicated with the first end of the air-cooled assembly heat exchanger, the second end of the first gas pipe is communicated with the compressor, and the first gas pipe can transport gaseous refrigerant.

[0027] The first end of the liquid pipe is connected to the second end of the air-cooled component heat exchanger, the second end of the liquid pipe is connected to the second end of the outdoor heat exchanger, and the liquid pipe is capable of transporting liquid refrigerant.

[0028] The air conditioning system further comprises a first gas pipe regulating valve and a controller. The first gas pipe regulating valve is arranged in the first gas pipe. The controller is configured to adjust the opening degree of the first gas pipe regulating valve from a preset opening degree until the discharge pressure of the compressor is within the preset discharge pressure range, under the condition that the water module independent heating operation is satisfied and the discharge pressure of the compressor is outside the preset discharge pressure range.

[0029] According to some embodiments of the present disclosure, an air conditioning system is provided. The air-cooled component and the outdoor unit in the air conditioning system are connected through a first gas pipe and a liquid pipe. The air conditioning system adjusts the flow of refrigerant entering the water module by arranging a first gas pipe regulating valve on the first gas pipe and adjusting the opening degree of the first gas pipe regulating valve, so that part of the refrigerant enters the air-cooled component. In this way, the air conditioning system avoids excessive or insufficient refrigerant entering the water module, so that the temperature of the water module can be maintained within a preset range, and the discharge pressure of the compressor can be maintained within a preset discharge pressure range, thereby ensuring stable operation of the air conditioning system.

[0030] In another aspect, an air conditioning system is provided, comprising an outdoor unit and at least one indoor unit.

[0031] The outdoor unit comprises a compressor, an outdoor heat exchanger, and an outdoor throttling component. The compressor. The first end of the outdoor heat exchanger is connected to the compressor. The outdoor throttling component is arranged at the second end of the outdoor heat exchanger and is capable of adjusting the flow of refrigerant flowing through the outdoor unit.

[0032] The at least one indoor unit is connected to the outdoor unit. The outdoor heat exchanger comprises a first sub-heat exchanger and a second sub-heat exchanger. The first port of the first sub-heat exchanger is connected to the outdoor throttling component, and the second port of the first sub-heat exchanger is connected to the outlet of the compressor and the inlet of the compressor. The first port of the second sub-heat exchanger is connected to the outdoor throttling component, and the second port of the second sub-heat exchanger is connected to the outlet of the compressor and the inlet of the compressor.

[0033] The air conditioning system further comprises a first switch, a second switch, a third switch and a fourth switch. The second port of the first sub-heat exchanger is connected to the outlet of the compressor through the first switch. The second port of the second sub-heat exchanger is connected to the outlet of the compressor through the second switch. The second port of the first sub-heat exchanger is connected to the inlet of the compressor through the third switch. The second port of the second sub-heat exchanger is connected to the inlet of the compressor through the fourth switch.

[0034] When defrosting the first sub-heat exchanger, the first switch and the fourth switch are turned on, and the second switch and the third switch are turned off. When defrosting the second sub-heat exchanger, the second switch and the third switch are turned on, and the first switch and the fourth switch are turned off.

[0035] According to the air conditioning system of some embodiments of the present disclosure, by means of four switches arranged in the refrigerant circulation system of the air conditioning system, a part of the high-temperature and high-pressure gaseous refrigerant discharged by the compressor is guided to the outdoor heat exchanger, so as to realize defrosting of the outdoor heat exchanger. In this way, during the defrosting process, the indoor unit can still operate in heating mode, thereby realizing uninterrupted heating of the indoor unit and improving the comfort of the indoor temperature during the defrosting process. BRIEF DESCRIPTION OF DRAWINGS

[0036] Fig. 1 is a structural diagram of an air conditioning system according to some embodiments;

[0037] Fig. 2 is a refrigeration cycle diagram of a refrigerant circulation system of an air conditioning system according to some embodiments;

[0038] Fig. 3 is a heating cycle diagram of a refrigerant circulation system of an air conditioning system according to some embodiments;

[0039] Fig. 4 is an installation diagram of an air conditioning system according to some embodiments;

[0040] Fig. 5 is a curve diagram of the change of indoor temperature in an air conditioning room over time in a refrigeration mode according to some embodiments;

[0041] Fig. 6 is a structural diagram of an indoor unit and a refrigerant cutoff component according to some embodiments;

[0042] Fig. 7 is a curve diagram of the change of indoor temperature in an air conditioning room over time in a heating mode according to some embodiments;

[0043] Fig. 8 is another structural diagram of an indoor unit and a refrigerant cutoff component according to some embodiments;

[0044] Fig. 9 is another structural diagram of an air conditioning system according to some embodiments;

[0045] FIG. 10 is another installation view of an air conditioning system according to some embodiments;

[0046] FIG. 11 is a configuration view of a controller according to some embodiments;

[0047] FIG. 12 is another configuration view of another air conditioning system according to some embodiments;

[0048] FIG. 13 is a refrigeration cycle view of a refrigerant circulation system of another air conditioning system according to some embodiments;

[0049] FIG. 14 is a heating cycle view of a refrigerant circulation system of another air conditioning system according to some embodiments;

[0050] FIG. 15 is another heating cycle view of a refrigerant circulation system of another air conditioning system according to some embodiments;

[0051] FIG. 16 is a configuration view of another air conditioning system according to some embodiments;

[0052] FIG. 17 is a configuration view of another air conditioning system according to some embodiments;

[0053] FIG. 18 is a configuration view of another air conditioning system according to some embodiments;

[0054] FIG. 19 is an installation position view of a controller in another air conditioning system according to some embodiments;

[0055] FIG. 20 is a flowchart of a control method of another air conditioning system according to some embodiments;

[0056] FIG. 21 is a flowchart of a control method of another air conditioning system according to some embodiments;

[0057] FIG. 22 is a flowchart of a control method of another air conditioning system according to some embodiments;

[0058] FIG. 23 is a flowchart of a control method of another air conditioning system according to some embodiments;

[0059] FIG. 24 is a refrigerant circulation system view of yet another air conditioning system according to some embodiments;

[0060] FIG. 25 is a refrigeration cycle view of a refrigerant circulation system of yet another air conditioning system according to some embodiments;

[0061] FIG. 26 is a heating cycle view of a refrigerant circulation system of yet another air conditioning system according to some embodiments;

[0062] FIG. 27 is a defrost cycle view of a first subheat exchanger of yet another air conditioning system according to some embodiments;

[0063] FIG. 28 is a defrost cycle diagram for a second subheat exchanger of yet another air conditioning system, according to some embodiments;

[0064] FIG. 29 is another refrigerant cycle system diagram for yet another air conditioning system, according to some embodiments;

[0065] FIG. 30 is yet another refrigerant cycle system diagram for yet another air conditioning system, according to some embodiments;

[0066] FIG. 31 is a refrigerant cycle system cooling cycle diagram for yet another air conditioning system, according to some embodiments;

[0067] FIG. 32 is a refrigerant cycle system heating cycle diagram for yet another air conditioning system, according to some embodiments;

[0068] FIG. 33 is a refrigerant cycle system first subheat exchanger defrost cycle diagram for yet another air conditioning system, according to some embodiments;

[0069] FIG. 34 is a refrigerant cycle system second subheat exchanger defrost cycle diagram for yet another air conditioning system, according to some embodiments;

[0070] FIG. 35 is yet another refrigerant cycle system diagram for yet another air conditioning system, according to some embodiments. DETAILED DESCRIPTION

[0071] In the following, some embodiments according to the present disclosure will be described in detail with reference to the accompanying drawings, wherein the described embodiments are merely a part of the embodiments of the present disclosure, rather than all the embodiments. Any person skilled in the art can obtain all other embodiments based on the embodiments provided by the present disclosure, and all other embodiments belong to the scope of protection of the present disclosure.

[0072] Unless the context clearly requires otherwise, throughout the description and the claims, the term "comprise," and variations thereof (e.g., "comprises" and "comprising"), will be construed to be inclusive in a manner consistent with the term's plain meaning, namely, "including but not limited to." In describing the disclosure, the terms "one embodiment," "some embodiments," "exemplary embodiments," "example," "specific example," or "some examples" are used to indicate that a particular feature, structure, material, or characteristic is included in at least one embodiment or example of the disclosure. Such terms are not necessarily used consistently in the specification and the claims, and are not necessarily used to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0073] Hereinafter, the terms "first", "second", etc. are used only for the purpose of description, and should not be construed as indicating or implying relative importance or implying that the indicated technical features are limited to the number. Thus, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the embodiments of the disclosure, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0074] In describing some embodiments, "coupled" and "connected," and variations thereof, can be used. The term "connected" should be interpreted broadly, for example, "connected" can be fixedly connected, or detachably connected, or integrated; can be directly connected, or indirectly connected through an intermediate medium. The term "coupled" indicates that two or more components have direct physical contact or electrical contact. The term "coupled" or "communicatively coupled" can also mean that two or more components do not have direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the content herein.

[0075] "A, B, and C at least one of" has the same meaning as "at least one of A, B, or C", and includes the following combinations of A, B, and C: only A, only B, only C, a combination of A and B, a combination of A and C, a combination of B and C, and a combination of A, B, and C.

[0076] "A and / or B" includes the following three combinations: only A, only B, and a combination of A and B.

[0077] The use of “adapted for” or “configured for” herein means open and inclusive language that does not exclude devices adapted for or configured for performing additional tasks or steps.

[0078] As used herein, “about,” “approximately” or “around” includes the recited value and the average value within an acceptable range of deviation from the particular value, as determined by one of ordinary skill in the art taking into account the measurement being discussed and the error associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0079] As used herein, “parallel,” “perpendicular,” “equal” includes the recited condition and conditions that approximate the recited condition, the approximation being within an acceptable range of deviation, as determined by one of ordinary skill in the art taking into account the measurement being discussed and the error associated with the measurement of the particular quantity (i.e., the limitations of the measurement system). For example, “parallel” includes absolute parallel and near parallel, where near parallel can have an acceptable range of deviation of, for example, within 5°; “perpendicular” includes absolute perpendicular and near perpendicular, where near perpendicular can also have an acceptable range of deviation of, for example, within 5°. “Equal” includes absolute equality and near equality, where near equality can have an acceptable range of deviation of, for example, less than or equal to 5% of either of the two quantities being equal.

[0080] The load of an air conditioning system generally refers to the amount of heat or moisture that needs to be removed or provided by the air conditioning system to maintain a constant temperature and humidity environment in a room.

[0081] The load of an air conditioning system can be divided into three types: cooling load, heating load and moisture load. In order to maintain the preset temperature of a room, the amount of cold supplied to the room is called cooling load. Conversely, the amount of heat supplied to the room to compensate for the heat lost by the room is called heating load. The amount of moisture removed or increased by the room to maintain the preset relative humidity in the room is called moisture load.

[0082] In a multi-split air conditioning system, the indoor unit in a small load condition can have an over-regulation phenomenon. Over-regulation refers to the phenomenon that the controlled parameters such as indoor temperature and humidity exceed the set values, which affects the accuracy of the air conditioning system in adjusting the parameters such as indoor temperature and humidity.

[0083] Under small load conditions, the indoor unit is prone to over-adjustment, mainly due to the following two reasons. On the one hand, the control system of the air conditioning system is not sensitive or too slow in response to load changes under small load conditions, that is, the control system has a delay in adjusting the refrigerant flow, so that the indoor unit continues to cool or heat after reaching the preset temperature. On the other hand, the air conditioning system does not fully consider the load matching of each indoor unit during design. For example, in the case where the load of some indoor units is much lower than the preset load, the control system still controls the refrigerant temperature to meet the load demand of the largest space. At this time, the refrigerant temperature of the indoor space with smaller load appears over-adjustment. After over-adjustment, the indoor unit can only adjust the indoor electronic expansion valve to change the refrigerant flow or continuously adjust the indoor fan to change the air circulation to compensate for the impact of over-adjustment of the refrigerant temperature. However, due to the thermal inertia of the indoor environment, the indoor temperature cannot be restored to the preset temperature range in a short time, and the user will feel uncomfortable for a period of time.

[0084] Some embodiments of the present disclosure provide an air conditioning system, which is provided with a refrigerant cutting component between the indoor unit and the outdoor unit. The refrigerant cutting component includes a first throttling component and a second throttling component, the first throttling component is arranged at the first end of the indoor heat exchanger, and the second throttling component is arranged at the second end of the indoor heat exchanger. The first throttling device and the second throttling device of the indoor electronic expansion valve can further adjust the refrigerant flow of the indoor unit. By arranging the first throttling component and the second throttling component, the accuracy of adjusting the refrigerant flow and temperature is improved, so as to ensure that the temperature and humidity in the indoor are within the preset range, and the over-adjustment problem of the indoor unit under small load conditions is solved.

[0085] In addition, the air conditioning system provided by some embodiments of the present disclosure determines the target refrigerant temperature by obtaining the temperature change rate of the indoor space and the degree of deviation from the target temperature, so as to determine the current load matching of the indoor unit according to the target refrigerant temperature, improve the energy utilization efficiency, and improve the comfort of the air conditioning system.

[0086] Some embodiments of the present disclosure provide an air conditioning system, which can be a multi-split air conditioning system.

[0087] In some embodiments, the air conditioning system 1000 includes an outdoor unit 100.

[0088] In some embodiments, the air conditioning system 1000 further includes at least one indoor unit 300, and the outdoor unit 100 is in communication with the at least one indoor unit 300.

[0089] The outdoor unit 100 can perform a heating operation or a cooling operation on the outdoor side to provide the indoor unit 300 with energy for increasing an indoor temperature or energy for decreasing the indoor temperature. The indoor unit 300 performs a cooling operation or a heating operation using the energy for increasing the indoor temperature or the energy for decreasing the indoor temperature generated by the outdoor unit 100.

[0090] In some embodiments, the outdoor unit 100 includes a compressor 1 configured to compress a refrigerant such that a low-pressure refrigerant is compressed to form a high-pressure refrigerant.

[0091] In some embodiments, the outdoor unit 100 further includes an outdoor heat exchanger 6 configured to exchange heat between outdoor air and a refrigerant transferred in the outdoor heat exchanger 6. A first end of the outdoor heat exchanger 6 is in communication with the compressor 1.

[0092] In some embodiments, the indoor unit 300 includes an indoor heat exchanger 340 configured to exchange heat between indoor air and a refrigerant transferred in the indoor heat exchanger 340. A first end of the indoor heat exchanger 340 is in communication with a second end of the outdoor heat exchanger 6, and a second end of the indoor heat exchanger 340 is in communication with the compressor 1.

[0093] The indoor heat exchanger 340 and the outdoor heat exchanger 6 can function as a condenser or an evaporator. In a heating mode, the indoor heat exchanger functions as a condenser, and the outdoor heat exchanger functions as an evaporator. In a cooling mode, the indoor heat exchanger functions as an evaporator, and the outdoor heat exchanger functions as a condenser.

[0094] In some embodiments, the air conditioning system 1000 further includes a throttling component disposed in at least one of the indoor unit 300 or the outdoor unit 100. The throttling component is configured to reduce the pressure of a high-temperature and high-pressure refrigerant liquid from the condenser to a low-pressure refrigerant and cause the low-pressure refrigerant to evaporate and absorb heat in the evaporator.

[0095] In some embodiments, the throttling component includes an outdoor electronic expansion valve 7 disposed in the outdoor unit 100 and connected to the outdoor heat exchanger 6. For example, the outdoor electronic expansion valve 7 is disposed at the second end of the outdoor heat exchanger 6. The outdoor electronic expansion valve 7 is configured to reduce the pressure of the refrigerant in the outdoor unit 100 and expand the refrigerant.

[0096] In some embodiments, the throttling component further includes an indoor electronic expansion valve 330 disposed in the indoor unit 300 and connected to the indoor heat exchanger 340. For example, the indoor electronic expansion valve 330 is disposed at the first end of the indoor heat exchanger 340. The indoor electronic expansion valve 330 is configured to reduce the pressure of the refrigerant in the indoor unit 300 and expand the refrigerant.

[0097] An air conditioning system forms a refrigerant circulation loop by a compressor 1, a condenser, a throttling component, and an evaporator. A refrigerant performs a refrigerant circulation in the refrigerant circulation loop. The refrigerant circulation includes a series of processes involving compression, condensation, expansion, and evaporation, by which a room is cooled or heated.

[0098] From a principle point of view, a low-temperature and low-pressure refrigerant enters the compressor 1, which compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant gas and discharges it. The discharged refrigerant gas flows into the condenser, which condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0099] The throttling component expands the high-temperature and high-pressure liquid-phase refrigerant formed in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the throttling component and returns the refrigerant in a low-temperature and low-pressure state to the compressor 1. The evaporator can achieve a refrigeration effect by exchanging heat with a material to be cooled (e.g., air) using the latent heat of evaporation of the refrigerant. Throughout the refrigerant circulation, the air conditioning system can adjust the temperature of the room.

[0100] In some embodiments, the air conditioning system 1000 further includes a liquid pipe 103. The liquid pipe 103 is disposed between the second end of the outdoor heat exchanger 6 and the first end of the indoor heat exchanger 340. A first end of the liquid pipe 103 communicates with the second end of the outdoor heat exchanger 6, and a second end of the liquid pipe 103 communicates with the first end of the indoor heat exchanger 340.

[0101] In some embodiments, the air conditioning system 1000 further includes a first gas pipe 101. The first gas pipe 101 is disposed between the compressor 1 and the second end of the indoor heat exchanger 340. A first end of the first gas pipe 101 communicates with the compressor 1, and a second end of the first gas pipe 101 communicates with the second end of the indoor heat exchanger 340.

[0102] In some embodiments, the outdoor unit 100 and the indoor unit 300 are in communication through the liquid pipe 103 and the first gas pipe 101 to form a refrigerant circulation loop. The liquid pipe 103 and the first gas pipe 101 are configured to flow refrigerant in the refrigerant circulation loop.

[0103] In some embodiments, the air conditioning system further includes a liquid pipe stop valve 63 disposed in the liquid pipe 103. The liquid pipe stop valve 63 is configured to control the flow and cutoff of the refrigerant in the liquid pipe 103.

[0104] In some embodiments, the air conditioning system further includes a first gas pipe stop valve 61 disposed in the first gas pipe 101. The first gas pipe stop valve 61 is configured to control the flow and cutoff of the refrigerant in the first gas pipe 101.

