An air source heat pump system

Abstract

This utility model relates to the field of heat pump system technology and discloses an air source heat pump system. By setting up a first compressor, a second compressor, and a first, second, and third heat exchanger, and utilizing a connecting valve group to control the flow direction of the first refrigerant, the air source heat pump system can switch between single-stage and two-stage circulation modes. It can flexibly adjust the system's operating mode according to ambient temperature and load demand, improving the system's applicability and operational stability. In single-stage circulation mode, the first refrigerant exchanges heat with water in the first heat exchanger and then returns to the first compressor through a throttling component and the second heat exchanger, achieving the production of medium-low temperature hot water to meet heating needs under normal temperature conditions. Simultaneously, it simplifies the refrigerant circulation path and reduces system energy consumption.

Description

Technical Field

[0001] This utility model relates to the field of heat pump system technology, specifically to an air source heat pump system. Background Technology

[0002] With the rapid development of the social economy and the increasing awareness of energy conservation and environmental protection, air source heat pumps, as a device that utilizes low-grade heat energy for efficient heat energy conversion, have been widely promoted and applied in my country in recent years. Air source heat pumps use low-temperature heat energy in the air as a heat source, converting it into high-grade heat energy through a compressor. They have advantages such as energy saving, environmental protection, safety, and convenient installation, and are widely used in various scenarios including residential hot water supply, building heating, industrial hot water preparation, and some industrial steam supply.

[0003] Existing air-source heat pump systems generally include a compressor, condenser, evaporator, throttling device, and corresponding control unit, achieving heat transfer between air and water or between air and air through refrigerant circulation. However, in extremely cold regions, due to the extremely low ambient temperature, the evaporation temperature of the air-source heat pump drops significantly, resulting in a significant decrease in heating capacity. This leads to low operating efficiency or even failure to operate normally in extremely cold environments. Furthermore, due to the significantly increased compressor load, the water temperature in the heating system is difficult to raise to a higher level. Existing units can generally only raise the water temperature to 50℃~55℃, which is insufficient to meet the demand for high-temperature hot water (such as above 60℃) in some scenarios.

[0004] Meanwhile, for industrial production scenarios requiring high-temperature steam, traditional air source heat pumps struggle to directly generate high-temperature steam, often relying on electric heaters or boilers as auxiliary heat sources for secondary heating. This increases energy consumption and raises the cost of equipment use and maintenance. Furthermore, in extremely cold environments, users may have simultaneous cooling and heating needs in certain scenarios. Existing air source heat pump systems are often limited by their structure and control methods, making it difficult to achieve stable coordinated operation of cooling and heating within the same system, and thus unable to handle efficient use under multiple operating conditions throughout the year. Utility Model Content

[0005] In view of this, the present invention provides an air source heat pump system to solve the problems of limited heating temperature, inability to directly produce high-temperature steam, and inability to simultaneously meet multiple operating conditions in the existing air source heat pump in extremely cold regions.

[0006] To solve the above-mentioned technical problems, the technical solution of this utility model is as follows:

[0007] This utility model provides an air source heat pump system, including: a first compressor, a second compressor, a first heat exchanger, a second heat exchanger, a third heat exchanger, a throttling component, and a flash evaporator;

[0008] A connecting valve assembly is provided at the outlet end of the first compressor, and the first compressor is connected to the first heat exchanger, the second heat exchanger and the third heat exchanger respectively through the connecting valve assembly;

[0009] In a single-stage cycle, the first refrigerant flows out from the first compressor, passes through the first heat exchanger, the throttling assembly, and the second heat exchanger, and then flows back into the first compressor. The first heat exchanger is connected to the flash evaporator to form a water system circulation loop. The first refrigerant exchanges heat with water in the first heat exchanger.

[0010] In a two-stage circulation mode, the first refrigerant flows out from the first compressor, passes through the third heat exchanger, the throttling assembly, and the second heat exchanger, and then flows back into the first compressor; the second refrigerant flows out from the second compressor, passes through the first heat exchanger and the third heat exchanger, and then flows back into the second compressor. The first and second refrigerants exchange heat in the third heat exchanger. The first heat exchanger is connected to the flash evaporator to form a water system circulation loop. The first refrigerant exchanges heat with water in the first heat exchanger.

[0011] A controller, which is communicatively connected to the connecting valve group, is adapted to control the opening direction of the connecting valve group to control the air source heat pump system to switch between a single-stage circulation state and a two-stage circulation state.

[0012] It has the following advantages:

[0013] This invention, by setting up a first compressor, a second compressor, and a first, second, and third heat exchanger, and utilizing a connecting valve group to control the flow direction of the first refrigerant, enables the air source heat pump system to switch between single-stage and two-stage circulation modes. This allows for flexible adjustment of the system's operating mode based on ambient temperature and load demand, improving the system's applicability and operational stability. In single-stage circulation mode, the first refrigerant exchanges heat with water in the first heat exchanger and then returns to the first compressor through a throttling component and the second heat exchanger, achieving the production of medium- and low-temperature hot water to meet heating needs in normal temperature environments. This also simplifies the refrigerant circulation path and reduces system energy consumption. In two-stage circulation mode, the first and second refrigerants exchange heat in the third heat exchanger, and the second refrigerant circulates through both the first and third heat exchangers, achieving multi-stage enthalpy increase and higher heat exchange efficiency. This enables the production of high-temperature hot water or high-temperature steam in extremely cold environments, overcoming the limitation of heating temperature in traditional air source heat pump systems at low ambient temperatures. This utility model's air-source heat pump system connects to a flash evaporator via a first heat exchanger, forming a water system circulation loop. This allows for simultaneous satisfaction of heat demands at different temperature levels and adaptability to various operating conditions, enhancing the system's application range and market competitiveness. The controller manages the opening direction of the connecting valve group, enabling intelligent switching of the system's circulation mode. This ensures the system maintains a high energy efficiency ratio under different operating conditions, further improving the system's energy utilization efficiency and operational economy.

[0014] According to a first aspect of the present invention, the single-stage cycle state includes a first heating cycle state and a cooling cycle state;

[0015] In the first heating cycle state, the first refrigerant flows out from the first compressor, flows sequentially through the first heat exchanger, the throttling component and the second heat exchanger to return to the first compressor;

[0016] In the refrigeration cycle, the first refrigerant flows out from the first compressor, flows sequentially through the second heat exchanger, the throttling component, and the first heat exchanger, and then flows back into the first compressor.

