Air conditioning system

Abstract

The invention relates to the technical field of air conditioning systems, and discloses an air conditioning system which comprises a compressor, a first multi-way valve, a second multi-way valve, an outdoor heat exchange module and an indoor heat exchange module. The compressor comprises a first compression cylinder with a first air return port and a second compression cylinder with a second air return port, and the first compression cylinder and the second compression cylinder exhaust air through an exhaust port; the indoor heat exchange module comprises a first evaporator and a second evaporator which are connected in parallel; wherein the exhaust port communicates with the outdoor heat exchange module through the first multi-way valve, the outdoor heat exchange module communicates with the indoor heat exchange module through the first liquid pipe, the first evaporator communicates with the first air return port through the first air pipe and the first multi-way valve in sequence, and the second evaporator communicates with the second air return port through the second air pipe and the second multi-way valve in sequence; 0.1 MPa < = P < = 0.5 MPa, and / or 0.8 < = V < = 2, P is the pressure difference between the first compression cylinder and the second compression cylinder, and V is the volume ratio of the second compression cylinder to the first compression cylinder.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air conditioning systems, for example to an air conditioning system. BACKGROUND

[0002] With the development of science and technology and the improvement of people's living standards, air conditioners are widely used, and people's requirements for air conditioners are also getting higher and higher, and the performance of air conditioners is also being continuously optimized. Among them, three-pipe air conditioners emerge as the times require and can be applied in different heat exchange scenes. However, the volume of gas that can be compressed by the compressor in the current three-pipe air conditioner is fixed, so it does not match the load demand of the indoor in some heat exchange scenes, resulting in low heat exchange efficiency of the air conditioner.

[0003] The related technology discloses an air conditioner, which comprises at least two indoor heat exchangers, a compressor, an outdoor heat exchanger and a refrigerant flow direction control module. The compressor is a double-cylinder compressor, which has two return gas ports and one exhaust port. The second port of the first heat exchanger in the indoor and the fourth port of the second heat exchanger in the indoor are connected with the sixth port of the outdoor heat exchanger. The two return gas ports and the exhaust port of the compressor are connected with the refrigerant flow direction control module. The two heat exchangers in the indoor are connected with the refrigerant flow direction control module through a first pipeline and a second pipeline respectively, and the outdoor heat exchanger is connected with the refrigerant flow direction control module through a third pipeline. The refrigerant flow direction control module is used for controlling the flow direction of the refrigerant in the first pipeline, the second pipeline and the third pipeline, and controlling the refrigerant to flow into the first compression cylinder and / or the second compression cylinder. In this way, the compressor can compress gas by using the first compression cylinder alone, compressing gas by using the first compression cylinder alone, and compressing gas by using the first compression cylinder and the second compression cylinder at the same time, thereby improving the heat exchange efficiency of the three-pipe air conditioner when applied in different heat exchange scenes.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

[0005] In the case of realizing double evaporation temperature by using a double-cylinder compressor, the energy efficiency of the air conditioning system is relatively low.

[0006] It should be noted that the information disclosed in the above background section is only used to strengthen the understanding of the background of the present application, and therefore can include information that does not constitute prior art known to those of ordinary skill in the art. SUMMARY

[0007] To have a basic understanding of some aspects of the disclosed embodiments, a brief overview is given below. The overview is not a comprehensive overview of the application, nor is it intended to identify key / important elements or delineate the scope of the embodiments. It is solely intended to serve as a preamble to the detailed description below.

[0008] The embodiments of the present disclosure provide an air conditioning system, which solves the problem of low energy efficiency of the air conditioning system.

[0009] In some embodiments, the air conditioning system comprises:

[0010] a compressor, a first multi-way valve, a second multi-way valve, an outdoor heat exchange module and an indoor heat exchange module; the compressor comprises a first compression cylinder with a first gas return port and a second compression cylinder with a second gas return port, and the first compression cylinder and the second compression cylinder discharge through a discharge port; the indoor heat exchange module comprises a first evaporator and a second evaporator in parallel;

[0011] wherein the discharge port is communicated with the outdoor heat exchange module through the first multi-way valve, the outdoor heat exchange module is communicated with the indoor heat exchange module through a first liquid pipe, the first evaporator is communicated with the first gas return port in turn through a first gas pipe and the first multi-way valve, and the second evaporator is communicated with the second gas return port in turn through a second gas pipe and the second multi-way valve;

[0012] and 0.1 MPa≤P≤0.5 MPa, and / or 0.8≤V≤2, P is the pressure difference between the first compression cylinder and the second compression cylinder, and V is the volume ratio of the second compression cylinder to the first compression cylinder.