[0105] The basic structure and functions of the outdoor unit 100 are described below. In an air conditioning system, the number of outdoor units 100 can also be expanded to multiple, and any one of the multiple outdoor units 100 can be connected to multiple indoor units 300, respectively, and the connection between the any one of the multiple outdoor units 100 and the multiple indoor units 300 can be the same as that in FIG. 1. The multiple outdoor units 100 and the connected indoor units 300 can operate in a group.

[0106] In some embodiments, the outdoor unit 100 further comprises an oil separator 2. The oil separator 2 is arranged at the outlet end of the compressor 1. The role of the oil separator 2 in the air conditioning system 1000 is to separate the lubricating oil and the refrigerant.

[0107] It should be noted that the compressor 1 needs lubricating oil to reduce friction and wear to ensure stable operation, and the lubricating oil will mix with the refrigerant when the compressor 1 is working. The oil separator 2 can separate the lubricating oil from the refrigerant by physical separation principle (such as centrifugal force or gravity), and the separated lubricating oil can be recycled and reused, while the refrigerant continues to flow in the refrigerant circulation loop.

[0108] In some embodiments, the outdoor unit 100 further comprises a one-way valve 8, which is arranged in conjunction with the oil separator 2. The one-way valve 8 is arranged at the end of the oil separator 2 away from the compressor 1.

[0109] In some embodiments, the outdoor unit 100 further comprises a gas-liquid separator 3, which is arranged at the suction side of the compressor 1. The gas-liquid separator 3 is configured to separate the gas and liquid in the refrigerant. For example, the gas-liquid separator can achieve gas-liquid separation according to the density difference between the gas and the liquid. When the gaseous refrigerant and the liquid refrigerant are mixed into the gas-liquid separator 3, due to the action of gravity, the liquid refrigerant with higher density will sink, and the gaseous refrigerant with lighter density will rise. In this way, the gas-liquid separator 3 can separate the liquid refrigerant and the gaseous refrigerant.

[0110] In some embodiments, the gas-liquid separator 3 is also configured to store excess refrigerant. It can be understood that the gaseous refrigerant separated by the gas-liquid separator 3 can return to the compressor 1, and the liquid refrigerant remains in the gas-liquid separator 3, thereby protecting the compressor 1.

[0111] In some embodiments, the outdoor unit 100 further comprises a switching valve 4, which is arranged at the end of the one-way valve 8 away from the oil separator 2. The switching valve 4 is configured to enable the air conditioning system to switch between the cooling mode and the heating mode.

[0112] In some embodiments, the switching valve 4 can be a four-way valve including four openings, namely a D opening, a C opening, an E opening and an S opening. The D opening of the four-way valve is communicated with the one-way valve 8, the C opening of the four-way valve is communicated with the second end of the outdoor heat exchanger 6, the S opening of the four-way valve is communicated with the gas-liquid separator 3, and the E opening of the four-way valve is communicated with the indoor heat exchanger 340.

[0113] In some embodiments, the outdoor unit 100 further includes an outdoor fan 5 disposed near the outdoor heat exchanger 6. The rotating speed of the outdoor fan 5 can be controlled to change the flow rate of air in heat exchange with the outdoor heat exchanger 6 by adjusting the rotating speed. The outdoor fan 5 can be an axial fan, a cross-flow fan or any other optional form of fan.

[0114] The structure and functions of the indoor unit 300 are described below.

[0115] In some embodiments, referring to FIGS. 1 to 3, the at least one indoor unit 300 includes four indoor units 300, namely a first indoor unit 301, a second indoor unit 302, a third indoor unit 303 and a fourth indoor unit 304.

[0116] The first indoor unit 301, the second indoor unit 302, the third indoor unit 303 and the fourth indoor unit 304 are respectively communicated with the outdoor unit 100.

[0117] It should be noted that the number of indoor units 300 is not limited in the present disclosure, and more or fewer indoor units 300 can be arranged in one air conditioning system, and the arrangement of the indoor units 300 can be the same as that shown in FIG. 1.

[0118] In some embodiments, any one of the at least one indoor unit 300 includes an indoor heat exchanger 340.

[0119] Referring to FIG. 1, the first indoor unit 301 includes a first indoor heat exchanger 19, the second indoor unit 302 includes a second indoor heat exchanger 30, the third indoor unit 303 includes a third indoor heat exchanger 41, and the fourth indoor unit 304 includes a fourth indoor heat exchanger 52.

[0120] In some embodiments, any one of the indoor units 300 further includes an indoor electronic expansion valve 330. The indoor electronic expansion valve 330 is disposed at the first end of the indoor heat exchanger 340.

[0121] Referring to FIG. 1, the first indoor unit 301 includes a first indoor electronic expansion valve 18, the second indoor unit 302 includes a second indoor electronic expansion valve 29, the third indoor unit 303 includes a third indoor electronic expansion valve 40, and the fourth indoor unit 304 includes a fourth indoor electronic expansion valve 51.

[0122] In some embodiments, any one of the indoor units 300 further comprises an indoor fan 350, which is disposed close to the indoor heat exchanger 340. The indoor fan 350 can be an axial fan, a cross-flow fan, or any other optional form of fan.

[0123] Referring to FIG. 1, the first indoor unit 301 comprises a first indoor fan 20, the second indoor unit 302 comprises a second indoor fan 31, the third indoor unit 303 comprises a third indoor fan 42, and the fourth indoor unit 304 comprises a fourth indoor fan 53.

[0124] In some embodiments, the air conditioning system 1000 further comprises at least one refrigerant cutoff component 200, which can be disposed in correspondence with the indoor unit 300. The refrigerant cutoff component 200 is disposed between the outdoor unit 100 and the indoor unit 300, and is configured to adjust the flow rate of refrigerant entering the indoor heat exchanger 340 and flowing out of the indoor heat exchanger 340.

[0125] In some embodiments, the liquid pipe 103 comprises a first liquid pipe (outdoor unit side liquid pipe), which is disposed between the second end of the outdoor heat exchanger 6 and the refrigerant cutoff component 200. The liquid pipe 103 further comprises a second liquid pipe (indoor unit side liquid pipe), which is disposed between the refrigerant cutoff component 200 and the first end of the indoor heat exchanger 340.

[0126] In some embodiments, the first gas pipe 101 comprises a first gas pipe (outdoor unit side gas pipe), which is disposed between the compressor 1 and the refrigerant cutoff component 200. The first gas pipe 101 further comprises a second gas pipe (indoor unit side gas pipe), which is disposed between the refrigerant cutoff component 200 and the second end of the indoor heat exchanger 340.

[0127] The refrigerant cutoff component 200 is in communication with the outdoor unit 100 via the first liquid pipe and the first gas pipe, and is in communication with the indoor unit 300 via the second liquid pipe and the second gas pipe.

[0128] For example, referring to FIG. 1, the at least one refrigerant cutoff component 200 comprises four refrigerant cutoff components 200, namely a first refrigerant cutoff component 201, a second refrigerant cutoff component 202, a third refrigerant cutoff component 203, and a fourth refrigerant cutoff component 204.

[0129] In some embodiments, any of the at least one refrigerant intercepting component 200 includes a first throttling component 210. The first throttling component 210 is disposed between the first liquid pipe and the second liquid pipe. That is, the first throttling component 210 is disposed in the liquid pipe 103. The first throttling component 210 can adjust the flow rate and pressure of the refrigerant flowing in the liquid pipe 103.

[0130] In some embodiments, the first throttling component 210 is disposed between the indoor electronic expansion valve 330 and the second end of the outdoor heat exchanger 340. For example, referring to FIG. 1, the first refrigerant intercepting component 201 includes the first sub-throttling component 12, the second refrigerant intercepting component 202 includes the third sub-throttling component 23, the third refrigerant intercepting component 203 includes the fifth sub-throttling component 34, and the fourth refrigerant intercepting component 204 includes the seventh sub-throttling component 45.

[0131] In some embodiments, any of the at least one refrigerant intercepting component 200 further includes a second throttling component 220 disposed between the first gas pipe and the second gas pipe. That is, the second throttling component 220 is disposed in the first gas pipe 101. The second throttling component 220 can adjust the flow rate and pressure of the refrigerant flowing in the first gas pipe 101.

[0132] In some embodiments, the second throttling component 220 is disposed between the second end of the indoor heat exchanger 340 and the compressor 1. For example, referring to FIG. 1, the first refrigerant intercepting component 201 includes the second sub-throttling component 13, the second refrigerant intercepting component 202 includes the fourth sub-throttling component 24, the third refrigerant intercepting component 203 includes the sixth sub-throttling component 35, and the fourth refrigerant intercepting component 204 includes the eighth sub-throttling component 46.

[0133] In some embodiments, the first throttling component 210 can be an electronic expansion valve.

[0134] In some embodiments, the second throttling component 220 can also be an electronic expansion valve.

[0135] In some embodiments, any of the at least one refrigerant intercepting component 200 further includes a first shutoff valve 230 disposed between the first liquid pipe and the first throttling component 210.

[0136] Referring to FIG. 1, the first refrigerant intercepting component 201 includes the first sub-shutoff valve 10, the second refrigerant intercepting component 202 includes the fifth sub-shutoff valve 21, the third refrigerant intercepting component 203 includes the ninth sub-shutoff valve 32, and the fourth refrigerant intercepting component 204 includes the thirteenth sub-shutoff valve 43.

[0137] In some embodiments, the any one refrigerant cut-off component 200 further comprises a second cut-off valve 240, which is arranged between the first gas pipe and the second throttling component 220.

[0138] Referring to FIG. 1, the first refrigerant cut-off component 201 comprises a second sub-cut-off valve 11, the second refrigerant cut-off component 202 comprises a sixth sub-cut-off valve 22, the third refrigerant cut-off component 203 comprises a tenth sub-cut-off valve 33, and the fourth refrigerant cut-off component 204 comprises a fourteenth sub-cut-off valve 44.

[0139] In some embodiments, the any one refrigerant cut-off component 200 further comprises a third cut-off valve 250, which is arranged between the second liquid pipe and the first throttling component 210.

[0140] Referring to FIG. 1, the first refrigerant cut-off component 201 comprises a third sub-cut-off valve 14, the second refrigerant cut-off component 202 comprises a seventh sub-cut-off valve 25, the third refrigerant cut-off component 203 comprises an eleventh sub-cut-off valve 36, and the fourth refrigerant cut-off component 204 comprises a fifteenth sub-cut-off valve 47.

[0141] In some embodiments, the any one refrigerant cut-off component 200 further comprises a fourth cut-off valve 260, which is arranged between the second gas pipe and the second throttling component 220.

[0142] Referring to FIG. 1, the first refrigerant cut-off component 201 comprises a fourth sub-cut-off valve 15, the second refrigerant cut-off component 202 comprises an eighth sub-cut-off valve 26, the third refrigerant cut-off component 203 comprises a twelfth sub-cut-off valve 37, and the fourth refrigerant cut-off component 204 comprises a sixteenth sub-cut-off valve 48.

[0143] The first cut-off valve 230, the second cut-off valve 240, the third cut-off valve 250, and the fourth cut-off valve 260 are configured to control the flow and cut-off of the refrigerant in the refrigerant cut-off component 200, so as to control the on-off of the refrigerant circulation loop between the indoor unit 300 and the outdoor unit 100.

[0144] In some embodiments, the refrigerant cut-off component 200 can be arranged in a housing alone and used in combination with the indoor unit 300.

[0145] In some embodiments, the refrigerant cut-off component 200 can be arranged in combination with a plurality of indoor units 300, or arranged in combination with part of the plurality of indoor units 300. That is, the number of the refrigerant cut-off components 200 can be equal to or less than the number of the indoor units 300.

[0146] In some embodiments, the outdoor unit 100 further comprises a seventh stop valve 71 (e.g., an outdoor-side liquid pipe stop valve) disposed at a position of the liquid pipe 103 close to the second end of the outdoor heat exchanger 6. For example, the seventh stop valve 71 is disposed between the outdoor electronic expansion valve 7 and the refrigerant cutoff component 200.

[0147] In some embodiments, the outdoor unit 100 further comprises an eighth stop valve 72 (e.g., an outdoor-side gas pipe stop valve) disposed at a position of the gas pipe 60 close to the outdoor unit 100.

[0148] In some embodiments, any of the indoor units 300 further comprises a fifth stop valve 310 (e.g., an indoor-side liquid pipe stop valve) disposed at a position of the liquid pipe 103 close to the first end of the indoor heat exchanger 340. For example, the fifth stop valve 310 is disposed between the refrigerant cutoff component 200 and the indoor electronic expansion valve 330.

[0149] Referring to FIG. 1, the first indoor unit 301 comprises a seventeenth sub-stop valve 16, the second indoor unit 302 comprises a nineteenth sub-stop valve 27, the third indoor unit 303 comprises a twenty-first sub-stop valve 38, and the fourth indoor unit 304 comprises a twenty-third sub-stop valve 49.

[0150] In some embodiments, any of the indoor units 300 further comprises a sixth stop valve 320 (e.g., an indoor-side gas pipe stop valve) disposed at a position of the first gas pipe 60 close to the indoor unit 300.

[0151] Referring to FIG. 1, the first indoor unit 301 comprises an eighteenth sub-stop valve 17, the second indoor unit 302 comprises a twentieth sub-stop valve 28, the third indoor unit 303 comprises a twenty-second sub-stop valve 39, and the fourth indoor unit 304 comprises a twenty-fourth sub-stop valve 50.

[0152] That is, the liquid pipe 103 is respectively provided with two groups of liquid pipe stop valves 63, namely the fifth stop valve 310 and the seventh stop valve 71. The first gas pipe 101 is provided with two groups of first gas pipe stop valves 61, namely the sixth stop valve 320 and the eighth stop valve 72.

[0153] The following describes the circulation process of the refrigerant in the air conditioning system 1000 in the cooling mode.

[0154] Referring to FIG. 1 and FIG. 2, in the cooling mode, the D port of the switching valve 4 (for example, a four-way valve) is communicated with the C port, and the E port is communicated with the S port. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 passes through the oil separator 2 and the switching valve 4 into the outdoor heat exchanger 6, and is condensed into high-temperature and high-pressure liquid refrigerant in the outdoor heat exchanger 6. The high-temperature and high-pressure liquid refrigerant flows out of the outdoor unit 100 after passing through the outdoor electronic expansion valve 7 and the seventh stop valve 71.

[0155] The high-temperature and high-pressure liquid refrigerant flowing out of the outdoor unit 100 passes through the refrigerant cutting member 200 into the indoor unit 300. For example, the high-temperature and high-pressure liquid refrigerant passes through the first stop valve 230, the first throttling member 210, the third stop valve 250, the fifth stop valve 310, and the indoor electronic expansion valve 330 in sequence into the indoor heat exchanger 340. In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the indoor heat exchanger 340, and the low-temperature and low-pressure gaseous refrigerant flows out of the second stop valve 240 after passing through the sixth stop valve 320 and the fourth stop valve 260 in sequence.

[0156] The low-temperature and low-pressure gaseous refrigerant flowing out of the second stop valve 240 converges and then passes through the eighth stop valve 72 and the switching valve 4 into the gas-liquid separator 3. The low-temperature and low-pressure gaseous refrigerant flows out of the gas-liquid separator 3 into the suction port of the compressor 1, and the cooling operation of the air conditioning system 1000 is thus completed.

[0157] For example, the air conditioning system 1000 includes a plurality of indoor units 300, and the high-temperature and high-pressure liquid refrigerant flowing out of the outdoor unit 100 is divided into multiple paths (for example, four paths as shown in FIG. 2) and enters the refrigerant cutting members 200 corresponding to the indoor units 300. The first part of the high-temperature and high-pressure liquid refrigerant passes through the first sub-stop valve 10, the first sub-throttling member 12, the third sub-stop valve 14, the seventeenth sub-stop valve 16, and the first indoor electronic expansion valve 18 in sequence into the first indoor heat exchanger 19. In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the first indoor heat exchanger 19, and the low-temperature and low-pressure gaseous refrigerant flows out of the second sub-stop valve 11 after passing through the eighteenth sub-stop valve 17, the fourth sub-stop valve 15, and the second sub-throttling member 13 in sequence.

[0158] The high-temperature and high-pressure liquid refrigerant of the second portion passes through the fifth sub-shutoff valve 21, the third sub-throttling member 23, the seventh sub-shutoff valve 25, the nineteenth sub-shutoff valve 27, and the second indoor electronic expansion valve 29 in sequence to enter the second indoor heat exchanger 30. In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the second indoor heat exchanger 30, and the low-temperature and low-pressure gaseous refrigerant passes through the twentieth sub-shutoff valve 28, the eighth sub-shutoff valve 26, and the fourth sub-throttling member 24 in sequence to flow out from the sixth sub-shutoff valve 22.

[0159] The high-temperature and high-pressure liquid refrigerant of the third portion passes through the ninth sub-shutoff valve 32, the fifth sub-throttling member 34, the eleventh sub-shutoff valve 36, the twenty-first sub-shutoff valve 38, and the third indoor electronic expansion valve 40 in sequence to enter the third indoor heat exchanger 41. In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the third indoor heat exchanger 41, and the low-temperature and low-pressure gaseous refrigerant passes through the twenty-second sub-shutoff valve 39, the twelfth sub-shutoff valve 37, and the sixth sub-throttling member 35 in sequence to flow out from the tenth sub-shutoff valve 33.

[0160] The high-temperature and high-pressure liquid refrigerant of the fourth portion passes through the thirteenth sub-shutoff valve 43, the seventh sub-throttling member 45, the fifteenth sub-shutoff valve 47, the twenty-third sub-shutoff valve 49, and the fourth indoor electronic expansion valve 51 in sequence to enter the fourth indoor heat exchanger 52. In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the fourth indoor heat exchanger 52, and the low-temperature and low-pressure gaseous refrigerant passes through the twenty-fourth sub-shutoff valve 50, the sixteenth sub-shutoff valve 48, and the eighth sub-throttling member 46 in sequence to flow out from the fourteenth sub-shutoff valve 44.

[0161] The low-temperature and low-pressure gaseous refrigerant flowing out from the second sub-shutoff valve 11, the sixth sub-shutoff valve 22, the tenth sub-shutoff valve 33, and the fourteenth sub-shutoff valve 44 is combined and then passes through the eighth shutoff valve 72 and the switching valve 4 to flow into the gas-liquid separator 3. The low-temperature and low-pressure gaseous refrigerant flows out from the gas-liquid separator 3 to enter the suction port of the compressor 1, and thus the refrigeration operation of the air conditioning system 1000 is completed.