[0017] According to a first aspect of the present invention, the dual-stage circulation state includes a second heating circulation state and a steam circulation state;

[0018] In the second heating cycle state, the first refrigerant flows out from the first compressor, flows sequentially through the third heat exchanger, the throttling component and the second heat exchanger and returns to the first compressor; the second refrigerant flows out from the second compressor, flows sequentially through the first heat exchanger and the third heat exchanger and returns to the second compressor, and the first refrigerant and the second refrigerant exchange heat in the third heat exchanger;

[0019] The temperature of the hot water prepared under the first heating cycle state is lower than the temperature of the hot water prepared under the second heating cycle state.

[0020] The system is set with a first threshold. The temperature of the hot water prepared in the first heating cycle state is greater than or equal to the first threshold. The controller is adapted to control the connecting valve group to turn so that the single-stage cycle state is changed to the two-stage cycle state, and the system enters the steam cycle state.

[0021] According to a first aspect of the present invention, the connecting valve group includes a first valve body and a second valve body, both of which are communicatively connected to the controller. The first valve body includes a first valve, a second valve, a third valve, and a fourth valve. The second valve body includes a first valve port, a second valve port, and a third valve port.

[0022] The first valve is connected to the outlet of the first compressor, the second valve is connected to the first valve port, the third valve is connected to the first end of the second heat exchanger, and the fourth valve is connected to the first inlet of the first compressor.

[0023] The second valve port is connected to the first heat exchanger, and the third valve port is connected to the third heat exchanger;

[0024] The controller is adapted to control the first valve body and the second valve body to turn in opposite directions, so that the system is in a single-stage circulation state or a two-stage circulation state.

[0025] According to a first aspect of the present invention, the throttling assembly includes a throttling valve group and an economizer. The throttling valve group is provided with a first interface, a second interface, a third interface, and a fourth interface. The economizer is provided with a first inlet, a second inlet, a first outlet, and a second outlet. The first inlet is connected to the first outlet, and the second inlet is connected to the second outlet.

[0026] The first interface is connected to the second end of the second heat exchanger, the second interface is connected to the first inlet, the third interface is connected to the first heat exchanger and / or the third heat exchanger, the fourth interface is connected to the first outlet, the second inlet is connected to the second interface through a throttling pipe, and the second outlet is connected to the second air inlet of the first compressor.

[0027] According to a first aspect of the present invention, the throttle valve assembly includes: a first check valve and a second check valve arranged in series, a third check valve and a fourth check valve arranged in series, the first check valve and the second check valve being arranged in opposite directions, the third check valve and the fourth check valve being arranged in opposite directions; the first check valve and the third check valve being arranged in the same direction, the fourth check valve and the second check valve being arranged in the same direction.

[0028] The first interface is located between the first check valve and the fourth check valve, the second interface is located between the first check valve and the second check valve, the third interface is located between the second check valve and the third check valve, and the fourth interface is located between the third check valve and the fourth check valve.

[0029] According to a first aspect of the present invention, the first heat exchanger is provided with a first port, a second port, a third port, a fourth port, a fifth port, a sixth port, a seventh port, and an eighth port; the first port and the second port are connected inside the first heat exchanger, the third port and the fourth port are connected inside the first heat exchanger, the fifth port and the sixth port are connected inside the first heat exchanger, and the seventh port and the eighth port are connected inside the first heat exchanger.

[0030] The third heat exchanger includes a ninth port, a tenth port, an eleventh port, and a twelfth port. The ninth port and the tenth port are connected within the third heat exchanger, and the eleventh port and the twelfth port are connected within the third heat exchanger.

[0031] The first port is connected to the second valve port, and the second port is connected to the tenth port; the third port and the eleventh port are connected, and the fourth port is connected to the outlet of the second compressor; the fifth port and the seventh port are both connected to the circulating water inlet of the flash evaporator, the sixth port and the eighth port are both connected to the circulating water outlet of the flash evaporator, the ninth port is connected to the third valve port, and the twelfth port is connected to the air inlet of the second compressor;

[0032] A first solenoid valve is provided between the fifth port and the circulating water inlet, and a second solenoid valve is provided between the seventh port and the circulating water inlet. Both the first solenoid valve and the second solenoid valve are communicatively connected to the controller.

[0033] In a single-stage cycle state, the controller controls the first solenoid valve to close and the second solenoid valve to open;

[0034] In the dual-stage cycle state, the controller controls the first solenoid valve to open and the second solenoid valve to close.

[0035] According to a first aspect of the present invention, the top of the flash evaporator is provided with an exhaust port for communicating with a steam pipe, the steam pipe is provided with a third solenoid valve, and the flash evaporator is provided with a pressure detection device, which is adapted to detect the pressure parameters inside the flash evaporator and feed them back to the controller, and the controller controls the opening and closing of the third solenoid valve according to the pressure parameters.

[0036] According to a first aspect of the present invention, the air source heat pump system further includes a fan, the fan being communicatively connected to the controller, the fan being disposed opposite to the second heat exchanger, and the controller controlling the fan to start during the first heating cycle state, the second heating cycle state, and the steam cycle state. Attached Figure Description

[0037] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0038] Figure 1 This is a schematic diagram of the operating principle of an air source heat pump system in the first heating cycle state provided in some embodiments of the present invention.

[0039] Figure 2 This is a schematic diagram illustrating the operating principle of an air source heat pump system in the second heating cycle state, provided in some embodiments of this utility model.

[0040] Figure 3 This is a schematic diagram illustrating the operating principle of an air source heat pump system under steam circulation conditions, provided in some embodiments of this utility model.

[0041] Figure 4 This is a schematic diagram illustrating the operating principle of an air source heat pump system in a refrigeration cycle state, provided in some embodiments of this utility model.

[0042] Figure 5 This is a schematic diagram of the throttling component of an air source heat pump system provided in some embodiments of the present invention;

[0043] Figure 6 This is a schematic diagram of the structure of the first valve body of an air source heat pump system provided in some embodiments of the present invention;

[0044] Figure 7 This is a schematic diagram of the structure of the first heat exchanger of an air source heat pump system provided in some embodiments of the present invention;

[0045] Figure 8 This is a schematic diagram of the structure of the third heat exchanger of an air source heat pump system provided in some embodiments of the present invention.

