Air conditioning system capable of efficiently refrigerating and heating

Abstract

The invention belongs to the technical field related to air conditioners, and discloses an air conditioning system capable of efficiently refrigerating and heating. In a refrigeration mode, a working medium at an outlet of the compressor sequentially passes through the second outdoor heat exchanger and the first outdoor heat exchanger for heat exchange and then enters the ejector; liquid in the gas-liquid separator enters the second indoor heat exchanger through the throttling mechanism, and the fluid subjected to heat exchange enters the ejector; fluid at an outlet of the ejector enters the first indoor heat exchanger; gas in the gas-liquid separator flows to the compressor; in the heating mode, a working medium at an outlet of the compressor sequentially enters the second indoor unit and the first indoor unit and then enters the ejector. Liquid in the gas-liquid separator enters the second outdoor heat exchanger through the throttling mechanism, and the fluid subjected to heat exchange enters the ejector; fluid at an outlet of the ejector enters the first outdoor heat exchanger, and a working medium subjected to heat exchange enters the gas-liquid separator; and gas in the gas-liquid separator flows back to the compressor. By means of the air conditioner, the problem that in the prior art, energy consumption is high in a refrigerating mode and a heating mode is solved.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning technology, and more specifically, relates to an efficient air conditioning system for cooling and heating. Background Technology

[0002] Against the backdrop of increasingly severe global warming, the replacement of energy-saving and environmentally friendly refrigerants has become a core issue for the refrigeration and air conditioning industry. Currently, compression refrigeration cycles all use throttling valves to reduce pressure and temperature, completely failing to recover the work done during the pressure reduction process, resulting in significant throttling losses and reduced system energy efficiency. Taking the natural working fluid CO2 as an example, CO2 is considered a highly promising alternative refrigerant due to its advantages such as a GWP of 1, non-toxicity, non-flammability, wide availability, and good economics. However, the CO2 cycle has certain energy efficiency bottlenecks. Its main energy losses come from throttling losses when the refrigerant flows through the expansion device, irreversible losses during the compressor compression process, and irreversible heat losses in the heat exchanger due to temperature differences. Therefore, improving system energy efficiency should focus on reducing throttling losses, enhancing heat transfer performance, and optimizing system matching. In this context, ejectors, due to their simple structure, lack of moving parts, reliable operation, and low cost, have received widespread attention in the performance optimization of compression refrigeration cycles, especially in CO2 systems. Studies have shown that integrating the injector into the transcritical CO2 cycle can effectively recover some of the expansion work, increase the compressor intake pressure and reduce the compression ratio, thereby significantly improving the overall system performance coefficient.

[0003] Currently, patent CN202110481981.6 discloses a dual-efficiency carbon dioxide air conditioning heat pump system. This solution uses CO2 as the working fluid and, through an innovative circulation design, allows the system to operate as a dual-temperature injection expansion cycle in cooling mode and switch to a conventional heat pump cycle in heating mode. Although this patent achieves the switching between cooling and heating when using an ejector instead of a throttle valve, the large number of valves and complex piping in this patent reduces the reliability of the system to some extent. Patent applications CN202510810548.0 and CN202510989039.9 successively disclose a carbon dioxide air conditioning heat pump system with an integrated multi-way valve and a reversing valve and air conditioning heat pump system. These two patent applications optimize the system architecture based on patent CN202110481981.6, replacing multiple one-way valves with a multi-way valve, similarly achieving the switching between cooling and heating when using an ejector instead of a throttle valve, thus significantly simplifying the system and improving its reliability. However, there is still room for further optimization of the above technologies. In patent CN202110481981.6, the ejector is only used in the cooling mode, and the heating mode of the system is still a conventional heat pump. In patents CN202510810548.0 and CN202510989039.9, the heating mode is a conventional single-evaporation temperature compression / ejection heat pump. Under low-temperature conditions, it still has shortcomings such as high compressor pressure ratio and significant system efficiency degradation. Existing technologies still have room for improvement in terms of system configuration and performance enhancement. Summary of the Invention

[0004] In view of the above-mentioned defects or improvement needs of the existing technology, the present invention provides an efficient air conditioning system for both cooling and heating, thereby improving the energy efficiency of the existing technology in both cooling and heating modes.

[0005] To achieve the above objectives, according to one aspect of the present invention, a high-efficiency cooling and heating air conditioning system is provided, the system comprising a compressor, a gas-liquid separator, a throttling mechanism, a first indoor heat exchanger, a second indoor heat exchanger, a first outdoor heat exchanger, a second outdoor heat exchanger, and an ejector, wherein: In cooling mode, the working fluid from the compressor outlet passes sequentially through the second outdoor heat exchanger and the first outdoor heat exchanger to achieve secondary heat exchange with the outdoor air. After heat exchange, the working fluid enters the ejector. The liquid in the gas-liquid separator is cooled and depressurized by the throttling mechanism and then enters the second indoor heat exchanger to achieve heat exchange with the indoor air. The fluid after heat exchange enters the ejector. The two streams of working fluid entering the ejector are evenly mixed and then flow out of the ejector and into the first indoor heat exchanger to achieve heat exchange with the indoor air. The working fluid flowing out of the first indoor heat exchanger enters the gas-liquid separator, and the gas separated from the gas-liquid separator flows back to the compressor. In heating mode, the working fluid from the compressor outlet sequentially enters the second indoor heat exchanger and the first indoor heat exchanger to exchange heat with the indoor air twice. After heat exchange, the working fluid enters the ejector. The liquid in the gas-liquid separator is cooled and depressurized by the throttling mechanism and then enters the second outdoor heat exchanger to exchange heat with the outdoor air. After heat exchange, the fluid enters the ejector. The two streams of working fluid entering the ejector are evenly mixed and then flow out of the ejector and into the first outdoor heat exchanger to exchange heat with the outdoor air. After heat exchange, the working fluid enters the gas-liquid separator, and the gas separated from the gas-liquid separator flows back to the compressor.