[0162] The following describes the circulation process of the refrigerant in the air conditioning system 1000 in the heating mode. Referring to FIGS. 1 and 3, in the heating mode, the D port and the E port of the switching valve 4 (for example, a four-way valve) are in communication, and the C port and the S port are in communication. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows out from the outdoor unit 100 after passing through the oil separator 2, the switching valve 4, and the eighth shutoff valve 72.

[0163] The high-temperature and high-pressure gaseous refrigerant after flowing out of the outdoor unit 100 enters the indoor unit 300 through the refrigerant intercepting component 200. For example, the high-temperature and high-pressure gaseous refrigerant flows through the second stop valve 240, the second throttling component 220, the fourth stop valve 260, and the sixth stop valve 320, and is condensed into high-temperature and high-pressure liquid refrigerant in the indoor heat exchanger 340. The high-temperature and high-pressure liquid refrigerant flows out of the first stop valve 230 in sequence through the indoor electronic expansion valve 330, the fifth stop valve 310, the third stop valve 250, and the first throttling component 210.

[0164] The liquid refrigerant flowing out of the first stop valve 230 is combined and flows out of the seventh stop valve 71, throttled into low-temperature and low-pressure refrigerant by the outdoor throttling component (for example, the outdoor electronic expansion valve 7), evaporated into low-temperature and low-pressure gaseous refrigerant in the outdoor heat exchanger 6, and sequentially flows through the switching valve 4 and the gas-liquid separator 3 into the suction port of the compressor 1, thereby completing the heating operation of the air conditioning system 1000.

[0165] For example, the high-temperature and high-pressure gaseous refrigerant after flowing out of the outdoor unit 100 is divided into multiple paths (for example, four paths as shown in FIG. 3), and enters the refrigerant intercepting components 200 corresponding to the indoor unit 300.

[0166] The high-temperature and high-pressure gaseous refrigerant of the first part flows through the second sub-stop valve 11, the second sub-throttling component 13, the fourth sub-stop valve 15, and the eighteenth sub-stop valve 17 into the first indoor heat exchanger 19, and is condensed into high-temperature and high-pressure liquid refrigerant in the first indoor heat exchanger 19. The high-temperature and high-pressure liquid refrigerant flows out of the first sub-stop valve 10 in sequence through the first indoor electronic expansion valve 18, the seventeenth sub-stop valve 16, the third sub-stop valve 14, and the first sub-throttling component 12.

[0167] The high-temperature and high-pressure gaseous refrigerant of the second part flows through the sixth sub-stop valve 22, the fourth sub-throttling component 24, the eighth sub-stop valve 26, and the twentieth sub-stop valve 28 into the second indoor heat exchanger 30, and is condensed into high-temperature and high-pressure liquid refrigerant in the second indoor heat exchanger 30. The high-temperature and high-pressure liquid refrigerant flows out of the fifth sub-stop valve 21 in sequence through the second indoor electronic expansion valve 29, the nineteenth sub-stop valve 27, the seventh sub-stop valve 25, and the third sub-throttling component 23.

[0168] The third portion of the high-temperature and high-pressure gaseous refrigerant passes through the tenth sub-shutoff valve 33, the sixth sub-throttling component 35, the twelfth sub-shutoff valve 37, and the twenty-second sub-shutoff valve 39 into the third indoor heat exchanger 41, and is condensed into a high-temperature and high-pressure liquid refrigerant in the third indoor heat exchanger 41. The high-temperature and high-pressure liquid refrigerant passes through the third indoor electronic expansion valve 40, the twenty-first sub-shutoff valve 38, the eleventh sub-shutoff valve 36, and the fifth sub-throttling component 34 in sequence, and flows out from the ninth sub-shutoff valve 32.

[0169] The fourth portion of the high-temperature and high-pressure gaseous refrigerant passes through the fourteenth sub-shutoff valve 44, the eighth sub-throttling component 46, the sixteenth sub-shutoff valve 48, and the twenty-fourth sub-shutoff valve 50 into the fourth indoor heat exchanger 52, and is condensed into a high-temperature and high-pressure liquid refrigerant in the fourth indoor heat exchanger 52. The high-temperature and high-pressure liquid refrigerant passes through the fourth indoor electronic expansion valve 51, the twenty-third sub-shutoff valve 49, the fifteenth sub-shutoff valve 47, and the seventh sub-throttling component 45 in sequence, and flows out from the thirteenth sub-shutoff valve 43.

[0170] The liquid refrigerant flowing out from the first sub-shutoff valve 10, the fifth sub-shutoff valve 21, the ninth sub-shutoff valve 32, and the thirteenth sub-shutoff valve 43 is combined with the liquid refrigerant flowing out from the seventh sub-shutoff valve 71, throttled into a low-temperature and low-pressure refrigerant by the outdoor throttling component (for example, the outdoor electronic expansion valve 7), evaporated into a low-temperature and low-pressure gaseous refrigerant in the outdoor heat exchanger 6, and passes through the switching valve 4 and the gas-liquid separator 3 in sequence to enter the suction port of the compressor 1, thereby completing the heating operation of the air conditioning system 1000.

[0171] Referring to FIG. 11, in some embodiments, the air conditioning system 1000 further includes a controller 600.

[0172] The controller 600 includes a processor 601 which can access a storage component to execute instructions or applications stored in the storage component to implement related functions. For example, the processor can be a general-purpose central processing unit (CPU), a microprocessor, an application specific integrated circuit (ASIC), etc.

[0173] In some embodiments, the controller 600 further includes a memory which can include at least one of a volatile memory 602 or a non-volatile memory 603. The volatile memory 602 has a fast access speed. The non-volatile memory 603 can store data after power-off. The processor 601 can access the memory to execute instructions or applications stored in the memory to implement related functions.

[0174] In some embodiments, the controller 600 further comprises a display device 604 configured to display information such as the operating mode, the wind speed, the preset temperature, the preset humidity, and the like of the air conditioning system 1000.

[0175] In some embodiments, the controller 600 further comprises an operation device 605 configured to receive various operations.

[0176] In some embodiments, the controller 600 further comprises a communication interface 606 through which the controller 600 can communicate with external devices. The communication interface 606 can comprise a wireless communication interface that can support different wireless communication protocols such as Wireless Fidelity (Wi-Fi), Bluetooth, Near Field Communication, and Narrow Band Internet of Things (NB-IoT), and the like, to be communicatively connected with external devices. Here, the external devices include a cloud server, a computer (host computer), a programmable logic controller, a smartphone, a tablet computer, a PDA, a smart control tool, a wearable device, and a vehicle-mounted device, and the like.

[0177] The communication interface 606 can also comprise a wired communication interface such as an Input / Output (I / O) interface that can be communicatively connected with various sensors arranged in the outdoor unit 100 to receive detection values of the various sensors arranged in the outdoor unit 100, such as a pressure sensor arranged at the discharge end of the compressor.

[0178] In some embodiments, the controller 600 further comprises a drive device 607 that is a hardware terminal interacting with a storage medium.

[0179] In some embodiments, the controller 600 further comprises a bus 608 through which the above-mentioned components are connected with each other.

[0180] In some embodiments, the controller 600 further comprises a storage medium including a medium that records information in an optical, electrical, or magnetic manner such as a Compact Disc Read-Only Memory (CD-ROM), a floppy disk, a magneto-optical disk, and the like (as shown as 609 in FIG. 11). The storage medium can also be a semiconductor memory that records information in a point-by-point manner such as a Read-Only Memory (ROM), a flash memory, and the like (as shown as 610 in FIG. 11).

[0181] In some embodiments, an outdoor control circuit is provided in the outdoor unit 100. The outdoor control circuit is usually provided in an electrical box with good sealing performance. The outdoor control circuit can receive detection values of various sensors provided in the outdoor unit 100, and is configured to be coupled with a frequency converter of the compressor 1, the outdoor fan 5, the switching valve 4, the outdoor electronic expansion valve 7, and the like, to output control instructions generated by a processor to the above components.

[0182] In some embodiments, an indoor control circuit is provided in the indoor unit 300. The structure of the indoor control circuit is similar to that of the outdoor control circuit.

[0183] The controller 600 can be integrated in the outdoor control circuit in the outdoor unit 100, or the indoor control circuit in the indoor unit 300. For example, the controller 600 can be a system on a board based on a microcontroller unit (MCU). Referring to FIGS. 1 and 4, the air conditioning rooms (room one, room two, room three, and room four) are respectively provided with the first indoor unit 301, the second indoor unit 302, the third indoor unit 303, and the fourth indoor unit 304, the first indoor unit 301 is connected with the first refrigerant cutting component 201, the second indoor unit 302 is connected with the second refrigerant cutting component 202, the third indoor unit 303 is connected with the third refrigerant cutting component 203, and the fourth indoor unit 304 is connected with the fourth refrigerant cutting component 204. The outdoor unit 100 is installed outdoors, and is connected with the first refrigerant cutting component 201, the second refrigerant cutting component 202, the third refrigerant cutting component 203, and the fourth refrigerant cutting component 204 through pipes, and is connected with the first indoor unit 301, the second indoor unit 302, the third indoor unit 303, and the fourth indoor unit 304 through the first refrigerant cutting component 201, the second refrigerant cutting component 202, the third refrigerant cutting component 203, and the fourth refrigerant cutting component 204, respectively.

[0184] In some embodiments, only part of the indoor units 300 can be provided with the refrigerant cutting component 200, that is, the number of the refrigerant cutting components 200 can be less than the number of the indoor units 300. Since the outdoor unit 100, the refrigerant cutting component 200, and the indoor unit 300 are respectively independently provided with a stop valve, the outdoor unit 100, the refrigerant cutting component 200, and the indoor unit 300 can be independently disassembled according to needs. In this way, it is convenient for later maintenance.

[0185] The functions of the controller 600 are described below.

[0186] In some embodiments, the controller 600 is configured to: obtain a temperature variation rate of the air-conditioned room where the indoor unit 300 is located, and a deviation degree of a temperature of the air-conditioned room from a target temperature; determine a target refrigerant temperature matching a current load of the air-conditioned room according to the temperature variation rate and the deviation degree; and determine the opening degrees of the indoor electronic expansion valve 330, the first throttling component 210 and the second throttling component 220 according to the target refrigerant temperature, at least one of a preset target superheat degree or a target subcooling degree.

[0187] It can be understood that the temperature variation rate and the deviation degree can represent the load condition of the air conditioning system 1000. In the cooling mode and the heating mode, the control process of the controller 600 on the opening degrees of the indoor electronic expansion valve 330, the first throttling component 210 and the second throttling component 220 is different.

[0188] The control process of the controller 600 in the cooling mode is described below. In some embodiments, in the cooling mode, the temperature variation curve of the air-conditioned room over time can refer to FIG. 5. According to FIG. 5, the temperature variation rate of the air-conditioned room in the cooling mode and the deviation degree of the temperature of the air-conditioned room from the target temperature can be obtained, so as to further construct a data table of the temperature variation rate of the air-conditioned room in the cooling mode, the deviation degree and the target refrigerant temperature.

[0189] It can be understood that in FIG. 5, the temperature in the air-conditioned room shows a downward trend. In FIG. 5: T i (n) is the temperature of the air-conditioned room at the nth moment, that is, the air temperature in the air-conditioned room; T i (n-1) is the temperature of the air-conditioned room at the (n-1)th moment; τ(n) is the nth moment; τ(n-1) is the (n-1)th moment; is the temperature variation rate of the air-conditioned room; ΔT(n) = T i (n)-T s (n), ΔT(n) is the deviation degree of the temperature of the air-conditioned room at the nth moment from the target temperature; ΔT(n-1) = T i (n-1)-T s (n-1), ΔT(n-1) is the deviation degree of the temperature of the air-conditioned room at the (n-1)th moment from the target temperature; T

[0190] Table 1 is a data table of the temperature variation rate of the air-conditioned room in the cooling mode, the deviation degree of the temperature of the air-conditioned room from the target temperature and the target refrigerant temperature.

[0191] Table 1 target refrigerant temperature of the indoor unit in the cooling mode

[0192] In Table 1, there are a1 < a2 < a3 < a4 < a5 <... < a n ≤ 0℃, b1 > b2 > b3 > b4 >... > b n ≥ 0℃.

[0193] It can be understood that the temperature change rate and the deviation degree represent the load condition of the air conditioning system 1000. In the cooling mode, the target refrigerant temperature in the data table satisfies the following relationship: along each row in the data table, the temperature change rate increases and the target refrigerant temperature decreases. Along each column in the data table, the deviation degree of the temperature of the air-conditioned room from the target temperature decreases and the target refrigerant temperature increases, that is, there are: T eo_11 > T eo_21 > T eo_31 > T eo_41 >... > T eo_n1 ; T eo_11 < T eo_12 < T eo_13 < T eo_14 <... < T eo_1n ; T eo_1n > T eo_2n > T eo_3n > T eo_4n >... > T eo_nn .

[0194] Table 2 is an example of a data table in the cooling mode.

[0195] Table 2

[0196] For the method of obtaining the target refrigerant, in addition to the data table, a thermal load model of the air-conditioned room can also be established according to the temperature change rate and the deviation degree, and the target refrigerant temperature is predicted by the thermal load model. For example, the thermal load model is established by training and learning the historical data of the temperature change rate and the deviation degree according to a machine learning algorithm (such as a neural network, a support vector machine, or a decision tree algorithm), the target refrigerant temperature is predicted by the thermal load model, or an empirical formula can also be established according to the temperature change rate and the deviation degree, the target refrigerant temperature is calculated according to the empirical formula, or the target refrigerant temperature can also be calculated by a polynomial fitting method under a plurality of known temperature change rates and deviation degrees.

[0197] In some embodiments, in the cooling mode, the controller 600 is further configured to: control the first throttling component 210 to be at a first preset opening degree; obtain a real-time refrigerant temperature in the current indoor heat exchanger 340 and a target refrigerant temperature, determine an opening degree of the indoor electronic expansion valve 330 according to the target refrigerant temperature and the real-time refrigerant temperature in the current indoor heat exchanger 340; obtain a real-time liquid pipe temperature of the current indoor heat exchanger 340 and a real-time gas pipe temperature of the current indoor heat exchanger 340, calculate a refrigerant superheat degree according to the real-time liquid pipe temperature of the current indoor heat exchanger 340 and the real-time gas pipe temperature of the current indoor heat exchanger 340, and determine an opening degree of the second throttling component 220 according to the target superheat degree and the refrigerant superheat degree.

[0198] It should be noted that the first preset opening degree can be the maximum opening degree of the first throttling component 210. In this way, the flow rate of the refrigerant entering the indoor heat exchanger 340 is increased, thereby improving the cooling effect of the indoor unit 300.

[0199] It can be understood that, in the cooling mode, the flow rate of the refrigerant flowing out of the indoor heat exchanger 340 can be adjusted by adjusting the opening degree of the second throttling component 220, thereby adjusting the flow rate and pressure of the refrigerant in the indoor unit 300.

[0200] In some embodiments, the indoor heat exchanger 340 is a finned tube heat exchanger. Referring to FIGS. 6 and 8, the indoor unit 300 further comprises a first sensor 505 (e.g., a coil temperature sensor) disposed at a position of an intermediate coil of the indoor heat exchanger 340. The first sensor 505 is configured to detect a real-time refrigerant temperature in the current indoor heat exchanger 340.

[0201] In some embodiments, the controller 600 is coupled with the first sensor 505 to obtain the real-time refrigerant temperature in the current indoor heat exchanger 340, and determine the opening degree of the indoor electronic expansion valve 330 according to the target refrigerant temperature and the real-time refrigerant temperature in the current indoor heat exchanger 340.

[0202] In some embodiments, in the cooling mode, the controller 600 is further configured to: obtain a real-time refrigerant temperature in the current indoor heat exchanger 340 and a target refrigerant temperature. If it is determined that the target refrigerant temperature is greater than the real-time refrigerant temperature in the current indoor heat exchanger 340, the opening degree of the indoor electronic expansion valve 330 is decreased. If it is determined that the target refrigerant temperature is less than the real-time refrigerant temperature in the current indoor heat exchanger 340, the opening degree of the indoor electronic expansion valve 330 is increased. If it is determined that the target refrigerant temperature is equal to the real-time refrigerant temperature in the current indoor heat exchanger 340, the opening degree of the indoor electronic expansion valve 330 is kept unchanged.

[0203] For example, in the cooling mode, the real-time refrigerant temperature of the current indoor heat exchanger 340 is denoted as Tsat , the target refrigerant temperature is denoted as T eo . That is, if it is determined that T sat > T eo , the controller 600 decreases the opening degree of the indoor electronic expansion valve 330 to reduce the real-time refrigerant temperature in the current indoor heat exchanger 340. If it is determined that T sat < T eo , the controller 600 increases the opening degree of the indoor electronic expansion valve 330 to increase the real-time refrigerant temperature in the current indoor heat exchanger 340. If it is determined that T sat = T eo , the controller 600 keeps the opening degree of the indoor electronic expansion valve 330 unchanged.

[0204] Referring to Table 3, taking room one and room two as examples, in the cooling mode, it is assumed that the target set temperature T s of the two rooms is 26°C. The initial temperature in room one and room two at time 0 is the same, for example, 35°C. According to the relationship between ΔT(n) and T , the target refrigerant temperature T eo of room one and room two at time 1, time 2, time 3, time 4, time 5, time 6, time 7, and time 8 is 11.2°C, 8.2°C; 11.5, 10.4°C; 13.7°C, 11.5°C; 14.8°C, 13.7°C; 15.9°C, 14.8°C; 16.8°C, 15.9°C; 16.8, 16.8°C; 16.8, 16.8°C, respectively. The controller 600 can obtain the current time T sat and T eo to control the opening degree of the indoor electronic expansion valve 330 according to the relationship between T sat and T eo .

[0205] Table 3 is an example of the change of the target refrigerant temperature T eo .

[0206] Table 3

[0207] In some embodiments, referring to FIGS. 6 and 8, the air conditioning system 1000 further comprises a second sensor 506 (for example, a liquid pipe temperature sensor) configured to detect the real-time liquid pipe temperature of the current indoor heat exchanger 340. For example, the second sensor 506 is arranged between the indoor electronic expansion valve 330 and the first end of the indoor heat exchanger 340 to detect the temperature of the liquid pipe 103 located at the position of the first end of the indoor heat exchanger 340.