[0046] Explanation of reference numerals in the attached figures:

[0047] 1. First compressor; 2. Second compressor; 3. Flash evaporator; 4. First heat exchanger; 41. First port; 42. Second port; 43. Third port; 44. Fourth port; 45. Fifth port; 46. Sixth port; 47. Seventh port; 48. Eighth port; 5. Second heat exchanger; 6. Third heat exchanger; 61. Ninth port; 62. Tenth port; 63. Eleventh port; 64. Twelfth port; 7. Connecting valve assembly; 71. First valve body; 72. Second valve body; 711, First valve; 712, Second valve; 713, Third valve; 714, Fourth valve; 8, Throttling assembly; 81, Throttling valve group; 82, Economizer; 811, First check valve; 812, Second check valve; 813, Third check valve; 814, Fourth check valve; 821, First inlet; 822, First outlet; 823, Second inlet; 824, Second outlet; 9, Fan; 10, First solenoid valve; 11, Second solenoid valve. Detailed Implementation

[0048] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0049] In the description of this utility model, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0050] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0051] Furthermore, the technical features involved in the different embodiments of this utility model described below can be combined with each other as long as they do not conflict with each other.

[0052] Reference Figure 1 As shown, in a first aspect of this utility model, this utility model provides an air source heat pump system, including: a first compressor 1, a second compressor 2, a first heat exchanger 4, a second heat exchanger 5, a third heat exchanger 6, a throttling assembly 8, and a flash evaporator 3;

[0053] A connecting valve assembly 7 is located at the outlet end of the first compressor 1. The first compressor 1 is connected to the first heat exchanger 4, the second heat exchanger 5 and the third heat exchanger 6 respectively through the connecting valve assembly 7.

[0054] In a single-stage cycle, the first refrigerant flows out from the first compressor 1, flows through the first heat exchanger 4, the throttling assembly 8, and the second heat exchanger 5, and then flows back into the first compressor 1. The first heat exchanger 4 is connected to the flash evaporator 3 to form a water system circulation loop. The first refrigerant exchanges heat with water in the first heat exchanger 4.

[0055] In a two-stage cycle, the first refrigerant flows out from the first compressor 1, passes through the third heat exchanger 6, the throttling assembly 8, and the second heat exchanger 5, and then flows back into the first compressor 1; the second refrigerant flows out from the second compressor 2, passes through the first heat exchanger 4 and the third heat exchanger 6, and then flows back into the second compressor 2. The first and second refrigerants exchange heat in the third heat exchanger 6. The first heat exchanger 4 is connected to the flash evaporator 3 to form a water system circulation loop; the first refrigerant exchanges heat with water in the first heat exchanger 4.

[0056] The controller is communicatively connected to the connecting valve group 7 and is adapted to control the opening direction of the connecting valve group 7 to control the air source heat pump system to switch between single-stage and two-stage circulation states.

[0057] Specifically, this invention, by setting up a first compressor 1, a second compressor 2, and a first heat exchanger 4, a second heat exchanger 5, and a third heat exchanger 6, and utilizing a connecting valve group 7 to control the flow direction of the first refrigerant, enables the air source heat pump system to switch between single-stage and two-stage circulation modes. This allows for flexible adjustment of the system's operating mode based on ambient temperature and load demand, improving the system's applicability and operational stability. In single-stage circulation mode, the first refrigerant exchanges heat with water in the first heat exchanger 4 and then returns to the first compressor 1 through the throttling component 8 and the second heat exchanger 5, achieving the production of medium-low temperature hot water to meet heating needs in normal temperature environments. This also simplifies the refrigerant circulation path and reduces system energy consumption. In two-stage circulation mode, the first and second refrigerants exchange heat in the third heat exchanger 6, and the second refrigerant circulates through the first and third heat exchangers 4 and 6, achieving multi-stage enthalpy increase and higher heat exchange efficiency. This enables the production of high-temperature hot water or high-temperature steam in extremely cold environments, overcoming the limitation of heating temperature in traditional air source heat pump systems at low ambient temperatures. The air-source heat pump system of this invention is connected to the flash evaporator 3 via the first heat exchanger 4, forming a water system circulation loop. This allows for the simultaneous fulfillment of heat demands at different temperature levels and enables the system to adapt to various operating conditions, thus enhancing its application range and market competitiveness. The controller manages the opening direction of the connecting valve group 7, enabling intelligent switching of the system's circulation mode. This ensures the system maintains a high energy efficiency ratio under different operating conditions, further improving the system's energy utilization efficiency and operational economy.

[0058] It is understood that this utility model, through the combined design of the first compressor 1, the second compressor 2 and multiple heat exchangers, and the setting of the connecting valve group 7 and the controller, adjusts the connection relationship of each component of the system, enabling the air source heat pump system to flexibly switch between single-stage and two-stage circulation states according to the ambient temperature, load demand and target heating temperature, thereby achieving adaptability to various working conditions, including medium-temperature hot water heating, high-temperature hot water preparation and high-temperature steam production, significantly expanding the application range of the system.

[0059] In the two-stage circulation mode, the first and second refrigerants exchange heat in the third heat exchanger 6. Through multi-stage enthalpy increase and heat superposition, the system's heating capacity in extremely cold environments is effectively improved. This allows the system to maintain a high exhaust temperature and heating efficiency even at ambient temperatures below zero, overcoming the problems of severe capacity reduction and limited outlet water temperature in existing air source heat pumps in extremely cold regions. In the two-stage circulation mode, this utility model system, through the enthalpy increase effect of the second compressor 2 and the synergistic heat exchange of the first and third heat exchangers 6, enables the second refrigerant to reach a higher condensation temperature. This allows for the production of high-temperature hot water and even high-temperature steam, meeting the needs of high-temperature heat sources such as industrial hot water supply, high-temperature process steam, and high-end heating systems. This breaks through the technical bottleneck of traditional air source heat pump systems, which cannot directly obtain high-temperature heat sources.

[0060] This invention intelligently schedules the operation of each heat exchanger and compressor within the system under different operating conditions. Under partial load conditions, it utilizes only a single-stage cycle to reduce energy consumption; when high-temperature heating is required, a two-stage cycle is activated to enhance capacity. The system can maintain a high efficiency under multiple operating conditions, improving the overall energy efficiency ratio, helping to reduce operating costs, and achieving greater energy savings. In the two-stage cycle state, the second refrigerant flows through the first heat exchanger 4 and the third heat exchanger 6. Utilizing a secondary refrigerant loop and multi-stage heat exchange, not only is heat exchange efficiency improved, but the temperature difference between each stage of the compressor is also reduced, lowering the compressor load and operating pressure. This helps extend the lifespan of system components and improves the overall reliability and stability of operation.

