Heat pump system, air conditioner control method, air conditioner and storage medium

Abstract

The present invention discloses a heat pump system, an air conditioner control method, an air conditioner, and a storage medium. In the heat pump system, a first pipeline is connected to a second pipeline for heat exchange; a compressor has an exhaust port and a return air port; an ejector has a first inlet, a second inlet, and an outlet; the exhaust port, the first inlet, the first heat exchanger, and the second heat exchanger are all connected to a reversing valve, and the outlet is connected to the return air port; the first heat exchanger, the first pipeline, and the second heat exchanger are connected in sequence; a throttling device is disposed between the first heat exchanger and the second heat exchanger. When the heat pump system is operating, a portion of the refrigerant condensed by the first heat exchanger or the second heat exchanger flows through the second pipeline and the second inlet in sequence before entering the ejector, while another portion flows through the throttling device, throttled, and then flows through the first pipeline into the second heat exchanger or the first heat exchanger. The present invention aims to achieve uniform diversion of the two-phase refrigerant flowing out of the condenser to improve the heat exchange efficiency of the heat pump system.

Description

Technical Field

[0001] The present invention relates to the technical field of household appliances, and in particular to a heat pump system, a control method for an air conditioner, an air conditioner, and a storage medium. Background Art

[0002] Many household appliances, such as air conditioners, utilize heat pump systems to regulate the environment in a specific area. During heat pump operation, the high-temperature, high-pressure liquid refrigerant at the condenser outlet is throttled and reduced in pressure to a low-temperature, low-pressure gas-liquid mixture.

[0003] However, when the gas-liquid mixed refrigerant flows directly into the evaporator for heat exchange, excessive gaseous refrigerant will lead to poor heat exchange effect, thereby reducing the overall heat exchange effect of the heat pump system. Summary of the Invention

[0004] The main purpose of the present invention is to provide a heat pump system, an air conditioner control method, an air conditioner and a storage medium, aiming to achieve uniform diversion of the two-phase refrigerant flowing out of the condenser to improve the heat exchange effect of the heat pump system.

[0005] To achieve the above object, the present invention provides a heat pump system, comprising a compressor, a reversing valve, a first heat exchanger, a second heat exchanger, an ejector, a throttling device, a first pipeline and a second pipeline, wherein the first pipeline is connected to the second pipeline for heat exchange;

[0006] The compressor has an exhaust port and a return air port, the ejector has a first inlet, a second inlet, and an outlet, the exhaust port, the first inlet, the first heat exchanger, and the second heat exchanger are all connected to the reversing valve, and the outlet is connected to the return air port;

[0007] The first heat exchanger, the first pipeline and the second heat exchanger are connected in sequence, and the throttling device is arranged between the first heat exchanger and the second heat exchanger. When the heat pump system is running, a part of the refrigerant condensed by the first heat exchanger or the second heat exchanger flows through the second pipeline and the second inlet in sequence and then enters the ejector, and the other part flows through the throttling device and then flows through the first pipeline to enter the second heat exchanger or the first heat exchanger after throttling.

[0008] Optionally, the throttling device includes a first throttling component and a second throttling component, the first throttling component is provided between the first heat exchanger and the first pipeline, and the pipeline between the first heat exchanger and the first throttling component is defined as a third pipeline; the second throttling component is provided between the first pipeline and the second heat exchanger, and the pipeline between the second heat exchanger and the second throttling component is defined as a fourth pipeline;

[0009] The heat pump system further includes a refrigerant regulating component, and the second inlet, the second pipeline, the third pipeline, and the fourth pipeline are all connected to the refrigerant regulating component;

[0010] The refrigerant regulating assembly is configured to operate in a first state when the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, so that a portion of the refrigerant flowing out of the first heat exchanger flows sequentially through the third pipeline, the second pipeline, and the second inlet before entering the ejector, and the other portion flows through the first throttling component and is throttled by the first throttling component before flowing sequentially through the first pipeline, the second throttling component, and the second heat exchanger;

[0011] The refrigerant regulating component is also used to operate in the second state when the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state so that a portion of the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline and the second inlet in sequence and then enters the ejector, and the other portion flows through the second throttling component and is throttled by the second throttling component and then flows through the first pipeline, the first throttling component and the first heat exchanger in sequence.

[0012] Optionally, the refrigerant conditioning component includes:

[0013] a first control valve disposed between the second inlet and the first end of the second pipeline;

[0014] a second control valve disposed between the second inlet and the second end of the second pipeline;

[0015] a third control valve, wherein a first end of the third control valve is in communication with the third pipeline, and a connecting pipeline between the second control valve and the second pipeline is in communication with a second end of the third control valve;

[0016] A fourth control valve, wherein a first end of the fourth control valve is communicated with the fourth pipeline, and a connecting pipeline between the first control valve and the second pipeline is communicated with a second end of the fourth control valve.

[0017] Optionally, the heat pump system further includes a gas-liquid separator disposed between the outlet and the return air port, the gas-liquid separator having a refrigerant inlet and an outlet, the outlet being connected to the refrigerant inlet, and the outlet being connected to the return air port.

[0018] In addition, to achieve the above-mentioned purpose, the present application also proposes a control method for an air conditioner, wherein the air conditioner includes the above-mentioned heat pump system, and the control method for the air conditioner includes:

[0019] Acquire an operating mode of the heat pump system and / or heat exchange states of the first heat exchanger and the second heat exchanger, wherein the operating mode can represent the heat exchange states of the first heat exchanger and the second heat exchanger;

[0020] When the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, controlling the refrigerant regulating assembly to operate in a first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline, and the second inlet in sequence before entering the ejector;

[0021] When the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state, the refrigerant regulating component is controlled to operate in a second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline and the second inlet in sequence and then enters the ejector.

[0022] Optionally, the refrigerant regulating assembly includes a first control valve, a second control valve, a third control valve and a fourth control valve, the first control valve is arranged between the second inlet and the first end of the second pipeline, the second control valve is arranged between the second inlet and the second end of the second pipeline, the first end of the third control valve is communicated with the third pipeline, the connecting pipeline between the second control valve and the second pipeline is communicated with the second end of the third control valve, the first end of the fourth control valve is communicated with the fourth pipeline, and the connecting pipeline between the first control valve and the second pipeline is communicated with the second end of the fourth control valve, and the step of controlling the refrigerant regulating assembly to operate in the first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline and the second inlet in sequence and then enters the ejector includes:

[0023] Controlling the first control valve to open, controlling the second control valve to close, controlling the third control valve to open, and controlling the fourth control valve to close;

[0024] The step of controlling the refrigerant regulating component to operate in the second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector includes:

[0025] The first control valve is controlled to be closed, the second control valve is controlled to be opened, the third control valve is controlled to be closed, and the fourth control valve is controlled to be opened.

[0026] Optionally, after the step of controlling the refrigerant regulating component to operate in the first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector, or the step of controlling the refrigerant regulating component to operate in the second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector, the step further includes:

[0027] Obtaining the exhaust gas superheat and the supply gas superheat corresponding to the compressor;

[0028] Controlling the operation of the first target component according to the exhaust gas superheat, and controlling the operation of the second target component according to the supplementary air superheat;

[0029] The first target component is the component located upstream of the first pipeline between the first throttling component and the second throttling component, and the second target component is the component located downstream of the first pipeline between the first throttling component and the second throttling component.

[0030] Optionally, the step of controlling the operation of the first target component according to the exhaust superheat comprises:

[0031] When the exhaust gas superheat is within a preset superheat range, controlling the first target component to maintain a current opening;

[0032] When the exhaust gas superheat is less than the preset superheat range, controlling the first target component to reduce the current opening according to the first opening adjustment value;

[0033] When the exhaust gas superheat is greater than the preset superheat range, the first target component is controlled to increase the current opening according to the second opening adjustment value.

[0034] Optionally, before the step of controlling the operation of the first target component according to the exhaust superheat, the method further includes:

[0035] Determining the preset superheat range according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state;

[0036] and / or, determining the first opening adjustment value according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state;

[0037] And / or, the second opening adjustment value is determined according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state.

[0038] Optionally, the step of obtaining the exhaust superheat of the air conditioner includes:

[0039] Acquire the exhaust temperature of the compressor and the coil temperature of the heat exchanger currently in a condensing state among the first heat exchanger and the second heat exchanger;

[0040] The exhaust gas superheat is determined according to a temperature difference between the exhaust gas temperature and the coil temperature.

[0041] Optionally, the step of controlling the operation of the second target component according to the supplementary air superheat comprises:

[0042] When the supplementary air superheat is greater than a preset superheat, controlling the second target component to reduce its opening;

[0043] When the supplementary air superheat is less than or equal to the preset superheat, the second target component is controlled to maintain a current opening.