[0208] In some embodiments, the air conditioning system 1000 further comprises a third sensor 507 (e.g., a gas pipe temperature sensor) configured to detect a real-time gas pipe temperature of the current indoor heat exchanger 340. For example, the third sensor 507 is arranged at the second end of the indoor heat exchanger 340 to detect the temperature of the first gas pipe 60 at the position of the second end of the indoor heat exchanger 340.

[0209] In some embodiments, the controller 600 is further coupled with the second sensor 506 and the third sensor 507 to obtain the real-time liquid pipe temperature of the current indoor heat exchanger 340 and the real-time gas pipe temperature of the current indoor heat exchanger 340, and determine the refrigerant superheat degree according to the real-time liquid pipe temperature of the current indoor heat exchanger 340 and the real-time gas pipe temperature of the current indoor heat exchanger 340.

[0210] In some embodiments, the controller 600 is further configured to: increase the opening degree of the second throttling component 220 if it is determined that the refrigerant superheat degree is greater than the target superheat degree; decrease the opening degree of the second throttling component 220 if it is determined that the refrigerant superheat degree is less than the target superheat degree; and keep the opening degree of the second throttling component 220 unchanged if it is determined that the refrigerant superheat degree is equal to the target superheat degree.

[0211] It can be understood that the refrigerant superheat degree can be calculated according to the real-time liquid pipe temperature (denoted as T l ) of the current indoor heat exchanger 340 and the real-time gas pipe temperature (denoted as T g ) of the current indoor heat exchanger 340, and the refrigerant superheat degree is denoted as SH, so SH = T g -T l The target superheat degree is denoted as SHo, which can be pre-set or calculated. The setting or calculation of the target superheat degree SHo can adopt the techniques disclosed in related technologies.

[0212] That is, if it is determined that SH > SHo, the controller 600 increases the opening degree of the second throttling component 220. If it is determined that SH < SHo, the controller 600 decreases the opening degree of the second throttling component 220. If it is determined that SH = SHo, the controller 600 keeps the opening degree of the second throttling component 220 unchanged.

[0213] The control process of the controller 600 in the heating mode is described below.

[0214] In some embodiments, in the heating mode, the temperature change curve of the air conditioning room over time can refer to FIG. 7. According to FIG. 7, the temperature change rate of the air conditioning room in the heating mode and the deviation degree of the temperature of the air conditioning room from the target temperature can be obtained. In this way, a data table of the temperature change rate of the air conditioning room in the heating mode, the deviation degree, and the target refrigerant temperature can be further constructed.

[0215] Further, a data table of the temperature change rate of the air-conditioned room, the deviation degree and the target refrigerant temperature can be constructed. Table 4 is an example of the data table.

[0216] It can be understood that the temperature in the air-conditioned room is in an upward trend in Fig. 7. In Fig. 7, T i (n) is the temperature of the air-conditioned room at the nth time, i.e. the air temperature in the air-conditioned room; T i (n-1) is the temperature of the air-conditioned room at the (n-1)th time; τ(n) is the nth time in the air-conditioned room; τ(n-1) is the (n-1)th time in the air-conditioned room; is the temperature change rate of the air-conditioned room; ΔT(n) = T i (n) - T s (n-1), ΔT(n) is the deviation degree of the temperature of the air-conditioned room from the target temperature at the nth time; ΔT(n-1) = T i (n-1) - T s (n-1) is the deviation degree of the temperature of the air-conditioned room from the target temperature at the (n-1)th time; T s is the target temperature set by the user in the air-conditioned room.

[0217] Table 4 Target refrigerant temperature of the indoor unit in the heating mode

[0218] In Table 4, there are γ1> γ2> γ3> γ4> γ5> … > γ n ≥ 0℃, η1> η2> η3> η4> … > η n ≥ 0℃.

[0219] It can be understood that the temperature change rate and the deviation degree represent the building load condition. In the heating mode, the target refrigerant temperature in the data table satisfies the following relationship: along each row in the data table, the temperature change rate is in a decreasing trend, and the target refrigerant temperature is in an increasing trend. Along each column in the data table, the deviation degree of the temperature of the air-conditioned room from the target temperature is in a decreasing trend, and the target refrigerant temperature is in a decreasing trend. That is, there are: T co_11 < T co_21 < T co_31 < T co_41 < … < T co_n1 ; T co_11 > T co_12 > T co_13 > T co_14 > … > T co_1n ; T co_1n < T co_2n < T co_3n < T co_4n < … < T co_nn .

[0220] Table 5 is an example of a data table in the heating mode.

[0221] Table 5

[0222] Of course, for the method of obtaining the target refrigerant, in addition to the data table, a heat load model of the air-conditioned room can also be established according to the temperature change rate and the deviation degree, the target refrigerant temperature is predicted through the heat load model, or the heat load model is established by training and learning the historical data of the temperature change rate and the deviation degree according to a machine learning algorithm (such as a neural network, a support vector machine, or a decision tree algorithm), the target refrigerant temperature is predicted through the heat load model, or the target refrigerant temperature can also be calculated according to an empirical formula established according to the temperature change rate and the deviation degree, or the target refrigerant temperature can also be calculated by a polynomial fitting method under a plurality of known temperature change rates and deviation degrees.

[0223] In some embodiments, in the heating mode, the controller 600 is further configured to: obtain a real-time refrigerant temperature of the current indoor heat exchanger 340, determine the opening degree of the second throttling component 220 according to the target refrigerant temperature and the real-time refrigerant temperature in the current indoor heat exchanger 340. Obtain a real-time liquid pipe temperature of the current indoor heat exchanger 340, calculate the refrigerant supercooling degree according to the real-time liquid pipe temperature of the current indoor heat exchanger 340 and the real-time refrigerant temperature of the current indoor heat exchanger 340, and determine the opening degree of the indoor electronic expansion valve 330 according to the target supercooling degree and the refrigerant supercooling degree. Control the first throttling component 210 to be at the second preset opening degree.

[0224] It should be noted that the second preset opening degree can be the maximum opening degree of the first throttling component 210. In this way, the flow rate of the refrigerant flowing out of the indoor heat exchanger 340 is increased, thereby improving the heating effect of the indoor unit 300.

[0225] It can be understood that in the heating mode, the flow rate of the refrigerant flowing into the indoor heat exchanger 340 can be adjusted by adjusting the opening degree of the second throttling component 220, thereby adjusting the flow rate and pressure of the refrigerant in the indoor unit 300.

[0226] In some embodiments, the controller 600 is further configured to: in the heating mode, obtain a real-time refrigerant temperature in the current indoor heat exchanger 340 and a target refrigerant temperature. If it is determined that the real-time refrigerant temperature of the current indoor heat exchanger 340 is greater than the target refrigerant temperature, the opening degree of the second throttling component 220 is reduced; if it is determined that the real-time refrigerant temperature of the current indoor heat exchanger 340 is less than the target refrigerant temperature, the opening degree of the second throttling component 220 is increased; and if it is determined that the real-time refrigerant temperature of the current indoor heat exchanger 340 is equal to the target refrigerant temperature, the opening degree of the second throttling component 220 is kept unchanged.

[0227] For example, in the heating mode, the real-time refrigerant temperature of the current indoor heat exchanger 340 is denoted as T sat , and the target refrigerant temperature is denoted as Tco. That is, if it is determined that T sat > Tco, the controller 600 reduces the opening degree of the second throttling component 220 to reduce the refrigerant temperature. If it is determined that T sat < Tco, the controller 600 increases the opening degree of the second throttling component 220 to increase the refrigerant temperature. If it is determined that T sat = Tco, the controller 600 keeps the opening degree of the second throttling component 220 unchanged.

[0228] Referring to Table 6, taking room one and room two as examples, in the heating mode, it is assumed that the target set temperature T s of the two rooms is 26°C. The initial temperature in room one and room two at time 0 is the same, for example, 15°C. According to the relationship between ΔT(n) and T , the target refrigerant temperature T co of room one and room two at time 1, time 2, time 3, time 4, time 5, time 6, time 7, time 8, and time 9 is 41.4°C, 46.0°C; 40.0, 44.7°C; 38.2°C, 41.2°C; 36.9°C, 38.8°C; 35.6°C, 36.4°C; 34.3°C, 35.6°C; 33.2, 34.3°C; 33.2, 33.2°C; 33.2, 33.2°C, respectively. The controller 600 can obtain Tco at the current time, and control the opening degree of the indoor electronic expansion valve 330 according to the relationship between T sat and Tco.

[0229] Table 6 is an example of the change of the target refrigerant temperature taking room one and room two as examples.

[0230] Table 6

[0231] In some embodiments, the controller 600 is further configured to: if it is determined that the refrigerant supercooling degree is greater than the target supercooling degree, increase the opening degree of the indoor electronic expansion valve 330; if it is determined that the refrigerant supercooling degree is less than the target supercooling degree, decrease the opening degree of the indoor electronic expansion valve 330; and if it is determined that the refrigerant supercooling degree is equal to the target supercooling degree, keep the opening degree of the indoor electronic expansion valve 330 unchanged.

[0232] It can be understood that the refrigerant supercooling degree is calculated according to the real-time refrigerant temperature T sat of the current indoor heat exchanger 340 and the real-time liquid pipe temperature T l of the current indoor heat exchanger 340, and the refrigerant supercooling degree is denoted as SC, so SC = T sat - T lThe target supercooling degree is denoted as SCo, which can be preset or calculated. The preset or calculated target supercooling degree SCo can adopt the technology disclosed in the related art.

[0233] That is, if it is determined that SC>SCo, the controller 600 increases the opening degree of the indoor electronic expansion valve 330. If it is determined that SC<SCo, the controller 600 decreases the opening degree of the indoor electronic expansion valve 330. If it is determined that SC=SCo, the controller 600 keeps the opening degree of the indoor electronic expansion valve 330 unchanged.

[0234] In summary, the air conditioning system provided by some embodiments of the present disclosure has multiple advantages in solving the problem of over-adjustment of the indoor unit under small load conditions. First, by the first throttling component and the second throttling component in the refrigerant cutting component, the air conditioning system can accurately adjust the refrigerant flow and temperature, avoiding temperature fluctuations caused by excessive adjustment or insufficient adjustment. Second, by obtaining the temperature change rate of the indoor space and the degree of deviation from the target temperature, the target refrigerant temperature is generated, ensuring that the control target matches the current load and avoiding loss of user experience due to control action delay and thermal inertia. In addition, the air conditioning system optimizes adjustment according to the current load matching situation, improving energy utilization efficiency, thereby comprehensively optimizing the performance, comfort, and energy efficiency of the air conditioning system.

[0235] It should be noted that the refrigerant cutting component 200 not only can adjust the temperature of the refrigerant, but also can avoid refrigerant leakage. That is, the refrigerant cutting component 200 includes two functions. On the one hand, in the case of unbalanced load of each air conditioning room, the first throttling component and the second throttling component of the refrigerant cutting component 200 can adjust the temperature of the refrigerant flowing through the indoor unit 300 to match the load with the capacity of the indoor unit 300, thereby avoiding frequent start-stop of the indoor unit 300 and causing temperature fluctuations in the air conditioning room. On the other hand, in the case of refrigerant leakage of the indoor unit 300, the first throttling component 210 and the second throttling component 220 of the refrigerant cutting component 200 can be closed to avoid refrigerant leakage into the air conditioning room.

[0236] In some embodiments, the air conditioning system 1000 further includes a fourth sensor 500 (e.g., a refrigerant leakage sensor) installed in the air conditioning room. The fourth sensor 500 is configured to detect whether refrigerant leakage occurs in the air conditioning room. For example, the fourth sensor 500 is a non-dispersive infrared (NDIR) sensor.

[0237] Referring to FIG. 10, the first indoor unit 301 includes a first sub-sensor 501 configured to detect the refrigerant concentration in room one. The second indoor unit 302 includes a second sub-sensor 502 configured to detect the refrigerant concentration in room two. The third indoor unit 303 includes a third sub-sensor 503 configured to detect the refrigerant concentration in room three. The fourth indoor unit 304 includes a fourth sub-sensor 504 configured to detect the refrigerant concentration in room four.

[0238] The structures of the first sub-sensor 501, the second sub-sensor 502, the third sub-sensor 503, and the fourth sub-sensor 504 can refer to the above description of the fourth sensor 500.

[0239] In some embodiments, the fourth sensor 500 is communicatively connected with the indoor unit 300, and the controller 600 is coupled with the fourth sensor 500 through the indoor unit 300 to obtain the refrigerant concentration in the air-conditioning room. The controller 600 is further configured to close the first throttling component 210 and the second throttling component 220 in the refrigerant cutting component 200 corresponding to the indoor unit 300 if it is determined that the refrigerant concentration in the air-conditioning room is greater than a set threshold.

[0240] In some embodiments, the air-conditioning system 1000 further includes an alarm component, such as a buzzer. The buzzer is configured to issue an alarm information, such as sound, light, or electrical signal, etc. to remind the user if the refrigerant concentration in the air-conditioning room is greater than a set threshold.

[0241] Referring to FIG. 10, the first indoor unit 301 includes a first buzzer 401. The second indoor unit 302 includes a second buzzer 402. The third indoor unit 303 includes a third buzzer 403. The fourth indoor unit 304 includes a fourth buzzer 404.

[0242] In some embodiments, the controller 600 is further coupled with the buzzer. If the refrigerant leakage occurs in the indoor unit 300, the controller 600 controls the first throttling component 210 and the second throttling component 220 in the refrigerant cutting component 200 to close, and controls the buzzer to issue an alarm signal to remind the user.

[0243] For example, referring to FIGS. 9 and 10, the refrigerant leakage occurs in the first indoor unit 301, causing the refrigerant concentration in room one to be greater than a set threshold. At this time, the controller 600 can close the first sub-throttling component 12 and the second sub-throttling component 13 in the first refrigerant cutting component 201 corresponding to the first indoor unit 301, and alarm through the first buzzer 401.

[0244] To sum up, the air conditioning system provided by some embodiments of the present disclosure not only solves the problem of indoor unit over-regulation under small load conditions, but also can cut off the refrigerant in the refrigerant circulation loop in the case of refrigerant leakage, thereby improving the reliability of the air conditioning system.

[0245] Some embodiments of the present disclosure also provide another air conditioning system 1000, which is a three-pipe air conditioning system.

[0246] The three-pipe air conditioning system includes a plurality of air-cooled assemblies 700, which can be independently controlled and serve different rooms or areas. "Three-pipe" is a configuration of a variable frequency multi-split air conditioning system. The main feature of "three-pipe" is that it uses three pipes to connect the air-cooled assembly 700 and the outdoor unit 100, and the three pipes include the first gas pipe 60, the liquid pipe 103, and the second gas pipe 102. The first gas pipe 60 is configured to transport gaseous refrigerant, the liquid pipe 103 is configured to transport liquid refrigerant, and the second gas pipe 102 can transport high-pressure gaseous refrigerant or low-pressure gaseous refrigerant depending on the working mode and working condition of the air conditioning system 1000.

[0247] The three-pipe air conditioning system can more flexibly adjust the refrigeration or heating needs of each air-cooled assembly 700. Through independent control of the three pipes, the air conditioning system 1000 can improve energy recovery efficiency and thus improve energy efficiency.

[0248] The three-pipe air conditioning system is commonly used in large buildings such as office buildings, hotels, and hospitals. The three-pipe air conditioning system can meet complex and diversified air conditioning needs and is suitable for large building environments that require independent control of multiple spaces.

[0249] The structure of the air conditioning system 1000 will be introduced below taking the three-pipe air conditioning system as an example.

[0250] In some embodiments, referring to FIG. 12, the air conditioning system 1000 includes an outdoor unit 100. The structure of the outdoor unit 100 is similar to that of some embodiments described above. The structures of the compressor 1, the gas-liquid separator 3, the outdoor heat exchanger 6, the outdoor electronic expansion valve 7, and the outdoor fan 5 provided in the outdoor unit 100 can refer to the descriptions in some embodiments described above, and will not be described here again.

[0251] It should be noted that when the same system architecture is adopted, the number of outdoor units 100 in the air conditioning system 1000 can also be expanded to multiple, and the multiple outdoor units 100 can operate in a grouped manner.

[0252] In some embodiments, the outdoor unit 100 includes two switching valves, namely a first switching valve 104 and a second switching valve 105. For example, the first switching valve 104 and the second switching valve 105 are four-way valves.

[0253] In some embodiments, the air conditioning system 1000 further comprises an air-cooled assembly 700. The air-cooled assembly 700 is in communication with the outdoor unit 100. The air-cooled assembly 700 refers to a terminal device that uses a fan to suck indoor air and exchanges heat between the indoor air and an air-cooled assembly heat exchanger. The air-cooled assembly 700 blows the processed air into the indoor to achieve the purpose of cooling, dehumidifying, etc.

[0254] The outdoor unit 100 can perform heating operation or cooling operation on the outdoor side to provide energy for increasing indoor temperature or energy for reducing indoor temperature to the air-cooled assembly 700. The air-cooled assembly 700 performs cooling operation or heating operation using the energy for increasing indoor temperature or the energy for reducing indoor temperature generated by the outdoor unit 100.

[0255] It should be noted that the number of air-cooled assemblies 700 is not limited in the present disclosure, and two or more air-cooled assemblies 700 can be arranged in one air conditioning system 1000. The air-cooled assembly 700 can be arranged in the same way as the air-cooled assembly 700 in FIG. 12. The following describes an example in which the air conditioning system 1000 comprises one air-cooled assembly 700.

[0256] The structure and function of the air-cooled assembly 700 are described below.

[0257] In some embodiments, the air-cooled assembly 700 comprises an air-cooled assembly heat exchanger 211. The first end of the air-cooled assembly heat exchanger 211 is in communication with the second end of the outdoor heat exchanger 6, and the second end of the air-cooled assembly heat exchanger 211 is in communication with the compressor 1.

[0258] In some embodiments, the air-cooled assembly heat exchanger 211 comprises a first sub-air-cooled assembly heat exchanger 2011, and the second end of the first sub-air-cooled assembly heat exchanger 2011 is in communication with the compressor 1 through the first four-way valve 104.

[0259] In some embodiments, the air-cooled assembly heat exchanger 211 further comprises a second sub-air-cooled assembly heat exchanger 2012, and the second end of the second sub-air-cooled assembly heat exchanger 2012 is in communication with the compressor 1 through the second four-way valve 105.

