Jet-propelled enthalpy-increasing heat pump system and control method, controller and air conditioner thereof

Abstract

The application discloses a jet augmenting heat pump system, a control method and controller thereof and an air conditioner. The jet augmenting heat pump system comprises a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange assembly and a flow regulating assembly. The gas-liquid separation heat exchange assembly comprises a first input end, a first output end and a second output end. The exhaust port of the compressor is connected with one end of the indoor heat exchanger, the other end of the indoor heat exchanger is connected with the first input end, the first output end is connected with one end of the outdoor heat exchanger, the other end of the outdoor heat exchanger is connected with the gas inlet of the compressor, the second output end is connected to the gas inlet of the compressor through a first branch, and the second output end is also connected to the air supplement inlet of the compressor through a second branch. The flow regulating assembly is arranged on the first branch or the second branch. The proportion of the refrigerant flow in the first branch and the second branch is regulated through the flow regulating assembly in the control, so that the heating performance is adjusted under different outdoor environment temperatures or different working conditions.

Description

Technical Field

[0001] This application relates to the field of vapor injection enthalpy enhancement technology, and in particular to a vapor injection enthalpy enhancement heat pump system and its control method, controller and air conditioner. Background Technology

[0002] Jet enthalpy-enhancing heat pump systems can maintain a certain heating capacity at relatively low ambient temperatures.

[0003] In ultra-low temperature environments, the pressure difference between the medium-pressure and high-pressure refrigerants in a vapor-jet enthalpy-enhancing heat pump system is not large, resulting in a small vapor jet volume and limited heat exchange by the economizer, thus affecting the system's heating capacity. In related technologies, two-stage vapor-jet enthalpy-enhancing heat pump systems improve heating capacity in ultra-low temperature environments by injecting vapor into the low-pressure side through a two-stage economizer structure. However, in medium- and high-temperature environments, the second-stage economizer of a two-stage vapor-jet enthalpy-enhancing heat pump system does not need to be activated, leading to wasted costs. Summary of the Invention

[0004] This application aims to address at least one of the technical problems existing in the prior art. To this end, this application proposes a vapor injection enthalpy-enhancing heat pump system and its control method, controller, and air conditioner, which reduces the hardware cost of the vapor injection enthalpy-enhancing heat pump system while ensuring heating capacity in ultra-low temperature environments.

[0005] An embodiment of the first aspect of this application provides a vapor injection enthalpy-increasing heat pump system, including a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulation component. The gas-liquid separation heat exchange component includes a first input terminal, a first output terminal, and a second output terminal. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input terminal. The first output terminal is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output terminal is connected to the air inlet of the compressor via a first branch, and the second output terminal is also connected to the air supply port of the compressor via a second branch. The flow regulation component is disposed on either the first branch or the second branch.

[0006] The vapor-induced enthalpy heat pump system of the first aspect of this application has at least the following beneficial effects: The system is equipped with a gas-liquid separation heat exchange component. The first output end of the gas-liquid separation heat exchange component, serving as the main outlet, is connected to an outdoor heat exchanger, allowing liquid refrigerant to be delivered to the outdoor heat exchanger for heat exchange. Furthermore, the second output end, serving as the auxiliary outlet, is divided into two branches: a first branch connects to the compressor's air inlet, and a second branch connects to the compressor's gas supply port. A flow regulating component is installed in either the first or second branch. This structure allows for the adjustment and distribution of gaseous refrigerant in the first and second branches. For example, with this structure, in medium-high temperature environments, one branch can be shut down (e.g., the first branch is equipped with a flow regulating component, and the first branch is shut off via the flow regulating component), making the system equivalent to a heat pump system with a single-stage gas-liquid separation heat exchange component. In low-temperature and ultra-low-temperature environments, where the compressor requires more gas supply, the gas supply ratio between the first and second branches can be changed by opening the flow regulating component, thereby achieving optimal system heating capacity and energy efficiency. Since the heat pump system in this embodiment only requires one gas-liquid separation heat exchange component, compared with the prior art scheme of supplementing gas through two-stage economizers, it is equivalent to merging two economizers into one economizer, thus reducing costs while ensuring the heating performance of the heat pump system.

[0007] According to some embodiments of this application, the gas-liquid separation heat exchange component is a flash tank, the input end of the flash tank is the first input end, the liquid output end of the flash tank is the first output end, and the gas output end of the flash tank is the second output end.

[0008] According to some embodiments of this application, the gas-liquid separation heat exchange component is a plate heat exchanger. The plate heat exchanger includes a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is the first input terminal, the second inlet is connected to the first outlet through an expansion valve, the first outlet is the first output terminal, and the second outlet is the second output terminal.

[0009] According to some embodiments of this application, a gas-liquid separator is also included, the gas-liquid separator having a second inlet and a third outlet, the second inlet being connected to the other end of the outdoor heat exchanger via a third branch, the first branch and the third branch converging at the second inlet, and the third outlet being connected to the air inlet of the compressor.

[0010] According to some embodiments of this application, a four-way valve is also included, the four-way valve including a first port, a second port, a third port and a fourth port, the first port being connected to the exhaust port of the compressor, the second port being connected to the indoor heat exchanger, the third port being connected to the third branch, and the fourth port being connected to the outdoor heat exchanger.

[0011] According to some embodiments of this application, an outdoor throttling device and an indoor throttling device are also included, wherein the outdoor throttling device is disposed between the outdoor heat exchanger and the first output terminal, and the indoor throttling device is disposed between the indoor heat exchanger and the first input terminal.

[0012] According to some embodiments of this application, the flow regulating component is disposed in the first branch, and the valve of the flow regulating component is used to be opened in a controlled manner to adjust the flow rate of gaseous refrigerant in the first branch.

[0013] According to some embodiments of this application, a first temperature sensor and a second temperature sensor are also included, wherein the first temperature sensor is used to detect the temperature of the outdoor heat exchanger and the second temperature sensor is used to detect the temperature of the indoor heat exchanger.

[0014] A second aspect of this application provides a control method for a vapor injection enthalpy-increasing heat pump system. The vapor injection enthalpy-increasing heat pump system includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulation component. The gas-liquid separation heat exchange component includes a first input terminal, a first output terminal, and a second output terminal. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input terminal. The first output terminal is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output terminal is connected to the air inlet of the compressor via a first branch, and the second output terminal is also connected to the air supply port of the compressor via a second branch. The flow regulation component is disposed on either the first branch or the second branch.

[0015] The control method includes:

[0016] When the outdoor ambient temperature is greater than the first temperature threshold, the flow regulation component is controlled so that all the refrigerant flowing out of the second output terminal enters the compressor's gas inlet through the second branch;

[0017] When the outdoor ambient temperature is lower than the first temperature threshold, the flow regulation component is controlled so that at least a portion of the refrigerant flowing out of the second output terminal enters the air inlet of the compressor through the first branch.