[0044] Optionally, the step of obtaining the supplementary air superheat degree includes:

[0045] Acquire a first temperature of the second inlet and a second temperature of the return air outlet;

[0046] The supplementary air superheat degree is determined according to a temperature difference between the first temperature and the second temperature.

[0047] In addition, in order to achieve the above-mentioned purpose, the present application also proposes an air conditioner, which includes:

[0048] A heat pump system as described above;

[0049] A control device, the heat pump system is connected to the control device, and the control device includes: a memory, a processor, and an air conditioner control program stored in the memory and executable on the processor, wherein the air conditioner control program, when executed by the processor, implements the steps of the air conditioner control method as described in any one of the above items.

[0050] In addition, in order to achieve the above-mentioned purpose, the present application also proposes a storage medium, on which a control program of an air conditioner is stored. When the control program of the air conditioner is executed by a processor, the steps of the control method of the air conditioner as described in any of the above items are implemented.

[0051] The present invention proposes a heat pump system, in which when the first heat exchanger or the second heat exchanger is in a condensing state, a part of the refrigerant flowing out after condensation flows through a throttling device to be throttled and reduced in pressure and then flows into the first pipeline, and the other part of the refrigerant flowing out after condensation flows through the second pipeline and is mixed with the refrigerant flowing out after evaporation in an ejector before flowing back to the compressor, wherein, after the gas-liquid two-phase refrigerant in the first pipeline exchanges heat with the high-temperature and high-pressure refrigerant in the second pipeline, the proportion of liquid-phase refrigerant in the first pipeline is increased and the proportion of gas-phase refrigerant in the second pipeline is reduced, thereby avoiding excessive gaseous refrigerant flowing into the evaporator to affect the evaporation effect, and the refrigerant flowing out of the second pipeline can replenish air to the compressor under the action of the ejector to improve energy efficiency. In this way, the two-phase refrigerant flowing out of the condenser is evenly diverted, thereby effectively improving the heat exchange effect of the heat pump system. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] Figure 1 This is a structural diagram of an implementation method of a heat pump system in an embodiment of the present invention;

[0053] Figure 2 This is a structural diagram of another implementation method of an embodiment of the heat pump system of the present invention.

[0054] Figure 3 A schematic diagram of the structure of another embodiment of the heat pump system of the present invention and a schematic diagram of the refrigerant flow direction under a first operating condition;

[0055] Figure 4 A schematic diagram of the structure of another embodiment of the heat pump system of the present invention and a schematic diagram of the refrigerant flow direction under a second operating condition;

[0056] Figure 5 Schematic diagram of the hardware structure involved in the operation of an air conditioner according to an embodiment of the present invention;

[0057] Figure 6 A flow chart of an embodiment of a method for controlling an air conditioner according to the present invention;

[0058] Figure 7 A flow chart of another embodiment of a method for controlling an air conditioner according to the present invention;

[0059] Figure 8 FIG. 4 is a flow chart of another embodiment of a method for controlling an air conditioner according to the present invention.

[0060] Description of Figure Numbers:

[0061] Label name Label name 100 heat pump system 40 Refrigerant conditioning components 11 compressor 41 First control valve 12 reversing valve 42 Second control valve 13 First heat exchanger 43 The third control valve 14 Second heat exchanger 44 Fourth control valve 15 ejector 5 Gas-liquid separator 1a Throttling device 6 Heat exchange module 16 First throttle component 200 Control device 17 Second throttle component 01 First temperature detection module 21 First pipeline 02 Second temperature detection module 22 Second pipeline 03 The third temperature detection module 31 The third pipeline 04 Fourth temperature detection module 32 Fourth pipeline

[0062] The purpose, features and advantages of the present invention will be further described with reference to the accompanying drawings and in conjunction with the embodiments. DETAILED DESCRIPTION

[0063] It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0064] An embodiment of the present invention provides a heat pump system 100. In this embodiment, the heat pump system 100 is provided in an air conditioner. In other embodiments, the heat pump system 100 may also be provided in other household appliances, such as a refrigerator, a water heater, etc.

[0065] In the embodiment of the present invention, referring to Figures 1 to 4 The heat pump system 100 includes a compressor 11, a reversing valve 12, a first heat exchanger 13, a second heat exchanger 14, an ejector 15, a throttling device 1a, a first pipeline 21 and a second pipeline 22, wherein the first pipeline 21 is connected to the second pipeline 22 for heat exchange;

[0066] The compressor 11 has an exhaust port and a return air port, the ejector 15 has a first inlet, a second inlet, and an outlet, the exhaust port, the first inlet, the first heat exchanger 13, and the second heat exchanger 14 are all connected to the reversing valve 12, and the outlet of the ejector 15 is connected to the return air port;

[0067] The first heat exchanger 13, the first pipeline 21 and the second heat exchanger 14 are connected in sequence, and the throttling device 1a is arranged between the first heat exchanger 13 and the second heat exchanger 14. When the heat pump system 100 is running, a part of the refrigerant condensed by the first heat exchanger 13 or the second heat exchanger 14 flows through the second pipeline 22 and the second inlet in sequence and then enters the ejector 15, and the other part flows through the throttling device 1a and then flows through the first pipeline 21 to enter the second heat exchanger 14 or the first heat exchanger 13 after throttling.

[0068] It should be noted that the return air port here is a refrigerant port connected to the side of the compressor 11 with the lowest air pressure, which is different from the air supply port connected to the medium-pressure chamber of the compressor 11.

[0069] The first pipeline 21 and the second pipeline 22 are connected by heat exchange module 6. In this embodiment, the heat exchange module 6 is a plate heat exchanger. In other embodiments, the first pipeline 21 and the second pipeline 22 can also be connected by heat exchange by bonding, etc.

[0070] The ejector 15 is a device that uses a high-speed, high-energy flow to eject another low-speed, low-energy flow. The ejecting flow and the ejected flow can mix inside the ejector 15. Through the mixing effect at the boundary, the ejecting flow transfers energy to the ejected flow. In this embodiment, the refrigerant flowing out of the reversing valve 12 flows into the ejector 15 from the first inlet, forming a high-speed, high-energy flow. Under this ejection effect, the refrigerant flowing out of the second pipeline 22 can be ejected from the second inlet into the ejector 15, mixed with the refrigerant flowing into the first inlet, and energy transfer occurs. The mixed refrigerant flows out of the ejector port and then flows back to the compressor 11 through the return port.

[0071] In this embodiment, the compressor 11 is a two-stage compressor 11. In other embodiments, the compressor 11 may also be a single-stage compressor 11.

[0072] In this embodiment, the throttling device 1a is a throttling component with adjustable opening, for example, the throttling device 1a includes one or more electronic expansion valves. In other embodiments, the throttling device 1a includes multiple parallel capillaries or other throttling components with non-adjustable opening.

[0073] In one implementation of this embodiment, the throttling device 1a includes a first throttling component 16, which is arranged between the first heat exchanger 13 and the first pipeline 21. When the first heat exchanger 13 is in a condensing state, a portion of the refrigerant condensed by the first heat exchanger 13 is throttled and depressurized by the first throttling component 16 and flows into the first pipeline 21.

[0074] In another implementation of this embodiment, the throttling device 1a includes a second throttling component 17, which is arranged between the first pipeline 21 and the second heat exchanger 14. When the second heat exchanger 14 is in a condensing state, a portion of the refrigerant condensed by the second heat exchanger 14 is throttled and depressurized by the second throttling component 17 and then flows into the first pipeline 21.

[0075] In one implementation, the pipeline between the first heat exchanger 13 and the first throttling component 16 is defined as the third pipeline 31. One end of the second pipeline 22 is connected to the third pipeline 31, and the other end of the second pipeline 22 is connected to the second inlet. In other embodiments, one end of the second pipeline 22 can be switchably connected or disconnected from the third pipeline 31, and the other end of the second pipeline 22 can be switchably connected or disconnected from the second inlet.

[0076] In another implementation, the pipeline between the second heat exchanger 14 and the second throttling component 17 is defined as a fourth pipeline 32. One end of the second pipeline 22 is connected to the fourth pipeline 32, and the other end of the second pipeline 22 is connected to the second inlet. In other embodiments, one end of the second pipeline 22 can be switchably connected to or disconnected from the fourth pipeline 32, and the other end of the second pipeline 22 can be switchably connected to or disconnected from the second inlet.

[0077] In this embodiment, the operating state of reversing valve 12 is described using a four-way valve as an example: the four-way valve has a first valve position and a second valve position. In the first valve position, the exhaust port is connected to the first heat exchanger 13, and the first inlet is connected to the second heat exchanger 14. The first heat exchanger 13 is in a condensing state, and the second heat exchanger 14 is in an evaporating state. In the second valve position, the exhaust port is connected to the second heat exchanger 14, and the first inlet is connected to the first heat exchanger 13. The first heat exchanger 13 is in an evaporating state, and the second heat exchanger 14 is in a condensing state. In other embodiments, reversing valve 12 may also be a combination of fluid control valves with equivalent refrigerant reversing functions, which will not be described in detail here.