[0061] This invention connects the first heat exchanger 4 with the flash evaporator 3 to form a water system circulation loop, enabling the system to efficiently transfer heating energy to the water side. Whether in a single-stage or two-stage circulation state, heat can be output through the water system, adapting to the diverse needs of different buildings, industries, hot water or steam processes, and improving the system's flexibility and market competitiveness.

[0062] This utility model, through the communication connection between the controller and the connecting valve group 7, can automatically adjust the valve group opening and flow path switching in real time according to the ambient temperature, load demand and system operating status, realize intelligent and smooth switching between single-stage circulation and double-stage circulation, avoid the increase in energy consumption and system impact caused by frequent start-stop, and improve the system response speed and intelligence level.

[0063] In a first aspect embodiment of the present invention, the single-stage cycle state includes a first heating cycle state and a cooling cycle state;

[0064] In the first heating cycle state, the first refrigerant flows out from the first compressor 1, flows through the first heat exchanger 4, the throttling assembly 8 and the second heat exchanger 5 in sequence, and then flows back into the first compressor 1.

[0065] In the refrigeration cycle, the first refrigerant flows out from the first compressor 1, and flows sequentially through the second heat exchanger 5, the throttling component 8 and the first heat exchanger 4 to return to the first compressor 1.

[0066] According to a first aspect of the present invention, the dual-stage circulation state includes a second heating circulation state and a steam circulation state;

[0067] In the second heating cycle state, the first refrigerant flows out from the first compressor 1, flows through the third heat exchanger 6, the throttling component 8 and the second heat exchanger 5 in sequence and flows back into the first compressor 1; the second refrigerant flows out from the second compressor 2, flows through the first heat exchanger 4 and the third heat exchanger 6 in sequence and flows back into the second compressor 2, and the first refrigerant and the second refrigerant exchange heat in the third heat exchanger 6.

[0068] The temperature of the hot water prepared under the first heating cycle is lower than the temperature of the hot water prepared under the second heating cycle.

[0069] The system is set with a first threshold. When the temperature of the hot water prepared in the first heating cycle is greater than or equal to the first threshold, the controller is adapted to control the connecting valve group 7 to turn so that the single-stage cycle state is changed to the two-stage cycle state and the system enters the steam cycle state.

[0070] Reference Figure 6 As shown, in the first aspect embodiment of this utility model, the connecting valve group 7 includes a first valve body 71 and a second valve body 72, both of which are communicatively connected to the controller. The first valve body 71 includes a first valve 711, a second valve 712, a third valve 713 and a fourth valve 714, and the second valve body 72 includes a first valve port, a second valve port and a third valve port.

[0071] The first valve 711 is connected to the outlet of the first compressor 1, the second valve 712 is connected to the first valve port, the third valve 713 is connected to the first end of the second heat exchanger 5, and the fourth valve 714 is connected to the first air inlet of the first compressor 1.

[0072] The second valve port is connected to the first heat exchanger 4, and the third valve port is connected to the third heat exchanger 6.

[0073] The controller is adapted to control the first valve body 71 and the second valve body 72 to turn in opposite directions, so that the system is in a single-stage cycle state or a two-stage cycle state.

[0074] In a first aspect embodiment of the present invention, the throttling assembly 8 includes a throttling valve group 81 and an economizer 82. The throttling valve group 81 is provided with a first interface, a second interface, a third interface and a fourth interface; the economizer 82 is provided with a first inlet 821, a second inlet 823, a first outlet 822 and a second outlet 824; the first inlet 821 is connected to the first outlet 822, and the second inlet 823 is connected to the second outlet 824.

[0075] The first interface is connected to the second end of the second heat exchanger 5, the second interface is connected to the first inlet 821, the third interface is connected to the first heat exchanger 4 and / or the third heat exchanger 6, the fourth interface is connected to the first outlet 822, the second inlet 823 is connected to the second interface through a throttling pipe, and the second outlet 824 is connected to the second air intake end of the first compressor 1.

[0076] Reference Figure 5 As shown, in a first aspect embodiment of the present invention, the throttle valve assembly 81 includes: a first check valve 811 and a second check valve 812 arranged in series, a third check valve 813 and a fourth check valve 814 arranged in series, the first check valve 811 and the second check valve 812 being arranged in opposite directions, the third check valve 813 and the fourth check valve 814 being arranged in opposite directions; the first check valve 811 and the third check valve 813 being arranged in the same direction, and the fourth check valve 814 and the second check valve 812 being arranged in the same direction.

[0077] The first interface is located between the first check valve 811 and the fourth check valve 814, the second interface is located between the first check valve 811 and the second check valve 812, the third interface is located between the second check valve 812 and the third check valve 813, and the fourth interface is located between the third check valve 813 and the fourth check valve 814.

[0078] Reference Figure 7 and Figure 8 As shown, in a first aspect embodiment of the present invention, the first heat exchanger 4 is provided with a first port 41, a second port 42, a third port 43, a fourth port 44, a fifth port 45, a sixth port 46, a seventh port 47, and an eighth port 48; the first port 41 and the second port 42 are connected inside the first heat exchanger 4, the third port 43 and the fourth port 44 are connected inside the first heat exchanger 4, the fifth port 45 and the sixth port 46 are connected inside the first heat exchanger 4, and the seventh port 47 and the eighth port 48 are connected inside the first heat exchanger 4.

[0079] The third heat exchanger 6 includes a ninth port 61, a tenth port 62, an eleventh port 63 and a twelfth port 64. The ninth port 61 and the tenth port 62 are connected within the third heat exchanger 6, and the eleventh port 63 and the twelfth port 64 are connected within the third heat exchanger 6.

[0080] The first port 41 is connected to the second valve port, the second port 42 is connected to the tenth port 62; the third port 43 and the eleventh port 63 are connected, the fourth port 44 is connected to the outlet of the second compressor 2; the fifth port 45 and the seventh port 47 are both connected to the circulating water inlet of the flash evaporator 3, the sixth port 46 and the eighth port 48 are both connected to the circulating water outlet of the flash evaporator 3, the ninth port 61 is connected to the third valve port, and the twelfth port 64 is connected to the air inlet of the second compressor 2.

[0081] A first solenoid valve 10 is provided between the fifth port 45 and the circulating water inlet, and a second solenoid valve 11 is provided between the seventh port 47 and the circulating water inlet. Both the first solenoid valve 10 and the second solenoid valve 11 are connected to the controller in communication.