[0260] When the air-cooled assembly heat exchanger 211 is used as a condenser, the air-cooled assembly 700 is used as a heater in heating mode. When the air-cooled assembly heat exchanger 211 is used as an evaporator, the air-cooled assembly 700 is used as a cooler in cooling mode.

[0261] In some embodiments, the air conditioning system 1000 further comprises a throttling component, which can be arranged in at least one of the outdoor unit 100 or the air-cooled assembly 700. The throttling component is configured to reduce the pressure of the refrigerant and expand the refrigerant.

[0262] In some embodiments, the throttling component comprises an outdoor electronic expansion valve 7, which is arranged in the outdoor unit 100. The outdoor electronic expansion valve 7 is connected to the second end of the outdoor heat exchanger 6.

[0263] In some embodiments, the throttling component further comprises an air-cooled assembly electronic expansion valve 213, which is arranged in the air-cooled assembly 700. The air-cooled assembly electronic expansion valve 213 is connected to the air-cooled assembly heat exchanger 211, and the air-cooled assembly electronic expansion valve 213 is arranged correspondingly to the air-cooled assembly heat exchanger 211. For example, the air-cooled assembly electronic expansion valve 213 is arranged at the first end of the air-cooled assembly heat exchanger 211.

[0264] In some embodiments, the air-cooled assembly electronic expansion valve 213 comprises a first sub-air-cooled assembly electronic expansion valve 2031, which is arranged at the first end of the first sub-air-cooled assembly heat exchanger 2011.

[0265] In some embodiments, the air-cooled assembly electronic expansion valve 213 further comprises a second sub-air-cooled assembly electronic expansion valve 2032, which is arranged at the first end of the second sub-air-cooled assembly electronic expansion valve 2032.

[0266] In some embodiments, the air-cooled assembly 700 further comprises an air-cooled assembly fan 730. The air-cooled assembly fan 730 can be arranged close to the air-cooled assembly heat exchanger 211. The air-cooled assembly fan 730 can be an axial fan, a cross-flow fan, or other forms of fan.

[0267] In some embodiments, the first sub-air-cooled assembly heat exchanger 2011 and the second sub-air-cooled assembly heat exchanger 2012 can share one air-cooled assembly fan 730.

[0268] In some embodiments, the air-cooled assembly 700 comprises two air-cooled assembly fans 730, which are a first sub-air-cooled assembly fan and a second sub-air-cooled assembly fan, respectively. The first sub-air-cooled assembly fan is arranged correspondingly to the first sub-air-cooled assembly heat exchanger 2011, and the second sub-air-cooled assembly fan is arranged correspondingly to the second sub-air-cooled assembly heat exchanger 2012.

[0269] In some embodiments, the air conditioning system 1000 further comprises a liquid pipe 103, which is arranged between the first end of the air-cooled assembly heat exchanger 211 and the second end of the outdoor heat exchanger 6. The first end of the liquid pipe 103 is communicated with the second end of the outdoor heat exchanger 6, and the second end of the liquid pipe 103 is communicated with the first end of the air-cooled assembly heat exchanger 211.

[0270] In some embodiments, the air conditioning system 1000 further comprises a first gas pipe 101 (e.g., a gas pipe) disposed between the first sub-air cooled component heat exchanger 2011 and the compressor 1. A first end of the first gas pipe 101 is connected to a second end of the first sub-air cooled component heat exchanger 2011, and a second end of the first gas pipe 101 is connected to the first four-way valve 104 and the compressor 1 through the first four-way valve 104.

[0271] Different from some of the above embodiments, in addition to the first gas pipe 101 and the liquid pipe 103, the air conditioning system 1000 further comprises a second gas pipe 102 (e.g., a high-low pressure gas pipe). The second gas pipe 102 is disposed between the second sub-air cooled component heat exchanger 2012 and the compressor 1. A first end of the second gas pipe 102 is connected to a second end of the second sub-air cooled component heat exchanger 2012, and a second end of the second gas pipe 102 is connected to the second four-way valve 105 and the compressor 1 through the second four-way valve 105.

[0272] The liquid pipe 103, the first gas pipe 101, and the second gas pipe 102 are connected between the outdoor unit 100 and the air cooled component 700 to form a refrigerant circulation loop. The liquid pipe 103, the first gas pipe 101, and the second gas pipe 102 are configured to flow refrigerant in the refrigerant circulation loop.

[0273] In some embodiments, the air conditioning system 1000 further comprises a liquid pipe stop valve 63 disposed in the liquid pipe 103, and the liquid pipe stop valve 63 is located between the air cooled component electronic expansion valve 213 and the outdoor electronic expansion valve 7.

[0274] In some embodiments, the air conditioning system 1000 further comprises a first gas pipe stop valve 61 disposed in the first gas pipe 101.

[0275] In some embodiments, the air conditioning system 1000 further comprises a second gas pipe stop valve 62 disposed in the second gas pipe 102.

[0276] In some embodiments, the air conditioning system 1000 further comprises a water module 800. In the field of air conditioning, the "water module" generally refers to a water module unit, which is an important component in a central air conditioning system. The water module 800 can exchange heat between the high-temperature and high-pressure refrigerant discharged by the compressor 1 and water, thereby transferring the heat energy of the refrigerant to the water, and using the heated water for applications such as floor heating, heating, or hot water supply.

[0277] In cold climate conditions, especially in the heating season, the temperature of the external air is low, and the heating efficiency using the traditional air-cooled assembly 700 is relatively low, and even cannot meet the heating demand. In contrast, using the water module 800 for heating can utilize the heat energy of the high-temperature and high-pressure refrigerant discharged by the compressor 1, thereby achieving the purpose of low-temperature heating. In this way, the heating effect of the air conditioning system 1000 in cold climate conditions is improved.

[0278] In some embodiments, the water module 800 includes a water module heat exchanger 311 configured to exchange heat between the high-temperature and high-pressure refrigerant discharged by the compressor 1 and water.

[0279] In some embodiments, the water module 800 includes a water module electronic expansion valve 312 configured to control the flow of refrigerant, thereby adjusting the temperature of the refrigerant.

[0280] In some embodiments, the air conditioning system 1000 further includes a first branch 70 (for example, an air side branch), a first end of the first branch 70 being communicated with the second air pipe 102, and a second end of the first branch 70 being communicated with the water module heat exchanger 311.

[0281] In some embodiments, the air conditioning system 1000 further includes a second branch 80 (for example, a liquid side branch), a first end of the second branch 80 being communicated with the water module heat exchanger 311, and a second end of the second branch 80 being communicated with the liquid pipe 103.

[0282] The water module 800 is communicated with the outdoor unit 100 through the first branch 70 and the second branch 80.

[0283] The following introduces the refrigerant circulation loop of the three-pipe air conditioning system in the cooling mode in combination with FIG. 13. In the cooling mode, the air-cooled assembly 700 is in cooling operation, and the water module 800 can be closed.

[0284] Referring to FIG. 13, in the cooling mode, the liquid pipe stop valve 63 is in the open valve state, the first air pipe stop valve 61 is in the open valve state, and the second air pipe stop valve 62 is in the open valve state. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the outdoor heat exchanger 6 through the first switching valve 104, and is condensed into high-temperature and high-pressure liquid refrigerant in the outdoor heat exchanger 6. The high-temperature and high-pressure liquid refrigerant flows out from the outdoor electronic expansion valve 7, enters the air-cooled assembly 700 through the liquid pipe 103. After entering the air-cooled assembly 700, the high-temperature and high-pressure liquid refrigerant is divided into two paths, one path flows through the first sub-air-cooled assembly electronic expansion valve 2031 into the first sub-air-cooled assembly heat exchanger 2011, and the other path flows through the second sub-air-cooled assembly electronic expansion valve 2032 into the second sub-air-cooled assembly heat exchanger 2012.

[0285] In this process, the high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure two-phase refrigerant (for example, liquid phase and gas phase) by the outdoor electronic expansion valve 7, the first sub-air-cooled assembly electronic expansion valve 2031 and the second sub-air-cooled assembly electronic expansion valve 2032. The low-temperature and low-pressure two-phase refrigerant is evaporated into low-temperature and low-pressure gaseous refrigerant in the first sub-air-cooled assembly heat exchanger 2011 and the second sub-air-cooled assembly heat exchanger 2012.

[0286] The low-temperature and low-pressure gaseous refrigerant flows out of the first sub-air-cooled assembly heat exchanger 2011 and the second sub-air-cooled assembly heat exchanger 2012, respectively. The low-temperature and low-pressure gaseous refrigerant flowing out of the first sub-air-cooled assembly heat exchanger 2011 returns to the outdoor unit 100 through the first gas pipe 101, and then flows into the gas-liquid separator 3 through the first switching valve 104. The low-temperature and low-pressure gaseous refrigerant flowing out of the second sub-air-cooled assembly heat exchanger 2012 returns to the outdoor unit 100 side through the second gas pipe 102, and then flows into the gas-liquid separator 3 through the second switching valve 105. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 returns to the suction port of the compressor 1, and thus the refrigeration cycle of the air conditioning system 1000 is completed.

[0287] It should be noted that during the refrigeration cycle, the water module electronic expansion valve 312 is in a closed state to prevent the water module 800 from malfunctioning due to excessively low temperature.

[0288] The refrigerant circulation loop of the three-pipe air conditioning system 1000 in the first heating mode is introduced below in conjunction with FIG. 14. In the first heating mode, the air-cooled assembly 700 and the water module 800 are simultaneously turned on for heating operation.

[0289] Referring to FIG. 14, in the first heating mode, the liquid pipe stop valve 63 is in an open valve state, the second gas pipe stop valve 62 is in an open valve state, and the first gas pipe stop valve 61 is in an open valve state. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 is divided into two paths, one of which enters the first sub-air-cooled assembly heat exchanger 2011 through the first switching valve 104 and the first gas pipe 101, and the other of which is divided into two paths again after passing through the second switching valve 105. One of the two paths enters the second sub-air-cooled assembly heat exchanger 2012 through the second gas pipe 102, and the other of the two paths flows to the water module heat exchanger 311 through the second gas pipe 102 and the first branch 70.

[0290] The high-temperature and high-pressure gaseous refrigerant is condensed into high-temperature and high-pressure liquid refrigerant in the first sub-air-cooled assembly heat exchanger 2011, the second sub-air-cooled assembly heat exchanger 2012 and the water module heat exchanger 311. The high-temperature and high-pressure liquid refrigerant flows out of the air-cooled assembly 700 through the first sub-air-cooled assembly electronic expansion valve 2031 and the second sub-air-cooled assembly electronic expansion valve 2032, and then converges with the refrigerant passing through the water module electronic expansion valve 312.

[0291] The refrigerant after the confluence flows to the outdoor electronic expansion valve 7, and becomes low-temperature and low-pressure refrigerant after throttling by the outdoor electronic expansion valve 7. The low-temperature and low-pressure refrigerant flows to the outdoor heat exchanger 6, and evaporates into low-temperature and low-pressure gaseous refrigerant in the outdoor heat exchanger 6. The low-temperature and low-pressure gaseous refrigerant flows into the gas-liquid separator 3 through the first switching valve 104, and the low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the heating cycle of the air conditioning system 1000 is completed.

[0292] Referring to FIG. 14, the first sub-air-cooled assembly electronic expansion valve 2031, the second sub-air-cooled assembly electronic expansion valve 2032, and the water module electronic expansion valve 312 are in the open state and the opening degree is adjustable. In this way, the heating effect of the air-cooled assembly 700 and the water module 800 is improved.

[0293] The refrigerant circulation loop of the three-pipe air conditioning system 1000 in the second heating mode is described below in combination with FIG. 14. In the second heating mode, the water module 800 independently opens the heating mode. The air-cooled assembly 700 can be in the closed state.

[0294] Referring to FIG. 15, in the second heating mode, the liquid pipe stop valve 63, the second gas pipe stop valve 62, and the first gas pipe stop valve 61 are in the closed state. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 flows to the water module heat exchanger 311 after passing through the second switching valve 105. The high-temperature and high-pressure gaseous refrigerant condenses into high-temperature and high-pressure liquid refrigerant in the water module heat exchanger 311. The high-temperature and high-pressure liquid refrigerant flows to the outdoor electronic expansion valve 7 after passing through the water module electronic expansion valve 312, and becomes low-temperature and low-pressure refrigerant after passing through the outdoor electronic expansion valve 7. The low-temperature and low-pressure refrigerant flows to the outdoor heat exchanger 6, and evaporates into low-temperature and low-pressure gaseous refrigerant in the outdoor heat exchanger 6. The low-temperature and low-pressure gaseous refrigerant flows into the gas-liquid separator 3 after passing through the first switching valve 104. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the independent heating cycle of the water module 800 is completed. Since the refrigerant charge of the air conditioning system 1000 is calculated according to the load of the air conditioning system 1000 and the performance data of the selected refrigerant, and a certain margin is also considered to ensure the stable operation of the air conditioning system under extreme working conditions, in the case that the water module 800 independently opens the heating mode, there can be more refrigerant allocated in the air-cooled assembly 700, resulting in insufficient heating capacity of the water module 800 and failing to reach the ideal set temperature within the expected time. At this time, if the refrigerant is directly prevented from entering the air-cooled assembly 700, it will also result in too much refrigerant circulating in the water module 800. Too much refrigerant circulating will result in high overall pressure of the air conditioning system 1000. In the case of high overall pressure of the air conditioning system, the compressor 1 will automatically reduce the frequency of operation, which will also result in reduced heat in the water module 800, causing fluctuations in the indoor temperature.

[0295] To solve this problem, in some embodiments, the air conditioning system 1000 further comprises a first gas pipe regulating valve 109, which is arranged in the first gas pipe 101. For example, the first gas pipe regulating valve 109 is located between the gas pipe stop valve 61 and the first switching valve 104.

[0296] In some embodiments, the air conditioning system further comprises a second gas pipe regulating valve 108, which is arranged in the second gas pipe 102. For example, the second gas pipe regulating valve 108 is located between the second gas pipe stop valve 62 and the second switching valve 105. The inlet of the first branch 70 of the water module 800 is located between the second gas pipe regulating valve 108 and the second switching valve 105.

[0297] In some embodiments, the first gas pipe regulating valve 109 is an electronic expansion valve.

[0298] In some embodiments, the first gas pipe regulating valve 109 is a pneumatic ball valve.

[0299] In some embodiments, referring to FIG. 17, the first gas pipe regulating valve 109 is a first gas pipe solenoid valve 110. The air conditioning system 1000 further comprises a first pressure reducer 111, and the first gas pipe solenoid valve 110 is connected in series with the first pressure reducer 111. The first pressure reducer 111 can be arranged between the first gas pipe stop valve 61 and the first gas pipe solenoid valve 110.

[0300] In some embodiments, the second gas pipe regulating valve 108 is an electronic expansion valve.

[0301] In some embodiments, the second gas pipe regulating valve 108 is a pneumatic ball valve.

[0302] In some embodiments, referring to FIG. 17, the second gas pipe regulating valve 108 is a second gas pipe solenoid valve 112. The air conditioning system 1000 further comprises a second pressure reducer 113, and the second gas pipe solenoid valve 112 is connected in series with the second pressure reducer 113. The second pressure reducer 113 can be arranged between the second gas pipe stop valve 62 and the second gas pipe solenoid valve 112.

[0303] In some embodiments, referring to FIGS. 12 and 16, the three-pipe air conditioning system further comprises a controller 600, which is coupled with the air-cooled assembly electronic expansion valve 213, the first gas pipe regulating valve 109, and the second gas pipe regulating valve 108. The controller 600 is configured to, under the condition that only the water module 800 is in heating operation and the discharge pressure of the compressor 1 deviates from a preset discharge pressure interval, adjust the opening degree of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 from a preset opening degree until the discharge pressure of the compressor 1 is within the preset discharge pressure interval.

[0304] In some embodiments, the preset opening degree can be the minimum opening degree (e.g., close to 0 opening degree) of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108.

[0305] In some embodiments, the preset opening degree can be calculated under experimental conditions, and the preset opening degree can enable the air conditioning system 1000 to operate stably when only the water module 800 is in heating operation.

[0306] Some embodiments of the present disclosure can keep the discharge pressure of the partial refrigerant compressor 1 within the preset discharge pressure range by automatically adjusting the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108, avoid excessive or insufficient refrigerant from entering the water module 800, improve the refrigeration or heating efficiency of the air conditioning system 1000, keep the temperature of the water module 800 within the preset range, and thus improve the use comfort of the air conditioning system 1000.

[0307] In some embodiments, the controller 600 is further configured to: when the conditions that only the water module is in heating operation, the duration of keeping only the water module in heating operation is greater than or equal to the first set duration, and the discharge pressure of the compressor 1 is greater than the upper threshold of the preset discharge pressure range are met, increase the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 from the preset opening degree until the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure range.

[0308] In some embodiments, the controller 600 is further configured to: if it is determined that the discharge pressure of the compressor 1 is greater than or equal to the preset pressure threshold, control the compressor 1 to operate at a reduced frequency.

[0309] In some embodiments, the upper threshold of the preset discharge pressure range is less than the preset pressure threshold.

[0310] It should be noted that when the air conditioning system 1000 is just started or the load changes, the refrigerant pressure will change accordingly, and then pressure fluctuation will occur, which will affect the accuracy of the control of the air conditioning system 1000. Therefore, after determining that the duration of the water module in heating operation is greater than or equal to the first set duration, it is further determined whether the discharge pressure of the compressor 1 is greater than the upper threshold of the preset discharge pressure range, and the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 are adjusted according to the determination result. In this way, it can be avoided that when only the water module 800 is in heating operation, the pressure of the air conditioning system 1000 is too high to cause the compressor 1 to operate at a reduced frequency.

[0311] It can be understood that, on the one hand, the air conditioning system 1000 needs to make part of the refrigerant enter the air-cooled component heat exchanger to prevent the amount of refrigerant in the water module heat exchanger from being too much. On the other hand, the air conditioning system 1000 also needs to avoid too much refrigerant entering the air-cooled component heat exchanger to prevent the amount of refrigerant in the water module heat exchanger 311 from being too little. Therefore, in some embodiments, the controller 600 is also configured to: after the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure range, obtain a preset intervention target supercooling degree, and obtain the current supercooling degree of the air-cooled component heat exchanger 211.

