Heat pump system and air conditioner

Abstract

This invention relates to the field of heat pump technology, specifically providing a heat pump system and air conditioner, aiming to solve the problems of low efficiency and poor reliability in non-azeotropic refrigerant systems. To this end, the heat pump system of this invention includes a compressor, a first heat exchanger, a first throttling component, and a second heat exchanger connected in sequence to form a refrigerant main circuit. A gas-liquid separator and an economizer for separating refrigerant components are connected in series in the main circuit. A branch circuit is also provided, connected upstream of the gas-liquid separator and between the compressor's gas inlet. This branch circuit has a second refrigerant flow path with an ejector and an economizer. The second inlet of the ejector is connected to the gas phase outlet of the gas-liquid separator, used to eject the separated gas phase refrigerant for enthalpy-increasing gas injection. Therefore, this invention improves the heat exchange efficiency and heating capacity of the heat pump system and avoids compressor liquid slugging.

Description

Technical Field

[0001] This invention relates to the field of heat pump technology, specifically providing a heat pump system and an air conditioner. Background Technology

[0002] Heat pump systems, especially air source heat pumps, are widely used as highly efficient cooling and heating devices. To meet environmental regulations, refrigerants are being developed towards lower Global Warming Potential (GWP). Among them, non-azeotropic refrigerants, such as R454C, are attracting significant attention due to their lower GWP.

[0003] However, non-azeotropic refrigerants have an inherent characteristic: their temperature changes during phase change, a phenomenon known as "temperature slip." In traditional heat exchangers, temperature slip reduces the effective heat exchange temperature difference between the refrigerant and the heat exchange medium, resulting in irreversible heat loss and thus reducing the overall system's heat exchange efficiency and energy efficiency.

[0004] To improve the heating performance of heat pump systems in low-temperature environments, the industry often employs economizer enthalpy enhancement technology. However, when traditional economizer enthalpy enhancement systems are applied to non-azeotropic refrigerant mixtures, they typically only split the throttled gas-liquid two-phase refrigerant mixture without considering the characteristics of the different components. This not only results in limited enthalpy enhancement but also poses a risk of "liquid slugging" due to liquid refrigerant entrained in the split branch entering the compressor's gas inlet, severely impacting the compressor's operational reliability and lifespan.

[0005] In addition, ejector technology is used to recover pressure energy during the throttling process to improve system performance. However, conventional ejector cycles also do not consider the component separation problem of non-azeotropic mixed refrigerants, and the energy recovery gain is largely offset by the heat transfer loss caused by temperature slip, resulting in a lack of significant improvement in the overall system energy efficiency.

[0006] Therefore, a new technical solution is needed in this field to solve the above problems. Summary of the Invention

[0007] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problems of low heat exchange efficiency, poor enthalpy increase effect and poor operation reliability of existing heat pump systems using non-azeotropic mixed refrigerants.

[0008] In a first aspect, the present invention provides a heat pump system comprising a compressor, a first heat exchanger, a first throttling member, and a second heat exchanger connected in sequence to form a refrigerant main circuit, wherein a gas-liquid separator and an economizer are connected in series on the main circuit between the first heat exchanger and the second heat exchanger. The gas-liquid separator is used to separate the gas and liquid components of a non-azeotropic refrigerant mixture. It has a refrigerant inlet, a gas phase outlet and a liquid phase outlet, and the refrigerant inlet and the liquid phase outlet are both connected to the main circuit. The economizer has a first refrigerant flow path and a second refrigerant flow path, with the first refrigerant flow path connected in series with the main circuit; The main circuit is also provided with a branch circuit, and the second refrigerant flow path is provided on the branch circuit. One end of the branch circuit is connected to the main circuit and the connection position is located upstream of the gas-liquid separator, and the other end is connected to the gas supply port of the compressor. The branch circuit is provided with an ejector and a second throttling component, and the second throttling component is located upstream of the ejector and the second refrigerant flow path. The ejector has a first inlet, a second inlet and an outlet. The first inlet is connected to the branch circuit, the second inlet is optionally connected to the gas phase outlet, and the outlet is connected to the gas supply port.