[0078] In one implementation of this embodiment, referring to Figure 1 When the reversing valve 12 is in the first valve position, the refrigerant discharged from the compressor 11 flows through the reversing valve 12 and flows into the first heat exchanger 13. The first heat exchanger 13 is in a condensing state and releases heat. The refrigerant flowing out of the first heat exchanger 13 after heat exchange flows into the third pipeline 31. A part of the refrigerant flowing into the third pipeline 31 flows through the second pipeline 22. The refrigerant flowing out of the second pipeline 22 flows into the ejector 15 through the second inlet. The other part of the refrigerant flowing into the third pipeline 31 after heat exchange in the first heat exchanger 13 flows through the first throttling component 16 for throttling and pressure reduction. After the pressure is reduced, the low-temperature, low-pressure gas-liquid mixed refrigerant flows into the first pipeline 21. The refrigerant flowing out of the first pipeline 21 flows into the second heat exchanger 14 to evaporate. The second heat exchanger 14 is in an evaporating state and absorbs heat. The refrigerant flowing out of the second heat exchanger 14 after heat exchange flows through the reversing valve 12 and then enters the ejector 15 through the first inlet. The refrigerant flowing into the ejector 15 from the first inlet and the second inlet is mixed and heat-exchanged and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor 11 through the return air port, thus completing a refrigerant circulation process. Among them, the refrigerant flowing through the second pipeline 22 exchanges heat with the refrigerant flowing through the first pipeline 21. The refrigerant in the second pipeline 22 releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline 22 increases, and the liquid proportion of the refrigerant in the first pipeline 21 increases. After the refrigerant enters the compressor 11, it can be compressed by the compressor 11 to form a high-temperature and high-pressure refrigerant and discharged from the exhaust port. The refrigerant cycle is then repeated in the above manner, which will not be described in detail here.

[0079] In another implementation of this embodiment, referring to Figure 2When the reversing valve 12 is in the second valve position, the refrigerant discharged from the compressor 11 flows through the reversing valve 12 and flows into the second heat exchanger 14. The second heat exchanger 14 is in a condensing state and releases heat. The refrigerant flowing out of the second heat exchanger 14 after heat exchange flows into the fourth pipeline 32. A part of the refrigerant flowing into the fourth pipeline 32 flows through the second pipeline 22. The refrigerant flowing out of the second pipeline 22 flows into the ejector 15 through the second inlet. The other part of the refrigerant flowing into the fourth pipeline 32 after heat exchange in the second heat exchanger 14 flows through the second throttling component 17 for throttling and pressure reduction. After the pressure is reduced, the low-temperature, low-pressure gas-liquid mixed refrigerant flows into the first pipeline 21. The refrigerant flowing out of the first pipeline 21 flows into the first heat exchanger 13 to evaporate. The first heat exchanger 13 is in an evaporating state and absorbs heat. The refrigerant flowing out of the first heat exchanger 13 after heat exchange flows through the reversing valve 12 and then enters the ejector 15 through the first inlet. The refrigerant flowing into the ejector 15 from the first inlet and the second inlet is mixed and heat-exchanged and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor 11 through the return air port, thus completing a refrigerant circulation process. Among them, the refrigerant flowing through the second pipeline 22 exchanges heat with the refrigerant flowing through the first pipeline 21. The refrigerant in the second pipeline 22 releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline 22 increases, and the liquid proportion of the refrigerant in the first pipeline 21 increases. After the refrigerant enters the compressor 11, it can be compressed by the compressor 11 to form a high-temperature and high-pressure refrigerant and discharged from the exhaust port. The refrigerant cycle is then repeated in the above manner, which will not be described in detail here.

[0080] A heat pump system 100 is proposed in an embodiment of the present invention. In the heat pump system 100, when the first heat exchanger 13 or the second heat exchanger 14 is in a condensing state, a portion of the refrigerant flowing out after condensation flows through the throttling device 1a to be throttled and reduced in pressure and then flows into the first pipeline 21. The other portion of the refrigerant flowing out of the first heat exchanger 13 flows through the second pipeline 22 and is mixed with the refrigerant flowing out after evaporation in the ejector 15 before returning to the compressor 11. Among them, after the gas-liquid two-phase refrigerant in the first pipeline 21 exchanges heat with the high-temperature and high-pressure refrigerant in the second pipeline 22, the proportion of liquid refrigerant in the first pipeline 21 is increased and the proportion of gaseous refrigerant in the second pipeline 22 is reduced, thereby avoiding excessive gaseous refrigerant flowing into the evaporator to affect the evaporation effect. The refrigerant flowing out of the second pipeline 22 can replenish air to the compressor 11 under the action of the ejector 15 to improve energy efficiency. In this way, the two-phase refrigerant flowing out of the condenser is evenly diverted, thereby effectively improving the heat exchange effect of the heat pump system 100.

[0081] Further, in another embodiment, referring to Figure 3 and Figure 4The throttling device 1a includes a first throttling component 16 and a second throttling component 17. The first throttling component 16 is provided between the first heat exchanger 13 and the first pipeline 21. The pipeline between the first heat exchanger 13 and the first throttling component 16 is defined as a third pipeline 31. The second throttling component 17 is provided between the first pipeline 21 and the second heat exchanger 14. The pipeline between the second heat exchanger 14 and the second throttling component 17 is defined as a fourth pipeline 32.

[0082] The heat pump system 100 also includes a refrigerant regulating component 40, and the second inlet, the second pipeline 22, the third pipeline 31 and the fourth pipeline 32 are all connected to the refrigerant regulating component 40. The refrigerant regulating component 40 is used to operate in a first state when the first heat exchanger 13 is in a condensing state and the second heat exchanger 14 is in an evaporating state, so that the refrigerant flowing out of the first heat exchanger 13 flows through the third pipeline 31, the second pipeline 22 and the second inlet in sequence and then enters the ejector 15. The refrigerant regulating component 40 is also used to operate in a second state when the second heat exchanger 14 is in a condensing state and the first heat exchanger 13 is in an evaporating state, so that the refrigerant flowing out of the second heat exchanger 14 flows through the fourth pipeline 32, the second pipeline 22 and the second inlet in sequence and then enters the ejector 15.

[0083] In this embodiment, the second throttle component 17 is a throttle component with adjustable opening, for example, the second throttle component 17 is a second electronic expansion valve. In other embodiments, the second throttle component 17 can also be a plurality of capillaries connected in parallel or other throttle components with non-adjustable opening.

[0084] The refrigerant regulating assembly 40 may include a flow control valve such as a multi-way valve, a combination of multiple solenoid valves and / or a one-way valve. In addition to the flow control valve, the refrigerant regulating assembly 40 may also include related connecting pipes, etc. Any one or more fluid components having the above-mentioned refrigerant regulating function may serve as the refrigerant regulating assembly 40 herein.

[0085] Specifically, the first end of the second pipeline 22 , the second end of the second pipeline 22 , the third pipeline 31 , and the fourth pipeline 32 are all connected to the refrigerant regulating assembly 40 .

[0086] In this embodiment, when the refrigerant regulating assembly 40 is operating in the first state, the refrigerant flowing out of the first heat exchanger 13 flows sequentially through the third pipeline 31, the first end of the second pipeline 22, the second end of the second pipeline 22, and the second inlet, and the refrigerant in the fourth pipeline 32 stops flowing into the second pipeline 22. In this embodiment, when the refrigerant regulating assembly 40 is operating in the second state, the refrigerant flowing out of the second heat exchanger 14 flows sequentially through the fourth pipeline 32, the second end of the second pipeline 22, the first end of the second pipeline 22, and the second inlet, and the refrigerant in the third pipeline 31 stops flowing into the second pipeline 22.