[0018] The control method of the second aspect of this application has at least the following beneficial effects: the flow regulating component is used to regulate the refrigerant operation of the heat pump system under different outdoor ambient temperatures. When the outdoor ambient temperature is high and greater than the first temperature threshold, the heat pump system closes the flow regulating component. At this time, all the refrigerant flowing out of the second output end enters the compressor's gas injection port through the second branch, realizing primary gas injection and meeting the heating needs in medium and high temperature environments. When the outdoor ambient temperature is low and less than the first temperature threshold, the heat pump system opens the flow regulating component, allowing at least a portion of the refrigerant flowing out of the second output end to enter the compressor's gas inlet, increasing the gas intake of the compressor's gas inlet, realizing primary and secondary gas injection. The flow ratio of the refrigerant in the first branch and the second branch can be adjusted by regulating the valve opening of the flow regulating component, thereby achieving optimal heating capacity and efficiency. In other words, in low temperature environments, the heat pump system injects gas from the low-pressure side, increasing the heating capacity of the heat pump system at low temperatures by increasing the gas injection volume.

[0019] In some embodiments, controlling the flow regulation component to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the compressor's intake port via the first branch when the outdoor ambient temperature is lower than the first temperature threshold includes:

[0020] When the outdoor ambient temperature is less than the first temperature threshold and greater than the second temperature threshold, the target valve opening is determined based on the first temperature of the outdoor heat exchanger and the second temperature of the indoor heat exchanger, and the flow regulating component is controlled according to the target valve opening, wherein the target valve opening is less than the maximum opening of the valve of the flow regulating component.

[0021] When the outdoor ambient temperature is lower than the second temperature threshold, the valve of the flow regulating component is controlled to be at its maximum opening.

[0022] In some embodiments, determining the valve opening of the flow regulating assembly based on a first temperature of the outdoor heat exchanger and a second temperature of the indoor heat exchanger includes:

[0023] The first saturated steam pressure of the outdoor heat exchanger is determined based on the first temperature, and the second saturated steam pressure of the indoor heat exchanger is determined based on the second temperature.

[0024] The valve opening of the flow regulating component is determined based on the difference between the first saturated steam pressure and the second saturated steam pressure.

[0025] In some embodiments, the heat pump system further includes an outdoor throttling device and an indoor throttling device, wherein the outdoor throttling device is disposed between the outdoor heat exchanger and the first output terminal, and the indoor throttling device is disposed between the indoor heat exchanger and the first input terminal;

[0026] When the flow regulating component is controlled to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the compressor's inlet via the first branch, the control method further includes:

[0027] Reduce the valve opening of the outdoor throttling device and / or the indoor throttling device.

[0028] A third aspect of this application provides a control method for a vapor injection enthalpy-increasing heat pump system. The vapor injection enthalpy-increasing heat pump system includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulation component. The gas-liquid separation heat exchange component includes a first input terminal, a first output terminal, and a second output terminal. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input terminal. The first output terminal is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output terminal is connected to the air inlet of the compressor via a first branch, and the second output terminal is also connected to the air supply port of the compressor via a second branch. The flow regulation component is disposed on either the first branch or the second branch.

[0029] The control method includes:

[0030] As the temperature of the indoor heat exchanger continues to rise, the valve opening of the flow regulating component is changed to continuously increase the flow rate of the refrigerant flowing out of the second output end and entering the air inlet of the compressor through the first branch.

[0031] When the superheat of the compressor's exhaust is less than the third temperature threshold, or when the exhaust temperature of the compressor continues to decrease, the valve opening of the flow regulating component remains unchanged.

[0032] The control method of the third aspect of this application has at least the following beneficial effects: the flow regulating component is used to regulate the refrigerant operation of the heat pump system under different exhaust superheats. When the temperature of the indoor heat exchanger continues to rise, the valve opening of the flow regulating component is continuously opened to increase the refrigerant flow at the compressor inlet, ensuring the heating capacity and energy efficiency in a low-temperature environment. Then, the exhaust superheat of the compressor is calculated. If the exhaust superheat is less than a third temperature threshold or continues to decrease, the valve opening of the flow regulating component is stopped, and the current opening of the flow regulating component is maintained to stabilize the state of the heat pump system.

[0033] A fourth aspect of this application provides a controller, including: a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the control method as described in the second or third aspect above when running the computer program.

[0034] A fifth aspect of this application provides a computer-readable storage medium storing computer-executable instructions for performing the control method as described in the second or third aspect above.

[0035] Other features and advantages of this application will be set forth in the description which follows, and will be apparent in part from the description, or may be learned by practicing the application. The objectives and other advantages of this application may be realized and obtained by means of the structures particularly pointed out in the description, claims and drawings. Attached Figure Description

[0036] Figure 1 This is a system architecture diagram of the jet enthalpy-enhancing heat pump system provided in the embodiments of this application;

[0037] Figure 2 This is a system architecture diagram of a flash tank as the gas-liquid separation heat exchange component in the jet enthalpy-enhancing heat pump system provided in this application embodiment;

[0038] Figure 3 This is a system architecture diagram of the gas-liquid separation heat exchange component of the jet enthalpy-enhancing heat pump system provided in the embodiments of this application, which is a plate heat exchanger;

[0039] Figure 4 This is a structural diagram of the system platform architecture provided in the embodiments of this application;

[0040] Figure 5 This is an overall flowchart of the control method provided in the embodiments of this application;

[0041] Figure 6 This is a flowchart of the control method in low temperature and ultra-low temperature environments provided in the embodiments of this application;

[0042] Figure 7 This is a flowchart of determining the valve opening based on a first temperature and a second temperature, provided in an embodiment of this application.

[0043] Figure 8 This is a flowchart illustrating the process of opening the flow regulation component while simultaneously closing the main throttling device, as provided in an embodiment of this application.

[0044] Figure 9 This is a flowchart of an embodiment of the present application showing how the valve opening of a flow regulating component is continuously adjusted according to the temperature of an indoor heat exchanger;

[0045] Figure 10 This is a flowchart illustrating the process of stopping the adjustment of the valve opening of the flow regulating component according to an embodiment of this application. Detailed Implementation

[0046] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application. Furthermore, the features, operations, or characteristics described in the specification can be combined in any suitable manner to form various implementations. Simultaneously, the steps or actions described in the method description can be rearranged or adjusted in a manner readily apparent to those skilled in the art. Therefore, the various orders in the specification and drawings are merely for the clear description of a particular embodiment and do not imply a mandatory order, unless otherwise stated that a particular order must be followed.

[0047] In the description of this application, "several" means one or more, "more than" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0048] The serial numbers assigned to components in this document, such as "first" and "second," are used only to distinguish the described objects and have no sequential or technical meaning. The terms "connection" and "linkage" used in this application, unless otherwise specified, include both direct and indirect connections (linkages).