[0009] In the preferred embodiment of the above heat pump system, the ejector is located upstream of the second refrigerant flow path, the first inlet is connected to the second throttling member, the outlet is connected to the inlet of the second refrigerant flow path, and the outlet of the second refrigerant flow path is connected to the air inlet.

[0010] In the preferred embodiment of the above heat pump system, the second refrigerant flow path is located upstream of the injector, the inlet of the second refrigerant flow path is connected to the second throttling member, the outlet of the second refrigerant flow path is connected to the first inlet, and the outlet is connected to the gas supply port.

[0011] In the preferred embodiment of the above heat pump system, an electromagnetic valve is provided between the gas phase outlet and the second inlet, and the electromagnetic valve is used to control the opening and closing of the gas phase outlet and the second inlet.

[0012] In the preferred embodiment of the above-mentioned heat pump system, the heat pump system further includes a four-way valve, which is connected to the exhaust port and the suction port of the compressor respectively. The first heat exchanger and the second heat exchanger are selectively connected to the exhaust port and the suction port of the compressor through the four-way valve.

[0013] In the preferred embodiment of the above heat pump system, the first throttling component includes a first throttling valve and a second throttling valve. The first throttling valve is disposed on the main circuit between the first heat exchanger and the gas-liquid separator, and the second throttling valve is disposed on the main circuit between the first refrigerant flow path of the economizer and the second heat exchanger. The second throttling component includes a third throttling valve, which is disposed on the branch line and located upstream of the injector and the second refrigerant flow path.

[0014] In the preferred embodiment of the above-mentioned heat pump system, the heat pump system further includes a rectifier check valve, which has a first port, a second port, a third port, and a fourth port. The first port is connected to the first throttle valve, the second port is connected to the refrigerant inlet, the third port is connected to the outlet of the first refrigerant flow path, and the fourth port is connected to the second throttle valve; A one-way valve is provided between the first port and the second port, between the second port and the third port, between the third port and the fourth port, and between the fourth port and the first port; The rectifier check valve is configured to maintain the refrigerant flowing in a predetermined direction between the gas-liquid separator and the economizer in both cooling and heating modes.

[0015] In the preferred technical solution of the above heat pump system, the non-azeotropic mixed refrigerant is R454C, which is composed of R32 and R1234yf, and the boiling point of R32 is lower than that of R1234yf. The gas-liquid separator can utilize the difference in boiling points to separate the non-azeotropic mixed refrigerant into a gas phase refrigerant rich in R32 and a liquid phase refrigerant rich in R1234yf. The gas phase refrigerant is discharged from the gas phase outlet, and the liquid phase refrigerant is returned to the main circuit from the liquid phase outlet.

[0016] In the preferred embodiment of the above-mentioned heat pump system, a one-way valve is provided between the outlet of the injector and the gas inlet of the compressor. The one-way valve is configured to allow refrigerant to flow from the injector to the gas inlet and to prevent refrigerant from flowing back from the gas inlet to the injector.

[0017] In a second aspect, the present invention provides an air conditioner comprising the heat pump system described in any of the preceding claims.