[0087] In this embodiment, the heat pump system 100 has two operating conditions. The operation of the heat pump system 100 under the two operating conditions is described in detail below:

[0088] Reference Figure 3 In the first operating condition, the four-way valve operates in the first valve position, the refrigerant discharged from the compressor 11 flows through the reversing valve 12 into the first heat exchanger 13, the first heat exchanger 13 is in a condensing state and releases heat, the refrigerant regulating component 40 operates in the first state, the refrigerant flowing out of the first heat exchanger 13 after heat exchange flows into the third pipeline 31, a part of the refrigerant flowing into the third pipeline 31 flows through the second pipeline 22, the refrigerant flowing out of the second pipeline 22 flows into the ejector 15 through the second inlet, and the other part of the refrigerant flowing into the third pipeline 31 after heat exchange in the first heat exchanger 13 flows through the first throttling component 16 for throttling and pressure reduction. The low-temperature, low-pressure gas-liquid mixed refrigerant flows into the first pipeline 21. The refrigerant flowing out of the first pipeline 21 is further throttled and reduced in pressure by the second throttling component 17 to form a low-pressure liquid refrigerant that flows into the second heat exchanger 14 for evaporation. The second heat exchanger 14 is in an evaporating state and absorbs heat. The refrigerant flowing out of the second heat exchanger 14 after heat exchange flows through the reversing valve 12 and enters the ejector 15 through the first inlet. The refrigerant flowing into the ejector 15 from the first inlet and the second inlet is mixed and heat-exchanged and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor 11 through the return air port, thus completing a refrigerant circulation process. Among them, the refrigerant flowing through the second pipeline 22 exchanges heat with the refrigerant flowing through the first pipeline 21. The refrigerant in the second pipeline 22 releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline 22 increases, and the liquid proportion of the refrigerant in the first pipeline 21 increases. After the refrigerant enters the compressor 11, it is compressed by the compressor 11 to form a high-temperature, high-pressure refrigerant, which is then discharged from the exhaust port. The refrigerant cycle then repeats as described above, which will not be described in detail here. In this embodiment, the heat pump system 100 is provided in an air conditioner, the first heat exchanger 13 is an outdoor heat exchanger, and the second heat exchanger 14 is an indoor heat exchanger. The first operating condition specifically refers to the cooling condition of the air conditioner.

[0089] Reference Figure 4In the second operating condition, the four-way valve operates in the second valve position, the refrigerant discharged from the compressor 11 flows through the reversing valve 12 into the second heat exchanger 14, the second heat exchanger 14 is in a condensing state and releases heat, the refrigerant regulating component 40 operates in the second state, the refrigerant flowing out of the second heat exchanger 14 after heat exchange flows into the fourth pipeline 32, a part of the refrigerant flowing into the fourth pipeline 32 flows through the second pipeline 22, the refrigerant flowing out of the second pipeline 22 flows into the ejector 15 through the second inlet, and the other part of the refrigerant flowing into the fourth pipeline 32 after heat exchange in the second heat exchanger 14 flows through the second throttling component 17 for throttling and pressure reduction. The low-temperature, low-pressure gas-liquid mixed refrigerant flows into the first pipeline 21. The refrigerant flowing out of the first pipeline 21 is further throttled and reduced in pressure by the first throttling component 16 to form a low-pressure liquid refrigerant, and then flows into the first heat exchanger 13 to evaporate. The first heat exchanger 13 is in an evaporating state and absorbs heat. The refrigerant flowing out of the first heat exchanger 13 after heat exchange flows through the reversing valve 12 and enters the ejector 15 through the first inlet. The refrigerant flowing into the ejector 15 from the first inlet and the second inlet is mixed and heat-exchanged and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor 11 through the return air port, thus completing a refrigerant circulation process. Among them, the refrigerant flowing through the second pipeline 22 exchanges heat with the refrigerant flowing through the first pipeline 21. The refrigerant in the second pipeline 22 releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline 22 increases, and the liquid proportion of the refrigerant in the first pipeline 21 increases. After the refrigerant enters compressor 11, it is compressed by compressor 11 to form high-temperature, high-pressure refrigerant, which is then discharged from the exhaust port. The refrigerant cycle then repeats as described above, which will not be described in detail here. In this embodiment, the heat pump system 100 is provided in an air conditioner, the first heat exchanger 13 is an outdoor heat exchanger, the second heat exchanger 14 is an indoor heat exchanger, and the second operating condition specifically refers to the heating condition of the air conditioner.

[0090] In this embodiment, the heat pump system 100 is further provided with a second throttling component 17 and a refrigerant regulating module, which can ensure that the heat pump system 100 can achieve uniform diversion of the two-phase refrigerant flowing out of the condenser under different working conditions, thereby effectively improving the heat exchange effect of the heat pump system 100.

[0091] Further, in this embodiment, referring to Figure 3 and Figure 4 , the refrigerant regulating component 40 includes:

[0092] a first control valve 41 , the first control valve 41 being disposed between the second inlet and the first end of the second pipeline 22 ;

[0093] a second control valve 42 , the second control valve 42 being disposed between the second inlet and the second end of the second pipeline 22 ;

[0094] a third control valve 43 , wherein a first end of the third control valve 43 is in communication with the third pipeline 31 , and a connecting pipeline between the second control valve 42 and the second pipeline 22 is in communication with a second end of the third control valve 43 ;

[0095] A fourth control valve 44 , wherein a first end of the fourth control valve 44 is in communication with the fourth pipeline 32 , and a connecting pipeline between the first control valve 41 and the second pipeline 22 is in communication with a second end of the fourth control valve 44 .

[0096] In this embodiment, the first control valve 41, the second control valve 42, the third control valve 43, and the fourth control valve 44 are all solenoid valves. In other embodiments, the first control valve 41, the second control valve 42, the third control valve 43, and the fourth control valve 44 may also be one-way valves, or some may be one-way valves and some may be solenoid valves.

[0097] The first control valve 41 , the second control valve 42 , the third control valve 43 and the fourth control valve 44 are respectively used to control the branches in which they are located to switch between the conducting state and the blocking state.

[0098] The regulating state (on or off) of the refrigerant flowing through the branch in which the first control valve 41, the second control valve 42, the third control valve 43 and the fourth control valve 44 are located can be determined according to the actual heat exchange state of the first heat exchanger 13 and the second heat exchanger 14. If the heat exchange state is different, the regulating function of the first control valve 41, the second control valve 42, the third control valve 43 and the fourth control valve 44 will be different.

[0099] The solution of this embodiment is described below in combination with the above two operating conditions:

[0100] Under the first operating condition, the first control valve 41 is regulated to connect the second inlet to the first end of the second pipeline 22, while the second control valve 42 is regulated to block the second inlet from the second end of the second pipeline 22. The third control valve 43 is regulated to connect the third pipeline 31 to the second end of the second pipeline 22, while the fourth control valve 44 is regulated to block the fourth pipeline 32 from the first end of the second pipeline 22. Consequently, no refrigerant flows through the branches containing the fourth control valve 44 and the second control valve 42. The refrigerant flowing from the third pipeline 31 into the first control valve 41 can all flow through the second pipeline 22. The refrigerant in the second pipeline 22 exchanges heat with the refrigerant in the first pipeline 21, then flows through the third control valve 43 and enters the ejector 15 through the second inlet.

[0101] Under the second operating condition, the first control valve 41 is regulated to block the second inlet from the first end of the second pipeline 22, while the second control valve 42 is regulated to connect the second inlet to the second end of the second pipeline 22. The third control valve 43 is regulated to block the third pipeline 31 from the second end of the second pipeline 22, while the fourth control valve 44 is regulated to connect the fourth pipeline 32 to the first end of the second pipeline 22. As a result, no refrigerant flows through the branches containing the third control valve 43 and the first control valve 41. The refrigerant flowing from the fourth pipeline 32 into the fourth control valve 44 can all flow through the second pipeline 22. The refrigerant in the second pipeline 22 exchanges heat with the refrigerant in the first pipeline 21, then flows through the second control valve 42 and enters the ejector 15 through the second inlet.

[0102] In this embodiment, the above-mentioned four control valves can adjust the on-off of the refrigerant in the branch where they are located. Through the coordinated adjustment of the four control valves, the refrigerant can be diverted to meet the needs under different operating conditions, ensuring the heat exchange effect between the second pipeline 22 and the first pipeline 21 under any working conditions, and the air replenishment effect under the ejector 15, so as to improve energy efficiency and improve the uniformity of the gas-liquid two-phase diversion of the system, thereby effectively improving the heat exchange effect of the heat pump system 100.

[0103] In other embodiments, the four control valves mentioned above may also be replaced by other fluid components such as multi-way valves, as long as the same refrigerant regulation function is achieved.

[0104] Furthermore, in one embodiment, the heat pump system 100 also includes a gas-liquid separator 5 arranged between the outlet and the return air port, the gas-liquid separator 5 has a refrigerant inlet and an outlet, the outlet is connected to the refrigerant inlet, and the outlet is connected to the return air port.

[0105] The refrigerant flowing into the gas-liquid separator 5 from the refrigerant inlet may be separated into liquid and gaseous states, wherein the gaseous refrigerant may enter the compressor 11 through the gas outlet.

[0106] In this embodiment, the addition of the gas-liquid separator 5 is beneficial to further avoid liquid in the return gas of the compressor 11, which is beneficial to improving the energy efficiency and operation reliability of the compressor 11, thereby further improving the heat exchange effect of the heat pump system 100.