[0049] In a vapor injection enthalpy-enhancing heat pump system, the compressor is equipped with a gas injection port. By separating a portion of the gaseous refrigerant from the refrigerant pipeline and inputting it into the compressor's gas injection port, the compressor's intake air volume can be increased, thus improving the operating performance of the vapor injection enthalpy-enhancing heat pump system. Therefore, it is often used in the field of air conditioners to improve the heating performance in low-temperature environments. It can overcome the shortcomings of traditional single-stage compressors, such as large attenuation of heat pump heating capacity, poor reliability, and low efficiency in low-temperature environments. Based on this, air source heat pump technology has been widely used in cold regions.

[0050] However, as the ambient temperature of the system further decreases, such as below -30 degrees Celsius, the pressure difference between the medium-pressure and high-pressure refrigerants in the vapor injection enthalpy-enhancing heat pump system becomes small. This results in a lower compressor vapor injection volume and a smaller heat exchange rate from the economizer, affecting the heating capacity of the vapor injection enthalpy-enhancing heat pump system. In this case, the intake air volume to the compressor is increased by using two economizers in the two-stage vapor injection enthalpy-enhancing heat pump system, thereby improving the refrigerant circulation quality and flow rate in ultra-low temperature environments. However, in medium- and high-temperature environments, the second-stage economizer in the two-stage economizer system does not need to be activated. The activation of the first-stage economizer is determined based on the temperature and the control strategy of the vapor injection enthalpy-enhancing heat pump system. Since the usage time in ultra-low temperature environments often only accounts for a small portion of the total usage time of the vapor injection enthalpy-enhancing heat pump system, the second-stage economizer remains inactive for extended periods, making it a low-utilization component and resulting in wasted costs.

[0051] Based on this, embodiments of this application provide a vapor jet enthalpy-increasing heat pump system and its control method, controller, and air conditioner. The system achieves the regulation capability of a two-stage economizer through a gas-liquid separation heat exchange component and a refrigerant pipeline branch with a flow regulation component. By controlling the valve opening of the flow regulation component, the system can adapt to the heating performance under different ambient temperatures. Compared with traditional vapor jet enthalpy-increasing heat pump systems with two-stage economizers, the system's component utilization rate can be improved.

[0052] The embodiments of this application will be further described below with reference to the accompanying drawings.

[0053] like Figure 1 As shown, Figure 1 This is a system architecture diagram of a vapor injection enthalpy-increasing heat pump system provided in one embodiment of this application. The vapor injection enthalpy-increasing heat pump system includes a compressor 1, an outdoor heat exchanger 2, an indoor heat exchanger 3, a gas-liquid separation heat exchange component 4, and a flow regulating component 5. The gas-liquid separation heat exchange component 4 includes a first input end, a first output end, and a second output end. The exhaust port of the compressor 1 is connected to one end of the indoor heat exchanger 3, and the other end of the indoor heat exchanger 3 is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger 2, and the other end of the outdoor heat exchanger 2 is connected to the air inlet of the compressor 1. The second output end is connected to the air inlet of the compressor 1 through a first branch 43, and the second output end is also connected to the air supply port of the compressor 1 through a second branch 44. The flow regulating component 5 is disposed on the first branch 43 or the second branch 44.

[0054] The refrigerant circulates in the heat pump system to achieve heat exchange between the outdoor and indoor environments. In heating mode, the refrigerant absorbs heat at the outdoor heat exchanger 2 and releases heat at the indoor heat exchanger 3. The refrigerant circulation process is driven by compressor 1. The intake port of compressor 1 receives refrigerant that has absorbed heat through the outdoor heat exchanger 2, primarily in gaseous form. The exhaust port of compressor 1 discharges refrigerant, primarily in liquid form, to the indoor heat exchanger 3. In low-temperature environments, heat exchange at the outdoor heat exchanger 2 becomes difficult, resulting in insufficient intake air volume for compressor 1 and affecting the heating capacity of the heat pump system. By using vapor injection enthalpy enhancement technology, a portion of the gaseous refrigerant in the refrigerant pipeline is input into the makeup air port of compressor 1, increasing the intake air volume of compressor 1 and ensuring its heating capacity in low-temperature environments. At lower ambient temperatures, the heat load demand of the enthalpy-increasing heat pump system increases. To ensure heating capacity, the intake air volume of compressor 1 needs to be further increased. Under relevant technologies, the enthalpy-increasing heat pump system supplements compressor 1 with air by setting up two-stage economizers. In non-ultra-low temperature environments, the first-stage economizer is controlled to be open and the second-stage economizer is closed to ensure a certain intake air volume. In ultra-low temperature environments, the first-stage economizer is controlled to be open and the second-stage economizer is opened. By supplementing air through two stages, the intake air volume of compressor 1 is guaranteed, thereby ensuring heating performance in ultra-low temperature environments.

[0055] As can be seen from the above two-stage economizer operation mode, the second-stage economizer is idle in non-ultra-low temperature environments. Since the enthalpy-increasing heat pump system operates in non-ultra-low temperature environments most of the time, the utilization rate of the second-stage economizer is not high, resulting in a certain amount of cost waste.

[0056] Therefore, the vapor injection enthalpy-enhancing heat pump system of this application embodiment is provided with a gas-liquid separation heat exchange component 4. In the heating mode, the refrigerant flowing through the indoor heat exchanger 3 flows into the first input end of the gas-liquid separation heat exchange component 4. The gas-liquid separation heat exchange component 4 separates the gas and liquid phases of the refrigerant. The liquid refrigerant flows out from the first output end to the outdoor heat exchanger 2, and the gaseous refrigerant flows out from the second output end and can enter the first branch 43 and the second branch 44. The first branch 43 is connected to the air inlet of the compressor 1, and the second branch 44 is connected to the air supply port of the compressor 1. By adjusting the flow rate of the gaseous refrigerant from the first branch 43 and the second branch 44 to the compressor 1, the heating performance of the heat pump system can be adjusted. That is, the flow rate of the gaseous refrigerant to the compressor 1 can be adjusted by the flow regulating component 5, thereby realizing the variable vapor injection enthalpy-enhancing function.

[0057] Understandably, the flow regulating component 5 is a component with a controllable valve opening, such as an electronic expansion valve or an electronic on / off valve. By controlling the valve opening of the flow regulating component 5, the refrigerant flow in the first branch 43 and the second branch 44 is regulated. Taking the flow regulating component 5 being located in the first branch 43 as an example, when the flow regulating component 5 is closed, all the gaseous refrigerant enters the air inlet of the compressor 1 through the second branch 44. When the flow regulating component 5 is open, a portion of the gaseous refrigerant enters the air inlet of the compressor 1 through the first branch 43, thereby increasing the air intake of the compressor 1. Correspondingly, the flow rate of the gaseous refrigerant in the second branch 44 decreases at this time. For example, in medium to high temperature environments (e.g., ambient temperature between 0°C and 20°C), only the second branch 44 needs to be turned on for gas replenishment to meet the heating demand. In this case, the heat pump system operates in the same way as a first-level economizer. In lower ambient temperatures (e.g., ambient temperature between -40°C and 5°C), the flow regulating component 5 is turned on to replenish gas to the low-pressure side. The flow regulating component 5 controls the distribution ratio to achieve optimal system capacity and energy efficiency.