[0018] Those skilled in the art will understand that the technical solution of the present invention provides a heat pump system, including a compressor, a first heat exchanger, a first throttling component, and a second heat exchanger connected in sequence to form a refrigerant main circuit. A gas-liquid separator and an economizer are connected in series on the main circuit between the first and second heat exchangers. The gas-liquid separator is used to separate the gas and liquid components of a non-azeotropic refrigerant mixture, and it has a refrigerant inlet, a gas phase outlet, and a liquid phase outlet, both of which are connected to the main circuit. The economizer has a first refrigerant flow path and a second refrigerant flow path. The refrigerant flow path is connected in series with the main circuit; a branch path is also provided on the main circuit, and a second refrigerant flow path is provided on the branch path. One end of the branch path is connected to the main circuit and the connection point is located upstream of the gas-liquid separator, and the other end is connected to the compressor's gas inlet. An ejector and a second throttling component are provided on the branch path, and the second throttling component is located upstream of the ejector and the second refrigerant flow path. The ejector has a first inlet, a second inlet, and an outlet. The first inlet is connected to the branch path, the second inlet is optionally connected to the gas phase outlet, and the outlet is connected to the gas inlet. With the above technical solution, the present invention can effectively solve the problems of low heat exchange efficiency, poor enthalpy increase effect, and poor operational reliability of non-azeotropic mixed refrigerant heat pump systems. Specifically, by installing a gas-liquid separator in the main circuit, the non-azeotropic refrigerant mixture can be effectively separated into gas and liquid components. This separation process allows for differentiated utilization of different components, effectively mitigating the heat exchange degradation caused by temperature slippage throughout the cycle, thereby improving the heat exchange efficiency of the first and second heat exchangers. Furthermore, by setting up an enthalpy-enhancing gas supply structure consisting of a branch circuit, an economizer, and an ejector, and introducing the high-enthalpy gaseous refrigerant separated by the gas-liquid separator into the second inlet of the ejector, high-quality gas supply is achieved. This not only significantly increases the compressor's gas supply enthalpy, enhancing the system's heating capacity under low-temperature conditions, but also effectively avoids the liquid slugging risk caused by liquid refrigerant entering the compressor in traditional solutions, thus improving the system's operational reliability, because the gaseous medium is gaseous. Attached Figure Description

[0019] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which: Figure 1 This is a schematic diagram of the heat pump system of the present invention. Figure 1 ; Figure 2 yes Figure 1 The diagram shows the refrigerant flow direction of the heat pump system in cooling mode. Figure 3 yes Figure 1 The diagram shows the refrigerant flow direction of the heat pump system in heating mode. Figure 4 This is a schematic diagram of the heat pump system of the present invention. Figure 2 ; Figure 5 yes Figure 4 The diagram shows the refrigerant flow direction of the heat pump system in cooling mode. Figure 6 yes Figure 4 The diagram shows the refrigerant flow direction of the heat pump system in heating mode.

[0020] List of reference numerals in the attached diagram: 1. Compressor; 2. First heat exchanger; 3. First throttling component; 31. First throttling valve; 32. Second throttling valve; 4. Second heat exchanger; 5. Gas-liquid separator; 6. Economizer; 7. Ejector; 8. Second throttling component; 9. Solenoid valve; 10. Four-way valve; 11. Rectifying check valve. Detailed Implementation

[0021] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the invention and are not intended to limit the scope of protection of the invention. For example, although the following embodiments are described in conjunction with a heat pump system, the heat pump system provided by the present invention is equally applicable to other products that need to address the problems of low heat exchange efficiency, poor enthalpy increase, and poor operational reliability inherent in existing heat pump systems using non-azeotropic refrigerants.

[0022] It should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "set" and "connection" should be interpreted broadly, for example, they can refer to a fixed connection, a detachable connection, or an integral connection. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0023] Based on the problems of low heat exchange efficiency, poor enthalpy increase, and poor operational reliability in existing heat pump systems using non-azeotropic mixed refrigerants, as pointed out in the background art, this invention provides a heat pump system that aims to effectively solve the problems of low heat exchange efficiency, poor enthalpy increase, and poor operational reliability in heat pump systems using non-azeotropic mixed refrigerants by directional separation of refrigerant components, phase-separated heat exchange, and efficient energy recovery and utilization.

[0024] like Figure 1 and Figure 2As shown in the embodiment of this application, a heat pump system is provided, the core of which lies in constructing a refrigerant main loop. This main loop is composed of a compressor 1, a first heat exchanger 2, a first throttling component 3, and a second heat exchanger 4 connected sequentially. This basic loop forms the foundation for heat transfer in the heat pump system. The compressor 1, as the power core of the system, compresses the refrigerant, increasing its temperature and pressure; the first heat exchanger 2 and the second heat exchanger 4 respectively act as condensers or evaporators under different operating conditions, realizing heat exchange with the outside environment; the first throttling component 3 is used to reduce the pressure of the high-pressure refrigerant, preparing for subsequent evaporation and heat absorption.