[0013] Optionally, the value of P includes 0.1 MPa, 0.2 MPa, 0.3 MPa, 0.4 MPa or 0.5 MPa.

[0014] Optionally, the value of V includes 0.8, 1, 1.2, 1.4, 1.6, 1.8 or 2.

[0015] Optionally, the first multi-way valve comprises a valve port C, a valve port D, a valve port E and a valve port S, the valve port C is communicated with the outdoor heat exchange module, the valve port D is communicated with the discharge port, the valve port E is communicated with the first gas pipe, and the valve port S is communicated with the first gas return port through a first gas return pipe section;

[0016] The second multi-way valve comprises a valve port J, a valve port K, a valve port M and a valve port N, the valve port J is closed, the valve port K is communicated with the discharge port, the valve port N is communicated with the second gas pipe, and the valve port M is communicated with the second gas return port through a second gas return pipe section; the first gas return pipe section is communicated with the second gas return pipe section through a controllable on-off communication branch;

[0017] And a main throttling element is arranged between the indoor heat exchange module and the outdoor heat exchange module, a first auxiliary throttling element is arranged on the side of the first evaporator communicated with the main throttling element, and a second auxiliary throttling element is arranged on the side of the second evaporator communicated with the main throttling element.

[0018] Optionally, the air conditioning system comprises a full refrigeration mode, and the full refrigeration mode corresponds to: the valve port C and the valve port D are conductive, the valve port E and the valve port S are conductive, the valve port K and the valve port J are conductive, the valve port M and the valve port N are conductive, the main throttling element is fully open, and the first auxiliary throttling element and the second auxiliary throttling element are throttled.

[0019] Optionally, the air conditioning system comprises a full heating mode, the full heating mode corresponding to: the valve port C and the valve port S being conducted, the valve port E and the valve port D being conducted, the valve port K and the valve port N being conducted, the valve port M and the valve port J being conducted, the main throttling element throttling, and the first auxiliary throttling element and the second auxiliary throttling element both fully opening.

[0020] Optionally, the air conditioning system comprises a reheating dehumidification mode, the reheating dehumidification mode corresponding to: the valve port C and the valve port D being conducted, the valve port E and the valve port S being conducted, the valve port K and the valve port N being conducted, the valve port M and the valve port J being conducted, the main throttling element fully opening, the first auxiliary throttling element throttling, and the second auxiliary throttling element fully opening.

[0021] Optionally, the air conditioning system comprises two indoor heat exchange modules in parallel, referred to as a first module and a second module respectively.

[0022] The air conditioning system comprises a reheating dehumidification and refrigeration mode, the reheating dehumidification and refrigeration mode corresponding to: the valve port C and the valve port D being conducted, the valve port E and the valve port S being conducted, the valve port K and the valve port N being conducted, the valve port M and the valve port J being conducted, the main throttling element fully opening, the first auxiliary throttling element of the first module throttling and the second auxiliary throttling element being closed, and the first auxiliary throttling element of the second module throttling and the second auxiliary throttling element fully opening.

[0023] Optionally, the air conditioning system comprises two indoor heat exchange modules in parallel, referred to as a first module and a second module respectively.

[0024] The air conditioning system comprises a reheating dehumidification and refrigeration mode, the reheating dehumidification and refrigeration mode corresponding to: the valve port C and the valve port D being conducted, the valve port E and the valve port S being conducted, the valve port K and the valve port N being conducted, the valve port M and the valve port J being conducted, the main throttling element fully opening, the first auxiliary throttling element of the first module throttling and the second auxiliary throttling element being closed, and the first auxiliary throttling element of the second module throttling and the second auxiliary throttling element fully opening.

[0025] Optionally, the air conditioning system comprises two indoor heat exchange modules in parallel, referred to as a first module and a second module respectively.