[0058] In some embodiments, refer to Figure 2 As shown, the gas-liquid separation heat exchange component 4 is a flash tank 41. The flash tank 41 includes an input end, a liquid output end and a gas output end. The input end of the flash tank 41 is the first input end, the liquid output end of the flash tank 41 is the first output end, and the gas output end of the flash tank 41 is the second output end.

[0059] The flash tank 41 includes an inlet, a liquid outlet, and a gaseous outlet. The function of flash evaporation is to transform high-pressure saturated refrigerant into a portion of saturated gaseous and liquid refrigerant at container pressure due to the sudden pressure drop after the high-pressure saturated refrigerant enters a relatively low-pressure container. In practice, it functions similarly to the gas-liquid separator 6. The gaseous refrigerant is output from the gaseous outlet of the flash tank 41, and the liquid refrigerant is output from the cold outlet. Through the flash evaporation effect of the flash tank 41, it ensures that the refrigerant entering the outdoor heat exchanger 2 is primarily liquid, while the refrigerant entering the compressor 1's injection port or inlet is primarily gaseous, thus improving the heat exchange capacity of the refrigerant at the outdoor heat exchanger 2 and increasing the effective intake volume of the compressor 1.

[0060] In some embodiments, refer to Figure 3 As shown, the gas-liquid separation heat exchange component 4 is a plate heat exchanger 42. The plate heat exchanger 42 includes a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is the first input end, the second inlet is connected to the first outlet through an expansion valve 45, the first outlet is the first output end, and the second outlet is the second output end.

[0061] The plate heat exchanger 42 has four ports: two inlets and two outlets, including a first inlet, a second inlet, a first outlet, and a second outlet. The plate heat exchanger 42 is typically composed of multiple stacked heat exchange plates, forming thin rectangular channels between them for heat exchange. The plate heat exchanger 42 is an ideal device for liquid-liquid and liquid-vapor heat exchange. It features high heat exchange efficiency, low heat loss, compact and lightweight structure, small footprint, wide application, and long service life. The first inlet of the plate heat exchanger 42 connects to the indoor heat exchanger 3 to receive the refrigerant flowing out of the indoor heat exchanger 3. These two-phase refrigerants exchange heat in the plate heat exchanger 42, outputting liquid refrigerant at the first outlet and gaseous refrigerant at the second outlet. Since the plate heat exchanger 42 has a two-inlet, two-outlet structure, it is equivalent to having two sets of pipes for heat exchange internally. Therefore, the second inlet also needs to be supplied with liquid refrigerant. In this embodiment, the second inlet is connected to the first outlet through an expansion valve 45, and part of the liquid refrigerant from the first outlet flows back to the second inlet and enters the plate heat exchanger 42. Thus, the plate heat exchanger 42 functions similarly to the gas-liquid separator 6, ensuring that the refrigerant entering the outdoor heat exchanger 2 is mostly liquid, while the refrigerant entering the compressor 1's air inlet or air outlet is mostly gaseous. This improves the heat exchange capacity of the refrigerant at the outdoor heat exchanger 2 and increases the effective air intake of the compressor 1.

[0062] In some embodiments, a gas-liquid separator 6 is also included, which includes a second inlet and a third outlet. The second inlet is connected to the outdoor heat exchanger 2 via a third branch. The first branch 43 and the third branch converge to the second inlet, and the third outlet is connected to the air inlet of the compressor 1.

[0063] In this embodiment, the gas-liquid separator 6 is mainly used to combine and output two parts of gaseous refrigerant to the inlet of the compressor 1. Two pipes are connected before the second inlet: one is the first branch 43, and the other is connected to the outdoor heat exchanger 2. That is, the second inlet combines the gaseous refrigerant from the first branch 43 with the gaseous refrigerant flowing out of the outdoor heat exchanger 2. It can be understood that the second inlet can also be split into two inlets: one connected to the first branch 43, and the other connected to the outdoor heat exchanger 2, i.e., the third branch. The effect is the same: combining and outputting the gaseous refrigerant from the first branch 43 and the third branch to the inlet of the compressor 1. Therefore, the intake volume of the compressor 1 is affected by the flow rates of the gaseous refrigerant in the first branch 43 and the third branch.

[0064] In some embodiments, a four-way valve 7 is also included, which includes a first port, a second port, a third port and a fourth port. The first port is connected to the exhaust port of the compressor 1, the second port is connected to the indoor heat exchanger 3, the third port is connected to the third branch, and the fourth port is connected to the outdoor heat exchanger 2.

[0065] The four-way valve 7 is used to switch the refrigerant flow path. In the heating mode of the heat pump system, the first port is connected to the second port and the third port is connected to the fourth port. In the cooling mode, the first port is connected to the fourth port and the second port is connected to the third port.

[0066] The heat pump system also includes an outdoor throttling device 21 and an indoor throttling device 31. The outdoor throttling device 21 is located between the outdoor heat exchanger 2 and the first output end, and the indoor throttling device 31 is located between the indoor heat exchanger 3 and the first input end.

[0067] In some embodiments, the flow regulating component 5 is disposed in the first branch 43, and the valve of the flow regulating component 5 is used to open in a controlled manner to increase the flow rate of the gaseous refrigerant in the first branch 43. During the controlled adjustment of the flow regulating component 5, due to the increase in the intake air volume, it is necessary to adjust the superheat of the refrigerant in the heat pump system. Therefore, while opening the valve of the flow regulating component 5, it is necessary to gradually close the outdoor throttling device 21 and / or the indoor throttling device 31.

[0068] In some embodiments, the system further includes a first temperature sensor and a second temperature sensor. The first temperature sensor detects the temperature of the outdoor heat exchanger 2, and the second temperature sensor detects the temperature of the indoor heat exchanger 3. The first temperature sensor detects the temperature t1 of the outdoor heat exchanger 2, and the second temperature sensor detects the temperature t2 of the indoor heat exchanger 3. In one possible control method, the opening degree of the flow regulating component 5 is determined based on the relationship between temperature t1 and temperature t2. The first temperature t1 can be the intermediate temperature of the outdoor heat exchanger 2, representing the temperature of the refrigerant inside the outdoor heat exchanger 2, and the first temperature sensor is located near the center of the outdoor heat exchanger 2. The second temperature t2 can be the intermediate temperature of the indoor heat exchanger 3, representing the temperature of the refrigerant inside the indoor heat exchanger 3, and the second temperature sensor is located near the center of the indoor heat exchanger 3. Of course, the first temperature t1 can also be measured with the first temperature sensor located at a non-central position on the outdoor heat exchanger 2, and the second temperature t2 can also be measured with the second temperature sensor located at a non-central position on the indoor heat exchanger 3; this is not limited here. In addition to the first and second temperature sensors mentioned above, a third temperature sensor can also be set to detect the discharge temperature t3 of the compressor 1; in one possible control method, the opening control process of the flow regulating component 5 is determined based on the discharge temperature t3 of the compressor 1 and its corresponding saturation pressure.