[0025] To address the problems caused by non-azeotropic refrigerant mixtures, this technical solution connects a gas-liquid separator 5 and an economizer 6 in series on the main loop between the first heat exchanger 2 and the second heat exchanger 4. The purpose of the gas-liquid separator 5 is to utilize the boiling point differences between different components (e.g., R32 and R1234yf) in the non-azeotropic refrigerant mixture (e.g., R454C). As the refrigerant flows through the gas-liquid separator 5, effective separation of the gas and liquid phases is achieved, resulting in a stratified gas phase rich in low-boiling-point components (e.g., R32) and a liquid phase rich in high-boiling-point components (e.g., R1234yf). Specifically, the gas-liquid separator 5 has a refrigerant inlet, a gas phase outlet, and a liquid phase outlet. Both the refrigerant inlet and liquid phase outlet are connected to the main loop, ensuring its continuity, while the gas phase outlet provides an independent channel for subsequent optimized utilization. In this way, the refrigerant components are managed at the source, laying the foundation for eliminating heat transfer losses caused by temperature slippage.

[0026] Economizer 6 is also connected in series in the main circuit, and it has a first refrigerant flow path and a second refrigerant flow path. The first refrigerant flow path, as part of the main circuit, is used to deeply subcool the liquid refrigerant in the main flow path, which can significantly increase the cooling capacity per unit mass of the refrigerant in the evaporator, thereby improving the cooling or heating efficiency of the entire system.

[0027] Furthermore, a branch circuit is provided on the main circuit of the system, and the second refrigerant flow path of the economizer 6 is located on this branch circuit. This branch circuit is designed such that one end is connected to the main circuit, and the connection point is located upstream of the gas-liquid separator 5. This means that the branch circuit obtains high-pressure liquid refrigerant that has not undergone gas-liquid separation; the other end is connected to the gas injection port of the compressor 1 to achieve enthalpy-increasing gas injection. This design aims to utilize a small portion of the high-pressure refrigerant to subcool the main refrigerant in the first refrigerant flow path by evaporating and absorbing heat in the second refrigerant flow path of the economizer 6. The evaporated gas is then sent to the compressor 1 for gas injection, thereby improving compression efficiency.

[0028] On this branch line, an ejector 7 and a second throttling component 8 are also provided. The second throttling component 8 is located upstream of the ejector 7 and the second refrigerant flow path of the economizer 6, and is used to initially throttle and reduce the pressure of the high-pressure liquid diverted from the main path. The ejector 7 plays a key role in energy recovery and mixing pressurization. It has a first inlet, a second inlet, and an outlet. Its first inlet is connected to the branch line and receives the refrigerant after being reduced in pressure by the second throttling component 8 as the driving flow. Its outlet is connected to the air supply port of the compressor 1 and delivers the mixed and pressurized refrigerant. In particular, the second inlet of the ejector 7 can be selectively connected to the gas phase outlet of the gas-liquid separator 5. This connection allows the gas phase separated from the gas-liquid separator 5, rich in low-boiling-point, high latent heat components (such as R32), to be introduced into the ejector 7 as an inlet flow. This design not only recovers some of the pressure energy during the throttling process using the ejector 7, but also creatively combines component separation with injection enthalpy enhancement technology, using highly efficient refrigerant components for the critical enthalpy enhancement process. This solves the problems of component distribution imbalance and liquid carryover during gas replenishment in the traditional economizer 6 system, achieving optimized utilization of energy and quality.

[0029] In a preferred embodiment, such as Figure 1 As shown, the second refrigerant flow path of the economizer 6 is located upstream of the ejector 7. Specifically, the refrigerant in the branch flow path sequentially flows through the second throttling member 8, the inlet of the second refrigerant flow path of the economizer 6, and the outlet of the second refrigerant flow path of the economizer 6, before entering the first inlet of the ejector 7 as the driving flow. In this structure, the refrigerant branched from the main path first evaporates in the economizer 6 to provide subcooling for the main circuit, and then enters the ejector 7 in gaseous form as the driving flow. The advantage of this design is that the driving flow is stable superheated vapor with a higher energy state, which can provide a stronger ejection capability for the ejector 7, thereby more effectively ejecting the gaseous refrigerant from the gas-liquid separator 5, and potentially achieving a higher pressure boost ratio.