[0006] More preferably, the system further includes a first four-way reversing valve, a second four-way reversing valve, and a first six-way reversing valve, wherein the first four-way reversing valve is used to adjust the connection relationship between the compressor, the second outdoor heat exchanger, the throttling mechanism, and the second indoor heat exchanger; the second four-way reversing valve is used to adjust the connection relationship between the gas-liquid separator, the first outdoor heat exchanger, the first indoor heat exchanger, and the main fluid inlet end of the ejector; and the first six-way reversing valve is used to adjust the connection relationship between the outlet end of the ejector, the first indoor heat exchanger, the second indoor heat exchanger, the ejector fluid inlet end of the ejector, and the second outdoor heat exchanger and the first outdoor heat exchanger.

[0007] More preferably, the first four-way directional valve is an electromagnetic four-way directional valve.

[0008] More preferably, the second four-way directional valve and the first six-way directional valve employ differential pressure driven valve cores.

[0009] More preferably, the second four-way reversing valve includes two pressure chambers, a valve core, and four ports. The pressure chambers are respectively located at both ends of the valve body, the valve core is located between the two pressure chambers, three ports are located on one side of the valve body, and one port is located on the other side of the valve body. The valve core is moved by forming a pressure difference between the two pressure chambers.

[0010] More preferably, the system further includes a first four-way reversing valve, a second six-way reversing valve, and a first six-way reversing valve, wherein the first four-way reversing valve is used to adjust the connection relationship between the compressor, the second outdoor heat exchanger, the throttling mechanism, and the second indoor heat exchanger; the second six-way reversing valve is used to adjust the connection relationship between the gas-liquid separator, the first outdoor heat exchanger, the first indoor heat exchanger, the internal heat exchanger, and the main fluid inlet end of the ejector; and the first six-way reversing valve is used to adjust the connection relationship between the outlet end of the ejector, the first indoor heat exchanger, the second indoor heat exchanger, the ejector fluid inlet end of the ejector, and the second outdoor heat exchanger and the first outdoor heat exchanger.

[0011] More preferably, the first six-way reversing valve includes two pressure chambers, a valve core, and six ports. The pressure chambers are respectively located at both ends of the valve body, the valve core is located between the two pressure chambers, five ports are located on one side of the valve body, and one port is located on the other side of the valve body. The valve core is moved by forming a pressure difference between the two pressure chambers.

[0012] More preferably, the system also includes an internal heat exchanger, which is connected as follows: When the system uses a second four-way reversing valve: in cooling mode, the gas-liquid separator, internal heat exchanger, and compressor are connected in sequence to form the first internal heat exchange path; the first outdoor heat exchanger, internal heat exchanger, and ejector are connected in sequence to form the second internal heat exchange path; in heating mode, the gas-liquid separator, internal heat exchanger, and compressor are connected in sequence to form the first internal heat exchange path; the first indoor heat exchanger, internal heat exchanger, and ejector are connected in sequence to form the second internal heat exchange path.

[0013] When the system uses the second six-way reversing valve: in cooling mode, the gas-liquid separator, the internal heat exchanger and the compressor are connected in sequence to form the first internal heat exchange passage, and the first outdoor heat exchanger, the internal heat exchanger and the ejector are connected in sequence to form the second internal heat exchange passage; in heating mode, the internal heat exchanger does not work.

[0014] More preferably, the injector is a single injector or multiple injectors arranged in parallel.

[0015] In summary, the technical solutions conceived by this invention have the following beneficial effects compared with the prior art: 1. This invention employs two outdoor heat exchangers and two indoor heat exchangers to achieve efficient heat exchange between refrigerant and air in both cooling and heating modes. Irreversible losses are reduced by optimizing the temperature matching between air and refrigerant. At the same time, by using ejectors to recover expansion work, increase compressor suction pressure, and achieve dual evaporation temperatures, the energy efficiency of existing technologies in both cooling and heating modes is improved.

[0016] 2. The system employs a dual indoor / outdoor heat exchanger design. In cooling mode, indoor air flows sequentially through the first indoor heat exchanger (acting as a medium-temperature evaporator) and the second indoor heat exchanger (acting as a low-temperature evaporator), undergoing progressive cooling. Simultaneously, outdoor air flows sequentially through the first and second outdoor heat exchangers, being heated in sequence. In heating mode, the high-temperature refrigerant from the compressor enters the second and first indoor heat exchangers sequentially, cooling and releasing heat. Meanwhile, indoor air flows sequentially through the first and second indoor heat exchangers, being heated. Simultaneously, outdoor air flows sequentially through the first outdoor heat exchanger (acting as a medium-temperature evaporator) and the second outdoor heat exchanger (acting as a low-temperature evaporator), undergoing progressive cooling. This optimized heat exchanger arrangement improves the temperature matching between indoor and outdoor air and the refrigerant in both cooling and heating modes, effectively reducing irreversible heat loss due to temperature differences.

[0017] 3. This invention achieves efficient switching between cooling and heating modes by integrating a four-way reversing valve and a six-way reversing valve and optimizing the system flow. In both operating modes, the ejector is effectively utilized to recover expansion work, increase the compressor suction pressure, and reduce the compression ratio. Simultaneously, the pressurization characteristics of the ejector are used to achieve dual evaporation temperatures, optimizing temperature matching in the heat exchange process and significantly improving cycle efficiency.

[0018] 4. This invention innovatively utilizes a four-way reversing valve and a six-way reversing valve to connect key components, achieving a highly integrated dual-mode system architecture. The cooling and heating modes fully share components such as the gas-liquid separator, throttling mechanism, ejector, heat exchanger, and piping, eliminating the need for additional valves or piping. Furthermore, the four-way and six-way reversing valves are pressure-driven, utilizing the pressure difference of the fluid within the system as the driving force, requiring no additional electrical or mechanical power input, thus achieving automatic reversing. Therefore, the system ensures high efficiency in both cooling and heating while maintaining the outstanding advantages of simple structure, compactness, reliability, and low cost.