[0069] For the valve opening control of the flow regulation component, please refer to the control method of the jet enthalpy-increasing heat pump system in the following embodiment.

[0070] like Figure 4 As shown, Figure 4This is a schematic diagram of a system architecture platform for implementing a control method for a jet enthalpy-enhancing heat pump system, provided in one embodiment of this application.

[0071] The system architecture platform 1000 of this application embodiment includes one or more processors 1100 and a memory 1200. Figure 4 The example uses a processor 1100 and a memory 1200.

[0072] The processor 1100 and the memory 1200 can be connected via a bus or other means. Figure 1 Taking the example of a connection between China and Israel via a bus.

[0073] Memory 1200, as a non-transitory computer-readable storage medium, can be used to store non-transitory software programs and non-transitory computer-executable programs. Furthermore, memory 1200 may include high-speed random access memory and may also include non-transitory memory, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. In some embodiments, memory 1200 may optionally include memory 1200 remotely located relative to processor 1100, and these remote memories can be connected to the system architecture platform 1000 via a network. Examples of such networks include, but are not limited to, the Internet, corporate intranets, local area networks, mobile communication networks, and combinations thereof.

[0074] Those skilled in the art will understand that Figure 1 The device structure shown does not constitute a limitation on the system architecture platform 1000 and may include more or fewer components than shown, or combine certain components, or have different component arrangements.

[0075] exist Figure 4 In the system architecture platform 1000 shown, the processor 1100 can be used to call the control program of the air conditioner stored in the memory 1200, thereby realizing the control method of the jet enthalpy heat pump system.

[0076] Based on the hardware structure of the aforementioned system architecture platform 1000, various embodiments of the control method for the jet enthalpy-enhancing heat pump system of this application are proposed.

[0077] Reference Figure 5 As shown, a second aspect of this application provides a control method for a jet enthalpy-enhancing heat pump system, such as... Figure 1As shown, the jet enthalpy-enhancing heat pump system includes a compressor 1, an outdoor heat exchanger 2, an indoor heat exchanger 3, a gas-liquid separation heat exchange component 4, and a flow regulating component 5. The gas-liquid separation heat exchange component 4 includes a first input end, a first output end, and a second output end. The exhaust port of the compressor 1 is connected to one end of the indoor heat exchanger 3, and the other end of the indoor heat exchanger 3 is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger 2, and the other end of the outdoor heat exchanger 2 is connected to the air inlet of the compressor 1. The second output end is connected to the air inlet of the compressor 1 through a first branch 43, and the second output end is also connected to the air supply port of the compressor 1 through a second branch 44. The flow regulating component 5 is located on the first branch 43 or the second branch 44.

[0078] The control method in this embodiment includes, but is not limited to, the following steps:

[0079] Step S100: When the outdoor ambient temperature is greater than the first temperature threshold, control the flow regulating component 5 so that all the refrigerant flowing out of the second output end enters the gas supply port of the compressor 1 through the second branch.

[0080] In step S200, when the outdoor ambient temperature is less than the first temperature threshold, the flow regulating component 5 is controlled so that at least a portion of the refrigerant flowing out of the second output terminal enters the air inlet of the compressor 1 through the first branch.

[0081] The control method of this application embodiment employs different controls on the flow regulating component 5 based on the outdoor ambient temperature. Specifically, the heating difficulty of the jet enthalpy-increasing heat pump system is determined according to the outdoor ambient temperature. When the outdoor ambient temperature is greater than the first temperature threshold, it indicates that the heating difficulty of the jet enthalpy-increasing heat pump system is low, the heat load demand is small, and it has good heating performance. At this time, the flow regulating component 5 can be controlled so that all the refrigerant flowing out of the second output terminal enters the air inlet of the compressor 1 through the second branch, and only the refrigerant flowing out of the outdoor heat exchanger 2 enters the air inlet of the compressor 1. At this time, the jet enthalpy-increasing heat pump system of this application embodiment is equivalent to a heat pump system with a first-level economizer, which can meet the heating demand under the current outdoor environment. When the outdoor ambient temperature is lower than the first temperature threshold, it indicates that the heating difficulty of the jet enthalpy-increasing heat pump system increases, the heat load demand increases, and the heating performance is affected. The pressure difference between the medium-pressure and high-pressure refrigerants in the refrigerant pipeline decreases, resulting in a reduction in the system's jet volume. Consequently, the heat exchange at the economizer (i.e., the gas-liquid separation heat exchange component 4) decreases. Therefore, it is necessary to adjust the flow regulating component 5 so that at least a portion of the refrigerant flowing out of the second output end enters the air inlet of the compressor 1 through the first branch, increasing the air intake of the compressor 1 and improving the heating performance of the heat pump system. Specifically, the lower the outdoor ambient temperature, the greater the refrigerant flow in the first branch when adjusting the flow regulating component 5, thereby enhancing the enthalpy injection capacity to the low-pressure side.

[0082] It is worth noting that the flow regulation component 5 in this application embodiment can be set in the first branch or the second branch, for example, referring to Figure 1 The jet enthalpy-increasing heat pump system shown has a flow regulation component 5 located in the first branch. When the outdoor ambient temperature is higher than a first temperature threshold, the valve of the flow regulation component 5 can be closed, preventing the gaseous refrigerant flowing from the second output end of the gas-liquid separation heat exchange component 4 from entering the compressor 1's inlet through the first branch. Instead, the refrigerant flows entirely through the second branch to the compressor 1's makeup inlet. When the outdoor ambient temperature is lower than the first temperature threshold, the valve of the flow regulation component 5 is opened, allowing some or all of the gaseous refrigerant flowing from the second output end to enter the compressor 1's inlet, thereby increasing the compressor 1's intake volume and improving the system's heating performance. If the flow regulation component 5 is located in the second branch, when the outdoor ambient temperature is higher than the first temperature threshold, the valve of the flow regulation component 5 can be fully opened, allowing all the gaseous refrigerant flowing from the second output end to pass through the second branch. When the outdoor ambient temperature is lower than the first temperature threshold, the valve of the flow regulation component 5 can be reduced, allowing a portion of the gaseous refrigerant flowing from the second output end to pass through the first branch.

[0083] In some embodiments, refer to Figure 6 As shown, in step S200 above, when the outdoor ambient temperature is lower than the first temperature threshold, the flow regulating component 5 is controlled to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the air inlet of the compressor 1 through the first branch. Specifically, this includes the following steps:

[0084] Step S210: When the outdoor ambient temperature is less than the first temperature threshold and greater than the second temperature threshold, the target valve opening is determined according to the first temperature of the outdoor heat exchanger 2 and the second temperature of the indoor heat exchanger 3, and the flow regulating component 5 is controlled according to the target valve opening. The target valve opening is less than the maximum opening of the valve of the flow regulating component 5.