[0030] In another preferred embodiment, such as Figure 4As shown, the ejector 7 is located upstream of the second refrigerant flow path of the economizer 6. Specifically, the refrigerant in the branch flow sequentially passes through the second throttling member 8, the first inlet of the ejector 7, and the outlet of the ejector 7, then enters the inlet of the second refrigerant flow path of the economizer 6, and after exiting the second refrigerant flow path of the economizer 6, it connects to the gas supply port of the compressor 1. In this layout, the ejector 7 first uses the driving flow (from the branch flow of the main path) and the ejector flow (from the gas phase of the gas-liquid separator 5) to mix and pressurize, and then sends the mixed medium-pressure gas-liquid two-phase fluid into the second refrigerant flow path of the economizer 6 for heat exchange. The advantage of this is that the economizer 6 can ensure that any droplets that may exist at the outlet of the ejector 7 are fully evaporated, ensuring that the gas supply port of the compressor 1 is superheated steam, thereby effectively ensuring the safe operation of the compressor 1 and avoiding liquid slugging. At the same time, the mixed fluid has already undergone a pressure boost before entering the economizer 6, which can have a beneficial effect on the subsequent heat exchange process.

[0031] It should be noted that the two layouts mentioned above each have their own emphasis and can be selected according to different design goals and operating conditions. This invention does not impose any specific limitations on them.

[0032] Furthermore, to achieve flexible control over the utilization of the gas phase components, a solenoid valve 9 can be installed between the gas phase outlet of the gas-liquid separator 5 and the second inlet of the ejector 7. This solenoid valve 9 controls the on / off state of this gas phase branch. For example, when the system is operating under high load or extreme low-temperature heating conditions, and maximizing enthalpy increase is required, the solenoid valve 9 can be opened to introduce the R32-rich gas phase into the ejector 7, thereby improving heating capacity and system efficiency. When the system is operating under light load or during transitional seasons, the enthalpy increase requirement is not significant, and the solenoid valve 9 can be closed to stop the introduction of the gas phase, thus saving energy and avoiding unnecessary circulation. This design, through simple on / off control, gives the system the ability to adaptively adjust to different operating conditions, achieving a balance between performance and energy consumption.

[0033] To enable the heat pump system of the present invention to switch between cooling and heating modes, the system preferably also includes a four-way valve 10. Figure 1 and Figure 2 As shown, the four-way valve 10 is connected to both the exhaust port and the suction port of the compressor 1. Simultaneously, the first heat exchanger 2 (e.g., a condenser serving as an outdoor heat exchanger) and the second heat exchanger 4 (e.g., a plate heat exchanger serving as an indoor heat exchanger) can be selectively connected to either the exhaust port or the suction port of the compressor 1 via the four-way valve 10. When in cooling mode (e.g.) Figure 2 and Figure 5As shown), the four-way valve 10 directs the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 to the first heat exchanger 2 (outdoor unit, acting as a condenser), and connects the second heat exchanger 4 (indoor unit, acting as an evaporator) to the suction port of the compressor 1. When switching to heating mode (as shown...), Figure 3 and Figure 6 As shown, the four-way valve 10 actuates, directing the high-temperature, high-pressure gaseous refrigerant to the second heat exchanger 4 (indoor unit, acting as a condenser), while the first heat exchanger 2 acts as an evaporator connected to the compressor 1's suction port. The switching action of the four-way valve 10 enables flexible switching of system functions.

[0034] In one specific implementation, the throttling components in the system are detailed. For example... Figure 1 and Figure 2 As shown, the first throttling component 3 may include a first throttling valve 31 and a second throttling valve 32. The first throttling valve 31 is located in the main circuit between the first heat exchanger 2 and the gas-liquid separator 5, while the second throttling valve 32 is located in the main circuit between the first refrigerant flow path of the economizer 6 and the second heat exchanger 4. The second throttling component 8 is specifically a third throttling valve, located on the branch line and upstream of the ejector 7 and the economizer 6. These three throttling valves are preferably electronic expansion valves. By precisely controlling their opening degree, the refrigerant flow rate and pressure in the main circuit and the branch line can be finely adjusted to adapt to the optimal operating point under different operating conditions, making them important actuators for achieving efficient system operation.