[0312] In some embodiments, the controller 600 is also configured to: if it is determined that the current supercooling degree deviates from the intervention target supercooling degree, adjust the opening degree of the air-cooled component electronic expansion valve 213 to make the current supercooling degree transition to the intervention target supercooling degree. That is, to make the current supercooling degree equal to the intervention target supercooling degree.

[0313] It should be noted that the current supercooling degree is the difference between the second sensor 506 arranged on one side of the communication liquid pipe of the air-cooled component heat exchanger 211 and the saturation temperature corresponding to the discharge pressure of the compressor 1.

[0314] In some embodiments, the intervention target supercooling degree can be set according to the reference design manual or industry standard first, and then tested for the influence of the intervention target supercooling degree on performance when only the water module works, and adjusted as needed. Further, the change of the current supercooling degree under different working conditions is observed, and the applicability of the intervention target supercooling degree is evaluated. Thereafter, the performance and operation data of the air-cooled component heat exchanger 211 are checked regularly, and whether the intervention target supercooling degree needs to be adjusted is analyzed according to the checking result.

[0315] In some embodiments, the intervention target supercooling degree can be predicted by a prediction model according to the load change of the water module 800, the running state of the compressor 1 and the adjustment of the air conditioning system.

[0316] The main features of the water module 800, such as the set temperature of the water module 800, the inlet temperature of the water module heat exchanger 311, the outlet temperature of the water module heat exchanger 311, the operating frequency of the compressor 1, the discharge pressure of the compressor 1, the opening degree of the first gas pipe regulating valve 109, the opening degree of the second gas pipe regulating valve 108, and the corresponding intervention target supercooling degree (e.g. manually obtained by the method provided in some embodiments described above) can be collected and preprocessed under experimental conditions. The collected data is divided into a training set and a test set, and a linear regression model, a support vector regression, an ensemble learning model, etc. are selected for modeling. The selected model is trained using the training set, and the model parameters are optimized to maximize the prediction accuracy. After that, the performance of the trained model is evaluated using the test set, and after training and verification are completed, the set temperature of the water module 800 is used as input to accurately predict the intervention target supercooling degree that matches the current load of the air conditioning system 1000, so that after the opening degree of the first gas pipe regulating valve 109 and the opening degree of the second gas pipe regulating valve 108 are determined, the opening degree of the air-cooled component electronic expansion valve 213 can be accurately determined. In this way, when only the water module is operating in heating mode, the refrigerant distribution of the entire air conditioning system 1000 is reasonably allocated, and the performance and energy efficiency of the air conditioning system 1000 are improved.

[0317] In some embodiments, the controller 600 is further configured to: after the discharge pressure of the compressor 1 decreases to less than the upper threshold of the preset discharge pressure range, obtain a preset intervention target supercooling degree, and obtain the current supercooling degree of the air-cooled component heat exchanger 211. If it is determined that the current supercooling degree is greater than the intervention target supercooling degree, the opening degree of the air-cooled component electronic expansion valve 213 is increased so that the current supercooling degree transitions to the intervention target supercooling degree. If it is determined that the current supercooling degree is less than the intervention target supercooling degree, the opening degree of the air-cooled component electronic expansion valve 213 is decreased so that the current supercooling degree transitions to the intervention target supercooling degree.

[0318] It can be understood that, since the multi-split air conditioning system is a complex multivariate system, even under the condition that the intervention target supercooling degree is calculated by the prediction model, it cannot be ensured that the pressure of the multi-split air conditioning system does not fluctuate during long-term operation. When the air conditioning system 1000 is used as a heat source for floor heating, the air conditioning system 1000 needs to operate stably over a long period of time.

[0319] To this end, in some embodiments, the controller 600 is further configured to, after the discharge pressure of the compressor 1 decreases to be less than the preset discharge pressure range upper threshold, keep the opening degrees of the adjusted first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 unchanged. Under the condition that only the water module 800 is in heating operation, the time length for keeping only the water module 800 in heating operation is greater than or equal to the second set time length, and the discharge pressure of the compressor 1 deviates from the preset discharge pressure range again, the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 are adjusted again from the adjusted opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108, until the discharge pressure of the compressor 1 is within the preset discharge pressure range.

[0320] For example, the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 are reduced from the adjusted opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108, until the discharge pressure of the compressor 1 is greater than or equal to the lower threshold of the preset discharge pressure range. At this time, the discharge pressure of the compressor 1 is within the preset discharge pressure range.

[0321] Some embodiments of the present disclosure also provide yet another air conditioning system, which is a two-pipe air conditioning system.

[0322] Referring to FIG. 18, the two-pipe air conditioning system includes the outdoor unit 100, the air-cooled assembly 700, and the water module 800. The compressor 1 is arranged in the outdoor unit 100, the air-cooled assembly heat exchanger 211 is arranged in the air-cooled assembly 700, and the air-cooled assembly electronic expansion valve 213 is correspondingly arranged. The difference from the three-pipe air conditioning system is that the outdoor unit 100 and the air-cooled assembly 700 are connected through the first gas pipe 101 and the liquid pipe 103, and the water module 800 is connected with the outdoor unit 100 through the first branch 70 and the second branch 80.

[0323] In some embodiments, the two-pipe air conditioning system further includes the first gas pipe regulating valve 109. The first gas pipe regulating valve 109 is arranged in the first gas pipe 101.

[0324] In some embodiments, referring to FIG. 19, the two-pipe air conditioning system further includes the controller 600, which is coupled with the air-cooled assembly electronic expansion valve 213 and the first gas pipe regulating valve 109. The controller 600 is configured to, under the condition that only the water module 800 is in heating operation and the discharge pressure of the compressor 1 deviates from the preset discharge pressure range, adjust the opening degree of the first gas pipe regulating valve 109 from the preset opening degree, until the discharge pressure of the compressor 1 is within the preset discharge pressure range.

[0325] In some embodiments, the controller 600 in the two-pipe air conditioning system is further configured to: after the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure interval, obtain a preset intervention target supercooling degree, and obtain a current supercooling degree of the air-cooled component heat exchanger 211; and when the current supercooling degree deviates from the intervention target supercooling degree, adjust the opening degree of the air-cooled component electronic expansion valve 213, so that the current supercooling degree transitions to the intervention target supercooling degree.

[0326] In some embodiments, the controller 600 in the two-pipe air conditioning system is further configured to: after the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure interval, obtain a preset intervention target supercooling degree, and obtain a current supercooling degree of the air-cooled component heat exchanger 211; and when the current supercooling degree deviates from the intervention target supercooling degree, adjust the opening degree of the air-cooled component electronic expansion valve 213, so that the current supercooling degree transitions to the intervention target supercooling degree.

[0327] In some embodiments, the controller 600 in the two-pipe air conditioning system is further configured to: after the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure interval, obtain a preset intervention target supercooling degree, and obtain a current supercooling degree of the air-cooled component heat exchanger 211; and when the current supercooling degree deviates from the intervention target supercooling degree, adjust the opening degree of the air-cooled component electronic expansion valve 213, so that the current supercooling degree transitions to the intervention target supercooling degree.

[0328] In some embodiments, the controller 600 in the two-pipe air conditioning system is further configured to: after the discharge pressure of the compressor 1 is reduced to be less than the upper threshold of the preset discharge pressure interval, maintain the adjusted opening degree of the first air pipe regulating valve 109 unchanged; when the conditions of only the water module 800 operating in heating mode, the time length of only the water module 800 operating in heating mode being greater than or equal to a second set time length, and the discharge pressure of the compressor 1 deviating from the preset discharge pressure interval again are met, adjust the opening degree of the first air pipe regulating valve 109 again from the adjusted opening degree of the first air pipe regulating valve 109, until the discharge pressure of the compressor 1 is within the preset discharge pressure interval.

[0329] In some embodiments, the first air pipe regulating valve 109 in the two-pipe air conditioning system is an electronic expansion valve, which is arranged between the first air pipe stop valve 61 and the first switching valve 104.

[0330] Some embodiments of the present disclosure also provide a control method of an air conditioning system 1000.

[0331] Referring to FIG. 20, the method comprises S101 to S105.

[0332] S101, determine whether only the water module 800 is operating in heating mode. If so, execute S102, and if not, execute S103.

[0333] S102, determine whether the discharge pressure of the compressor 1 deviates from the preset discharge pressure range. If so, execute S104, and if not, execute S103.

[0334] S103, maintain the current operating state unchanged.

[0335] S104, adjust the opening degree of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 from the preset opening degree.

[0336] S105, determine whether the discharge pressure of the compressor 1 is within the preset discharge pressure range. If so, end the process, and if not, execute S104.

[0337] Referring to FIG. 21, the method further comprises S201 to S206.

[0338] S201, determine whether only the water module 800 is operating in heating mode. If so, execute S202, and if not, execute S203.

[0339] S202, determine whether the duration of the water module 800 operating in heating mode is greater than or equal to a first set duration. If so, execute S204, and if not, re-execute S201.

[0340] S203, maintain the current operating state unchanged.

[0341] S204, determine whether the discharge pressure of the compressor 1 is greater than the upper threshold of the preset discharge pressure range. If so, execute S205, and if not, execute S203.

[0342] S205, adjust the opening degree of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 from the preset opening degree.

[0343] S206, determine whether the discharge pressure of the compressor 1 is reduced to be less than or equal to the upper threshold of the preset discharge pressure range. If so, end the process, and if not, execute S205.

[0344] Referring to FIG. 22, after step S206, the method further comprises S301 to S303.

[0345] S301, obtain the preset intervention target supercooling degree of the air cooling assembly.

[0346] S302, determine whether the current supercooling degree of the air cooling assembly 700 deviates from the intervention target supercooling degree. If so, execute S303, and if not, end the process.

[0347] S303, adjust the opening degree of the electronic expansion valve 213 of the air cooling assembly to make the current supercooling degree of the air cooling assembly 700 transition to the intervention target supercooling degree.

[0348] Referring to FIG. 23, the method comprises S401 to S414.

[0349] S401, determine whether only the water module 800 is in heating operation. If yes, execute S402, and if no, execute S403.

[0350] S402, determine whether the duration of the heating operation of the water module 800 is greater than or equal to a first set duration. If yes, execute S404, and if no, re-execute S401.

[0351] S403, keep the current operation state unchanged.

[0352] S404, determine whether the discharge pressure of the compressor 1 is within a preset discharge pressure range. If yes, execute S405, and if no, execute S406.

[0353] S405, adjust the opening degrees of the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 from the closed state.

[0354] S406, the first gas pipe regulating valve 109 and the second gas pipe regulating valve 108 are in the closed state.

[0355] S407, determine whether the discharge pressure of the compressor 1 is reduced to be less than or equal to the upper threshold value of the preset discharge pressure range. If yes, execute S408, and if no, execute S405.

[0356] S408, obtain the current supercooling degree of the air cooling assembly of the preset intervention target supercooling degree.

[0357] S409, determine whether the current supercooling degree of the air cooling assembly 700 deviates from the intervention target supercooling degree. If yes, execute S410, and if no, execute S406.

[0358] S410, adjust the opening degree of the electronic expansion valve 213 of the air cooling assembly to make the current supercooling degree of the air cooling assembly 700 transition to the intervention target supercooling degree.

[0359] S411, determine whether only the water module 800 is in heating operation. If yes, execute S412, and if no, re-execute S406.

[0360] S412, determine whether the duration of the heating operation of the water module 800 is greater than or equal to a second set duration. If yes, execute S413, and if no, re-execute S411.

[0361] S413, determine whether the discharge pressure of the compressor 1 is reduced to less than the lower threshold of the preset discharge pressure range. If yes, perform S414, if not, perform S406.

[0362] S414, reduce the opening degree of the first and second gas pipe regulating valves 109 and 108 from the adjusted opening degree.

[0363] When the outdoor unit of the air conditioning system operates as an evaporator in an outdoor environment with high humidity or low temperature, the outdoor heat exchanger is prone to frosting. Frosting increases the wind resistance and heat transfer resistance, and the heat exchange effect of the unit is deteriorated, and the capacity is gradually reduced. In order to ensure the continuous heating of the unit, the unit has to enter the defrosting control.

[0364] The traditional air conditioning system generally adopts the reverse defrosting method, that is, the switching of the unit from heating operation to refrigeration operation is realized by reversing the four-way valve. The outdoor heat exchanger is switched from the evaporator to the condenser, and the heat dissipation of the compressor and the heat absorption of the indoor unit together provide the outdoor heat exchanger with defrosting. This method only needs to reverse the four-way valve when the defrosting condition is reached. The disadvantage of this defrosting method is that during the defrosting operation, the air conditioning system not only cannot supply heat to the indoor side, but also needs to absorb heat from the indoor side to lower the indoor temperature. Therefore, the air conditioning system needs to start the heating mode to increase the indoor temperature after defrosting. In this way, the defrosting time is long, and the comfort of the indoor side is reduced.

[0365] Some embodiments of the present disclosure also provide another air conditioning system to improve the traditional defrosting method.

[0366] Referring to FIG. 24, the difference between the air conditioning system and the above-mentioned some embodiments is that the outdoor unit 100 of the air conditioning system 1000 includes two outdoor heat exchangers, and one end of the two outdoor heat exchangers is connected to the inlet of the compressor 1 through a pipeline, so that part of the high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 can enter the two outdoor heat exchangers for defrosting.

[0367] In some embodiments, the outdoor heat exchanger 6 includes a first sub-heat exchanger 610, and a first port of the first sub-heat exchanger 610 is connected to an outdoor throttling component, such as an outdoor electronic expansion valve 7. The second port of the first sub-heat exchanger 610 is connected to the outlet of the compressor 1 and the inlet of the compressor 1 through a pipeline, respectively.

[0368] In some embodiments, the outdoor heat exchanger 6 further includes a second sub-heat exchanger 620, and a first port of the second sub-heat exchanger 620 is connected to the outdoor electronic expansion valve 7. The second port of the second sub-heat exchanger 620 is connected to the outlet of the compressor 1 and the inlet of the compressor 1 through a pipeline, respectively.

[0369] In some embodiments, the outdoor unit 100 further comprises a first switch 701, the second port of the first sub-cooler 610 is connected to the outlet of the compressor 1 through the first switch 701.

[0370] In some embodiments, the outdoor unit 100 further comprises a third switch 703, the second port of the first sub-cooler 610 is connected to the inlet of the compressor 1 through the third switch 703.

[0371] In some embodiments, the outdoor unit 100 further comprises a second switch 702, the second port of the second sub-cooler 620 is connected to the outlet of the compressor 1 through the second switch 702.

[0372] In some embodiments, the outdoor unit 100 further comprises a fourth switch 704, the second port of the second sub-cooler 620 is connected to the inlet of the compressor 1 through the fourth switch 704.

[0373] In some embodiments, the outdoor fan 5 comprises a first sub-fan 510, the first sub-fan 510 is arranged corresponding to the first sub-cooler 610.

[0374] In some embodiments, the outdoor fan 5 further comprises a second sub-fan 520, the second sub-fan 520 is arranged corresponding to the second sub-cooler 620.

[0375] In some embodiments, the outdoor unit 100 and the indoor unit 300 are connected through the first gas pipe stop valve 61 and the liquid pipe stop valve 63.

[0376] That is, the first ports of the first sub-cooler 610 and the second sub-cooler 620 are connected with the outdoor electronic expansion valve 7, the second ports of the first sub-cooler 610 and the second sub-cooler 620 are connected to the outlet of the compressor 1 through the first switch 701 and the second switch 702 respectively, and the second ports of the first sub-cooler 610 and the second sub-cooler 620 are connected to the inlet of the compressor 1 through the third switch 703 and the fourth switch 704 respectively.

[0377] In some embodiments, when defrosting the first sub-cooler 610, the first switch 701 and the fourth switch 704 are turned on, and the second switch 702 and the third switch 703 are turned off. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the first sub-cooler 610, thereby improving the defrosting efficiency of the first sub-cooler 610. The refrigerant discharged from the first sub-cooler 610 and the refrigerant discharged from the indoor unit enter the second sub-cooler 620 and return to the compressor 1. The first sub-cooler 610 and the indoor heat exchanger 340 are condensers, and the second sub-cooler 620 is an evaporator. The first sub-cooler 610 is defrosted. In this process, the indoor heat exchanger 340 still heats, realizing the effect of efficient defrosting of the first sub-cooler 610 and uninterrupted heating of the indoor unit, ensuring the indoor comfort.

[0378] In some embodiments, when defrosting the second sub-coil 620, the second switch 702 and the third switch 703 are turned on, and the first switch 701 and the fourth switch 704 are turned off. When defrosting the second sub-coil 620, the high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the second sub-coil 620, thereby improving the defrosting efficiency of the second sub-coil 620. The refrigerant discharged from the second sub-coil 620 and the refrigerant discharged from the indoor coil enter the first sub-coil 610 and return to the compressor 1. The second sub-coil 620 and the indoor coil 340 are condensers, and the first sub-coil 610 is an evaporator, and the second sub-coil 620 is defrosted. In this process, the indoor coil 340 is still heating, achieving the effect of uninterrupted heating of the indoor coil 300 while efficiently defrosting the second sub-coil 620.

[0379] Some embodiments of the present disclosure achieve defrosting of the first sub-coil 610 or the second sub-coil 620 by setting four switches. During the defrosting process, the indoor coil 300 is in operation. In this way, the comfort of the indoor temperature can be avoided by excessive loss of heat from the indoor coil 300, thereby achieving uninterrupted heating of the indoor coil 300. In this way, the energy waste of the air conditioning system 1000 during the defrosting process is reduced, and the operating energy efficiency of the air conditioning system 1000 is improved.

[0380] In some embodiments, the air conditioning system further comprises a switching valve 4 to switch between the cooling mode and the heating mode.

[0381] In some embodiments, the air conditioning system further comprises a fifth switch 705, and the second ports of the first sub-coil 610 and the second sub-coil 620 are connected through the fifth switch 705.

[0382] When defrosting the first sub-coil 610, the first switch 701 and the fourth switch 704 are turned on, and the second switch 702, the third switch 703, and the fifth switch 705 are turned off. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the first sub-coil 610.

[0383] When defrosting the second sub-coil 620, the second switch 702 and the third switch 703 are turned on, and the first switch 701, the fourth switch 704, and the fifth switch 705 are turned off. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 enters the second sub-coil 620.