[0082] In single-stage cycle mode, the controller controls the first solenoid valve 10 to close and the second solenoid valve 11 to open.

[0083] In the dual-stage cycle state, the controller controls the first solenoid valve 10 to open and the second solenoid valve 11 to close.

[0084] In a first aspect embodiment of the present invention, the top of the flash evaporator 3 is provided with an exhaust port for communicating with a steam pipe, a third solenoid valve is provided on the steam pipe, and a pressure detection device is provided inside the flash evaporator 3. The pressure detection device is adapted to detect the pressure parameters inside the flash evaporator 3 and feed them back to the controller. The controller controls the opening and closing of the third solenoid valve according to the pressure parameters.

[0085] Detailed explanation: Figures 1 to 4 The arrows in the diagram indicate the flow direction of the first refrigerant, the second refrigerant, and the water.

[0086] Reference Figure 1 As shown, the operating principle in the first heating cycle state is as follows:

[0087] The discharge port of the first compressor 1 generates a high-temperature, high-pressure gaseous refrigerant. An oil-gas separator is provided at the discharge port of the first compressor 1. The first refrigerant flows through the oil-gas separator to the first valve body 71. At this time, the first valve 711 and the second valve 712 are connected in the first valve body 71. The first refrigerant flows to the second valve body 72. The first valve port and the second valve port are connected in the second valve body 72. The first refrigerant enters the first heat exchanger 4 from the first port 41 and flows out from the second port 42. At the same time as the first refrigerant flows into the first heat exchanger 4, the controller controls the second solenoid valve 11 to open and the first solenoid valve 10 to close. Water enters the first heat exchanger 4 from the seventh port 47 and flows out from the eighth port 48. The first refrigerant and water exchange heat in the first heat exchanger 4. The first heat exchanger 4 is a shell-and-tube heat exchanger.

[0088] After the first refrigerant is heated by the first heat exchanger 4, it condenses into a low-temperature, high-pressure liquid refrigerant. It then enters the throttling valve group 81 through the third port via a pipeline, flows out through the second port via the second check valve 812, and after passing through the receiver, it splits into two loops. One loop enters the economizer 82 from the first inlet 821 and flows out from the first outlet 822. After passing through the expansion valve, it flows back to the throttling valve group 81 from the fourth port, then flows out from the first port via the fourth check valve 814, enters the second heat exchanger 5 for heat exchange, and then flows back to the first intake end of the first compressor 1. The other loop flows through the solenoid valve and the expansion valve, enters the economizer 82 from the second inlet 823, flows out from the second outlet 824, and flows back to the second intake end of the first compressor 1, thus forming the first heating cycle.

[0089] Reference Figure 2 As shown, the operating principle in the second heating cycle state is as follows:

[0090] The discharge port of the first compressor 1 generates a high-temperature and high-pressure gaseous first refrigerant. An oil-gas separator is provided at the discharge port of the first compressor 1. The first refrigerant flows through the oil-gas separator to the first valve body 71. At this time, the first valve 711 and the second valve 712 are connected in the first valve body 71. The first refrigerant flows to the second valve body 72. The first valve port and the third valve port are connected in the second valve body 72. The first refrigerant enters from the ninth port 61 of the third heat exchanger 6 and exits from the tenth port 62.

[0091] The outlet of the second compressor 2 generates a high-temperature and high-pressure gaseous second refrigerant, which enters the first heat exchanger 4 from the fourth port 44, flows out from the third port 43, passes through the liquid receiver, filter and expansion valve, enters the third heat exchanger 6 from the eleventh port 63, flows out from the twelfth port 64, and returns to the second compressor 2 after passing through the gas-liquid separator.

[0092] The controller notifies the first solenoid valve 10 to open, and water enters the first heat exchanger 4 from the flash evaporator 3 through the fifth port 45 and flows out from the sixth port 46.

[0093] The first refrigerant and the second refrigerant exchange heat in the third heat exchanger 6, and the second refrigerant and water exchange heat in the first heat exchanger 4.

[0094] After the first refrigerant is heated by the third heat exchanger 6, it condenses into a low-temperature, high-pressure liquid refrigerant. It then enters the throttling valve group 81 through the third port via a pipeline, flows out from the second port through the second one-way valve 812, and after passing through the liquid receiver, it splits into two loops. One loop enters the economizer 82 from the first inlet 821 and flows out from the first outlet 822. After passing through the expansion valve, it flows back to the throttling valve group 81 from the fourth port, then flows out from the first port through the fourth one-way valve 814, enters the second heat exchanger 5 for heat exchange, and then flows back to the first intake end of the first compressor 1. The other loop flows through the solenoid valve and the expansion valve, enters the economizer 82 from the second inlet 823, flows out from the second outlet 824, and flows back to the second intake end of the first compressor 1.

[0095] This completes the second heating cycle.

[0096] Reference Figure 3 As shown, the operating principle under steam circulation conditions is as follows:

[0097] First, the first heating cycle state is started. The system has a first threshold. When the control state command is steam cycle, the temperature in the flash evaporator 3 is greater than or equal to the first threshold in the first heating cycle state. The controller controls the second compressor 2 to start and controls the second valve body 72 to switch, start the first solenoid valve 10 and close the second solenoid valve 11 so that the system enters the second heating cycle state. The pressure detection device in the flash evaporator 3 detects the pressure parameters in the flash evaporator 3. When the pressure parameters reach the set threshold, steam can be released, thereby completing the steam cycle state.

[0098] Reference Figure 4 As shown, the operating principle under refrigeration cycle conditions is as follows:

[0099] When the first compressor 1 starts, the controller controls the first valve 711 and the third valve 713 in the first valve body 71 to connect, and the second valve 712 and the fourth valve 714 to connect. The first refrigerant enters the second heat exchanger 5 through the first valve body 71, flows out from the second end of the second heat exchanger 5, enters the throttle valve group 81 from the first interface, flows out through the first check valve 811 and the second interface, and after passing through the liquid receiver and the radiator, it is divided into two circuits.

[0100] After entering the economizer 82 from the first inlet 821, the primary loop flows out from the first outlet 822, passes through the expansion valve, and then flows back to the throttle valve group 81 from the fourth interface. After passing through the third check valve 813, it flows out from the third interface, enters the first heat exchanger 4 through the second port 42, and flows out from the first port 41. After passing through the second valve body 72 and the first valve body 71, it flows back to the first compressor 1.