[0035] To complement the reversing function of the four-way valve 10 and ensure that the refrigerant flow direction within the gas-liquid separator 5 and the economizer 6 remains consistent in both cooling and heating modes, thereby guaranteeing the stability of its separation and heat exchange functions, this application also preferably employs a rectifier check valve 11. For example... Figure 1 and Figure 2 As shown, the rectifier check valve 11 has first, second, third, and fourth ports. Their connections are as follows: the first port is connected to the first throttle valve, the second port is connected to the refrigerant inlet of the gas-liquid separator 5, the third port is connected to the outlet of the first refrigerant flow path of the economizer 6, and the fourth port is connected to the second throttle valve. A rectifier bridge is formed between these ports by setting four check valves. Whether in cooling or heating mode, when the refrigerant flow direction reverses, the rectifier check valve 11 automatically rectifies the refrigerant to flow in a preset direction through the gas-liquid separator 5 and the economizer 6, and then flows to the subsequent pipeline. This design greatly simplifies the piping and control logic, ensuring that the core components always operate under designed conditions, and is key to achieving dual-mode full-flow-path adaptive component control.

[0036] One of the core advantages of this invention lies in the optimization of a specific refrigerant. In a preferred embodiment, the non-azeotropic refrigerant mixture is R454C. R454C is a mixture of two components, R32 and R1234yf, wherein the boiling point of R32 is significantly lower than that of R1234yf. Utilizing this physical property, the gas-liquid separator 5 can efficiently separate the throttled R454C refrigerant into a gaseous phase rich in low-boiling-point R32 and a liquid phase rich in high-boiling-point R1234yf. The R32-rich gaseous phase, due to its high latent heat, is an ideal source of enthalpy-increasing gas and is therefore discharged from the gas phase outlet and sent to the ejector 7. The R1234yf-rich liquid phase, on the other hand, is discharged from the liquid phase outlet and returned to the main loop to continue its circulation. In this way, not only is the heat transfer loss caused by the temperature slippage of R454C in the heat exchanger mitigated, but the advantages of different components are also utilized, achieving a synergistic gain effect among the various technical components.

[0037] To further enhance system stability and reliability, a one-way valve (not shown in the figure) can be installed between the outlet of injector 7 and the gas inlet of compressor 1. The purpose of this one-way valve is to allow refrigerant to flow only from injector 7 (or its downstream economizer 6) to the gas inlet of compressor 1, while strictly preventing gas from flowing back from the gas inlet to injector 7 and the branch circuit under certain operating conditions (such as compressor 1 shutdown, pressure fluctuations, etc.). This effectively protects compressor 1 from the impact of medium-pressure gas and maintains stable pressure in the branch circuit.

[0038] The heat pump system provided in this application can be widely used in various devices requiring temperature regulation. Therefore, this application also provides an air conditioner, which can be a household air conditioner, a commercial central air conditioner, an air source heat pump water heater, etc. This air conditioner internally includes the heat pump system of any of the aforementioned embodiments. By employing the heat pump system of this invention, the air conditioner can significantly improve its operating energy efficiency (COP / SEER) over a wide temperature range while using low-GWP environmentally friendly refrigerants such as R454C, particularly improving its heating capacity and reliability in low-temperature winter environments, while maintaining efficient cooling in high-temperature summer environments. For example, an air source heat pump equipped with the system of this invention can provide sufficient heating capacity even in extremely cold weather of -15°C through vapor phase enthalpy enhancement and ejector 7 circulation, avoiding the problem of drastic reduction in heating capacity or even the need to start electric auxiliary heating in traditional heat pumps.