[0019] 5. In this invention, the internal heat exchanger is designed as an optional module, which can be flexibly selected for configuration based on factors such as actual application energy efficiency requirements, cost budget, and space constraints. When the internal heat exchanger is selected, the second four-way reversing valve can be retained or replaced with the second six-way reversing valve, depending on the system design and operating conditions, to adjust the heat exchange of the internal heat exchanger during heating. For different schemes, only the connections of the inlet and outlet pipes and the connection of the ejector's main fluid inlet end need to be adjusted, while the other components of the system and their layout remain unchanged, demonstrating the system's high degree of inclusiveness and flexibility. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the cooling mode of an air conditioning system for high-efficiency cooling and heating without an internal heat exchanger, according to a preferred embodiment of the present invention.

[0021] Figure 2 This is a schematic diagram of the heating mode of an efficient cooling and heating air conditioning system without an internal heat exchanger, according to a preferred embodiment of the present invention.

[0022] Figure 3 This is a schematic diagram of the cooling mode of an air conditioning system with an internal heat exchanger provided according to a preferred embodiment of the present invention.

[0023] Figure 4 This is a schematic diagram of the heating mode of an air conditioning system with an internal heat exchanger configured according to a preferred embodiment of the present invention.

[0024] Figure 5 This is a schematic diagram of the cooling mode of the second four-way reversing valve provided according to a preferred embodiment of the present invention.

[0025] Figure 6 This is a schematic diagram of the heating mode of the second four-way reversing valve provided according to a preferred embodiment of the present invention.

[0026] Figure 7 This is a schematic diagram of the cooling mode structure of the first six-way reversing valve according to a preferred embodiment of the present invention.

[0027] Figure 8 This is a schematic diagram of the heating mode structure of the first six-way reversing valve provided according to a preferred embodiment of the present invention.

[0028] Figure 9 This is a schematic diagram of an air conditioning system without an internal heat exchanger in cooling mode, according to a preferred embodiment of the present invention, showing a second four-way reversing valve and a first six-way reversing valve.

[0029] Figure 10 This is a schematic diagram of an air conditioning system without an internal heat exchanger in heating mode, according to a preferred embodiment of the present invention, showing a second four-way reversing valve and a first six-way reversing valve.

[0030] Figure 11 This is a schematic diagram of an air conditioning system with an internal heat exchanger, configured according to a preferred embodiment of the present invention, in cooling mode, featuring a second four-way reversing valve and a first six-way reversing valve.

[0031] Figure 12 This is a schematic diagram of an air conditioning system with an internal heat exchanger, configured according to a preferred embodiment of the present invention, in heating mode, featuring a second four-way reversing valve and a first six-way reversing valve.

[0032] Figure 13This is a schematic diagram of an air conditioning system with an internal heat exchanger, configured according to a preferred embodiment of the present invention, in cooling mode, featuring a first six-way reversing valve and a second six-way reversing valve.

[0033] Figure 14 This is a schematic diagram of an air conditioning system with an internal heat exchanger, configured according to a preferred embodiment of the present invention, in heating mode, featuring a first six-way reversing valve and a second six-way reversing valve.

[0034] In all the accompanying drawings, the same reference numerals are used to denote the same elements or structures, wherein: 1-Compressor, 2-Gas-liquid separator, 3-First four-way reversing valve, 4-Second four-way reversing valve, 5-Throttle mechanism, 6-Internal heat exchanger, 7-First indoor heat exchanger, 8-Second indoor heat exchanger, 9-First outdoor heat exchanger, 10-Second outdoor heat exchanger, 11-Fan, 12-First six-way reversing valve, 13-Ejector, 14-Second six-way reversing valve. Detailed Implementation

[0035] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention. Furthermore, the technical features involved in the various embodiments of this invention described below can be combined with each other as long as they do not conflict with each other.

[0036] like Figure 1 and 2 As shown, in one embodiment of the present invention, an efficient air conditioning system for cooling and heating is provided. The system includes a compressor 1, a gas-liquid separator 2, a first four-way reversing valve 3, a second four-way reversing valve 4, a throttling mechanism 5, a first indoor heat exchanger 7, a second indoor heat exchanger 8, a first outdoor heat exchanger 9, a second outdoor heat exchanger 10, a fan 11, a first six-way reversing valve 12, and an ejector 13.

[0037] As a further preferred embodiment, the first four-way reversing valve 3 is electromagnetically driven. It receives external commands to realize the refrigerant reversal when switching between cooling and heating functions. The first four-way reversing valve 3 has four ports, namely 3a to 3d. Port 3a of the first four-way reversing valve 3 is connected to the outlet of the throttling mechanism 5, port 3b of the first four-way reversing valve 3 is connected to the inlet of the second outdoor heat exchanger 10, port 3c of the first four-way reversing valve 3 is connected to the outlet of the compressor 1, and port 3d of the first four-way reversing valve 3 is connected to the inlet of the second indoor heat exchanger 8.

[0038] As a further preferred option, such as Figure 5 and 6 , Figure 9 and10 As shown, the second four-way reversing valve 4 is driven by the internal pressure difference of the system. That is, it uses the pressure difference of the fluid formed when the system is cooling or heating to drive the four-way reversing valve to work, realizing the refrigerant reversal required to adapt to the system's cooling or heating. The second four-way reversing valve 4 has four ports, namely 4a to 4d. Port 4a of the second four-way reversing valve 4 is connected to the inlet of the gas-liquid separator 2, port 4b of the second four-way reversing valve 4 is connected to the outlet of the first outdoor heat exchanger 9, port 4c of the second four-way reversing valve 4 is connected to the first inlet of the ejector 13, and port 4d of the second four-way reversing valve 4 is connected to the outlet of the first indoor heat exchanger 7.

[0039] In cooling mode, the fluid flowing through port 4b of the second four-way directional valve 4 is a high-pressure fluid, while the fluid flowing through port 4d of the second four-way directional valve 4 is a relatively low-pressure fluid. Under the pressure difference between the high-pressure and low-pressure fluids, the second four-way directional valve 4 internally forms a flow path connection relationship of 4b→4c and 4d→4a, that is, port 4b is connected to port 4c and port 4a is connected to port 4d, thereby enabling the system to enter the cooling cycle operation state. In heating mode, the fluid flowing through port 4d of the second four-way directional valve 4 is a high-pressure fluid, while the fluid flowing through port 4b of the second four-way directional valve 4 is a relatively low-pressure fluid. Under the pressure difference between the high-pressure and low-pressure fluids, the second four-way directional valve 4 internally forms a flow path connection relationship of 4b→4a and 4d→4c, that is, port 4b is connected to port 4a and port 4c is connected to port 4d, thereby enabling the system to enter the heating cycle operation state.