[0085] Step S220: When the outdoor ambient temperature is less than the second temperature threshold, control the valve of the flow regulating component 5 to the maximum opening degree.

[0086] The above steps apply to the case where the flow regulating component 5 is installed in the first branch. When the outdoor ambient temperature is less than the first temperature threshold, it indicates that the outdoor ambient temperature is low, and it can be further divided into two levels: low temperature and ultra-low temperature. The boundary between low temperature and ultra-low temperature is set as the second temperature threshold. If the outdoor ambient temperature is greater than the second temperature threshold but less than the first temperature threshold, it indicates that the outdoor ambient temperature is in the low temperature range, and the valve opening of the flow regulating component 5 is determined based on the temperatures of the outdoor heat exchanger 2 and the indoor heat exchanger 3. If the outdoor ambient temperature is less than the second temperature threshold, it indicates that the outdoor ambient temperature is in the ultra-low temperature range, and the valve opening of the flow regulating component 5 is directly fully opened. In determining the valve opening of the flow regulating component 5 based on the temperatures of the outdoor heat exchanger 2 and the indoor heat exchanger 3, different calculation methods can be used to calculate the valve opening. For example, the opening value can be determined based on the ratio between the temperatures of the outdoor heat exchanger 2 and the indoor heat exchanger 3, or the opening value can be calculated after converting the temperatures of the outdoor heat exchanger 2 and the indoor heat exchanger 3, etc., and no restrictions are imposed here.

[0087] It is understandable that the first temperature t1 can be the intermediate temperature of the outdoor heat exchanger 2, representing the temperature of the refrigerant inside the outdoor heat exchanger 2, with the first temperature sensor located near the center of the outdoor heat exchanger 2; the second temperature t2 can be the intermediate temperature of the indoor heat exchanger 3, representing the temperature of the refrigerant inside the indoor heat exchanger 3, with the second temperature sensor located near the center of the indoor heat exchanger 3. Of course, the first temperature t1 can also be measured with the first temperature sensor located at a non-central position on the outdoor heat exchanger 2, and the second temperature t2 can also be measured with the second temperature sensor located at a non-central position on the indoor heat exchanger 3; this is not limited here. For the aforementioned non-central temperature cases, different calculation methods can be set according to the actual placement of the temperature sensors to calculate the target valve opening.

[0088] In some embodiments, refer to Figure 7 As shown, in step S210 above, determining the valve opening of the flow regulating component 5 based on the first temperature of the outdoor heat exchanger 2 and the second temperature of the indoor heat exchanger 3 specifically includes the following steps:

[0089] Step S211: Determine the first saturated steam pressure of the outdoor heat exchanger 2 based on the first temperature, and determine the second saturated steam pressure of the indoor heat exchanger 3 based on the second temperature.

[0090] Step S212: Determine the valve opening of the flow regulating component 5 based on the difference between the first saturated steam pressure and the second saturated steam pressure.

[0091] In this embodiment, the valve opening of the flow regulating component 5 is calculated as follows: The first saturation pressure p1 is determined based on the first temperature t1 of the outdoor heat exchanger 2, and the second saturation pressure p2 is determined based on the second temperature t2 of the indoor heat exchanger 3. Then, the valve opening of the flow regulating component 5 is determined based on the difference between the first saturation pressure p1 and the second saturation pressure p2. The specific calculation formula for the valve opening is as follows:

[0092] A = f(p1 - p2)

[0093] Where A represents the valve opening degree (usually expressed as a percentage), and f is a coefficient.

[0094] The aforementioned first temperature t1 and second temperature t2 can be obtained by first and second temperature sensors installed at the outdoor heat exchanger 2 and indoor heat exchanger 3, respectively. The correspondence between saturation pressure and heat exchanger temperature can be preset in the heat pump system for direct use, or the heat exchanger temperature can be converted into saturation pressure according to a certain calculation method. Based on the temperatures measured at different acquisition points (for example, the first temperature t1 is not the intermediate temperature of the outdoor heat exchanger 2, and the second temperature t2 is not the intermediate temperature of the indoor heat exchanger 3), the correspondence between temperature and saturation pressure, as well as the value of the coefficient f, can be adjusted to calculate the accurate valve opening value.

[0095] In some embodiments, refer to Figure 8 As shown, when the valve of the flow regulating component 5 is opened, the valve of the throttling device in the main circuit of the heat pump system can be closed synchronously. Specifically, the control method of this application embodiment, when controlling the flow regulating component 5 to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the air inlet of the compressor 1 through the first branch, further includes:

[0096] Step S300: Reduce the valve opening of the outdoor throttling device 21 and / or the indoor throttling device 31.

[0097] Reference Figure 9 and Figure 10 As shown, a third aspect of this application provides a control method for a jet enthalpy-enhancing heat pump system, such as... Figure 1As shown, the jet enthalpy-enhancing heat pump system includes a compressor 1, an outdoor heat exchanger 2, an indoor heat exchanger 3, a gas-liquid separation heat exchange component 4, and a flow regulating component 5. The gas-liquid separation heat exchange component 4 includes a first input end, a first output end, and a second output end. The exhaust port of the compressor 1 is connected to one end of the indoor heat exchanger 3, and the other end of the indoor heat exchanger 3 is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger 2, and the other end of the outdoor heat exchanger 2 is connected to the air inlet of the compressor 1. The second output end is connected to the air inlet of the compressor 1 through a first branch 43, and the second output end is also connected to the air supply port of the compressor 1 through a second branch 44. The flow regulating component 5 is located on the first branch 43 or the second branch 44.

[0098] The control method in this embodiment includes, but is not limited to, the following steps:

[0099] Step S400: When the temperature of the indoor heat exchanger 3 continues to rise, the valve opening of the flow regulating component 5 is changed to continuously increase the flow rate of the refrigerant flowing out of the second output end and entering the air inlet of the compressor 1 through the first branch.

[0100] In step S500, when the exhaust superheat of compressor 1 is less than the third temperature threshold, or when the exhaust temperature of compressor 1 continues to decrease, the valve opening of flow regulating component 5 remains unchanged.

[0101] This embodiment describes another method for controlling the valve opening of the flow regulating component 5. Taking the flow regulating component 5 as an example located in the first branch, assuming the valve of the flow regulating component 5 is initially closed, the second temperature t2 of the indoor heat exchanger 3 is collected, and the decision on whether to open the valve of the flow regulating component 5 is based on the change in the second temperature t2. When the second temperature t2 of the indoor heat exchanger 3 continues to rise (a preset time period can be set, within which it is determined whether the change in the second temperature t2 conforms to the pattern of continuous rise), the valve of the flow regulating component 5 is opened, and the valve opening of the flow regulating component 5 is continuously increased.