[0039] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A heat pump system, characterized in that, It includes a compressor (1), a first heat exchanger (2), a first throttling component (3) and a second heat exchanger (4) connected in sequence to form a refrigerant main circuit. A gas-liquid separator (5) and an economizer (6) are connected in series on the main circuit between the first heat exchanger (2) and the second heat exchanger (4). The gas-liquid separator (5) is used to separate the gas and liquid components of a non-azeotropic mixed refrigerant. It has a refrigerant inlet, a gas phase outlet and a liquid phase outlet. The refrigerant inlet and the liquid phase outlet are both connected to the main circuit. The economizer (6) has a first refrigerant flow path and a second refrigerant flow path, wherein the first refrigerant flow path is connected in series with the main circuit; The main circuit is also provided with a branch circuit, and the second refrigerant flow path is provided on the branch circuit. One end of the branch circuit is connected to the main circuit and the connection position is located upstream of the gas-liquid separator (5), and the other end is connected to the gas supply port of the compressor (1). The branch circuit is provided with an ejector (7) and a second throttling component (8), and the second throttling component (8) is located upstream of the ejector (7) and the second refrigerant flow path. The ejector (7) has a first inlet, a second inlet and an outlet. The first inlet is connected to the branch circuit, the second inlet is optionally connected to the gas phase outlet, and the outlet is connected to the gas supply port.

2. The heat pump system according to claim 1, characterized in that, The injector (7) is located upstream of the second refrigerant flow path. The first inlet is connected to the second throttling member (8), the outlet is connected to the inlet of the second refrigerant flow path, and the outlet of the second refrigerant flow path is connected to the air supply port.

3. The heat pump system according to claim 1, characterized in that, The second refrigerant flow path is located upstream of the injector (7), the inlet of the second refrigerant flow path is connected to the second throttling member (8), the outlet of the second refrigerant flow path is connected to the first inlet, and the outlet is connected to the air supply port.

4. The heat pump system according to claim 1, characterized in that, A solenoid valve (9) is provided between the gas phase outlet and the second inlet, and the solenoid valve (9) is used to control the opening and closing of the gas phase outlet and the second inlet.

5. The heat pump system according to claim 1, characterized in that, The heat pump system also includes a four-way valve (10), which is connected to the exhaust port and the intake port of the compressor (1) respectively. The first heat exchanger (2) and the second heat exchanger (4) are selectively connected to the exhaust port and the intake port of the compressor (1) through the four-way valve (10).

6. The heat pump system according to claim 1, characterized in that, The first throttling component (3) includes a first throttling valve (31) and a second throttling valve (32). The first throttling valve (31) is located on the main circuit between the first heat exchanger (2) and the gas-liquid separator (5). The second throttling valve (32) is located on the main circuit between the first refrigerant flow path of the economizer (6) and the second heat exchanger (4). The second throttling component (8) includes a third throttling valve, which is disposed on the branch line and located upstream of the injector (7) and the second refrigerant flow path.

7. The heat pump system according to claim 6, characterized in that, The heat pump system also includes a rectifier check valve (11), which has a first port, a second port, a third port, and a fourth port. The first port is connected to the first throttle valve (31), the second port is connected to the refrigerant inlet, the third port is connected to the outlet of the first refrigerant flow path, and the fourth port is connected to the second throttle valve (32); A one-way valve is provided between the first port and the second port, between the second port and the third port, between the third port and the fourth port, and between the fourth port and the first port; The rectifier check valve (11) is configured to maintain the refrigerant flowing in a predetermined direction between the gas-liquid separator (5) and the economizer (6) in both cooling and heating modes.

8. The heat pump system according to claim 1, characterized in that, The non-azeotropic mixed refrigerant is R454C, which is composed of R32 and R1234yf, and the boiling point of R32 is lower than that of R1234yf. The gas-liquid separator (5) can utilize the difference in boiling points to separate the non-azeotropic mixed refrigerant into a gas phase refrigerant rich in R32 and a liquid phase refrigerant rich in R1234yf. The gas phase refrigerant is discharged from the gas phase outlet, and the liquid phase refrigerant is returned to the main circuit from the liquid phase outlet.

9. The heat pump system according to claim 1, characterized in that, A one-way valve is provided between the outlet of the injector (7) and the air inlet of the compressor (1). The one-way valve is configured to allow refrigerant to flow from the injector (7) to the air inlet and to prevent refrigerant from flowing back from the air inlet to the injector (7).

10. An air conditioner, characterized in that, The heat pump system included in any one of claims 1 to 9.

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