[0040] As a further preferred option, such as Figure 7 and 8 , Figure 9 and 10 As shown, the first six-way reversing valve 12 has six ports, designated 12A to 12F. Port 12A of the first six-way reversing valve 12 is connected to the outlet of the ejector 13, port 12B of the first six-way reversing valve 12 is connected to the inlet of the first indoor heat exchanger 7, port 12C of the first six-way reversing valve 12 is connected to the outlet of the second indoor heat exchanger 8, port 12D of the first six-way reversing valve 12 is connected to the second inlet of the ejector 13, port 12E of the first six-way reversing valve 12 is connected to the outlet of the second outdoor heat exchanger 10, and port 12F of the first six-way reversing valve 12 is connected to the inlet of the first outdoor heat exchanger 9. By switching the first four-way reversing valve 3, the second four-way reversing valve 4, and the first six-way reversing valve 12, the flow direction of the refrigerant is changed, thereby enabling the system to switch between cooling mode and heating mode.

[0041] The first six-way reversing valve 12 is a two-position six-way reversing valve driven by pressure difference. It utilizes the pressure difference of the fluids generated during system cooling or heating to drive the valve, achieving refrigerant reversal to suit the system's cooling or heating needs. In cooling mode, the fluid flowing through port 12E of the first six-way reversing valve 12 is a high-pressure fluid, while the fluid flowing through port 12C is a relatively low-pressure fluid. Under the pressure difference between the high-pressure and low-pressure fluids, the first six-way reversing valve 12 internally forms flow path connections of 12A→12B, 12C→12D, and 12E→12F. Specifically, ports 12A and 12B, 12C and 12D, and 12E and 12F of the first six-way reversing valve 12 are connected, thereby enabling the system to enter a refrigeration cycle operation. In heating mode, the fluid flowing through port 12C of the first six-way directional valve 12 is a high-pressure fluid, and the fluid flowing through port 12E of the first six-way directional valve 12 is a relatively low-pressure fluid. Under the pressure difference between the high-pressure fluid and the low-pressure fluid, the first six-way directional valve 12 forms a flow path connection relationship of 12A→12F, 12C→12B, and 12E→12D. That is, port 12A of the first six-way directional valve 12 is connected to port 12F, port 12B is connected to port 12C, and port 12D is connected to port 12E, thereby enabling the system to enter the heating cycle operation state.

[0042] As a further preferred embodiment, in both cooling and heating dual modes, both the indoor and outdoor heat exchangers achieve counter-current heat exchange between the heat exchange medium and the air. In cooling mode, the indoor air sequentially passes through the first indoor heat exchanger 7, the medium-temperature evaporator, the second indoor heat exchanger 8, and the low-temperature evaporator for sequential cooling. The two indoor heat exchangers achieve independent air drying and dehumidification, while the outdoor air is sequentially heated through the first outdoor heat exchanger 9 and the second outdoor heat exchanger 10. In heating mode, the high-temperature, high-pressure refrigerant from the compressor 1 sequentially enters the second indoor heat exchanger 8 and the first indoor heat exchanger 7 for sequential cooling and heat release, while the indoor air is sequentially heated through the first indoor heat exchanger 7 and the second indoor heat exchanger 8. Simultaneously, the outdoor air sequentially passes through the first outdoor heat exchanger 9, the medium-temperature evaporator, the second outdoor heat exchanger 10, and the low-temperature evaporator for sequential cooling. The indoor / outdoor dual heat exchanger design reduces irreversible losses in the heat exchange process in both modes, achieving efficient cooling and efficient heating of the system.

[0043] As a further preferred embodiment, the system may be equipped with an internal heat exchanger 6, which is an optional module and can be selected for inclusion or exclusion based on actual application requirements and space costs. If the internal heat exchanger 6 is selected, its heat exchange characteristics during heating can be chosen according to the system design and operating conditions.

[0044] like Figure 9 and 10As shown, when the internal heat exchanger 6 is not configured, the gas outlet of the gas-liquid separator 2 is directly connected to the suction end of the compressor. In the cooling mode, the refrigerant flows out of the first outdoor heat exchanger 9 and then flows through the 4b port of the second four-way reversing valve 4 to the 4c ​​port, and then enters the first inlet of the ejector 13. In addition, the refrigerant vapor from the gas outlet of the gas-liquid separator 2 directly enters the suction port of the compressor 1. In the heating mode, the refrigerant flows out of the first indoor heat exchanger 7 and then flows through the 4d port of the second four-way reversing valve 4 to the 4c ​​port, and then enters the first inlet of the ejector 13. In addition, the refrigerant vapor from the gas outlet of the gas-liquid separator 2 directly enters the suction port of the compressor 1.

[0045] like Figure 11 and 12 As shown, when the internal heat exchanger 6 is configured and exchanges heat in both cooling and heating modes, the 3a port of the first four-way reversing valve 3 is connected to the outlet of the throttling mechanism 5, the 3b port is connected to the inlet of the second outdoor heat exchanger 10, the 3c port is connected to the outlet of the compressor 1, and the 3d port is connected to the inlet of the second indoor heat exchanger 8; the 4a port of the second four-way reversing valve 4 is connected to the inlet of the gas-liquid separator 2, the 4b port is connected to the outlet of the first outdoor heat exchanger 9 and the pressure chamber 1 of the second four-way reversing valve 4, and the 4c ​​port is connected to the inlet of the second passage of the internal heat exchanger 6. The 4d interface is connected to the outlet of the first indoor heat exchanger 7 and to the pressure chamber 2 of the second four-way reversing valve 4; the 12A interface of the first six-way reversing valve 12 is connected to the outlet of the ejector 13, the 12B interface is connected to the inlet of the first indoor heat exchanger 7, the 12C interface is connected to the outlet of the second indoor heat exchanger 8 and to the pressure chamber 2 of the first six-way reversing valve 12, the 12D interface is connected to the second inlet of the ejector 13, the 12E interface is connected to the outlet of the second outdoor heat exchanger 10 and to the pressure chamber 1 of the first six-way reversing valve 12, and the 12F interface is connected to the inlet of the first outdoor heat exchanger 9.