[0101] Another circuit enters the economizer 82 from the second inlet 823 via the solenoid valve and the expansion valve, and flows out from the second outlet 824 and back into the first compressor 1;

[0102] The controller controls the first solenoid valve 10 to close and the second solenoid valve 11 to open. Water enters the first heat exchanger 4 from the seventh port 47, exchanges heat with the first refrigerant, and then flows out from the eighth port 48 into the flash evaporator 3 before being output.

[0103] The water that has undergone heat exchange in the first heat exchanger 4 is further cooled in the flash evaporator 3, producing cold water below 7°C.

[0104] In a first aspect of the present invention, the air source heat pump system further includes a fan 9, which is communicatively connected to a controller. The fan 9 is disposed opposite to the second heat exchanger 5. In the first heating cycle state, the second heating cycle state, and the steam cycle state, the controller controls the fan 9 to start.

[0105] Secondly, this utility model also provides a control method for an air source heat pump system, including the following steps;

[0106] Input mode commands, which include first heating cycle state, second heating cycle state, cooling cycle state, and steam cycle state;

[0107] The system has a first mode switching temperature. When setting the output water temperature Parameters are lower than the mode switching temperature At this time, the controller controls the first valve 711 to connect with the second valve 712, the third valve 713 to connect with the fourth valve 714, and the first valve port to connect with the second valve port; the controller controls the first solenoid valve 10 to close and the second solenoid valve 11 to open; the system is in the first heating cycle state.

[0108] When setting the output water temperature The parameter is higher than the mode switching temperature. And output water temperature When the temperature is below 100℃, the controller controls the first valve 711 and the second valve 712 to connect, the third valve 713 and the fourth valve 714 to connect, and the first valve port to connect with the third valve port; the second compressor 2 starts, and the controller controls the first solenoid valve 10 to open and the second solenoid valve 11 to close; the system is in the second heating cycle state.

[0109] When the mode command is steam circulation state, when the water tank temperature inside flash evaporator 3 is lower than the first threshold, the controller control system is in the first heating cycle state. When the water tank temperature inside flash evaporator 3 is higher than the first threshold, the controller control system is in the second heating cycle state. The pressure detection device inside flash evaporator 3 detects the pressure parameters and feeds them back to the controller. The controller controls the opening and closing of the third solenoid valve according to the pressure parameters so that the system is in steam circulation state.

[0110] When the mode command is in the refrigeration cycle state, the controller controls the first valve 711 to connect with the third valve 713, the second valve 712 to connect with the fourth valve 714, and the first valve port to connect with the second valve port; the controller controls the first solenoid valve 10 to close and the second solenoid valve 11 to open.

[0111] Specifically, this utility model, through setting mode commands and combining the control of multiple valves and solenoid valves, enables the air source heat pump system to flexibly switch between the first heating cycle state, the second heating cycle state, the cooling cycle state, and the steam cycle state. This meets the diverse heating, cooling, and high-temperature steam needs of users in different seasons and usage scenarios, significantly improving the system's application range and practicality. Temperature can be switched by setting the mode. And combined with the user-set output water temperature The parameters enable intelligent determination and switching of the heating mode. When the output water temperature is low, the system adopts the first heating cycle state, simplifying the refrigerant circulation path and reducing system energy consumption; while when the demand is higher... When the temperature is below 100℃, the system automatically switches to the second heating cycle state. Through the enthalpy-increasing effect of the second compressor 2, the system ensures it can produce hot water at higher temperatures, improving the applicability and efficiency of the heat pump system in medium- and high-temperature heating applications. This invention also features a steam circulation state, using dual temperature and pressure detection in the water tank within the flash evaporator 3 to intelligently switch between heating and steam production. When the water tank temperature exceeds the first threshold, the system enters the second heating cycle state. Using high-temperature, high-pressure refrigerant, and controlled by the third solenoid valve, steam generation and output are achieved. This allows the heat pump system to not only provide heating but also produce high-temperature steam, overcoming the technical bottleneck of traditional air-source heat pumps that cannot directly produce high-temperature steam. By controlling the opening and closing of valves and solenoid valves, a cooling cycle state can be achieved, allowing the air-source heat pump system to switch to cooling operation mode in summer, effectively achieving both heating and cooling, improving the system's overall utilization rate and economy, and aligning with the trends of energy conservation, environmental protection, and green building development. The system employs a precise control scheme with multiple valve groups and multiple solenoid valves. Through real-time monitoring and adjustment of temperature, pressure, and flow path by the controller, the system can quickly respond to load changes, reduce system impact and frequent start-stop phenomena, ensure long-term stable and reliable operation of the system, help extend equipment service life, and reduce maintenance costs.

[0112] This invention, through its dual-stage circulation design and steam circulation function, can maintain the system's exhaust temperature and heating capacity at a high level even in extremely cold environments by utilizing the enthalpy increase and heat superposition of the second compressor 2. This overcomes the problems of severe heating capacity attenuation and limited outlet water temperature in existing air source heat pumps at low ambient temperatures, thus expanding the application range of heat pump technology in cold regions.

[0113] Thirdly, this utility model also provides a control method for an air source heat pump system, including the following steps;

[0114] A pressure sensor is provided on the pipeline between the first valve body 71 and the second valve body 72. The pressure sensor is suitable for detecting the condensation pressure parameter in the pipeline.

[0115] The saturation temperature is obtained based on the detected condensation pressure parameters and the parameter table. And calculate the intermediate temperature according to the formula. The calculation formula is as follows:

[0116]

[0117] in For ambient temperature, Where K is the outlet water temperature, and K is the intermediate temperature coefficient.

[0118] Based on the system's set intermediate temperature deviation value ;

[0119] when At that time, the controller controls the first compressor 1 and the second compressor 2 to reduce their frequency within the cycle;

[0120] when At that time, the controller controls the first compressor 1 and the second compressor 2 to increase their frequency within the cycle;

[0121] when At that time, the controller keeps the frequency of the first compressor 1 and the second compressor 2 constant.