[0026] The air conditioning system comprises a reheating dehumidification and refrigeration mode, the reheating dehumidification and refrigeration mode corresponding to: the valve port C and the valve port D being conducted, the valve port E and the valve port S being conducted, the valve port K and the valve port N being conducted, the valve port M and the valve port J being conducted, the main throttling element fully opening, the first auxiliary throttling element of the first module throttling and the second auxiliary throttling element being closed, and the first auxiliary throttling element of the second module throttling and the second auxiliary throttling element fully opening.

[0027] The air conditioning system provided by the embodiments of the present disclosure can achieve the following technical effects:

[0028] The compressor of the present application can be referred to as a double-suction single-row double-cylinder compressor, and the double-evaporation temperature can be realized by arranging two parallel evaporators and corresponding pipeline layout in the room. The volume and back pressure of the two compression cylinders directly affect the performance of the air conditioning system. Among them, the volume of the first compression cylinder is denoted as v1, the volume of the second compression cylinder is denoted as v2, v2 / v1=V, and 0.8≤V≤2. Limiting the value of V in this range can improve the energy saving effect of the air conditioning system. The back pressure of the first compression cylinder is denoted as p1, the back pressure of the second compression cylinder is denoted as p2, p1-p2=P, and 0.1MPa≤P≤0.5MPa. Limiting the value of P in this range can effectively improve the energy saving effect of the air conditioning system. Moreover, when the values of V and P are simultaneously within the corresponding value ranges, the back pressure difference and volume ratio of the two compression cylinders can be adapted, thereby greatly improving the energy efficiency of the air conditioning system.

[0029] The foregoing general description and the following description are only exemplary and explanatory, and are not used to limit the present application. BRIEF DESCRIPTION OF DRAWINGS

[0030] One or more embodiments are exemplarily illustrated by corresponding drawings, which do not constitute a limitation on the embodiments, elements with the same reference numerals in the drawings are shown as similar elements, the drawings do not constitute a proportional limitation, and wherein:

[0031] Figure 1 is a structural schematic diagram of an air conditioning system provided by the embodiments of the present disclosure;

[0032] Figure 2 is a relationship diagram of volume ratio V and energy efficiency ratio COP provided by the embodiments of the present disclosure;

[0033] Figure 3 is a relationship diagram of back pressure difference P and energy efficiency ratio COP under rated refrigeration working condition provided by the embodiments of the present disclosure;

[0034] Figure 4 is a relationship diagram of back pressure difference P and energy efficiency ratio COP under low-temperature intermediate refrigeration working condition provided by the embodiments of the present disclosure;

[0035] Figure 5 is a refrigerant flow path schematic diagram of full refrigeration mode provided by the embodiments of the present disclosure;

[0036] Figure 6 is a refrigerant flow path schematic diagram of full heating mode provided by the embodiments of the present disclosure;

[0037] Figure 7 is a refrigerant flow path schematic diagram of reheat dehumidification mode provided by the embodiments of the present disclosure;

[0038] Figure 8is a refrigerant flow path schematic diagram of a reheating dehumidification and refrigeration mode provided by the embodiments of the present disclosure;

[0039] Figure 9 is a refrigerant flow path schematic diagram of a reheating dehumidification and heating mode provided by the embodiments of the present disclosure;

[0040] Figure 10 is a refrigerant flow path schematic diagram of a simultaneous cooling and heating mode provided by the embodiments of the present disclosure.

[0041] Reference signs:

[0042] 1, compressor; 11, first compression cylinder; 111, first back gas port; 12, second compression cylinder; 121, second back gas port; 122, exhaust port; 13, first multi-way valve; 14, second multi-way valve;

[0043] 2, outdoor heat exchange module; 21, main throttling element;

[0044] 3, indoor heat exchange module; 31, first evaporator; 311, first auxiliary throttling element; 32, second evaporator; 321, second auxiliary throttling element; 33, first module; 34, second module;

[0045] 4, first liquid pipe; 41, first gas pipe; 411, first back gas pipe section; 42, second gas pipe; 421, second back gas pipe section; 43, communication branch. DETAILED DESCRIPTION

[0046] In order to enable a more detailed understanding of the features and technical content of the embodiments of the present disclosure, the implementation of the embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings, which are only used for reference and do not limit the embodiments of the present disclosure. In the following technical description, in order to facilitate explanation, a plurality of details are provided to provide a full understanding of the disclosed embodiments. However, one or more embodiments can still be implemented without these details. In other cases, in order to simplify the drawings, well-known structures and devices can be simplified.