[0046] like Figure 13 and 14As shown, when the internal heat exchanger 6 is configured and only performs heat exchange in cooling mode, and not in heating mode, the second four-way reversing valve 4 is replaced by the second six-way reversing valve 14. The second six-way reversing valve 14 is similar in structure and working principle to the first six-way reversing valve 12. The 3a port of the first four-way reversing valve 3 is connected to the outlet of the throttling mechanism 5, the 3b port is connected to the inlet of the second outdoor heat exchanger 10, the 3c port is connected to the outlet of the compressor 1, and the 3d port is connected to the inlet of the second indoor heat exchanger 8. The 14A port of the second six-way reversing valve 14 is connected to the outlet of the first indoor heat exchanger 7, the 14B port is connected to the inlet of the gas-liquid separator 2, the 14C port is connected to the outlet of the first outdoor heat exchanger 9, and the 14D port is connected to the inlet of the second passage of the internal heat exchanger 6. The 14E port is connected to the outlet of the second passage of the internal heat exchanger 6, and the 14F port is connected to the first inlet of the ejector 13; the 12A port of the first six-way reversing valve 12 is connected to the outlet of the ejector 13, the 12B port is connected to the inlet of the first indoor heat exchanger 7, the 12C port is connected to the outlet of the second indoor heat exchanger 8, the 12D port is connected to the second inlet of the ejector 13, the 12E port is connected to the outlet of the second outdoor heat exchanger 10, and the 12F port is connected to the inlet of the first outdoor heat exchanger 9.

[0047] As a further preferred embodiment, the ejector 13 has three interfaces: a first inlet, a second inlet, and an outlet. The ejector 13 can be a single ejector or multiple ejectors connected in parallel, i.e., an ejector group. The specific configuration should be designed according to actual application requirements and space costs. In both cooling and heating modes of the system, the ejector 13 can effectively recover expansion work, increase the compressor suction pressure, and reduce system throttling losses and compressor power consumption.

[0048] like Figure 1 and 2 As shown below, the working principle of the air conditioning system without an internal heat exchanger in cooling and heating modes will be introduced.

[0049] In cooling mode, the 3a and 3d ports of the first four-way reversing valve 3 are connected, as are the 3b and 3c ports; the 4a and 4d ports of the second four-way reversing valve 4 are connected, as are the 4b and 4c ports; and the 12A and 12B ports of the first six-way reversing valve 12 are connected, as are the 12C and 12D ports, and the 12E and 12F ports. After the compressor 1 compresses the refrigerant to a high temperature and pressure, it flows through the 3c port of the first four-way reversing valve 3 to the 3b port, entering the second outdoor heat exchanger 10 for heat release, and then through the first six-way reversing valve... The fluid flows from port 12E of valve 12 to port 12F, entering the first outdoor heat exchanger 9 for heat release. The outflowing fluid flows from port 4b of the second four-way reversing valve 4 to port 4c, and then enters the first inlet of ejector 13. Ejector 13 has three ports: a first inlet, a second inlet, and an outlet. High-pressure refrigerant, acting as the driving fluid, enters ejector 13 from the first inlet and is then injected, creating a first pressure and a second pressure at the outlet and second inlet of ejector 13, respectively. The first pressure is higher than the second pressure, while both the first and second pressures are lower than the pressure at the ejector 13. The refrigerant vapor at the inlet high-pressure gas pressure and the outlet pressure of the second indoor heat exchanger 8 flows from port 12C of the first six-way reversing valve 12 to port 12D. It then enters the ejector 13 through the second inlet of the ejector and mixes with the motive fluid refrigerant. The pressure of the mixed refrigerant is increased to the first pressure, and it flows out from the outlet of the ejector 13. The refrigerant at the first pressure at the outlet of the ejector 13 flows from port 12A of the first six-way reversing valve 12 to port 12B, and then enters the first indoor heat exchanger 7 for evaporation and heat absorption. The refrigerant at the outlet of the first indoor heat exchanger 7 flows through the second four-way reversing valve... The refrigerant flows from port 4d of reversing valve 4 to port 4a, and then enters gas-liquid separator 2. In gas-liquid separator 2, the refrigerant liquid that has not been completely evaporated in the first indoor heat exchanger 7 is separated from the liquid outlet of gas-liquid separator 2. After being throttled and depressurized by throttling mechanism 5, it flows through port 3a of the first four-way reversing valve 3 to port 3d, enters the second indoor heat exchanger 8, evaporates and absorbs heat, and is then drawn into the second inlet of ejector 13 through the first six-way reversing valve 12. The refrigerant vapor at the gas outlet of gas-liquid separator 2 directly enters the suction port of compressor 1, completing the refrigeration cycle.