[0102] The exhaust temperature of compressor 1 is then continuously monitored, and subsequent valve control is determined based on changes in exhaust temperature or the magnitude of exhaust superheat. Specifically, when the exhaust temperature of compressor 1 continues to decrease, the valve opening of flow regulating component 5 is stopped from being adjusted, and the current valve opening remains unchanged; when the exhaust superheat of compressor 1 is less than the third temperature threshold, the valve opening of flow regulating component 5 is stopped from being adjusted, and the current valve opening remains unchanged. Here, exhaust superheat = exhaust temperature - exhaust pressure corresponding to saturation temperature.

[0103] Through the various steps of the above control method, the cooperation of the valve of the flow regulating component 5 and the gas-liquid separation heat exchange component 4 realizes the first-stage gas replenishment and the second-stage gas replenishment. The flow ratio of the refrigerant in the first branch and the second branch can be adjusted by adjusting the valve opening of the flow regulating component 5, thereby achieving the best heating capacity and efficiency. In other words, in a low-temperature environment, the heat pump system replenishes gas from the low-pressure side, and the heating capacity of the heat pump system at low temperatures is increased by increasing the amount of gas replenishment.

[0104] The following is a detailed description of the jet enthalpy-enhancing heat pump system and its control method based on a specific example.

[0105] The jet enthalpy-increasing heat pump system includes a compressor 1, a four-way valve 7, an outdoor heat exchanger 2, an indoor heat exchanger 3, an outdoor throttling device 21 for the outdoor heat exchanger 2, an indoor throttling device 31 for the indoor heat exchanger 3, and a gas-liquid separation heat exchange assembly 4. The auxiliary outlet of the gas-liquid separation heat exchange assembly 4 is divided into two parts: one is connected to the gas supply port of the compressor 1, and the other is connected to the low-pressure side component and is equipped with a flow regulating assembly 5. The temperature detection results of the outdoor sensor and the indoor sensor are the first temperature t1 and the second temperature t2, respectively.

[0106] The first control method: In heating mode, the refrigerant from compressor 1 enters the indoor heat exchanger 3 through the four-way valve 7, and then enters the outdoor heat exchanger 2 from the main circuit through the gas-liquid separation heat exchange component 4. The refrigerant from the auxiliary circuit is distributed according to the detected outdoor ambient temperature T.

[0107] When T > the first temperature threshold, the flow regulation component 5 is completely shut off, and all the refrigerant in the auxiliary circuit enters the gas supply port of the compressor 1.

[0108] When the first temperature threshold < T ≤ the first temperature threshold, the opening degree of the flow regulating component 5 is related to the difference f(p2-p1) between the saturation pressures p1 / p2 corresponding to t1 and t2.

[0109] When T ≤ the second temperature threshold, the flow regulation component 5 is fully opened, and all refrigerant in the auxiliary circuit is introduced into the low-pressure side.

[0110] The first temperature threshold range is -10 degrees Celsius to 10 degrees Celsius; in this example, 0 degrees Celsius is selected.

[0111] The second temperature threshold range is -35 degrees Celsius to -5 degrees Celsius; in this example, -15 degrees Celsius is selected.

[0112] While turning on the flow regulation component 5, the throttling components on the main road need to be gradually turned off.

[0113] The second control method: In heating mode, the refrigerant from compressor 1 enters the indoor heat exchanger 3 through the four-way valve 7, and then enters the outdoor heat exchanger 2 from the main circuit through the gas-liquid separation heat exchange component 4. The refrigerant from the auxiliary circuit is distributed according to the detected exhaust temperature and the second temperature t2.

[0114] When the detected exhaust superheat is less than the third temperature threshold, stop opening the flow regulation component 5 (the range of the third temperature threshold is 5 degrees Celsius to 20 degrees Celsius, and 12 degrees Celsius is selected in this example);

[0115] When the exhaust temperature continues to drop, the valve opening of the flow regulating component 5 should be stopped.

[0116] As t2 continues to rise, the valve opening of the flow regulation component 5 is continuously increased.

[0117] Furthermore, this application embodiment also provides a controller, including a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, it implements the aforementioned control method. The aforementioned controller is used to execute the aforementioned control method. Through the cooperation of the valve of the flow regulating component 5 and the gas-liquid separation heat exchange component 4, it realizes primary and secondary gas replenishment. It can also adjust the flow ratio of refrigerant in the first and second branches by adjusting the opening of the valve of the flow regulating component 5, thereby achieving optimal heating capacity and efficiency. That is, in medium and high temperature environments, adjusting the valve of the flow regulating component 5 adjusts the jet enthalpy-increasing heat pump system to a system architecture similar to a single-stage economizer. In low temperature environments, adjusting the valve of the flow regulating component 5 allows the heat pump system to replenish gas from the low-pressure side, thereby increasing the heating capacity of the heat pump system at low temperatures. Therefore, by executing the above method, the controller can determine the corresponding heating performance according to different outdoor ambient temperatures, saving certain hardware costs compared to a two-stage economizer heat pump system.

[0118] This application also provides an air conditioner, including the aforementioned jet enthalpy-increasing heat pump system, or including the aforementioned controller.

[0119] By incorporating the aforementioned vapor injection enthalpy-enhancing heat pump system, or including the aforementioned controller, the air conditioner executes the aforementioned control method. Through the cooperation of the valve of the flow regulating component 5 and the gas-liquid separation heat exchange component 4, primary and secondary gas replenishment are achieved. The flow ratio of refrigerant in the first and second branches can be adjusted by regulating the valve opening of the flow regulating component 5, thereby achieving optimal heating capacity and efficiency. In other words, in medium- and high-temperature environments, adjusting the valve of the flow regulating component 5 adjusts the vapor injection enthalpy-enhancing heat pump system to a system architecture similar to a single-stage economizer. In low-temperature environments, adjusting the valve of the flow regulating component 5 allows the heat pump system to replenish gas from the low-pressure side, thereby increasing the heating capacity of the heat pump system at low temperatures. Therefore, by executing the above method, the controller can determine the corresponding heating performance according to different outdoor ambient temperatures, saving certain hardware costs compared to a two-stage economizer heat pump system.

[0120] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate; that is, they may be located in one place or distributed across multiple network nodes. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs.

[0121] Those skilled in the art will understand that all or some of the steps and systems in the methods disclosed above can be implemented as software, firmware, hardware, and suitable combinations thereof. Some or all of the physical components can be implemented as software executed by a processor, such as a central processing unit, digital signal processor, or microprocessor, or as hardware, or as an integrated circuit, such as an application-specific integrated circuit. Such software can be distributed on a computer-readable medium, which can include computer-readable storage media (or non-transitory media) and communication media (or transient media). As is known to those skilled in the art, the term computer-readable storage media includes volatile and non-volatile, removable and non-removable media implemented in any method or technology for storing information (such as computer-readable instructions, data structures, program modules, or other data). Computer-readable storage media include, but are not limited to, RAM, ROM, EEPROM, flash memory or other memory technologies, CD-ROM, digital versatile disc (DVD) or other optical disc storage, magnetic cartridges, magnetic tape, disk storage or other magnetic storage devices, or any other medium that can be used to store desired information and is accessible to a computer. Furthermore, as is known to those skilled in the art, communication media typically contain computer-readable instructions, data structures, program modules, or other data in modulated data signals such as carrier waves or other transmission mechanisms, and may include any information delivery medium.