[0384] In the cooling mode or the heating mode of the air conditioning system 1000, the first switch 701, the second switch 702, and the fourth switch 704 are turned off, and the third switch 703 and the fifth switch 705 are turned on.

[0385] Referring to FIG. 25, in the cooling mode, the first switch 701, the second switch 702, and the fourth switch 704 are turned off, and the third switch 703 and the fifth switch 705 are turned on.

[0386] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the outdoor heat exchanger 340 through the switching valve 4. A part of the high-temperature and high-pressure gaseous refrigerant flows into the first sub heat exchanger 610 through the third switch 703, and another part of the high-temperature and high-pressure gaseous refrigerant flows into the second sub heat exchanger 620 through the third switch 703 and the fifth switch 705. The high-temperature and high-pressure gaseous refrigerant is condensed into high-temperature and high-pressure liquid refrigerant in the first sub heat exchanger 610 and the second sub heat exchanger 620.

[0387] The high-temperature and high-pressure liquid refrigerant flows out from the outdoor electronic expansion valve 7, passes through the liquid pipe stop valve 63, and flows into the indoor throttling device (for example, the indoor electronic expansion valve 330). The high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure two-phase refrigerant by the indoor electronic expansion valve 330. The low-temperature and low-pressure two-phase refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the indoor heat exchanger 340. The low-temperature and low-pressure gaseous refrigerant flows out from the indoor heat exchanger 340, passes through the first gas pipe stop valve 61, and then passes through the switching valve 4 to flow into the gas-liquid separator 3. The low-temperature and low-pressure gaseous refrigerant flowing out from the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the cooling cycle is completed.

[0388] Referring to FIG. 26, in the heating mode, the first switch 701, the second switch 702, and the fourth switch 704 are turned off, and the third switch 703 and the fifth switch 705 are turned on.

[0389] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the indoor heat exchanger 340 through the switching valve 4 and the first gas pipe stop valve 61, and the high-temperature and high-pressure gaseous refrigerant is condensed into high-temperature and high-pressure liquid refrigerant in the indoor heat exchanger 340. The high-temperature and high-pressure liquid refrigerant flows out from the indoor electronic expansion valve 330 and flows to the outdoor electronic expansion valve 7 through the liquid pipe stop valve 63.

[0390] The high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant by the outdoor electronic expansion valve 7. The low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the first sub heat exchanger 610 and the second sub heat exchanger 620. The low-temperature and low-pressure gaseous refrigerant flowing out from the first sub heat exchanger 610 flows through the third switch 703 into the switching valve 4, and the low-temperature and low-pressure gaseous refrigerant flowing out from the second sub heat exchanger 620 flows through the fifth switch 705 and the third switch 703 into the switching valve 4, and then flows into the gas-liquid separator 3 through the switching valve 4. The low-temperature and low-pressure gaseous refrigerant flowing out from the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the heating cycle is completed.

[0391] The defrosting of the air conditioning system 1000 includes two cases, defrosting the first sub-cooler 610 and defrosting the second sub-cooler 620.

[0392] Referring to Fig. 27, when defrosting the first sub-cooler 610, the first switch 701 and the fourth switch 704 are turned on, and the second switch 702, the third switch 703 and the fifth switch 705 are turned off.

[0393] When defrosting the first sub-cooler 610, the flow direction of the refrigerant at the indoor unit side is the same as that in the heating cycle, which will not be described again here, and only the flow direction of the refrigerant at the outdoor unit side will be described below.

[0394] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the indoor unit 300 for heating, and a part of the high-temperature and high-pressure gaseous refrigerant flows into the first sub-cooler 610 through the fourth switch 704 to be condensed and release heat, thereby melting the frost layer attached to the first sub-cooler 610. The high-temperature and high-pressure liquid refrigerant flowing out of the first sub-cooler 610 is combined with the low-temperature and low-pressure gaseous-liquid two-phase refrigerant flowing out of the indoor unit 300 and then throttled by the outdoor electronic expansion valve 7, and then the combined refrigerant is evaporated and absorbs heat in the second sub-cooler 620 to become low-temperature and low-pressure gaseous refrigerant. The low-temperature and low-pressure gaseous refrigerant flowing out of the second sub-cooler 620 flows into the gas-liquid separator 3 through the fourth switch 704. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the defrosting cycle of the first sub-cooler 610 is completed.

[0395] Referring to Fig. 28, when defrosting the second sub-cooler 620, the second switch 702 and the third switch 703 are turned on, and the first switch 701, the fourth switch 704 and the fifth switch 705 are turned off.

[0396] When defrosting the second sub-cooler 620, the flow direction of the refrigerant at the indoor unit side is the same as that in the heating cycle, which will not be described again here, and only the flow direction of the refrigerant at the outdoor unit side will be described below.

[0397] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the indoor unit 300 for heating, and a portion of the high-temperature and high-pressure gaseous refrigerant flows into the second sub-cooler 620 through the second switch 702 to be condensed and release heat, thereby melting frost attached to the second sub-cooler 620. The high-temperature and high-pressure liquid refrigerant flowing out of the second sub-cooler 620 is combined with the low-temperature and low-pressure gaseous-liquid two-phase refrigerant flowing out of the indoor unit 300 and then throttled by the outdoor electronic expansion valve 7, and then the combined refrigerant is evaporated and absorbs heat in the first sub-cooler 610. The low-temperature and low-pressure gaseous refrigerant flowing out of the first sub-cooler 610 flows into the gas-liquid separator 3 through the third switch 703 and the first switching valve 104. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the defrosting cycle of the second sub-cooler 620 is completed.

[0398] In some embodiments, referring to FIGS. 24-28, the first switch 701 and the second switch 702 are electronic expansion valves with adjustable opening degrees. The air conditioning system 1000 can adjust the flow rate of the refrigerant by adjusting the opening degrees of the first switch 701 and the second switch 702. The third switch 703, the fourth switch 704, and the fifth switch 705 can be solenoid valves.

[0399] In some embodiments, referring to FIG. 29, the first switch 701, the second switch 702, the third switch 703, the fourth switch 704, and the fifth switch 705 can be solenoid valves.

[0400] Some embodiments of the present disclosure also provide yet another air conditioning system. Referring to FIG. 30, unlike the air conditioning systems in some embodiments described above, the indoor unit 300 includes two indoor heat exchangers, i.e., a third sub-cooler 341 and a fourth sub-cooler 342. The indoor unit 300 and the outdoor unit 100 are connected through the liquid pipe 103, the first gas pipe 101, and the second gas pipe 102.

[0401] At this time, the air conditioning system includes two four-way valves, i.e., a first switching valve 104 and a second switching valve 105. The third sub-cooler 341 is connected to the compressor 1 through the first switching valve 104, and the fourth sub-cooler 342 is connected to the compressor 1 through the second switching valve 105.

[0402] It can be understood that when the first switching valve 104 is switched to the third sub-cooler 341 for heating and the second switching valve 105 is switched to the fourth sub-cooler 342 for cooling, or when the first switching valve 104 is switched to the third sub-cooler 341 for cooling and the second switching valve 105 is switched to the fourth sub-cooler 342 for heating, the first switch 701, the second switch 702, and the fourth switch 704 are turned off, and the third switch 703 and the fifth switch 705 are turned on. In this way, non-temperature-lowering dehumidification of the indoor unit is achieved.

[0403] In some embodiments, the indoor unit further comprises two indoor throttling components, a first sub-indoor throttling component 331 and a second sub-indoor throttling component 332. The third sub-heat exchanger 341 is connected with the first sub-indoor throttling component 331, and the fourth sub-heat exchanger 342 is connected with the second sub-indoor throttling component 332.

[0404] The first sub-indoor throttling component 331 and the second sub-indoor throttling component 332 are connected with the outdoor electronic expansion valve 7 through the liquid pipe stop valve 63. For example, the indoor throttling component is an indoor electronic expansion valve.

[0405] The third sub-heat exchanger 341 is connected with the first switching valve 104 through the first gas pipe stop valve 61, and the fourth sub-heat exchanger 342 is connected with the second switching valve 105 through the second gas pipe stop valve 62.

[0406] In some embodiments, the third sub-heat exchanger 341 and the fourth sub-heat exchanger 342 can share the indoor fan 350.

[0407] In some embodiments, the indoor unit 300 comprises two indoor fans, a third sub-fan and a fourth sub-fan. The third sub-fan is arranged corresponding to the third sub-heat exchanger 341, and the fourth sub-fan is arranged corresponding to the fourth sub-heat exchanger 342.

[0408] The outdoor unit 100 and the indoor unit 300 are connected through the first gas pipe stop valve 61, the second gas pipe stop valve 62 and the liquid pipe stop valve 63.

[0409] Referring to FIG. 31, in the cooling mode, the air conditioning system 1000, the first switch 701, the second switch 702 and the fourth switch 704 are cut off, and the third switch 703 and the fifth switch 705 are turned on.

[0410] The high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 is divided into two parts after passing through the first switching valve 104. One part of the high-temperature and high-pressure gaseous refrigerant enters the first sub-heat exchanger 610 through the third switch 703, and the other part of the high-temperature and high-pressure gaseous refrigerant enters the second sub-heat exchanger 620 through the third switch 703 and the fifth switch 705, and is condensed into high-temperature and high-pressure liquid refrigerant in the first sub-heat exchanger 610 and the second sub-heat exchanger 620. The high-temperature and high-pressure liquid refrigerant flows out from the outdoor electronic expansion valve 7, passes through the liquid pipe stop valve 63, and flows into the first sub-indoor throttling component 331 and the second sub-indoor throttling component 332. The high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure two-phase refrigerant by the first sub-indoor throttling component 331 and the second sub-indoor throttling component 332, respectively.

[0411] The low-temperature and low-pressure two-phase refrigerant is evaporated into low-temperature and low-pressure gaseous refrigerant in the third sub-cooler 341 and the fourth sub-cooler 342. The low-temperature and low-pressure gaseous refrigerant flows out of the third sub-cooler 341 and the fourth sub-cooler 342, and flows out of the indoor unit 300 through the first gas pipe stop valve 61 and the second gas pipe stop valve 62, respectively. Then, the low-temperature and low-pressure gaseous refrigerant flows into the gas-liquid separator 3 through the first switching valve 104 and the second switching valve 105, respectively. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and the refrigeration cycle is completed.

[0412] In some embodiments, the second switching valve 105 can be adjusted to make the refrigerant discharged from the compressor 1 enter the fourth sub-cooler 342 through the second switching valve 105 on the basis of the refrigeration cycle. At this time, the fourth sub-cooler 342 is a condenser, and the third sub-cooler 341 is an evaporator, so that the heating of the indoor unit 300 is realized while dehumidification is achieved.

[0413] Referring to FIG. 32, in the heating mode of the air conditioning system, the first switch 701, the second switch 702, and the fourth switch 704 are turned off, and the third switch 703 and the fifth switch 705 are turned on.

[0414] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 is divided into two paths. One path flows to the third sub-cooler 341 through the first switching valve 104 and the first gas pipe stop valve 61, and the other path flows to the fourth sub-cooler 342 through the second switching valve 105 and the second gas pipe stop valve 62. The high-temperature and high-pressure gaseous refrigerant is condensed into high-temperature and high-pressure liquid refrigerant in the third sub-cooler 341 and the fourth sub-cooler 342. The high-temperature and high-pressure liquid refrigerant flows out of the first sub-indoor throttling part 331 and the second sub-indoor throttling part 332, respectively, and flows to the outdoor electronic expansion valve 7 through the liquid pipe stop valve 63.

[0415] The high-temperature and high-pressure liquid refrigerant is throttled into low-temperature and low-pressure refrigerant by the outdoor electronic expansion valve 7, and the low-temperature and low-pressure refrigerant evaporates into low-temperature and low-pressure gaseous refrigerant in the first sub-cooler 610 and the second sub-cooler 620. The low-temperature and low-pressure gaseous refrigerant flowing out of the first sub-cooler 610 flows through the third switch 703 into the first switching valve 104, and the low-temperature and low-pressure gaseous refrigerant flowing out of the second sub-cooler 620 flows through the fifth switch 705 and the third switch 703 into the first switching valve 104, and then flows into the gas-liquid separator 3 through the first switching valve 104. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and the heating cycle is completed.

[0416] The defrosting of the air conditioning system 1000 is divided into two cases, which are defrosting of the first sub-cooler 610 and defrosting of the second sub-cooler 620, respectively.

[0417] Referring to Fig. 33, when defrosting the first sub-cooler 610, the first switch 701 and the fourth switch 704 are turned on, and the second switch 702, the third switch 703 and the fifth switch 705 are turned off.

[0418] When defrosting the first sub-cooler 610, the flow direction of the indoor unit side refrigerant is the same as that in the heating cycle, which will not be described here again, and only the flow direction of the outdoor unit side refrigerant will be described below.

[0419] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1, in addition to one path flowing to the indoor unit 300 for heating, has another path flowing into the first sub-cooler 610 through the fourth switch 704 to perform condensation and heat release, and the heat melts the frost layer attached to the first sub-cooler 610. The high-temperature and high-pressure liquid refrigerant flowing out of the first sub-cooler 610 is combined with the low-temperature and low-pressure gaseous-liquid two-phase refrigerant flowing out of the indoor unit 300 and then throttled by the outdoor electronic expansion valve 7, and then performs evaporation and heat absorption through the second sub-cooler 620. The low-temperature and low-pressure gaseous refrigerant flowing out of the second sub-cooler 620 flows into the gas-liquid separator 3 through the fourth switch 704. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the defrosting cycle of the first sub-cooler 610 is completed.

[0420] Referring to Fig. 34, when defrosting the second sub-cooler 620, the second switch 702 and the third switch 703 are turned on, and the first switch 701, the fourth switch 704 and the fifth switch 705 are turned off.

[0421] When defrosting the second sub-cooler 620, the flow direction of the indoor unit side refrigerant is the same as that in the heating cycle, which will not be described here again, and only the flow direction of the outdoor unit side refrigerant will be described below.

[0422] The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1, in addition to one path flowing to the indoor unit 300 for heating, has another path flowing into the second sub-cooler 620 through the second switch 702 to perform condensation and heat release, and the heat melts the frost layer attached to the second sub-cooler 620. The high-temperature and high-pressure liquid refrigerant flowing out of the second sub-cooler 620 is combined with the low-temperature and low-pressure gaseous-liquid two-phase refrigerant flowing out of the indoor unit and then throttled by the outdoor electronic expansion valve 7, and then performs evaporation and heat absorption through the first sub-cooler 610. The low-temperature and low-pressure gaseous refrigerant flowing out of the first sub-cooler 610 flows into the gas-liquid separator 3 through the third switch 703 and the first switching valve 104. The low-temperature and low-pressure gaseous refrigerant flowing out of the gas-liquid separator 3 flows into the suction port of the compressor 1, and thus the defrosting cycle of the second sub-cooler 620 is completed.

[0423] In some embodiments, referring to FIGS. 31-34, the first switch 701 and the second switch 702 are electronic expansion valves with adjustable opening degrees, the refrigerant flow can be adjusted by adjusting the opening degrees of the first switch 701 and the second switch 702, and the third switch 703, the fourth switch 704, and the fifth switch 705 can be electromagnetic valves.

[0424] In some embodiments, referring to FIG. 35, the first switch 701, the second switch 702, the third switch 703, the fourth switch 704, and the fifth switch 705 can be electromagnetic valves.

[0425] It should be noted that the air conditioning system shown in FIGS. 30-35 is a three-pipe air conditioning system, which can achieve dehumidification without temperature drop and uninterrupted heating in the indoor during defrosting, and improves the defrosting effect compared with a two-pipe air conditioning system.

[0426] It should be noted that any one of the technical solutions disclosed in the present disclosure can solve one or more of the above technical problems to a certain extent and achieve certain disclosed purposes; multiple technical disclosures can also be combined into one overall scheme to solve one or more of the above technical problems and achieve certain disclosed purposes; or part of the technical disclosures can be combined into one overall scheme, while related technologies and degraded schemes are used, but the degraded trend can be compensated by the technical disclosure means, and the overall technical problems and certain disclosed purposes can be solved to a certain extent; each technical disclosure is combined into a complete technical scheme, which constitutes an organic and indivisible overall scheme, and solves the technical problems and achieves certain disclosed purposes.

[0427] Any technical disclosure in the present disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical scheme and solve one or more of the above technical problems to achieve the disclosed purposes, which belongs to the content of the present disclosure and is directly and without doubt determined according to the content of the present disclosure.

[0428] Those skilled in the art will understand that the scope of the disclosure of the present disclosure is not limited to the above specific embodiments, and certain elements of the embodiments can be modified and replaced without departing from the spirit of the present application. The scope of the present application is limited by the appended claims.

Claims

1. An air conditioning system, comprising: an outdoor unit, the outdoor unit comprising: a compressor; and an outdoor heat exchanger, a first end of the outdoor heat exchanger being in communication with the compressor; at least one indoor unit, the at least one indoor unit being in communication with the outdoor unit; any one of the at least one indoor unit comprising: an indoor heat exchanger, a first end of the indoor heat exchanger being in communication with a second end of the outdoor heat exchanger, a second end of the indoor heat exchanger being in communication with the compressor; and an indoor electronic expansion valve, the indoor electronic expansion valve being disposed at the first end of the indoor heat exchanger and being capable of adjusting a flow rate of refrigerant flowing through the indoor heat exchanger; wherein the air conditioning system further comprises a refrigerant intercepting component, the refrigerant intercepting component being disposed between the outdoor unit and the at least one indoor unit; the refrigerant intercepting component comprising: a first throttling component, the first throttling component being disposed between the indoor electronic expansion valve and the second end of the outdoor heat exchanger; and a second throttling component, the second throttling component being disposed between the second end of the indoor heat exchanger and the compressor; a controller, the controller being configured to: obtain a temperature change rate of an air conditioning room in which the any one of the at least one indoor unit is located, and a deviation degree of a temperature of the air conditioning room from a target temperature; determine a target refrigerant temperature matching a current load of the air conditioning room according to the temperature change rate and the deviation degree; determine an opening degree of the indoor electronic expansion valve, the first throttling component, and the second throttling component according to at least one of the target refrigerant temperature, a preset target superheat degree, or a preset target subcooling degree.

2. The air conditioning system of claim 1, wherein, the at least one indoor unit comprises a plurality of indoor units; a number of the refrigerant intercepting components is less than or equal to a number of the plurality of indoor units.