[0050] In heating mode, ports 3a and 3b of the first four-way reversing valve 3 are connected, and ports 3c and 3d are connected; ports 4a and 4b of the second four-way reversing valve 4 are connected, and ports 4c and 4d are connected; ports 12A and 12F of the first six-way reversing valve 12 are connected, ports 12B and 12C are connected, and ports 12D and 12E are connected. After the compressor 1 compresses the refrigerant to a high temperature and pressure, it flows through port 3c of the first four-way reversing valve 3 to port 3d, and enters the second indoor heat exchanger 8 to release heat. The outflowing fluid flows through port 12C of the first six-way reversing valve 12 to port 12B, and enters the first indoor heat exchanger 7 for further heat release. Then, it flows through port 4d of the second four-way reversing valve 4 to port 4c, and enters the first inlet of the ejector 13. The refrigerant at the second pressure at the outlet of the second outdoor heat exchanger 10 flows through port 12E of the first six-way reversing valve 12 to port 12D. The refrigerant then enters the ejector 13 through the second inlet of the ejector and mixes with the motive fluid refrigerant. After the pressure of the mixed refrigerant is increased to the first pressure, it flows out from the outlet of the ejector 13. The refrigerant at the first pressure at the outlet of the ejector 13 flows through the 12A port of the first six-way reversing valve 12 to the 12F port, and then enters the first outdoor heat exchanger 9 for evaporation. The outflowing fluid flows through the 4b port of the second four-way reversing valve 4 to the 4a port and enters the gas-liquid separator 2. After gas-liquid separation, the refrigerant liquid flows out from the liquid outlet of the gas-liquid separator 2. After being throttled and depressurized by the throttling mechanism 5, it flows through the 3a port of the first four-way reversing valve 3 to the 3b port, and then enters the second outdoor heat exchanger 10. The low-temperature and low-pressure refrigerant absorbs heat and evaporates in the second outdoor heat exchanger 10. After being drawn in by the second inlet of the ejector 13 through the first six-way reversing valve 12, the refrigerant vapor at the gas outlet of the gas-liquid separator 2 directly enters the suction port of the compressor 1, completing the heating cycle.

[0051] In another embodiment of the invention, the air conditioning system further includes an internal heat exchanger 6.

[0052] like Figure 3 and 4 As shown below, the working principle of the air conditioning system with an internal heat exchanger (dual-mode heat exchange) for cooling and heating is described.

[0053] In cooling mode, the 3a and 3d ports of the first four-way reversing valve 3 are connected, as are the 3b and 3c ports; the 4a and 4d ports of the second four-way reversing valve 4 are connected, as are the 4b and 4c ports; and the 12A and 12B ports of the first six-way reversing valve 12 are connected, as are the 12C and 12D ports, and the 12E and 12F ports. After the compressor 1 compresses the refrigerant to a high temperature and pressure, it flows through the 3c port of the first four-way reversing valve 3 to the 3b port, entering the second outdoor heat exchanger 10 for heat release. Then, it flows through the 12E port of the first six-way reversing valve 12 to the 12F port. The refrigerant enters the first outdoor heat exchanger 9 to release heat. The outflowing fluid flows from port 4b to port 4c of the second four-way reversing valve 4, and then enters the second passage of the internal heat exchanger 6. After exchanging heat with the returning low-temperature refrigerant gas in the internal heat exchanger 6, the refrigerant enters the first inlet of the ejector 13. The ejector 13 has three ports: a first inlet, a second inlet, and an outlet. The high-pressure refrigerant, as the driving fluid, enters the ejector 13 from the first inlet and is injected. After being injected, a first pressure and a second pressure are formed at the outlet and the second inlet of the ejector 13, respectively, where the first pressure is higher than the second pressure. Both the first and second pressures are less than the high-pressure gas pressure at the first inlet of ejector 13. Refrigerant vapor at the second pressure at the outlet of the second indoor heat exchanger 8 flows from port 12C to port 12D of the first six-way reversing valve 12, then enters ejector 13 through the second inlet of the ejector and mixes with the motive fluid refrigerant. The pressure of the mixed refrigerant is increased to the first pressure and then flows out from the outlet of ejector 13. Refrigerant at the first pressure at the outlet of ejector 13 flows from port 12A to port 12B of the first six-way reversing valve 12, then enters the first indoor heat exchanger 7 for evaporation, heat absorption, and cooling. The refrigerant at the outlet of the first indoor heat exchanger 7... The refrigerant flows from port 4d of the second four-way reversing valve 4 to port 4a, and then enters the gas-liquid separator 2. In the gas-liquid separator 2, the refrigerant liquid that has not been completely evaporated in the first indoor heat exchanger 7 is separated from the liquid outlet of the gas-liquid separator 2. After being throttled and depressurized by the throttling mechanism 5, it flows through port 3a of the first four-way reversing valve 3 to port 3d, enters the second indoor heat exchanger 8, evaporates and absorbs heat, and is then drawn into the second inlet of the ejector 13 through the first six-way reversing valve 12. The refrigerant vapor at the gas outlet of the gas-liquid separator 2 is heated by the internal heat exchanger 6 and then enters the suction port of the compressor 1, completing the refrigeration cycle.

[0054] In heating mode, the 3a and 3b ports of the first four-way reversing valve 3 are connected, and the 3c and 3d ports are connected; the 4a and 4b ports of the second four-way reversing valve 4 are connected, and the 4c ​​and 4d ports are connected; the 12A and 12F ports of the first six-way reversing valve 12 are connected, the 12B and 12C ports are connected, and the 12D and 12E ports are connected; after the compressor 1 compresses the refrigerant to a high temperature and high pressure, it flows through the 3c port of the first four-way reversing valve 3 to the 3d port. The refrigerant flows into the second indoor heat exchanger 8 for heat release. The outflowing fluid flows through port 12C of the first six-way reversing valve 12 to port 12B, then enters the first indoor heat exchanger 7 for further heat release. Afterwards, it flows through port 4d of the second four-way reversing valve 4 to port 4c, entering the internal heat exchanger 6. There, it exchanges heat with the returning low-temperature refrigerant gas before entering the first inlet of the ejector 13. The refrigerant at the second pressure at the outlet of the second outdoor heat exchanger 10 flows through port 12C of the first six-way reversing valve 12. The refrigerant flows from port E to port 12D, then through the second inlet of the ejector into ejector 13 to mix with the motive fluid refrigerant. After the pressure of the mixed refrigerant is increased to the first pressure, it flows out from the outlet of ejector 13. The refrigerant at the first pressure at the outlet of ejector 13 flows through port 12A of the first six-way reversing valve 12 to port 12F, and then enters the first outdoor heat exchanger 9 for evaporation. The outflowing fluid flows through port 4b of the second four-way reversing valve 4 to port 4a, and then enters the gas-liquid separator 2. After gas-liquid separation, the refrigerant liquid flows out from the liquid outlet of the gas-liquid separator 2. After being throttled and depressurized by the throttling mechanism 5, it flows through port 3a of the first four-way reversing valve 3 to port 3b, and then enters the second outdoor heat exchanger 10. The low-temperature, low-pressure refrigerant absorbs heat and evaporates in the second outdoor heat exchanger 10, and then is drawn into the second inlet of ejector 13 through the first six-way reversing valve 12. The refrigerant vapor at the gas outlet of the gas-liquid separator 2 exchanges heat with the internal heat exchanger 6 and then enters the suction port of compressor 1, completing the heating cycle.