[0107] The embodiment of the present invention further provides an air conditioner, which can be any type of equipment used to adjust the indoor environment, such as a wall-mounted air conditioner, a cabinet air conditioner, a through-the-wall air conditioner, or a ceiling-mounted air conditioner.

[0108] In an embodiment of the present invention, an air conditioner includes the heat pump system 100 and a control device 200, wherein the first throttle component 16, the reversing valve 12, and the compressor 11 in the heat pump system 100 are all connected to the control device 200. Furthermore, the second throttle component 17 in the heat pump system 100 can also be connected to the control device 200.

[0109] The specific structure of the heat pump system 100 in this embodiment refers to the above embodiments. Since the air conditioner adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be described one by one here.

[0110] Furthermore, in one embodiment, the air conditioner also includes a first temperature detection module 01, which is connected to the control device 200. The first temperature detection module 01 can be arranged on the first heat exchanger 13 and / or the second heat exchanger 14. The first temperature detection module 01 can be used to detect the coil temperature of the heat exchanger in which it is located.

[0111] Furthermore, in one embodiment, the air conditioner further includes a second temperature detection module 02, which is connected to the control device 200 and is located in the environment where the air conditioner is located, specifically for detecting the ambient temperature. In this embodiment, the second temperature detection module 02 is located in an outdoor environment, for detecting the outdoor ambient temperature.

[0112] Furthermore, in one embodiment, the air conditioner further includes a third temperature detection module 03 connected to the control device 200. The third temperature detection module 03 is provided at the exhaust port of the compressor 11 and is used to detect the exhaust temperature of the compressor 11.

[0113] Furthermore, in one embodiment, the air conditioner further comprises a fourth temperature detection module 04, which is connected to the control device 200. The fourth temperature detection module 04 is provided at the second inlet of the ejector 15, and is used to detect the refrigerant temperature at the second inlet.

[0114] In the embodiment of the present invention, referring to Figure 5 Air conditioner control device 200 includes a processor 1001 (e.g., a CPU), a memory 1002, a timer 1003, and the like. The various components of control device 200 are connected via a communication bus. Memory 1002 can be a high-speed RAM memory or a non-volatile memory such as a disk drive. Memory 1002 can also optionally be a storage device independent of processor 1001.

[0115] Those skilled in the art will understand that Figure 5The device structure shown in the figure does not constitute a limitation of the device, and may include more or fewer components than shown in the figure, or combine certain components, or arrange the components differently.

[0116] like Figure 5 As shown, the memory 1002 as a storage medium may include the control program of the air conditioner. Figure 5 In the device shown, the processor 1001 can be used to call the air conditioner control program stored in the memory 1002 and execute the relevant steps of the air conditioner control method in the following embodiments.

[0117] An embodiment of the present invention further provides a method for controlling an air conditioner, which is applied to the above-mentioned air conditioner.

[0118] Reference Figure 6 , an embodiment of a control method for an air conditioner of the present application is proposed. In this embodiment, the control method for an air conditioner includes:

[0119] Step S10, obtaining an operating mode of the heat pump system and / or heat exchange states of the first heat exchanger and the second heat exchanger, wherein the operating mode can represent the heat exchange states of the first heat exchanger and the second heat exchanger;

[0120] In this embodiment, the heat exchange state can be obtained by obtaining the operating parameters of the reversing valve. When the current operating parameters of the reversing valve are in the first valve position, the heat exchange state is that the first heat exchanger is in the condensing state and the second heat exchanger is in the evaporating state. When the current operating parameters of the reversing valve are in the second valve position, the heat exchange state is that the first heat exchanger is in the evaporating state and the second heat exchanger is in the condensing state.

[0121] In other embodiments, the heat exchange state can also be determined by obtaining the operating mode of the air conditioner. When the operating mode is cooling mode or dehumidification mode, the heat exchange state is that the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state; when the operating mode is heating mode or sterilization mode, the heat exchange state is that the first heat exchanger is in an evaporating state and the second heat exchanger is in a condensing state.

[0122] In addition, when the operating mode is cooling mode or dehumidification mode, the heat exchange state is characterized by the first heat exchanger being in a condensing state and the second heat exchanger being in an evaporating state; when the operating mode is heating mode or sterilization mode, the heat exchange state is characterized by the first heat exchanger being in an evaporating state and the second heat exchanger being in a condensing state.

[0123] Step S20: When the heat exchange state is that the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, controlling the refrigerant regulating assembly to operate in a first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline, and the second inlet in sequence before entering the ejector;

[0124] In this embodiment, when the refrigerant regulating component operates in the first state, the refrigerant flows through the third pipeline, the first end of the second pipeline, the second end of the second pipeline and the second inlet in sequence, and the refrigerant in the fourth pipeline can stop flowing into the second pipeline under the regulation of the pressure difference or the fluid control valve.

[0125] The refrigerant regulating component operates in the first state. The refrigerant flowing out of the first heat exchanger after heat exchange flows into the third pipeline. A part of the refrigerant flowing into the third pipeline flows through the second pipeline. The refrigerant flowing out of the second pipeline flows into the ejector through the second inlet. The other part of the refrigerant flowing into the third pipeline after heat exchange in the first heat exchanger flows through the first throttling component for throttling and pressure reduction. The low-temperature and low-pressure gas-liquid mixed refrigerant after throttling and pressure reduction flows into the first pipeline. The refrigerant flowing out of the first pipeline is further throttled and reduced in pressure through the second throttling component to form a low-pressure liquid refrigerant which flows into the second heat exchanger for evaporation. The second heat exchanger absorbs heat in the evaporating state. The refrigerant flowing out of the second heat exchanger after heat exchange flows through the reversing valve and then enters the ejector through the first inlet. The refrigerant flowing into the ejector from the first inlet and the second inlet is mixed for heat exchange and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor through the return air port, thus completing a refrigerant circulation process. The refrigerant flowing through the second pipeline exchanges heat with the refrigerant flowing through the first pipeline, and the refrigerant in the second pipeline releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline increases, and the liquid proportion of the refrigerant in the first pipeline increases. After the refrigerant enters the compressor, it can be compressed by the compressor to form a high-temperature and high-pressure refrigerant and discharged from the exhaust port. Then, the refrigerant circulation is carried out again in the above-mentioned manner, which will not be elaborated here. In this embodiment, the first heat exchanger is an outdoor heat exchanger, and the second heat exchanger is an indoor heat exchanger. When the heat exchange state is that the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, the air conditioner is in a cooling state.

[0126] Step S30, when the heat exchange state is that the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state, the refrigerant regulating component is controlled to operate in a second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline and the second inlet in sequence and then enters the ejector.

[0127] In this embodiment, when the refrigerant regulating component operates in the second state, the refrigerant flows through the fourth pipeline, the second end of the second pipeline, the first end of the second pipeline and the second inlet in sequence, and the refrigerant in the third pipeline stops flowing into the second pipeline under the regulation of the pressure difference or the fluid control valve.

[0128] The refrigerant regulating component operates in the second state. The refrigerant flowing out of the second heat exchanger after heat exchange flows into the fourth pipeline. A part of the refrigerant flowing into the fourth pipeline flows through the second pipeline. The refrigerant flowing out of the second pipeline flows through the second inlet and enters the ejector. The other part of the refrigerant flowing into the fourth pipeline after heat exchange in the second heat exchanger flows through the second throttling component for throttling and pressure reduction. The low-temperature and low-pressure gas-liquid mixed refrigerant after throttling and pressure reduction flows into the first pipeline. The refrigerant flowing out of the first pipeline is further throttled and reduced in pressure by the first throttling component to form a low-pressure liquid refrigerant and then flows into the first heat exchanger for evaporation. The first heat exchanger is in an evaporating state and absorbs heat. The refrigerant flowing out of the first heat exchanger after heat exchange flows through the reversing valve and then enters the ejector through the first inlet. The refrigerant flowing into the ejector from the first inlet and the second inlet is mixed and heat exchanged and then ejected from the outlet. The refrigerant ejected from the outlet flows into the compressor through the return air port, thus completing a refrigerant circulation process. Among them, the refrigerant flowing through the second pipeline exchanges heat with the refrigerant flowing through the first pipeline, and the refrigerant in the second pipeline releases heat and becomes supercooled. During the heat exchange process, the gaseous proportion of the refrigerant in the second pipeline increases, and the liquid proportion of the refrigerant in the first pipeline increases. After the refrigerant enters the compressor, it can form a high-temperature and high-pressure refrigerant under the compression action of the compressor and be discharged from the exhaust port. Then the refrigerant circulation is carried out again in the above-mentioned manner, which will not be elaborated here. In this embodiment, the first heat exchanger is an outdoor heat exchanger, and the second heat exchanger is an indoor heat exchanger. When the heat exchange state is that the first heat exchanger is in an evaporating state and the second heat exchanger is in a condensing state, the air conditioner is in a cooling state.