[0047] The terms "first", "second", and the like in the specification and claims of the embodiments of the present disclosure and the above drawings are used to distinguish similar objects, and do not necessarily have to describe a specific order or sequence. It should be understood that the data thus used can be interchanged under appropriate circumstances in order to describe the embodiments of the present disclosure herein. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion.

[0048] In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "back" and the like indicate the orientation or positional relationship shown in the drawings. These terms are mainly used to better describe the embodiments of the present disclosure and its embodiments, and are not used to limit the indicated devices, elements or components to have a specific orientation, or to be constructed and operated in a specific orientation. In addition, in addition to indicating the orientation or positional relationship, the above-mentioned terms can also be used to indicate other meanings, for example, the term "upper" can also be used to indicate a certain dependent relationship or connection relationship in some cases. For those skilled in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to the specific circumstances.

[0049] In addition, the terms "set", "connected", "fixed" should be broadly understood. For example, "connected" can be fixedly connected, detachably connected, or integrally configured; can be mechanically connected, or electrically connected; can be directly connected, or indirectly connected through an intermediate medium, or internal communication between two devices, elements or components. For those skilled in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to the specific circumstances.

[0050] Unless otherwise specified, the term "a plurality of" means two or more.

[0051] In the embodiments of the present disclosure, the character " / " represents a "or" relationship between the objects before and after it. For example, A / B means: A or B.

[0052] The term "and / or" is a description of the association between objects, which means that there can be three relationships. For example, A and / or B means: A or B, or, A and B, the three relationships.

[0053] It should be noted that the embodiments in the embodiments of the present disclosure and the features in the embodiments can be combined with each other without conflict.

[0054] The present disclosure provides an air conditioning system, which comprises a compressor 1, a first multi-way valve 13, a second multi-way valve 14, an outdoor heat exchange module 2 and an indoor heat exchange module 3. As shown in the drawings, Figure 1As shown, the compressor 1 includes a first compression cylinder 11 with a first gas return port 111 and a second compression cylinder 12 with a second gas return port 121, and the first compression cylinder 11 and the second compression cylinder 12 are exhausted through an exhaust port 122. The indoor heat exchange module 3 includes a first evaporator 31 and a second evaporator 32 in parallel. Among them, the exhaust port 122 is communicated with the outdoor heat exchange module 2 through the first multi-way valve 13, the outdoor heat exchange module 2 is communicated with the indoor heat exchange module 3 through the first liquid pipe 4, the first evaporator 31 is communicated with the first gas return port 111 through the first gas pipe 41 and the first multi-way valve 13 in turn, and the second evaporator 32 is communicated with the second gas return port 121 through the second gas pipe 42 and the second multi-way valve 14 in turn. Moreover, 0.1MPa≤P≤0.5MPa, and / or 0.8≤V≤2, P is the gas return pressure difference of the first compression cylinder 11 and the second compression cylinder 12, and V is the volume ratio of the second compression cylinder 12 and the first compression cylinder 11. Here, the first compression cylinder 11 can be called a medium-pressure cylinder, and the second compression cylinder 12 can be called a low-pressure cylinder.

[0055] In the embodiment, the compressor 1 can be called a double-suction single-discharge double-cylinder compressor, and the two compression cylinders independently compress the gas and have the same rotating speed. The indoor heat exchange module 3 adopts two first evaporators 31 and second evaporators 32 in parallel, the first evaporator 31 returns gas to the first gas return port 111 through the first gas pipe 41, and the second evaporator 32 returns gas to the second gas return port 121 through the second gas pipe 42. In this way, by arranging two evaporators in parallel in the indoor unit and corresponding pipe layout, the first evaporator 31 and the second evaporator 32 can form different evaporation temperatures, that is, double evaporation temperatures are realized.

[0056] In the air conditioning system, the volumes and gas return pressures of the two compression cylinders directly affect the performance of the air conditioning system. Among them, the volume of the first compression cylinder 11 is denoted as v1, the volume of the second compression cylinder 12 is denoted as v2, v2 / v1=V, and 0.8≤V≤2. Limiting the value of V in this range can improve the energy-saving effect of the air conditioning system. The gas return pressure of the first compression cylinder 11 is denoted as p1, the gas return pressure of the second compression cylinder 12 is denoted as p2, p1-p2=P, and 0.1MPa≤P≤0.5MPa. Limiting the value of P in this range can effectively improve the energy-saving effect of the air conditioning system. Moreover, when the values of V and P are simultaneously within the corresponding value ranges, the gas return pressure difference and the volume ratio of the two compression cylinders can be matched, thereby greatly improving the energy efficiency of the air conditioning system.