[0055] like Figure 13 and 14 As shown below, the working principle of cooling and heating of an air conditioning system equipped with an internal heat exchanger (heat exchange only in cooling mode) is described.

[0056] In cooling mode, the 3a and 3d ports of the first four-way reversing valve 3 are connected, as are the 3b and 3c ports; the 14A and 14B ports of the second six-way reversing valve 14 are connected, as are the 14C and 14D ports, and the 14E and 14F ports; the 12A and 12B ports of the first six-way reversing valve 12 are connected, as are the 12C and 12D ports, and the 12E and 12F ports. After the compressor 1 compresses the refrigerant to a high temperature and pressure, it flows through the 3c port of the first four-way reversing valve 3 to the 3b port, entering the second outdoor heat exchanger 10 for heat release. Then, the refrigerant flows through the 12E port of the first six-way reversing valve 12. The refrigerant flows to port 12F and enters the first outdoor heat exchanger 9 to release heat. The outflowing fluid flows from port 14C of the second six-way reversing valve 14 to port 14D, and then enters the second passage of the internal heat exchanger 6. After exchanging heat with the returning low-temperature refrigerant gas in the internal heat exchanger 6, the refrigerant flows from port 14E of the second six-way reversing valve 14 to port 14F and enters the first inlet of the ejector 13. The ejector 13 has three ports: a first inlet, a second inlet, and an outlet. The high-pressure refrigerant, as the driving fluid, enters the ejector 13 from the first inlet and is injected, forming a first pressure at the outlet and the second inlet of the ejector 13, respectively. The first pressure is higher than the second pressure, and both the first and second pressures are less than the high-pressure gas pressure at the first inlet of ejector 13. The refrigerant vapor at the second pressure at the outlet of the second indoor heat exchanger 8 flows from port 12C to port 12D of the first six-way reversing valve 12, then enters ejector 13 through the second inlet of the ejector and mixes with the motive fluid refrigerant. The pressure of the mixed refrigerant is increased to the first pressure, and then it flows out from the outlet of ejector 13. The refrigerant at the first pressure at the outlet of ejector 13 flows from port 12A to port 12B of the first six-way reversing valve 12, and then enters the first indoor heat exchanger 7 for evaporation, heat absorption, and cooling. The refrigerant at the outlet of heat exchanger 7 flows to port 14B through port 14A of the second six-way reversing valve 14, and then enters the gas-liquid separator 2. In the gas-liquid separator 2, the refrigerant liquid that has not been completely evaporated in the first indoor heat exchanger 7 is separated into gas and liquid and flows out from the liquid outlet of the gas-liquid separator 2. After being throttled, depressurized and cooled by the throttling mechanism 5, it flows to port 3d through port 3a of the first four-way reversing valve 3 and enters the second indoor heat exchanger 8. After evaporating and absorbing heat, it is drawn into the second inlet of the ejector 13 through the first six-way reversing valve 12. The refrigerant vapor at the gas outlet of the gas-liquid separator 2 is heated by the internal heat exchanger 6 and then enters the suction port of the compressor 1, completing the refrigeration cycle.

[0057] In heating mode, the 3a and 3b ports of the first four-way reversing valve 3 are connected, and the 3c and 3d ports are connected; the 14A and 14F ports of the second six-way reversing valve 14 are connected, the 14B and 14C ports are connected, and the 14D and 14E ports are connected; the 12A and 12F ports of the first six-way reversing valve 12 are connected, the 12B and 12C ports are connected, and the 12D and 12E ports are connected; the compressor 1 compresses the refrigerant to a high temperature and high pressure, and then the refrigerant passes through the 3c port of the first four-way reversing valve 3. The refrigerant flows from the 3d port to the second indoor heat exchanger 8 for heat release. The outflowing fluid flows through the 12C port of the first six-way reversing valve 12 to the 12B port, entering the first indoor heat exchanger 7 for further heat release. Then, it flows through the 14A port of the second six-way reversing valve 14 to the 14F port, entering the first inlet of the ejector 13. The refrigerant at the second pressure at the outlet of the second outdoor heat exchanger 10 flows from the 12E port of the first six-way reversing valve 12 to the 12D port, and then enters the ejector 13 through the second inlet of the ejector. The refrigerant is mixed with a fluid, and after the pressure of the mixed refrigerant is increased to a first pressure, it flows out from the outlet of ejector 13. The refrigerant at the first pressure at the outlet of ejector 13 flows through the 12A port of the first six-way reversing valve 12 to the 12F port, and then enters the first outdoor heat exchanger 9 for evaporation. The outflowing fluid flows through the 14C port of the second six-way reversing valve 14 to the 14B port, and enters the gas-liquid separator 2. After gas-liquid separation, the refrigerant liquid flows out from the liquid outlet of the gas-liquid separator 2. After being throttled and depressurized by the throttling mechanism 5, it flows out through the first four-way reversing valve 13. The refrigerant flows from port 3a of the reversing valve 3 to port 3b, and then enters the second outdoor heat exchanger 10. The low-temperature, low-pressure refrigerant absorbs heat and evaporates in the second outdoor heat exchanger 10, and is then drawn into the second inlet of the ejector 13 through the first six-way reversing valve 12. The refrigerant vapor from the gas outlet of the gas-liquid separator 2 flows through the first passage of the internal heat exchanger 6 and then enters the suction port of the compressor 1. At this time, the inlet and outlet of the second passage of the internal heat exchanger 6 are connected to ports 14D and 14E of the second six-way reversing valve 14, respectively, forming a closed flow path independent of the main cycle.