[0122] Specifically, this utility model uses a pressure sensor installed on the pipe between the first valve body 71 and the second valve body 72 to monitor the condensing pressure parameters in real time during system operation. This allows for the acquisition of important data reflecting the load status of the heat exchanger and the system, and the corresponding saturation temperature is calculated in conjunction with a parameter table. Then, by calculating the intermediate temperature This allows for precise judgment of the current system operating status, enabling accurate adjustment of the frequencies of the first compressor 1 and the second compressor 2, thereby improving the system's dynamic response capability and operating efficiency. Based on the intermediate temperature... The saturation temperature corresponding to the detected condensation pressure The deviation relationship is adopted. As a control threshold, when the system deviates from the target operating condition, it automatically triggers frequency increase or decrease control, effectively avoiding excessive fluctuations in refrigerant pressure or temperature, ensuring that the system operates in the optimal operating range, improving the system's operational stability, and reducing energy consumption fluctuations.

[0123] This invention introduces ambient temperature. With outlet water temperature The difference between them is adjusted by the intermediate temperature coefficient K. This allows the system to flexibly adjust operating parameters according to actual environmental conditions. Especially at low ambient temperatures, by appropriately increasing the compressor frequency, it maintains the system's heating capacity, overcoming the problem of reduced heating capacity in traditional air-source heat pumps at low temperatures and improving the system's adaptability to extremely cold conditions. By employing differential control, frequent start-stop of the compressor unit is avoided. Maintaining a stable frequency within the range reduces mechanical shock and energy waste to the compressor motor. At the same time, it responds to load changes by increasing or decreasing the frequency in a timely manner when the load fluctuates significantly, thereby improving the overall energy efficiency ratio and reducing the long-term operating cost of the system.

[0124] This invention utilizes a combination of pressure sensors and intelligent algorithms to achieve automated control driven by multiple parameters such as environmental conditions, outlet water temperature, and system pressure. This significantly reduces human intervention, improves control accuracy and system reliability, and helps extend equipment lifespan and reduce failure rates. By controlling the intermediate temperature... and with By setting sensitivity for different operating conditions, the control method of this utility model is not only applicable to heating conditions, but also to cooling conditions and transitional season conditions, thus having a wider range of applicability and being able to meet the needs of building heating, cooling and industrial applications for different outlet water temperatures and load changes.

[0125] According to a third aspect of the present invention, the initial frequency of the first compressor 1 is obtained by combining the detected environmental parameter temperature and the required outlet water temperature with a compressor frequency mode calculation table.

[0126] When the operating frequency of the first compressor 1 is lower than the frequency corresponding to the compressor frequency mode calculation table, the controller adjusts the real-time speed of the fan 9 to ensure that... ;

[0127] in At the lowest speed, This refers to the actual rotational speed. The highest speed, where the lowest speed is... and maximum speed Set system preset parameters;

[0128] actual speed The calculation formula is:

[0129]

[0130] in, This refers to the actual operating frequency of the first compressor 1. The initial frequency corresponding to the compressor frequency mode calculation table for the first compressor 1.

[0131] Specifically, this utility model combines the detected environmental parameter temperature and the required outlet water temperature, and uses a compressor frequency mode calculation table to determine the initial operating frequency of the first compressor 1. This allows the compressor's start-up and operating frequency to more accurately match the actual working conditions, avoiding energy waste or insufficient performance caused by the mismatch between the fixed frequency setting and the actual environment in traditional systems. This improves the overall adaptability and operating efficiency of the system.

[0132] When the actual operating frequency of the first compressor 1 is detected to be lower than the target frequency determined by the calculation table, this invention achieves dynamic matching of the system's heat exchange capacity by controlling the real-time speed of the fan 9. The fan 9 speed is controlled by... The calculation formula is adaptively adjusted to ensure precise coordination between the output of fan 9 and compressor output, avoiding energy waste caused by mismatch between refrigerant flow and heat exchange capacity, helping to maintain the system in the high-efficiency range and improving the system's performance coefficient.

[0133] This invention utilizes the linkage control of fan 9 speed and compressor frequency to reduce fan 9 speed when the compressor load is low. This reduces frequent compressor start-stop cycles or large frequency fluctuations, minimizing mechanical shock and electrical load fluctuations, thereby extending the service life of core components such as the compressor and fan 9, and improving system reliability. The control strategy of this invention can increase heat exchange efficiency by increasing fan 9 speed at low ambient temperatures. Even with a low compressor operating frequency, it ensures sufficient heat exchange capacity, overcoming the problem of insufficient heat exchange capacity in traditional heat pump systems operating at low frequencies and low flow rates, and significantly improving the system's heating performance in extremely cold environments. This is achieved through precise adjustment of the actual fan 9 speed. To keep it always at and Within the preset range, this design avoids both the extra energy consumption caused by high fan speed and the impact of low fan speed on heat exchange. This invention effectively reduces overall system energy consumption and operating costs while meeting heating or cooling requirements, demonstrating excellent energy-saving performance.

[0134] This invention organically combines ambient temperature, outlet water temperature, compressor frequency, and fan speed, and achieves intelligent control through calculation tables and formulas. It can respond to changes in environment or load in real time, improve the system's ability to adapt quickly to dynamic working conditions, and ensure that the system can operate efficiently and stably under various working conditions.

[0135] Although embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. An air source heat pump system, characterized in that, include: First compressor (1), second compressor (2), first heat exchanger (4), second heat exchanger (5), third heat exchanger (6), throttling assembly (8) and flash evaporator (3); A connecting valve assembly (7) is provided at the outlet end of the first compressor (1). The first compressor (1) is connected to the first heat exchanger (4), the second heat exchanger (5) and the third heat exchanger (6) respectively through the connecting valve assembly (7). In a single-stage cycle, the first refrigerant flows out from the first compressor (1), flows through the first heat exchanger (4), the throttling component (8) and the second heat exchanger (5) and flows back into the first compressor (1). The first heat exchanger (4) is connected to the flash evaporator (3) to form a water system circulation loop. The first refrigerant exchanges heat with water in the first heat exchanger (4). In a two-stage circulation state, the first refrigerant flows out from the first compressor (1), flows through the third heat exchanger (6), the throttling component (8), and the second heat exchanger (5) and flows back into the first compressor (1); the second refrigerant flows out from the second compressor (2), flows through the first heat exchanger (4) and the third heat exchanger (6) and flows back into the second compressor (2), and the first refrigerant and the second refrigerant exchange heat in the third heat exchanger (6); the first heat exchanger (4) is connected to the flash evaporator (3) to form a water system circulation loop; the first refrigerant exchanges heat with water in the first heat exchanger (4); The controller is communicatively connected to the connecting valve group (7) and is adapted to control the opening direction of the connecting valve group (7) to control the air source heat pump system to switch between a single-stage circulation state and a two-stage circulation state.