[0057] Optionally, the value of P includes 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa or 0.5MPa.

[0058] Optionally, the value of V includes 0.8, 1, 1.2, 1.4, 1.6, 1.8 or 2.

[0059] In combination with the above embodiments, the influence of the volume ratio V on the energy efficiency ratio COP of the air conditioning system is shown in Figure 2 . In the figure, the abscissa is the volume ratio V of the second compression cylinder 12 to the first compression cylinder 11, and the ordinate is the energy efficiency ratio COP. It can be seen that as the volume ratio V of the two compression cylinders increases, the energy efficiency ratio COP first increases and then decreases. When 0.8≤V≤2, the energy efficiency ratio COP remains at a high level, and the energy efficiency ratio is highest when V is 1.4. Further, under the rated refrigeration working condition, the influence of the back pressure difference P on the energy efficiency ratio COP of the air conditioning system using the compressor 1 with V being 1.4 is shown in Figure 3 ; and under the low-temperature intermediate refrigeration working condition, the influence of the back pressure difference P on the energy efficiency ratio COP of the air conditioning system is shown in Figure 4 . In the figure, the abscissa is the back pressure difference P of the first compression cylinder 11 to the second compression cylinder 12, and the ordinate is the energy efficiency ratio COP. It can be seen that as the back pressure difference P of the two compression cylinders increases, the energy efficiency ratio COP first increases and then decreases. When 0.25MPa≤P≤0.35MPa, the energy efficiency ratio COP remains at a high level, and the energy efficiency ratio COP is optimal when P is about 0.3MPa. Therefore, by limiting the values of the parameters V and P within the above ranges, excellent technical effects can be achieved, and the energy efficiency ratio of the air conditioning system can be greatly improved.

[0060] Alternatively, as shown in Figure 1 , the first multi-way valve 13 includes valve ports C, D, E and S, the valve port C is communicated with the outdoor heat exchange module 2, the valve port D is communicated with the exhaust port 122, the valve port E is communicated with the first gas pipe 41, and the valve port S is communicated with the first back gas port 111 through the first back gas pipe section 411. The second multi-way valve 14 includes valve ports J, K, M and N, the valve port J is closed, the valve port K is communicated with the exhaust port 122, the valve port N is communicated with the second gas pipe 42, and the valve port M is communicated with the second back gas port 121 through the second back gas pipe section 421. The first back gas pipe section 411 is communicated with the second back gas pipe section 421 through the controllable communication branch 43. Furthermore, the main throttling element 21 is arranged between the indoor heat exchange module 3 and the outdoor heat exchange module 2, the first side of the first evaporator 31 communicated with the main throttling element 21 is provided with the first auxiliary throttling element 311, and the side of the second evaporator 32 communicated with the main throttling element 21 is provided with the second auxiliary throttling element 321.

[0061] In the embodiment, the multiple valve ports of the first multi-way valve 13 can switch the communication relationship, and the multiple valve ports of the second multi-way valve 14 can switch the communication relationship. The specific types of the main throttling element 21, the first auxiliary throttling element 311, and the second auxiliary throttling element 321 include electronic expansion valves, and the working states include throttling, full opening, and closing. In the throttling state, the throttling element can throttle and depress the refrigerant, in the full opening state, the throttling element is only used for the refrigerant to pass without throttling effect, and in the closing state, the throttling element blocks the refrigerant. In the case where the communication branch 43 is turned on, the return gas of the first return gas pipe section 411 and the return gas of the second return gas pipe section 421 are communicated. For example, in the case where only the return gas of the first return gas pipe section 411 exists, the communication branch 43 is controlled to be turned on, and at this time, the refrigerant of the first return gas pipe section 411 can flow to the second return gas pipe section 421 through the communication branch 43, and then the refrigerant flows to the second compression cylinder 12 for compression.