[0058] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-efficiency cooling and heating air conditioning system, characterized in that, The system includes a compressor (1), a gas-liquid separator (2), a throttling mechanism (5), a first indoor heat exchanger (7), a second indoor heat exchanger (8), a first outdoor heat exchanger (9), a second outdoor heat exchanger (10), and an ejector (13), wherein: In cooling mode, the working fluid at the outlet of the compressor (1) passes through the second outdoor heat exchanger (10) and the first outdoor heat exchanger (9) in sequence to achieve secondary heat exchange with the outdoor air. After heat exchange, the working fluid enters the ejector (13). The liquid in the gas-liquid separator (2) is cooled and depressurized by the throttling mechanism (5) and then enters the second indoor heat exchanger (8) to achieve heat exchange with the indoor air. After heat exchange, the fluid enters the ejector (13). The two streams of working fluid entering the ejector (13) are evenly mixed and then flow out of the ejector and into the first indoor heat exchanger (7) to achieve heat exchange with the indoor air. The working fluid flowing out of the first indoor heat exchanger (7) enters the gas-liquid separator (2), and the gas separated from the gas-liquid separator (2) flows back to the compressor (1). In heating mode, the working fluid from the compressor (1) outlet sequentially enters the second indoor heat exchanger and the first indoor heat exchanger to exchange heat with the indoor air twice. The working fluid after heat exchange enters the ejector (13). The liquid in the gas-liquid separator (2) is cooled and depressurized by the throttling mechanism (5) and then enters the second outdoor heat exchanger (10) to exchange heat with the outdoor air. The fluid after heat exchange enters the ejector (13). The two streams of working fluid entering the ejector (13) are evenly mixed and then flow out of the ejector and into the first outdoor heat exchanger (9) to exchange heat with the outdoor air. The working fluid after heat exchange enters the gas-liquid separator (2), and the gas separated from the gas-liquid separator (2) flows back to the compressor (1).

2. The high-efficiency cooling and heating air conditioning system as described in claim 1, characterized in that, The system also includes a first four-way reversing valve (3), a second four-way reversing valve (4), and a first six-way reversing valve (12). The first four-way reversing valve (3) is used to adjust the connection relationship between the compressor (1), the second outdoor heat exchanger (10), the throttling mechanism (5), and the second indoor heat exchanger (8). The second four-way reversing valve (4) is used to adjust the connection relationship between the gas-liquid separator (2), the first outdoor heat exchanger (9), the first indoor heat exchanger (7), and the main fluid inlet of the ejector (13). The first six-way reversing valve (12) is used to adjust the connection relationship between the outlet of the ejector (13), the first indoor heat exchanger (7), the second indoor heat exchanger (8), the ejector fluid inlet of the ejector (13), and the second outdoor heat exchanger (10) and the first outdoor heat exchanger (9).

3. The high-efficiency cooling and heating air conditioning system as described in claim 2, characterized in that, The first four-way directional valve (3) is an electromagnetic four-way directional valve.

4. A high-efficiency cooling and heating air conditioning system as described in claim 2 or 3, characterized in that, The second four-way directional valve (4) and the first six-way directional valve (12) are driven by differential pressure.

5. The high-efficiency cooling and heating air conditioning system as described in claim 4, characterized in that, The second four-way reversing valve (4) includes two pressure chambers, a valve core and four ports. The pressure chambers are respectively located at both ends of the valve body, the valve core is located between the two pressure chambers, three ports are located on one side of the valve body and one port is located on the other side of the valve body. The valve core is moved by forming a pressure difference between the two pressure chambers.

6. The high-efficiency cooling and heating air conditioning system as described in claim 1, characterized in that, The system also includes a first four-way reversing valve (3), a second six-way reversing valve (14), and a first six-way reversing valve (12). The first four-way reversing valve (3) is used to adjust the connection relationship between the compressor (1), the second outdoor heat exchanger (10), the throttling mechanism (5), and the second indoor heat exchanger (8). The second six-way reversing valve (14) is used to adjust the connection relationship between the main fluid inlet end of the gas-liquid separator (2), the first outdoor heat exchanger (9), the first indoor heat exchanger (7), the internal heat exchanger (6), and the ejector (13). The first six-way reversing valve (12) is used to adjust the connection relationship between the outlet end of the ejector (13), the first indoor heat exchanger (7), the second indoor heat exchanger (8), the ejector fluid inlet end of the ejector (13), and the connection relationship between the second outdoor heat exchanger (10) and the first outdoor heat exchanger (9).

7. A high-efficiency cooling and heating air conditioning system as described in claim 2 or 6, characterized in that, The first six-way reversing valve (12) includes two pressure chambers, a valve core and six ports. The pressure chambers are respectively located at both ends of the valve body, the valve core is located between the two pressure chambers, five ports are located on one side of the valve body and one port is located on the other side of the valve body. The valve core is moved by forming a pressure difference between the two pressure chambers.

8. The high-efficiency cooling and heating air conditioning system as described in claim 7, characterized in that, The system is also equipped with an internal heat exchanger (6), and the connection method of the internal heat exchanger is as follows: When the system uses the second four-way reversing valve: in the cooling mode, the gas-liquid separator (2), the internal heat exchanger (6) and the compressor (1) are connected in sequence to form the first internal heat exchange passage; the first outdoor heat exchanger (9), the internal heat exchanger (6) and the ejector (13) are connected in sequence to form the second internal heat exchange passage; in the heating mode, the gas-liquid separator (2), the internal heat exchanger (6) and the compressor (1) are connected in sequence to form the first internal heat exchange passage; the first indoor heat exchanger (7), the internal heat exchanger (6) and the ejector (13) are connected in sequence to form the second internal heat exchange passage. When the system uses the second six-way reversing valve: in the cooling mode, the gas-liquid separator (2), the internal heat exchanger (6) and the compressor (1) are connected in sequence to form the first internal heat exchange passage, and the first outdoor heat exchanger (9), the internal heat exchanger (6) and the ejector (13) are connected in sequence to form the second internal heat exchange passage; in the heating mode, the internal heat exchanger does not work.

9. The high-efficiency cooling and heating air conditioning system as described in claim 1, characterized in that, The injector (13) can be a single injector or multiple injectors connected in parallel.

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