[0122] The above is a detailed description of the preferred embodiments of this application. However, this application is not limited to the above embodiments. Those skilled in the art can make various equivalent modifications or substitutions without departing from the spirit of this application. All such equivalent modifications or substitutions are included within the scope defined by the claims of this application.

Claims

1. A jet-induced enthalpy-enhancing heat pump system, characterized in that, The device includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulating component. The gas-liquid separation heat exchange component includes a first input end, a first output end, and a second output end. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output end is connected to the air inlet of the compressor via a first branch, and the second output end is also connected to the air supply port of the compressor via a second branch. The flow regulating component is located on either the first branch or the second branch. The jet enthalpy-enhancing heat pump system also includes a controller, which is configured to: When the outdoor ambient temperature is greater than the first temperature threshold, the flow regulation component is controlled so that all the refrigerant flowing out of the second output terminal enters the compressor's gas inlet through the second branch; When the outdoor ambient temperature is lower than the first temperature threshold, the flow regulation component is controlled so that at least a portion of the refrigerant flowing out of the second output terminal enters the air inlet of the compressor through the first branch.

2. The system according to claim 1, characterized in that, The gas-liquid separation heat exchange component is a flash tank, the input end of the flash tank is the first input end, the liquid output end of the flash tank is the first output end, and the gas output end of the flash tank is the second output end.

3. The system according to claim 1, characterized in that, The gas-liquid separation heat exchange component is a plate heat exchanger. The plate heat exchanger includes a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is the first input terminal, the second inlet is connected to the first outlet through an expansion valve, the first outlet is the first output terminal, and the second outlet is the second output terminal.

4. The system according to claim 1, characterized in that, It also includes a gas-liquid separator, which has a second inlet and a third outlet. The second inlet is connected to the other end of the outdoor heat exchanger via a third branch. The first branch and the third branch converge at the second inlet. The third outlet is connected to the air inlet of the compressor.

5. The system according to claim 4, characterized in that, It also includes a four-way valve, which has a first port, a second port, a third port and a fourth port. The first port is connected to the exhaust port of the compressor, the second port is connected to the indoor heat exchanger, the third port is connected to the third branch, and the fourth port is connected to the outdoor heat exchanger.

6. The system according to claim 1, characterized in that, It also includes an outdoor throttling device and an indoor throttling device, wherein the outdoor throttling device is disposed between the outdoor heat exchanger and the first output terminal, and the indoor throttling device is disposed between the indoor heat exchanger and the first input terminal.

7. The system according to claim 1, characterized in that, The flow regulating component is disposed in the first branch, and the valve of the flow regulating component is used to be opened in a controlled manner to adjust the flow rate of gaseous refrigerant in the first branch.

8. The system according to claim 1, characterized in that, It also includes a first temperature sensor and a second temperature sensor, the first temperature sensor being used to detect the temperature of the outdoor heat exchanger and the second temperature sensor being used to detect the temperature of the indoor heat exchanger.

9. A control method for a jet-induced enthalpy-enhancing heat pump system, characterized in that, The jet enthalpy-enhancing heat pump system includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulation component. The gas-liquid separation heat exchange component includes a first input end, a first output end, and a second output end. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output end is connected to the air inlet of the compressor through a first branch, and the second output end is also connected to the air supply port of the compressor through a second branch. The flow regulation component is located on either the first branch or the second branch. The control method includes: When the outdoor ambient temperature is greater than the first temperature threshold, the flow regulation component is controlled so that all the refrigerant flowing out of the second output terminal enters the compressor's gas inlet through the second branch; When the outdoor ambient temperature is lower than the first temperature threshold, the flow regulation component is controlled so that at least a portion of the refrigerant flowing out of the second output terminal enters the air inlet of the compressor through the first branch.

10. The method according to claim 9, characterized in that, When the outdoor ambient temperature is lower than the first temperature threshold, controlling the flow regulation component to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the compressor's intake port via the first branch includes: When the outdoor ambient temperature is less than the first temperature threshold and greater than the second temperature threshold, the target valve opening is determined based on the first temperature of the outdoor heat exchanger and the second temperature of the indoor heat exchanger, and the flow regulating component is controlled according to the target valve opening, wherein the target valve opening is less than the maximum opening of the valve of the flow regulating component. When the outdoor ambient temperature is lower than the second temperature threshold, the valve of the flow regulating component is controlled to be at its maximum opening.

11. The method according to claim 10, characterized in that, Determining the valve opening of the flow regulating component based on the first temperature of the outdoor heat exchanger and the second temperature of the indoor heat exchanger includes: The first saturated steam pressure of the outdoor heat exchanger is determined based on the first temperature, and the second saturated steam pressure of the indoor heat exchanger is determined based on the second temperature. The valve opening of the flow regulating component is determined based on the difference between the first saturated steam pressure and the second saturated steam pressure.

12. The method according to claim 9, characterized in that, The heat pump system further includes an outdoor throttling device and an indoor throttling device. The outdoor throttling device is disposed between the outdoor heat exchanger and the first output terminal, and the indoor throttling device is disposed between the indoor heat exchanger and the first input terminal. When controlling the flow regulating component to cause at least a portion of the refrigerant flowing out of the second output terminal to enter the compressor's inlet via the first branch, the method further includes: Reduce the valve opening of the outdoor throttling device and / or the indoor throttling device.

13. A control method for a jet-induced enthalpy-enhancing heat pump system, characterized in that, The jet enthalpy-enhancing heat pump system includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a gas-liquid separation heat exchange component, and a flow regulation component. The gas-liquid separation heat exchange component includes a first input end, a first output end, and a second output end. The exhaust port of the compressor is connected to one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected to the first input end. The first output end is connected to one end of the outdoor heat exchanger, and the other end of the outdoor heat exchanger is connected to the air inlet of the compressor. The second output end is connected to the air inlet of the compressor through a first branch, and the second output end is also connected to the air supply port of the compressor through a second branch. The flow regulation component is located on either the first branch or the second branch. The method includes: As the temperature of the indoor heat exchanger continues to rise, the valve opening of the flow regulating component is changed to continuously increase the flow rate of the refrigerant flowing out of the second output end and entering the air inlet of the compressor through the first branch. When the superheat of the compressor's exhaust is less than the third temperature threshold, or when the exhaust temperature of the compressor continues to decrease, the valve opening of the flow regulating component remains unchanged.

14. A controller, characterized in that, include: A memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor, when executing the computer program, performs the method as claimed in any one of claims 9 to 12 or the method as claimed in claim 13.

15. An air conditioner, characterized in that, Includes the jet enthalpy-enhancing heat pump system as described in any one of claims 1 to 8 or includes the controller as described in claim 14.

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