[0062] Optionally, the air conditioning system includes a full refrigeration mode, and the full refrigeration mode corresponds to that the valve port C and the valve port D are turned on, the valve port E and the valve port S are turned on, the valve port K and the valve port J are turned on, the valve port M and the valve port N are turned on, the main throttling element 21 is fully opened, and the first auxiliary throttling element 311 and the second auxiliary throttling element 321 are throttled.

[0063] In the embodiment, the flow path of the refrigerant is as shown in Figure 5 The refrigerant discharged from the compressor 1 flows to the outdoor heat exchange module 2 through the valve port D and the valve port C in sequence. In the case where the first auxiliary throttling element 311 is throttled, the first evaporator 31 refrigerates. In the case where the second auxiliary throttling element 321 is throttled, the second evaporator 32 refrigerates. At this time, the overall indoor heat exchange module 3 achieves the refrigeration effect.

[0064] Optionally, the air conditioning system includes a full heating mode, and the full heating mode corresponds to that the valve port C and the valve port S are turned on, the valve port E and the valve port D are turned on, the valve port K and the valve port N are turned on, the valve port M and the valve port J are turned on, the main throttling element 21 is throttled, and the first auxiliary throttling element 311 and the second auxiliary throttling element 321 are fully opened.

[0065] In the embodiment, the flow path of the refrigerant is as shown in Figure 6 The refrigerant discharged from the compressor 1 has two flow paths, one of which flows to the first gas pipe 41 through the valve port D and the valve port E in sequence, and the other of which flows to the second gas pipe 42 through the valve port K and the valve port N in sequence. Moreover, the refrigerant of the first gas pipe 41 flows into the first evaporator 31 to heat, and the refrigerant of the second gas pipe 42 flows into the second evaporator 32 to heat. At this time, the overall indoor heat exchange module 3 achieves the heating effect.

[0066] Optionally, the air conditioning system comprises a reheat dehumidification mode, which corresponds to: valve port C and valve port D are connected, valve port E and valve port S are connected, valve port K and valve port N are connected, valve port M and valve port J are connected, the main throttling element 21 is fully opened, and the first auxiliary throttling element 311 is throttled and the second auxiliary throttling element 321 is fully opened.

[0067] In this embodiment, the flow path of the refrigerant is as shown in Figure 7 The refrigerant discharged by the compressor 1 has two flow paths, one of which flows to the outdoor heat exchange module 2 along valve port D and valve port C in sequence, and the other of which flows to the second gas pipe 42 along valve port K and valve port N in sequence. In the case where the main throttling element 21 is fully opened and the first auxiliary throttling element 311 is throttled, the first evaporator 31 cools. And the refrigerant of the second gas pipe 42 flows to the second evaporator 32 to heat. At this time, the indoor air first flows through the first evaporator 31 to achieve dehumidification effect, and then flows through the second evaporator 32 to achieve reheat effect, improving the comfort of the user.

[0068] Optionally, the air conditioning system comprises two parallel indoor heat exchange modules 3, which are respectively referred to as the first module 33 and the second module 34. By adjusting the working state of the plurality of throttling elements, a plurality of operating modes can be realized. It should be noted that in the case where the air conditioning system comprises three or more parallel indoor heat exchange modules 3, it is still within the protection scope of the present application.

[0069] Optionally, the air conditioning system comprises a reheat dehumidification and cooling mode, which corresponds to: valve port C and valve port D are connected, valve port E and valve port S are connected, valve port K and valve port N are connected, valve port M and valve port J are connected, the main throttling element 21 is fully opened, the first auxiliary throttling element 311 of the first module 33 is throttled and the second auxiliary throttling element 321 is closed, and the first auxiliary throttling element 311 of the second module 34 is throttled and the second auxiliary throttling element 321 is fully opened.

[0070] In this embodiment, the flow path of the refrigerant is as shown in Figure 8 The refrigerant discharged by the compressor 1 has two flow paths, one of which flows to the outdoor heat exchange module 2 along valve port D and valve port C in sequence, and the other of which flows to the second gas pipe 42 along valve port K and valve port N in sequence. In the case where the main throttling element 21 is fully opened and the first auxiliary throttling element 311 is throttled, the first evaporator 31 cools and the second evaporator 32 has no refrigerant flow. In the case where the main throttling element 21 is fully opened and the first auxiliary throttling element 311 is throttled, the first evaporator 31 of the first module 33 dehumidifies and the second evaporator 32 reheats. At this time, the first module 33 is used to achieve the cooling effect, and the second module 34 is used to achieve the reheat dehumidification effect.