[0129] A control method for an air conditioner proposed in an embodiment of the present invention controls the refrigerant regulating component in the above manner, thereby ensuring that the heat pump system can achieve uniform diversion of the two-phase refrigerant flowing out of the condenser under different working conditions, thereby effectively improving the heat exchange effect of the heat pump system.

[0130] Furthermore, based on the above embodiment, another embodiment of the control method for the air conditioner of the present application is proposed. In this embodiment, the refrigerant regulating assembly includes a first control valve, a second control valve, a third control valve, and a fourth control valve. The first control valve is disposed between the second inlet and the first end of the second pipeline, the second control valve is disposed between the second inlet and the second end of the second pipeline, the first end of the third control valve is in communication with the third pipeline, the connecting pipeline between the second control valve and the second pipeline is in communication with the second end of the third control valve, the first end of the fourth control valve is in communication with the fourth pipeline, and the connecting pipeline between the first control valve and the second pipeline is in communication with the second end of the fourth control valve. In this embodiment, the first control valve, the second control valve, the third control valve, and the fourth control valve are all solenoid valves.

[0131] Reference Figure 7 , the step S20 includes:

[0132] Step S21, when the heat exchange state is that the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, controlling the first control valve to open, controlling the second control valve to close, controlling the third control valve to open, and controlling the fourth control valve to close;

[0133] Under the regulation of the first control valve, the second inlet is connected to the first end of the second pipeline. Under the regulation of the second control valve, the second inlet is blocked from the second end of the second pipeline. Under the regulation of the third control valve, the third pipeline is connected to the second end of the second pipeline. Under the regulation of the fourth control valve, the fourth pipeline is blocked from the first end of the second pipeline. As a result, no refrigerant flows through the branches containing the fourth control valve and the second control valve. The refrigerant in the third pipeline that flows into the first control valve can all flow through the second pipeline. The refrigerant in the second pipeline exchanges heat with the refrigerant in the first pipeline, then flows through the third control valve and enters the ejector through the second inlet.

[0134] Reference Figure 6 , step S30 includes:

[0135] Step S31, when the heat exchange state is that the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state, control the first control valve to be closed, control the second control valve to be open, control the third control valve to be closed, and control the fourth control valve to be open.

[0136] Under the regulation of the first control valve, the second inlet is blocked from the first end of the second pipeline. Under the regulation of the second control valve, the second inlet is connected to the second end of the second pipeline. Under the regulation of the third control valve, the third pipeline is blocked from the second end of the second pipeline. Under the regulation of the fourth control valve, the fourth pipeline is connected to the first end of the second pipeline. Based on this, no refrigerant flows through the branch where the third control valve and the first control valve are located. The refrigerant in the fourth pipeline that flows into the fourth control valve can all flow through the second pipeline. The refrigerant in the second pipeline exchanges heat with the refrigerant in the first pipeline, flows through the second control valve, and enters the ejector through the second inlet.

[0137] In this embodiment, the above-mentioned four control valves can adjust the on-off of the refrigerant in the branch where they are located. Through the coordinated adjustment of the four control valves, the refrigerant can be diverted to meet the needs under different operating conditions, ensuring the combination of the heat exchange effect between the second pipeline and the first pipeline under any working conditions, as well as the air replenishment effect under the ejector, so as to improve energy efficiency and the uniformity of the gas-liquid two-phase diversion of the system, thereby effectively improving the heat exchange effect of the heat pump system.

[0138] Furthermore, based on any of the above embodiments, another embodiment of the control method of the air conditioner of the present application is proposed. In this embodiment, referring to Figure 8 , after step S20 or step S30, further comprising:

[0139] Step S40, obtaining the exhaust gas superheat and the supply gas superheat corresponding to the compressor;

[0140] Specifically, step S40 is performed when the refrigerant conditioning component is operating in the first state or the second state.

[0141] The exhaust superheat specifically represents the superheat value related to the compressor exhaust. The air supply superheat specifically represents the superheat value related to the air supply effect of other refrigerants other than the refrigerant flowing out of the evaporator (in this embodiment, the refrigerant that flows into the ejector through the second inlet and then into the return air port of the compressor) on the compressor.

[0142] In this embodiment, the process of obtaining the exhaust superheat is as follows: obtaining the exhaust temperature of the compressor and the coil temperature of the heat exchanger currently in the condensing state of the first and second heat exchangers; and determining the exhaust superheat based on the temperature difference between the exhaust temperature and the coil temperature. Specifically, when the heat exchange state is that the first heat exchanger is in the condensing state and the second heat exchanger is in the evaporating state, the first coil temperature of the first heat exchanger is obtained, and the temperature difference between the exhaust temperature and the first coil temperature is determined. This temperature difference may be used directly as the exhaust superheat, or the temperature difference may be corrected by a preset coefficient to obtain the exhaust superheat. Furthermore, when the heat exchange state is that the second heat exchanger is in the condensing state and the first heat exchanger is in the evaporating state, the second coil temperature of the second heat exchanger is obtained, and the first temperature difference between the exhaust temperature and the second coil temperature is determined. This first temperature difference may be used directly as the exhaust superheat, or the first temperature difference may be corrected by a preset coefficient to obtain the exhaust superheat.

[0143] In this embodiment, the process for obtaining the supply air superheat is as follows: obtaining a first temperature at the second inlet and a second temperature at the return air outlet; and determining the supply air superheat based on the temperature difference between the first and second temperatures. Specifically, the second temperature difference between the first and second temperatures can be determined and used directly as the supply air superheat; or the second temperature difference can be corrected by a preset coefficient to obtain the supply air superheat. Furthermore, a third temperature at the first inlet can be obtained, and a deviation between the third temperature and the second temperature can be determined. The second temperature difference can then be corrected based on the deviation to obtain the supply air superheat.

[0144] Step S50, controlling the operation of the first target component according to the exhaust gas superheat, and controlling the operation of the second target component according to the supplementary air superheat;

[0145] The first target component is the component located upstream of the first pipeline between the first throttling component and the second throttling component, and the second target component is the component located downstream of the first pipeline between the first throttling component and the second throttling component.

[0146] When the heat exchange state is that the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, the first throttling component is the first target component and the second throttling component is the second target component; when the heat exchange state is that the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state, the second throttling component is the first target component and the first throttling component is the second target component.

[0147] In this embodiment, both the first throttle component and the second throttle component are electronic expansion valves. Specifically, a first target opening of the first target component can be determined based on the exhaust gas superheat, and operation of the first target component can be controlled based on the first target opening. A second target opening of the second target component can be determined based on the supply gas superheat, and operation of the second target component can be controlled based on the second target opening. Alternatively, a first opening adjustment value for the first target component can be determined based on the exhaust gas superheat, and the opening of the first target component can be adjusted based on the first opening adjustment value. A second opening adjustment value for the second target component can be determined based on the supply gas superheat, and the opening of the second target component can be adjusted based on the second opening adjustment value.

[0148] In other embodiments, the first throttling component and the second throttling component may also be multiple capillaries in parallel, and the number of capillaries connected to the refrigerant flow path in the first target component may be adjusted according to the exhaust superheat, and the number of capillaries connected to the refrigerant flow path in the second target component may be adjusted according to the supply air superheat.

[0149] It should be noted that the operation of the first target component is controlled according to the exhaust gas superheat, and the operation of the second target component is controlled according to the supplementary air superheat.

[0150] In this embodiment, on the basis of achieving uniform diversion of the refrigerant flowing out of the condenser through the heat exchange effect between the first pipeline and the second pipeline and the ejector, the exhaust superheat and the supply air superheat can comprehensively reflect the reliability risk of the compressor operation in the heat pump system. Therefore, the operation of the first target component is regulated by the exhaust superheat, and the operation of the second target component is regulated by the supply air superheat, thereby ensuring that the overall throttling and pressure reduction effect achieved by the cooperation of the first throttling component and the second throttling component can make the exhaust superheat and supply air superheat of the compressor within the target range of reliable operation, thereby improving the heat exchange effect of the heat pump system while further improving the reliability of the compressor operation.

[0151] Furthermore, based on any of the above embodiments, another embodiment of the control method for the air conditioner of the present application is provided. In this embodiment, the step of controlling the operation of the first target component based on the exhaust gas superheat comprises: when the exhaust gas superheat is within a preset superheat range, controlling the first target component to maintain its current opening; when the exhaust gas superheat is less than the preset superheat range, controlling the first target component to reduce its current opening according to a first opening adjustment value; and when the exhaust gas superheat is greater than the preset superheat range, controlling the first target component to increase its current opening according to a second opening adjustment value.

[0152] In this embodiment, the preset superheat interval is a set superheat value. In other embodiments, the preset superheat interval may also be an interval set including more than one superheat value.