2. The air source heat pump system according to claim 1, characterized in that, The single-stage cycle state includes a first heating cycle state and a cooling cycle state; In the first heating cycle state, the first refrigerant flows out from the first compressor (1), flows through the first heat exchanger (4), the throttling component (8) and the second heat exchanger (5) in sequence to return to the first compressor (1); In the refrigeration cycle state, the first refrigerant flows out from the first compressor (1), flows through the second heat exchanger (5), the throttling component (8) and the first heat exchanger (4) in sequence to return to the first compressor (1).

3. The air source heat pump system according to claim 2, characterized in that, The dual-stage circulation state includes a second heating cycle state and a steam cycle state; In the second heating cycle state, the first refrigerant flows out from the first compressor (1), flows through the third heat exchanger (6), the throttling component (8) and the second heat exchanger (5) in sequence and flows back into the first compressor (1); the second refrigerant flows out from the second compressor (2), flows through the first heat exchanger (4) and the third heat exchanger (6) in sequence and flows back into the second compressor (2), and the first refrigerant and the second refrigerant exchange heat in the third heat exchanger (6); The temperature of the hot water prepared under the first heating cycle state is lower than the temperature of the hot water prepared under the second heating cycle state. The system is set with a first threshold. The temperature of the hot water prepared in the first heating cycle state is greater than or equal to the first threshold. The controller is adapted to control the connecting valve group (7) to turn so that the single-stage cycle state is changed to the two-stage cycle state and the system enters the steam cycle state.

4. The air source heat pump system according to claim 3, characterized in that, The connecting valve group (7) includes a first valve body (71) and a second valve body (72) that are both communicatively connected to the controller. The first valve body (71) includes a first valve (711), a second valve (712), a third valve (713), and a fourth valve (714). The second valve body (72) includes a first valve port, a second valve port, and a third valve port. The first valve (711) is connected to the outlet of the first compressor (1), the second valve (712) is connected to the first valve port, the third valve (713) is connected to the first end of the second heat exchanger (5), and the fourth valve (714) is connected to the first inlet end of the first compressor (1). The second valve port is connected to the first heat exchanger (4), and the third valve port is connected to the third heat exchanger (6); The controller is adapted to control the first valve body (71) and the second valve body (72) to turn so that the system is in a single-stage cycle state or a two-stage cycle state.

5. The air source heat pump system according to claim 4, characterized in that, The throttling assembly (8) includes a throttling valve group (81) and an economizer (82). The throttling valve group (81) is provided with a first interface, a second interface, a third interface and a fourth interface. The economizer (82) is provided with a first inlet (821), a second inlet (823), a first outlet (822) and a second outlet (824). The first inlet (821) is connected to the first outlet (822), and the second inlet (823) is connected to the second outlet (824). The first interface is connected to the second end of the second heat exchanger (5), the second interface is connected to the first inlet (821), the third interface is connected to the first heat exchanger (4) and / or the third heat exchanger (6), the fourth interface is connected to the first outlet (822), the second inlet (823) is connected to the second interface through a throttling pipe, and the second outlet (824) is connected to the second air inlet of the first compressor (1).

6. The air source heat pump system according to claim 5, characterized in that, The throttle valve assembly (81) includes: a first check valve (811) and a second check valve (812) connected in series, a third check valve (813) and a fourth check valve (814) connected in series, the first check valve (811) and the second check valve (812) being arranged in opposite directions, the third check valve (813) and the fourth check valve (814) being arranged in opposite directions; the first check valve (811) and the third check valve (813) being arranged in the same direction, the fourth check valve (814) and the second check valve (812) being arranged in the same direction; The first interface is located between the first check valve (811) and the fourth check valve (814), the second interface is located between the first check valve (811) and the second check valve (812), the third interface is located between the second check valve (812) and the third check valve (813), and the fourth interface is located between the third check valve (813) and the fourth check valve (814).

7. The air source heat pump system according to claim 6, characterized in that, The first heat exchanger (4) is provided with a first port (41), a second port (42), a third port (43), a fourth port (44), a fifth port (45), a sixth port (46), a seventh port (47), and an eighth port (48); the first port (41) and the second port (42) are connected inside the first heat exchanger (4), the third port (43) and the fourth port (44) are connected inside the first heat exchanger (4), the fifth port (45) and the sixth port (46) are connected inside the first heat exchanger (4), and the seventh port (47) and the eighth port (48) are connected inside the first heat exchanger (4); The third heat exchanger (6) includes a ninth port (61), a tenth port (62), an eleventh port (63) and a twelfth port (64). The ninth port (61) and the tenth port (62) are connected within the third heat exchanger (6), and the eleventh port (63) and the twelfth port (64) are connected within the third heat exchanger (6). The first port (41) is connected to the second valve port, the second port (42) is connected to the tenth port (62); the third port (43) and the eleventh port (63) are connected, the fourth port (44) is connected to the outlet of the second compressor (2); the fifth port (45) and the seventh port (47) are both connected to the circulation inlet of the flash evaporator (3), the sixth port (46) and the eighth port (48) are both connected to the circulation outlet of the flash evaporator (3), the ninth port (61) is connected to the third valve port, and the twelfth port (64) is connected to the air inlet of the second compressor (2); A first solenoid valve (10) is provided between the fifth port (45) and the circulating water inlet, and a second solenoid valve (11) is provided between the seventh port (47) and the circulating water inlet. Both the first solenoid valve (10) and the second solenoid valve (11) are communicatively connected to the controller. In a single-stage cycle state, the controller controls the first solenoid valve (10) to close and the second solenoid valve (11) to open; In the dual-stage cycle state, the controller controls the first solenoid valve (10) to open and the second solenoid valve (11) to close.

8. The air source heat pump system according to claim 3, characterized in that, The top of the flash evaporator (3) is provided with an exhaust port for connecting to a steam pipe. A third solenoid valve is provided on the steam pipe. A pressure detection device is provided inside the flash evaporator (3). The pressure detection device is adapted to detect the pressure parameters inside the flash evaporator (3) and feed them back to the controller. The controller controls the opening and closing of the third solenoid valve according to the pressure parameters.

9. The air source heat pump system according to claim 3, characterized in that, It also includes a fan (9), which is communicatively connected to the controller. The fan (9) is positioned opposite to the second heat exchanger (5). In the first heating cycle state, the second heating cycle state, and the steam cycle state, the controller controls the fan (9) to start.

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