[0071] Optionally, the air conditioning system comprises a reheat dehumidification and heating mode, which corresponds to: the valve port C and the valve port D being communicated, the valve port E and the valve port S being communicated, the valve port K and the valve port N being communicated, the valve port M and the valve port J being communicated, the main throttling element 21 being fully opened, the first sub-throttling element 311 of the first module 33 being closed and the second sub-throttling element 321 being fully opened, and the first sub-throttling element 311 of the second module 34 being throttled and the second sub-throttling element 321 being fully opened.

[0072] In the embodiment, the flow path of the refrigerant is as shown in Figure 9 The refrigerant discharged by the compressor 1 has two flow paths, one of which flows to the outdoor heat exchange module 2 along the valve port D and the valve port C in sequence, and the other of which flows to the second air pipe 42 along the valve port K and the valve port N in sequence. Under the working state of the above-mentioned multiple throttling elements, the first evaporator 31 of the first module 33 has no refrigerant flow and the second evaporator 32 heats, and the first evaporator 31 of the first module 33 dehumidifies and the second evaporator 32 reheats. At this time, the heating effect is realized by using the first module 33, and the reheat dehumidification effect is realized by using the second module 34.

[0073] Optionally, the air conditioning system comprises a simultaneous cooling and heating mode, which corresponds to: the valve port C and the valve port D being communicated, the valve port E and the valve port S being communicated, the valve port K and the valve port N being communicated, the valve port M and the valve port J being communicated, the main throttling element 21 being fully opened, the first sub-throttling element 311 of the first module 33 being closed and the second sub-throttling element 321 being fully opened, and the first sub-throttling element 311 of the second module 34 being throttled and the second sub-throttling element 321 being closed.

[0074] In the embodiment, the flow path of the refrigerant is as shown in Figure 10 The refrigerant discharged by the compressor 1 has two flow paths, one of which flows to the outdoor heat exchange module 2 along the valve port D and the valve port C in sequence, and the other of which flows to the second air pipe 42 along the valve port K and the valve port N in sequence. Under the working state of the above-mentioned multiple throttling elements, the first evaporator 31 of the first module 33 has no refrigerant flow and the second evaporator 32 heats, and the first evaporator 31 of the first module 33 dehumidifies and the second evaporator 32 reheats. At this time, the heating effect is realized by using the first module 33, and the reheat dehumidification effect is realized by using the second module 34.

[0075] The above description and drawings suffice to fully enable one skilled in the art to practice the embodiments of the present disclosure. Other embodiments can include structural and other changes. The embodiments are merely representative of possible variations. Individual components and functions are optional unless explicitly required, and the order of operations can be varied. Portions and features of some embodiments can be included in, or substituted for, portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the drawings, and can be varied in a variety of ways. The scope of the present disclosure is limited only by the claims that follow.

Claims

1. An air conditioning system, characterized in that: include: A compressor (1), a first multi-way valve (13), a second multi-way valve (14), an outdoor heat exchange module (2), and an indoor heat exchange module (3); the compressor (1) comprises a first compression cylinder (11) having a first air return port (111) and a second compression cylinder (12) having a second air return port (121), and the first compression cylinder (11) and the second compression cylinder (12) exhaust air through an exhaust port (122); the indoor heat exchange module (3) comprises a first evaporator (31) and a second evaporator (32) connected in parallel; The exhaust port (122) is connected to the outdoor heat exchange module (2) through the first multi-way valve (13), the outdoor heat exchange module (2) is connected to the indoor heat exchange module (3) through the first liquid pipe (4), the first evaporator (31) is connected to the first return air port (111) through the first air pipe (41) and the first multi-way valve (13), and the second evaporator (32) is connected to the second return air port (121) through the second air pipe (42) and the second multi-way valve (14). Furthermore, 0.1 MPa≤P≤0.5 MPa, and / or, 0.8≤V≤2, P is the return air pressure difference between the first compression cylinder (11) and the second compression cylinder (12), and V is the volume ratio of the second compression cylinder (12) to the first compression cylinder (11).

2. The air conditioning system according to claim 1, characterized in that The values ​​of P include 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa or 0.5MPa.

3. The air conditioning system according to claim 1, characterized in that The values ​​of V include 0.8, 1, 1.2, 1.4, 1.6, 1.8 or 2.