[0153] The preset superheat range is the superheat range required for the compressor to operate reliably. The preset superheat range can be a pre-set fixed range or a range determined according to the actual operating state of the air conditioner.

[0154] The first opening adjustment value may be a first adjustment amplitude, a first adjustment coefficient, and / or a first adjustment speed. The first opening adjustment value may be a preset fixed value or a value determined based on the actual operating state of the air conditioner. For example, the first opening adjustment value may be determined based on the deviation between the exhaust gas superheat and a minimum threshold value within a preset superheat range.

[0155] The second opening adjustment value may be a second adjustment amplitude, a second adjustment coefficient, and / or a second adjustment speed. The second opening adjustment value may be a preset fixed value or a value determined based on the actual operating state of the air conditioner. For example, the second opening adjustment value may be determined based on the deviation between the exhaust gas superheat and a maximum threshold value within a preset superheat range.

[0156] In this embodiment, the second opening adjustment value is the same as the first opening adjustment value. In other embodiments, the second opening adjustment value and the first opening adjustment value may also be different.

[0157] In this embodiment, the above-mentioned method can ensure that the exhaust superheat of the compressor is within the reliable operating range, thereby ensuring that the reliability of the compressor is effectively improved during the uniform diversion of the two-phase refrigerant.

[0158] Furthermore, in this embodiment, the preset superheat range is determined according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state;

[0159] and / or, determining the first opening adjustment value according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state;

[0160] And / or, the second opening adjustment value is determined according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state.

[0161] In one implementation of this embodiment, a preset superheat interval is determined based on the outdoor ambient temperature and the heat exchange state. Different outdoor ambient temperatures and different heat exchange states correspond to different preset superheat intervals. Specifically, under the same heat exchange state, different outdoor ambient temperatures correspond to different preset superheat intervals. Under different heat exchange states, the correspondence between the outdoor ambient temperature and the preset superheat intervals varies. Based on this, a target correspondence between the outdoor ambient temperature and the preset superheat intervals can be determined based on the heat exchange state. Based on this target correspondence, the preset superheat interval corresponding to the current outdoor ambient temperature can be determined.

[0162] In another implementation of this embodiment, a preset superheat interval is determined based on the outdoor ambient temperature and the operating mode. Different outdoor ambient temperatures and operating modes correspond to different preset superheat intervals. Specifically, under the same operating mode, different outdoor ambient temperatures correspond to different preset superheat intervals. Different operating modes have different correspondences between the outdoor ambient temperature and the preset superheat intervals. Based on this, a target correspondence between the outdoor ambient temperature and the preset superheat intervals can be determined based on the operating mode. Based on this target correspondence, the preset superheat interval corresponding to the current outdoor ambient temperature can be determined.

[0163] In this embodiment, the target correspondence relationship includes a correspondence between different outdoor temperature intervals and superheat intervals. Based on this correspondence, the outdoor temperature interval within which the outdoor ambient temperature falls is determined as the target interval, and the superheat interval corresponding to the target interval is used as the preset superheat interval. In other embodiments, the target correspondence relationship may be a calculation formula between the outdoor ambient temperature and a threshold value of the preset superheat interval. Based on this calculation formula, the preset superheat interval can be calculated from the outdoor ambient temperature.

[0164] In this embodiment, the preset superheat interval is determined based on the outdoor ambient temperature and / or heat exchange state and / or operating mode, which is conducive to ensuring the accuracy of the preset superheat interval, so as to achieve accurate regulation of the first target component based on the size relationship between the preset superheat interval and the exhaust superheat, thereby helping to further improve the operating reliability of the compressor.

[0165] Furthermore, the deviation value between the superheat of the supplementary air and the preset superheat value can be determined, and the preset superheat range here is determined according to the deviation value, the outdoor ambient temperature and the heat exchange state and / or according to the deviation value, the outdoor ambient temperature and the operating mode, so as to improve the coordination of the operation of the first target component and the second target component, so as to ensure that the reliability of the compressor can be further improved under the comprehensive adjustment of the two throttling components.

[0166] In other embodiments, the preset superheat range may also be determined according to one of the outdoor ambient temperature, the heat exchange state, and the operation mode.

[0167] Furthermore, in one implementation of this embodiment, the first opening adjustment value is determined based on the outdoor ambient temperature. Different outdoor ambient temperatures correspond to different first opening adjustment values. The first opening adjustment value is positively correlated with the outdoor ambient temperature. Specifically, a temperature range within which the outdoor ambient temperature falls can be determined, and the first opening adjustment value is determined based on the temperature range.

[0168] In other embodiments, the first opening adjustment value may be determined based on the outdoor ambient temperature and the heat exchange state, or based on a mild outdoor ambient operating mode. Different outdoor ambient temperatures and different heat exchange states correspond to different first opening adjustment values, and different outdoor ambient temperatures and different operating modes correspond to different first opening adjustment values. The first opening adjustment value may also be determined based on the heat exchange state, and different heat exchange states correspond to different first opening adjustment values.

[0169] Furthermore, in one implementation of this embodiment, the second opening adjustment value is determined based on the outdoor ambient temperature. Different outdoor ambient temperatures correspond to different second opening adjustment values. The second opening adjustment value is positively correlated with the outdoor ambient temperature. Specifically, a temperature range within which the outdoor ambient temperature falls can be determined, and the second opening adjustment value is determined based on the temperature range.

[0170] In other embodiments, the second opening adjustment value may be determined based on the outdoor ambient temperature and the heat exchange state, or based on a mild outdoor ambient operating mode. Different outdoor ambient temperatures and different heat exchange states correspond to different second opening adjustment values, and different outdoor ambient temperatures and different operating modes correspond to different second opening adjustment values. The second opening adjustment value may also be determined based on the heat exchange state, and different heat exchange states correspond to different second opening adjustment values.

[0171] In order to better understand the regulation of the first target component based on the exhaust superheat in this embodiment, the following is a detailed description of different working conditions:

[0172] 1. Under the first operating condition, the air conditioner operates in cooling mode. The heat exchange state is that the first heat exchanger is in the condensing state and the second heat exchanger is in the evaporating state. The preset superheat range is defined as M, the exhaust superheat is ΔTd1, the outdoor ambient temperature is T4, and the opening adjustment value is Δp. A positive value corresponding to Δp indicates an increase in the opening, and a negative value indicates a decrease in the opening. The relationship between the outdoor ambient temperature, the exhaust superheat, and the opening adjustment value can be seen in Table 1:

[0173]

[0174] Table 1

[0175] 2. Under the second operating condition, the air conditioner operates in the heating mode. The heat exchange state is that the first heat exchanger is in the evaporating state and the second heat exchanger is in the condensing state. The preset superheat interval is defined as N, the exhaust superheat is ΔTd2, the outdoor ambient temperature is T4, and the opening adjustment value is Δp. A positive value corresponding to Δp indicates an increase in the opening, and a negative value indicates a decrease in the opening. The relationship between the outdoor ambient temperature, the exhaust superheat, and the opening adjustment value can be seen in Table 2:

[0176]

[0177] Furthermore, based on any of the above embodiments, another embodiment of the air conditioner control method of the present application is provided. In this embodiment, the step of controlling the operation of the second target component based on the supplemental air superheat comprises: controlling the second target component to decrease its opening when the supplemental air superheat is greater than a preset superheat; and controlling the second target component to maintain its current opening when the supplemental air superheat is less than or equal to the preset superheat.

[0178] The preset superheat is the critical superheat value used to determine whether the compressor is at risk of return air carryover. If the supply air superheat exceeds the preset superheat, the compressor is at risk of return air carryover. If the supply air superheat is less than or equal to the preset superheat, the compressor is not at risk of return air carryover.

[0179] The opening adjustment value during the process of reducing the opening degree of the second target component can be an adjustment amplitude, an adjustment coefficient, and / or an adjustment speed. The opening adjustment value can be a preset fixed value or a value determined based on the actual operating state of the air conditioner. For example, the opening adjustment value of the second target component can be determined based on the deviation between the supply air superheat and a preset superheat.

[0180] Specifically, in this embodiment, the opening adjustment value of the second target component can be determined according to the opening adjustment value of the first target component, thereby ensuring that the system can operate stably and reliably during the opening adjustment process of the two components.

[0181] In this embodiment, the above-mentioned method can ensure that the air supply superheat of the compressor is within the reliable operating range, thereby ensuring that the reliability of the compressor is effectively improved during the uniform diversion of the two-phase refrigerant.

[0182] In addition, an embodiment of the present invention further provides a storage medium on which a control program for an air conditioner is stored. When the control program for the air conditioner is executed by a processor, the relevant steps of any embodiment of the above-mentioned method for controlling an air conditioner are implemented.