3. The air conditioning system of claim 1 or 2, further comprising: a liquid pipe, the liquid pipe being in communication with the second end of the outdoor heat exchanger and the first end of the indoor heat exchanger; a first gas pipe, the first gas pipe being in communication with the compressor and the second end of the indoor heat exchanger; a first sensor, the first sensor being disposed in the indoor heat exchanger and being capable of detecting a refrigerant temperature in the indoor heat exchanger; a second sensor, the second sensor being disposed between the indoor electronic expansion valve and the first end of the indoor heat exchanger and being capable of detecting a temperature of the liquid pipe at the first end of the indoor heat exchanger; and a third sensor, the third sensor being disposed at the second end of the indoor heat exchanger and being capable of detecting a temperature of the first gas pipe at a position of the second end of the indoor heat exchanger; wherein the controller is coupled with the first sensor, the second sensor, and the third sensor; the air conditioning system having a refrigeration mode, in the refrigeration mode, the controller is further configured to: control the first throttling component to be at a first preset opening degree; obtain a current refrigerant temperature of the indoor heat exchanger and a corresponding target refrigerant temperature, and determine the opening degree of the indoor electronic expansion valve according to the target refrigerant temperature and the current refrigerant temperature of the indoor heat exchanger. ​ obtaining a liquid pipe temperature of a current indoor heat exchanger and a gas pipe temperature of the current indoor heat exchanger, calculating a refrigerant superheat degree according to the liquid pipe temperature of the current indoor heat exchanger and the gas pipe temperature of the current indoor heat exchanger, and determining the opening degree of the second throttling component according to the target superheat degree and the refrigerant superheat degree.

4. The air conditioning system of claim 3, wherein, The controller is further configured to: if it is determined that the target refrigerant temperature is greater than the refrigerant temperature of the current indoor heat exchanger, controlling the opening degree of the indoor electronic expansion valve to decrease; if it is determined that the target refrigerant temperature is less than the refrigerant temperature of the current indoor heat exchanger, controlling the opening degree of the indoor electronic expansion valve to increase; if it is determined that the target refrigerant temperature is equal to the refrigerant temperature of the current indoor heat exchanger, controlling the opening degree of the indoor electronic expansion valve to remain unchanged.

5. The air conditioning system of claim 4, wherein, The controller is further configured to: if it is determined that the refrigerant superheat degree is greater than the target superheat degree, controlling the opening degree of the second throttling component to increase; if it is determined that the refrigerant superheat degree is less than the target superheat degree, controlling the opening degree of the second throttling component to decrease; if it is determined that the refrigerant superheat degree is equal to the target superheat degree, controlling the opening degree of the second throttling component to remain unchanged.

6. The air conditioning system according to claim 1 or 2, further comprising: a liquid pipe, which is in communication with the second end of the outdoor heat exchanger and the first end of the indoor heat exchanger; a first sensor, which is arranged in the indoor heat exchanger and is capable of detecting a refrigerant temperature in the indoor heat exchanger; and a second sensor, which is arranged between the indoor electronic expansion valve and the first end of the indoor heat exchanger and is capable of detecting a temperature of the liquid pipe at the first end of the indoor heat exchanger; wherein the air conditioning system further has a heating mode, in which the controller is further configured to: obtain a refrigerant temperature of a current indoor heat exchanger and the corresponding target refrigerant temperature, and determine the opening degree of the second throttling component according to the target refrigerant temperature and the refrigerant temperature of the current indoor heat exchanger; obtain a liquid pipe temperature of the current indoor heat exchanger, calculate a refrigerant subcooling degree according to the liquid pipe temperature of the current indoor heat exchanger and the refrigerant temperature of the current indoor heat exchanger, and determine the opening degree of the indoor electronic expansion valve according to the target subcooling degree and the refrigerant subcooling degree; control the first throttling component to be at a second preset opening degree.

7. The air conditioning system of claim 6, wherein, The controller is further configured to: if it is determined that the refrigerant temperature of the current indoor heat exchanger is greater than the target refrigerant temperature, controlling the opening degree of the second throttling component to decrease; if it is determined that the refrigerant temperature of the current indoor heat exchanger is less than the target refrigerant temperature, controlling the opening degree of the second throttling component to increase; if it is determined that the refrigerant temperature of the current indoor heat exchanger is equal to the target refrigerant temperature, controlling the opening degree of the second throttling component to remain unchanged.

8. The air conditioning system of claim 7, wherein, The controller is further configured to: if it is determined that the refrigerant subcooling degree is greater than the target subcooling degree, controlling the opening degree of the indoor electronic expansion valve to increase; if it is determined that the refrigerant subcooling degree is less than the target subcooling degree, controlling the opening degree of the indoor electronic expansion valve to decrease; If it is determined that the refrigerant supercooling degree is less than the target supercooling degree, the opening degree of the indoor electronic expansion valve is controlled to decrease; If it is determined that the refrigerant supercooling degree is equal to the target supercooling degree, the opening degree of the indoor electronic expansion valve is controlled to remain unchanged.

9. The air conditioning system of any one of claims 1 to 8, wherein, The controller is further configured to: obtain a temperature change rate of an air-conditioned room where the any one indoor unit is located, and a deviation degree of a temperature of the air-conditioned room from a target temperature; determine the target refrigerant temperature matching a current load of the air-conditioned room according to the temperature change rate, the deviation degree and a preset data table. 10.The air conditioning system according to any one of claims 1 to 9, further comprising a fourth sensor disposed in the air conditioned room and capable of detecting a concentration of refrigerant in the air conditioned room; wherein, The controller is coupled with the fourth sensor; the controller is further configured to: If it is determined that the concentration of the refrigerant in the air-conditioned room is greater than a set threshold, the first throttling component and the second throttling component in the refrigerant cutting component corresponding to the indoor unit in the air-conditioned room are controlled to be closed.

11. An air conditioning system, comprising: an outdoor unit, comprising: a compressor; and an outdoor heat exchanger, a first end of the outdoor heat exchanger being communicated with the compressor; an air-cooled assembly connected with the outdoor unit; the air-cooled assembly comprising: an air-cooled assembly heat exchanger, the air-cooled assembly heat exchanger comprising: a first sub-air-cooled assembly heat exchanger, a first end of the first sub-air-cooled assembly heat exchanger being communicated with the compressor, and a second end of the first sub-air-cooled assembly heat exchanger being communicated with a second end of the outdoor heat exchanger; and a second sub-air-cooled assembly heat exchanger, a first end of the second sub-air-cooled assembly heat exchanger being communicated with the compressor, and a second end of the second sub-air-cooled assembly heat exchanger being communicated with the second end of the outdoor heat exchanger; a water module connected with the outdoor unit; the water module comprising a water module heat exchanger; a first gas pipe, a first end of the first gas pipe being communicated with the first end of the first sub-air-cooled assembly heat exchanger, a second end of the first gas pipe being communicated with the compressor, and the first gas pipe being capable of conveying gaseous refrigerant; a liquid pipe, a first end of the liquid pipe being communicated with the second end of the first sub-air-cooled assembly heat exchanger and the second end of the second sub-air-cooled assembly heat exchanger, and a second end of the liquid pipe being communicated with the second end of the outdoor heat exchanger; a second gas pipe, a first end of the second gas pipe being communicated with the first end of the second sub-air-cooled assembly heat exchanger, and a second end of the second gas pipe being communicated with the compressor; wherein the outdoor unit and the air-cooled assembly are connected through the first gas pipe, the liquid pipe and the second gas pipe; a first branch, a first end of the first branch being communicated with the second gas pipe, and a second end of the first branch being communicated with a first end of the water module heat exchanger; a second branch, a first end of the second branch being communicated with a second end of the water module heat exchanger, and a second end of the second branch being communicated with the second end of the outdoor heat exchanger; wherein the water module is connected with the outdoor unit through the first branch and the second branch; a first regulating valve arranged in the first gas pipe; and a second regulating valve arranged in the second gas pipe; wherein the air conditioning system further comprises a controller configured to: In a condition that the water module heating operation is met and the discharge pressure of the compressor is located outside the preset discharge pressure range, the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve is adjusted from the preset opening degree until the discharge pressure of the compressor is located within the preset discharge pressure range.

12. The air conditioning system of claim 11, wherein, The controller is further configured to: In a condition that the water module independent heating operation is met, the duration of the water module heating operation is greater than or equal to a first set duration, and the discharge pressure of the compressor is greater than an upper threshold of the preset discharge pressure range, the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve is increased from the preset opening degree until the discharge pressure of the compressor is reduced to be less than or equal to the upper threshold of the preset discharge pressure range.

13. The air conditioning system of claim 12, wherein, The air-cooled assembly further comprises an air-cooled assembly electronic expansion valve, which is correspondingly arranged with the air-cooled assembly heat exchanger; the controller is further configured to: After the discharge pressure of the compressor is reduced to be less than the upper threshold of the preset discharge pressure range, a preset intervention target supercooling degree is obtained, and a current supercooling degree of the air-cooled assembly heat exchanger is obtained; If it is determined that the current supercooling degree deviates from the intervention target supercooling degree, the opening degree of the air-cooled assembly electronic expansion valve is adjusted to make the current supercooling degree transition equal to the intervention target supercooling degree.

14. The air conditioning system of claim 13, wherein, The controller is further configured to: After the discharge pressure of the compressor is reduced to be less than the upper threshold of the preset discharge pressure range, a preset intervention target supercooling degree is obtained, and a current supercooling degree of the air-cooled assembly heat exchanger is obtained; If it is determined that the current supercooling degree is greater than the intervention target supercooling degree, the opening degree of the air-cooled assembly electronic expansion valve is increased to make the current supercooling degree transition equal to the intervention target supercooling degree; If it is determined that the current supercooling degree is less than the intervention target supercooling degree, the opening degree of the air-cooled assembly electronic expansion valve is reduced to make the current supercooling degree transition equal to the intervention target supercooling degree.

15. The air conditioning system of claim 13 or 14, wherein, The controller is further configured to: After the discharge pressure of the compressor is reduced to be less than the upper threshold of the preset discharge pressure range, the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve is kept unchanged; In a condition that the water module independent heating operation is met, the duration of the water module heating operation is greater than or equal to a second set duration, and the discharge pressure of the compressor is located outside the preset discharge pressure range again, the opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve is adjusted again from the adjusted opening degree of the first gas pipe regulating valve and the second gas pipe regulating valve until the discharge pressure of the compressor is located within the preset discharge pressure range.

16. An air conditioning system, comprising: an outdoor unit, comprising: a compressor; and an outdoor heat exchanger; an air-cooled assembly connected with the outdoor unit, the air-cooled assembly comprising an air-cooled assembly heat exchanger; a first gas pipe, a first end of the first gas pipe being connected with the first end of the air-cooled assembly heat exchanger, a second end of the first gas pipe being connected with the compressor, and the first gas pipe being capable of conveying gaseous refrigerant; and a second gas pipe, a first end of the second gas pipe being connected with the second end of the air-cooled assembly heat exchanger, a second end of the second gas pipe being connected with the compressor, and the second gas pipe being capable of conveying gaseous refrigerant. A liquid pipe, a first end of the liquid pipe being communicated with the second end of the air-cooled component heat exchanger, a second end of the liquid pipe being communicated with the second end of the outdoor heat exchanger, and the liquid pipe being capable of conveying liquid refrigerant; The air conditioner system further comprises: A water module connected with the outdoor unit; A first gas pipe adjustment valve arranged in the first gas pipe; and The controller is configured to: when the water module is independently heating and the discharge pressure of the compressor is outside the preset discharge pressure range, adjust the opening degree of the first gas pipe adjustment valve from a preset opening degree until the discharge pressure of the compressor is within the preset discharge pressure range. The controller is further configured to:

17. The air conditioning system of claim 16, wherein, When the water module is independently heating and the duration of the water module heating is greater than or equal to a first set duration, and the discharge pressure of the compressor is greater than the upper threshold of the preset discharge pressure range, increase the opening degree of the first gas pipe adjustment valve from the preset opening degree until the discharge pressure of the compressor is reduced to less than the upper threshold of the preset discharge pressure range. The air-cooled component further comprises an air-cooled component electronic expansion valve corresponding to the air-cooled component heat exchanger; 18. The air conditioning system of claim 17, wherein, The controller is further configured to: After the discharge pressure of the compressor is reduced to less than the upper threshold of the preset discharge pressure range, obtain a preset intervention target supercooling degree, and obtain a current supercooling degree of the air-cooled component heat exchanger; If it is determined that the current supercooling degree deviates from the intervention target supercooling degree, adjust the opening degree of the air-cooled component electronic expansion valve to make the current supercooling degree transition to the intervention target supercooling degree. The controller is further configured to:

19. The air conditioning system of claim 18, wherein, After the discharge pressure of the compressor is reduced to less than the upper threshold of the preset discharge pressure range, obtain a preset intervention target supercooling degree, and obtain a current supercooling degree of the air-cooled component heat exchanger; If it is determined that the current supercooling degree is greater than the intervention target supercooling degree, increase the opening degree of the air-cooled component electronic expansion valve to make the current supercooling degree transition to the intervention target supercooling degree; If it is determined that the current supercooling degree is less than the intervention target supercooling degree, decrease the opening degree of the air-cooled component electronic expansion valve to make the current supercooling degree transition to the intervention target supercooling degree. The controller is further configured to:

20. The air conditioning system of claim 18 or 19, wherein, After the discharge pressure of the compressor is reduced to less than the upper threshold of the preset discharge pressure range, keep the adjusted opening degree of the first gas pipe adjustment valve unchanged; When the water module is independently heating and the duration of the water module heating is greater than or equal to a second set duration, and the discharge pressure of the compressor is again outside the preset discharge pressure range, adjust the opening degree of the first gas pipe adjustment valve and the second gas pipe adjustment valve from the adjusted opening degree of the first gas pipe adjustment valve and the second gas pipe adjustment valve until the discharge pressure of the compressor is within the preset discharge pressure range. ​ 21. An air conditioning system comprising: an outdoor unit comprising: a compressor; an outdoor heat exchanger, a first end of the outdoor heat exchanger being in communication with the compressor; an outdoor throttling component, provided at a second end of the outdoor heat exchanger; and at least one indoor unit, connected to the outdoor unit; wherein the outdoor heat exchanger comprises: a first sub-heat exchanger, a first port of the first sub-heat exchanger being connected to the outdoor throttling component, a second port of the first sub-heat exchanger being connected to an outlet of the compressor and an inlet of the compressor; and a second sub-heat exchanger, a first port of the second sub-heat exchanger being connected to the outdoor throttling component, a second port of the second sub-heat exchanger being connected to the outlet of the compressor and the inlet of the compressor; wherein the air conditioning system further comprises: a first switch, the second port of the first sub-heat exchanger being connected to the outlet of the compressor through the first switch; a second switch, the second port of the second sub-heat exchanger being connected to the outlet of the compressor through the second switch; a third switch, the second port of the first sub-heat exchanger being connected to the inlet of the compressor through the third switch; and a fourth switch, the second port of the second sub-heat exchanger being connected to the inlet of the compressor through the fourth switch; when defrosting the first sub-heat exchanger, the first switch and the fourth switch are turned on, and the second switch and the third switch are turned off; when defrosting the second sub-heat exchanger, the second switch and the third switch are turned on, and the first switch and the fourth switch are turned off.

22. The air conditioning system of claim 21, further comprising a fifth switch, the second port of the first sub-heat exchanger and the second port of the second sub-heat exchanger being connected through the fifth switch; when defrosting the first sub-heat exchanger, the first switch and the fourth switch are turned on, and the second switch, the third switch and the fifth switch are turned off; when defrosting the second sub-heat exchanger, the second switch and the third switch are turned on, and the first switch, the fourth switch and the fifth switch are turned off; when the air conditioning system is executing one of a cooling mode and a heating mode, the first switch, the second switch and the fourth switch are turned off, and the third switch and the fifth switch are turned on.

23. The air conditioning system of claim 22, wherein, any one of the at least one indoor unit comprises an indoor heat exchanger; the indoor heat exchanger comprises: a third sub-heat exchanger, a first end of the third sub-heat exchanger being in communication with the compressor, a second end of the third sub-heat exchanger being in communication with the outdoor heat exchanger; and a fourth sub-heat exchanger, a first end of the fourth sub-heat exchanger being in communication with the compressor, a second end of the fourth sub-heat exchanger being in communication with the outdoor heat exchanger; the air conditioning system further comprises: a first four-way valve, the third sub-heat exchanger being connected to the compressor through the first four-way valve; and a second four-way valve, the fourth sub-heat exchanger being connected to the compressor through the second four-way valve. Wherein, when one of the following conditions is met: the first four-way valve switches to the third sub-cooler for heating, the second four-way valve switches to the fourth sub-cooler for cooling; and the first four-way valve switches to the third sub-cooler for cooling, the second four-way valve switches to the fourth sub-cooler for heating, the first switch, the second switch and the fourth switch are turned off, and the third switch and the fifth switch are turned on.

24. The air conditioning system of claim 23, further comprising: a first indoor sub-throttling component disposed at the second end of the third sub-cooler; and a second indoor sub-throttling component disposed at the second end of the fourth sub-cooler.

25. The air conditioning system of claim 24, further comprising a liquid pipe stop valve, the first indoor sub-throttling component and the second indoor sub-throttling component are connected to the outdoor throttling component through the liquid pipe stop valve, respectively.

26. The air conditioning system of any one of claims 23 to 25, further comprising: a first gas pipe stop valve, the first sub-cooler is connected to the first four-way valve through the first gas pipe stop valve; and a second gas pipe stop valve, the second sub-cooler is connected to the second four-way valve through the second gas pipe stop valve. The at least one indoor unit comprises a plurality of indoor units, and one or more indoor units of the plurality of indoor units comprise the third sub-cooler and the fourth sub-cooler. The outdoor unit further comprises:

27. The air conditioning system of any of claims 23-26, wherein, a first sub-fan corresponding to the first sub-cooler; and 28. The air conditioning system of any of claims 21 to 27, wherein, a second sub-fan corresponding to the second sub-cooler. The first switch and the second switch are electronic expansion valves with adjustable opening degrees, and the third switch, the fourth switch and the fifth switch are solenoid valves. The first switch, the second switch, the third switch, the fourth switch and the fifth switch are solenoid valves.

29. The air conditioning system of any of claims 22-27, wherein, ​ 30. The air conditioning system of any one of claims 22-27, wherein, ​

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