4. The air conditioning system according to any one of claims 1 to 3, characterized in that: The first multi-way valve (13) includes a valve port C, a valve port D, a valve port E, and a valve port S, wherein the valve port C is connected to the outdoor heat exchange module (2), the valve port D is connected to the exhaust port (122), the valve port E is connected to the first air pipe (41), and the valve port S is connected to the first air return port (111) via the first air return pipe section (411); The second multi-way valve (14) includes a valve port J, valve ports K, M, and valve port N. The valve port J is closed, the valve port K is connected to the exhaust port (122), the valve port N is connected to the second air pipe (42), and the valve port M is connected to the second air return port (121) via the second air return pipe section (421); the first air return pipe section (411) is connected to the second air return pipe section (421) via a controllable connecting branch (43); In addition, a main throttling element (21) is provided between the indoor heat exchange module (3) and the outdoor heat exchange module (2), a first auxiliary throttling element (311) is provided on the side of the first evaporator (31) that is connected to the main throttling element (21), and a second auxiliary throttling element (321) is provided on the side of the second evaporator (32) that is connected to the main throttling element (21).

5. The air conditioning system according to claim 4, characterized in that The air conditioning system includes a full cooling mode, which corresponds to: valve port C is connected to valve port D, valve port E is connected to valve port S, valve port K is connected to valve port J, valve port M is connected to valve port N, the main throttling element (21) is fully open, and the first sub-throttling element (311) and the second sub-throttling element (321) are both throttled.

6. The air conditioning system according to claim 4, characterized in that The air conditioning system includes a full heating mode, which corresponds to: valve port C is connected to valve port S, valve port E is connected to valve port D, valve port K is connected to valve port N, valve port M is connected to valve port J, the main throttling element (21) is throttled, and the first sub-throttling element (311) and the second sub-throttling element (321) are both fully open.

7. The air conditioning system according to claim 4, characterized in that The air conditioning system includes a reheat dehumidification mode, which corresponds to: valve port C is connected to valve port D, valve port E is connected to valve port S, valve port K is connected to valve port N, valve port M is connected to valve port J, the main throttling element (21) is fully opened, the first auxiliary throttling element (311) is throttled, and the second auxiliary throttling element (321) is fully opened.

8. The air conditioning system according to claim 4, characterized in that The air conditioning system includes two indoor heat exchange modules (3) connected in parallel, respectively referred to as a first module (33) and a second module (34); The air conditioning system includes a reheat dehumidification and cooling mode, and the reheat dehumidification and cooling mode corresponds to: valve port C is connected to valve port D, valve port E is connected to valve port S, valve port K is connected to valve port N, valve port M is connected to valve port J, the main throttling element (21) is fully opened, the first sub-throttling element (311) of the first module (33) is throttled and the second sub-throttling element (321) is closed, and the first sub-throttling element (311) of the second module (34) is throttled and the second sub-throttling element (321) is fully opened.

9. The air conditioning system according to claim 4, characterized in that The air conditioning system includes two indoor heat exchange modules (3) connected in parallel, respectively referred to as a first module (33) and a second module (34); The air conditioning system includes a reheat dehumidification and heating mode, and the reheat dehumidification and heating mode corresponds to: valve port C is connected to valve port D, valve port E is connected to valve port S, valve port K is connected to valve port N, valve port M is connected to valve port J, the main throttling element (21) is fully opened, the first sub-throttling element (311) of the first module (33) is closed and the second sub-throttling element (321) is fully opened, and the first sub-throttling element (311) of the second module (34) is throttled and the second sub-throttling element (321) is fully opened.

10. The air conditioning system according to claim 4, characterized in that The air conditioning system includes two indoor heat exchange modules (3) connected in parallel, respectively referred to as a first module (33) and a second module (34); The air conditioning system includes a simultaneous cooling and heating mode, and the simultaneous cooling and heating mode corresponds to: valve port C is connected to valve port D, valve port E is connected to valve port S, valve port K is connected to valve port N, valve port M is connected to valve port J, the main throttling element (21) is fully open, the first auxiliary throttling element (311) of the first module (33) is closed and the second auxiliary throttling element (321) is fully open, and the first auxiliary throttling element (311) of the second module (34) is throttled and the second auxiliary throttling element (321) is closed.

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