[0183] It should be noted that, in this document, the terms "comprises," "includes," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a process, method, article, or system comprising a series of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or system. In the absence of further limitations, an element defined by the phrase "comprising a ..." does not exclude the presence of other identical elements in the process, method, article, or system comprising the element.

[0184] The serial numbers of the above embodiments of the present invention are for description only and do not represent the advantages or disadvantages of the embodiments.

[0185] Through the description of the above embodiments, those skilled in the art can clearly understand that the above embodiment methods can be implemented by means of software plus the necessary general hardware platform, and of course can also be implemented by hardware, but in many cases the former is a better embodiment. Based on this understanding, the technical solution of the present invention is essentially or the part that contributes to the prior art can be embodied in the form of a software product, which is stored in a storage medium (such as ROM / RAM, magnetic disk, optical disk) as described above, and includes a number of instructions for enabling a terminal device (which can be a mobile phone, computer, server, air conditioner, or network device, etc.) to execute the methods described in each embodiment of the present invention.

[0186] The above are only preferred embodiments of the present invention and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention description and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A heat pump system, characterized in that: The heat pump system includes a compressor, a reversing valve, a first heat exchanger, a second heat exchanger, an ejector, a throttling device, a first pipeline and a second pipeline, wherein the first pipeline is connected to the second pipeline for heat exchange; The compressor has an exhaust port and a return air port, the ejector has a first inlet, a second inlet, and an outlet, the exhaust port, the first inlet, the first heat exchanger, and the second heat exchanger are all connected to the reversing valve, and the outlet is connected to the return air port; The first heat exchanger, the first pipeline and the second heat exchanger are connected in sequence, and the throttling device is arranged between the first heat exchanger and the second heat exchanger. When the heat pump system is running, a part of the refrigerant condensed by the first heat exchanger or the second heat exchanger flows through the second pipeline and the second inlet in sequence and then enters the ejector, and the other part flows through the throttling device and then flows through the first pipeline to enter the second heat exchanger or the first heat exchanger after throttling.

2. The heat pump system according to claim 1, wherein The throttling device includes a first throttling component and a second throttling component, the first throttling component is arranged between the first heat exchanger and the first pipeline, and the pipeline between the first heat exchanger and the first throttling component is defined as a third pipeline. The second throttling component is arranged between the first pipeline and the second heat exchanger, and the pipeline between the second heat exchanger and the second throttling component is defined as a fourth pipeline. The heat pump system further includes a refrigerant regulating component, and the second inlet, the second pipeline, the third pipeline, and the fourth pipeline are all connected to the refrigerant regulating component; The refrigerant regulating assembly is configured to operate in a first state when the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, so that a portion of the refrigerant flowing out of the first heat exchanger flows sequentially through the third pipeline, the second pipeline, and the second inlet before entering the ejector, and the other portion flows through the first throttling component and is throttled by the first throttling component before flowing sequentially through the first pipeline, the second throttling component, and the second heat exchanger; The refrigerant regulating component is also used to operate in the second state when the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state so that a portion of the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline and the second inlet in sequence and then enters the ejector, and the other portion flows through the second throttling component and is throttled by the second throttling component and then flows through the first pipeline, the first throttling component and the first heat exchanger in sequence.

3. The heat pump system according to claim 2, wherein: The refrigerant conditioning component comprises: a first control valve disposed between the second inlet and the first end of the second pipeline; a second control valve disposed between the second inlet and the second end of the second pipeline; a third control valve, wherein a first end of the third control valve is in communication with the third pipeline, and a connecting pipeline between the second control valve and the second pipeline is in communication with a second end of the third control valve; A fourth control valve, wherein a first end of the fourth control valve is communicated with the fourth pipeline, and a connecting pipeline between the first control valve and the second pipeline is communicated with a second end of the fourth control valve.

4. The heat pump system according to any one of claims 1 to 3, characterized in that The heat pump system further includes a gas-liquid separator disposed between the outlet and the return air port, the gas-liquid separator having a refrigerant inlet and an outlet, the outlet being communicated with the refrigerant inlet, and the outlet being communicated with the return air port.

5. A method for controlling an air conditioner, characterized in that: The air conditioner includes the heat pump system according to claim 2 or 3, and the control method of the air conditioner includes: Acquire an operating mode of the heat pump system and / or heat exchange states of the first heat exchanger and the second heat exchanger, wherein the operating mode can represent the heat exchange states of the first heat exchanger and the second heat exchanger; When the first heat exchanger is in a condensing state and the second heat exchanger is in an evaporating state, controlling the refrigerant regulating component to operate in a first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline, and the second inlet in sequence before entering the ejector; When the second heat exchanger is in a condensing state and the first heat exchanger is in an evaporating state, the refrigerant regulating component is controlled to operate in a second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline and the second inlet in sequence and then enters the ejector.

6. The air conditioner control method according to claim 5, wherein: The refrigerant regulating assembly includes a first control valve, a second control valve, a third control valve and a fourth control valve, the first control valve is arranged between the second inlet and the first end of the second pipeline, the second control valve is arranged between the second inlet and the second end of the second pipeline, the first end of the third control valve is communicated with the third pipeline, the connecting pipeline between the second control valve and the second pipeline is communicated with the second end of the third control valve, the first end of the fourth control valve is communicated with the fourth pipeline, the connecting pipeline between the first control valve and the second pipeline is communicated with the second end of the fourth control valve, and the step of controlling the refrigerant regulating assembly to operate in a first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline and the second inlet in sequence and then enters the ejector includes: Controlling the first control valve to open, controlling the second control valve to close, controlling the third control valve to open, and controlling the fourth control valve to close; The step of controlling the refrigerant regulating component to operate in the second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector includes: The first control valve is controlled to be closed, the second control valve is controlled to be opened, the third control valve is controlled to be closed, and the fourth control valve is controlled to be opened.

7. The air conditioner control method according to claim 5 or 6, characterized in that: After the step of controlling the refrigerant regulating component to operate in the first state so that the refrigerant flowing out of the first heat exchanger flows through the third pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector, or the step of controlling the refrigerant regulating component to operate in the second state so that the refrigerant flowing out of the second heat exchanger flows through the fourth pipeline, the second pipeline, and the second inlet in sequence and then enters the ejector, the step further includes: Obtaining the exhaust gas superheat and the supply gas superheat corresponding to the compressor; Controlling the operation of the first target component according to the exhaust gas superheat, and controlling the operation of the second target component according to the supplementary air superheat; The first target component is the component located upstream of the first pipeline between the first throttling component and the second throttling component, and the second target component is the component located downstream of the first pipeline between the first throttling component and the second throttling component.

8. The air conditioner control method according to claim 7, wherein: The step of controlling the operation of the first target component according to the exhaust superheat comprises: When the exhaust gas superheat is within a preset superheat range, controlling the first target component to maintain a current opening; When the exhaust gas superheat is less than the preset superheat range, controlling the first target component to reduce the current opening according to the first opening adjustment value; When the exhaust gas superheat is greater than the preset superheat range, the first target component is controlled to increase the current opening according to the second opening adjustment value.

9. The air conditioner control method according to claim 8, wherein: Before the step of controlling the operation of the first target component according to the exhaust superheat, the method further includes: Determining the preset superheat range according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state; and / or, determining the first opening adjustment value according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state; And / or, the second opening adjustment value is determined according to the outdoor ambient temperature and / or the operating mode and / or the heat exchange state.

10. The air conditioner control method according to claim 7, wherein: The step of obtaining the exhaust superheat of the air conditioner comprises: Acquire the exhaust temperature of the compressor and the coil temperature of the heat exchanger currently in a condensing state among the first heat exchanger and the second heat exchanger; The exhaust gas superheat is determined according to a temperature difference between the exhaust gas temperature and the coil temperature.

11. The air conditioner control method according to claim 7, wherein: The step of controlling the operation of the second target component according to the supplementary air superheat comprises: When the supplementary air superheat is greater than a preset superheat, controlling the second target component to reduce its opening; When the supplementary air superheat is less than or equal to the preset superheat, the second target component is controlled to maintain a current opening.

12. The air conditioner control method according to claim 7, wherein: The step of obtaining the air supply superheat degree comprises: Acquire a first temperature of the second inlet and a second temperature of the return air outlet; The supplementary air superheat degree is determined according to a temperature difference between the first temperature and the second temperature.

13. An air conditioner, characterized in that: The air conditioner comprises: The heat pump system according to claim 2 or 3; A control device, the heat pump system is connected to the control device, the control device includes: a memory, a processor and an air conditioner control program stored in the memory and executable on the processor, the air conditioner control program, when executed by the processor, implements the steps of the air conditioner control method as described in any one of claims 5 to 12.

14. A storage medium, characterized in that The storage medium stores a control program for the air conditioner, and when the control program for the air conditioner is executed by the processor, the steps of the control method for the air conditioner according to any one of claims 5 to 12 are implemented.

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