Air source heat pump system

Abstract

The utility model discloses an air source heat pump system which comprises a compressor, an outdoor side heat exchanger, at least one indoor unit, a first throttling device and a heat exchanger. The outdoor heat exchanger comprises a first refrigerant port and a second refrigerant port, the indoor unit comprises a third refrigerant port and a fourth refrigerant port, the heat exchanger comprises a fifth refrigerant port, a sixth refrigerant port, a seventh refrigerant port and an eighth refrigerant port, and the fifth refrigerant port and the sixth refrigerant port are communicated to form an enthalpy increasing main path. One end of the first throttling device is connected to a pipeline between the third refrigerant port and the fifth refrigerant port, and the other end of the first throttling device is communicated with the eighth refrigerant port through the seventh refrigerant port to form an enthalpy increasing auxiliary path. The first refrigerant port is connected with an outlet of the compressor, the sixth refrigerant port is connected with the second refrigerant port, and the fourth refrigerant port and the eighth refrigerant port are connected with an inlet of the compressor. The heat exchanger and the first throttling device are arranged at the outlet of the outdoor heat exchanger, so that the temperature of the refrigerant entering the indoor unit is lower, and the refrigerating effect in summer is improved.

Description

Technical Field

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

[0002] Air source heat pump HVAC equipment generally has both cooling and heating functions in summer and winter. However, the stability of the equipment's function is highly dependent on the ambient temperature, whether it is cooling or heating. This is because the essence of air source heat pumps is to transfer heat between indoors and outdoors. In cold weather, the equipment cannot reliably absorb heat from the external environment, while in hot weather, there may be insufficient subcooling of the refrigerant. Utility Model Content

[0003] The technical problem to be solved by this utility model is to address at least one defect in the related technologies mentioned in the background: the air source heat pump equipment of the related technologies has the problem of insufficient subcooling of the refrigerant in hot weather, and to provide an air source heat pump system.

[0004] The technical solution adopted by this utility model to solve its technical problem is: to construct an air source heat pump system, including:

[0005] The compressor is used to compress refrigerant;

[0006] An outdoor heat exchanger, the outdoor heat exchanger including a first refrigerant port and a second refrigerant port, the first refrigerant port being connected to the second refrigerant port;

[0007] At least one indoor unit, the indoor unit including a third refrigerant port and a fourth refrigerant port, the third refrigerant port being connected to the fourth refrigerant port;

[0008] First throttling device; and,

[0009] A heat exchanger includes a fifth refrigerant port, a sixth refrigerant port, a seventh refrigerant port, and an eighth refrigerant port; the fifth refrigerant port and the sixth refrigerant port are connected to form an enthalpy-increasing main path; one end of a first throttling device is connected to the pipeline between the third refrigerant port and the fifth refrigerant port, and the other end of the first throttling device is connected to the eighth refrigerant port via the seventh refrigerant port to form an enthalpy-increasing auxiliary path;

[0010] The first refrigerant port is connected to the outlet of the compressor, the sixth refrigerant port is connected to the second refrigerant port, the eighth refrigerant port is connected to the inlet of the compressor, and the fourth refrigerant port is connected to the inlet of the compressor.

[0011] In some embodiments, the compressor outlet is also connected to the fourth refrigerant port, and the first refrigerant port is also connected to the compressor inlet;

[0012] The air source heat pump system also includes:

[0013] The first switching valve and the second switching valve, the eighth refrigerant port is connected to the compressor inlet via the first switching valve, and the other end of the eighth refrigerant port is connected to the compressor enthalpy-increasing port via the second switching valve.

[0014] In some embodiments, the air source heat pump system further includes:

[0015] A heat recovery heat exchanger is used to realize heat exchange between refrigerant and heat storage medium for heat storage. The heat recovery heat exchanger includes a first refrigerant inlet and a first refrigerant outlet, and the first refrigerant inlet and the first refrigerant outlet are connected.

[0016] The compressor outlet is connected to the first refrigerant inlet, and the first refrigerant outlet is connected to the first refrigerant port, the fourth refrigerant port, and the sixth refrigerant port.

[0017] In some embodiments, under the cooling and total heat recovery domestic hot water production mode, the refrigerant exiting the compressor outlet passes through the first refrigerant inlet, the first refrigerant outlet, and the enthalpy-increasing main path, then splits into two paths: one path returns to the compressor inlet via the third and fourth refrigerant ports, and the other path returns to the compressor inlet via the enthalpy-increasing auxiliary path and the first switching valve; simultaneously, all the heat of the refrigerant is exchanged in the heat recovery heat exchanger.

[0018] In the cooling and waste heat recovery mode for domestic hot water production, the refrigerant exits from the compressor outlet and, after passing through the first refrigerant inlet, the first refrigerant outlet, the first refrigerant port, the second refrigerant port, and the enthalpy-increasing main path, splits into two paths. One path returns to the compressor inlet via the third and fourth refrigerant ports, while the other path returns to the compressor inlet via the enthalpy-increasing auxiliary path and the first switching valve. Simultaneously, some of the heat from the refrigerant is exchanged in the heat recovery heat exchanger.

[0019] In the heating and domestic hot water mode, the refrigerant exits from the compressor outlet and splits into two paths after passing through the first refrigerant inlet, the first refrigerant outlet, the fourth refrigerant port, and the third refrigerant port. One path passes through the enthalpy-increasing main path, the second refrigerant port, and the first refrigerant port before returning to the compressor inlet. The other path passes through the enthalpy-increasing auxiliary path and the second switching valve before returning to the compressor's enthalpy-increasing port. Simultaneously, some of the refrigerant's heat is exchanged in the heat recovery heat exchanger.

[0020] In some embodiments, the air source heat pump system further includes:

[0021] A high-pressure gas-liquid separator includes a second refrigerant inlet, a second refrigerant outlet, and a third refrigerant outlet. The second refrigerant inlet is connected to both the second and third refrigerant outlets. The second refrigerant outlet is used to output gaseous refrigerant after gas-liquid separation, and the third refrigerant outlet is used to output liquid refrigerant after gas-liquid separation.

[0022] The first refrigerant outlet is connected to the second refrigerant inlet, the second refrigerant outlet is connected to the first refrigerant port and the fourth refrigerant port respectively, and the third refrigerant outlet is connected to the sixth refrigerant port.

[0023] In some embodiments, the air source heat pump system further includes:

[0024] The third switching valve connects one outlet of the compressor to the first refrigerant inlet, and the other outlet of the compressor is connected to both the first refrigerant port and the fourth refrigerant port.

[0025] In some embodiments, the air source heat pump system further includes:

[0026] The first reversing valve connects the second refrigerant outlet to the first refrigerant port and the fourth refrigerant port, respectively.

[0027] In some embodiments, the air source heat pump system further includes:

[0028] The second throttling device connects the third refrigerant outlet to the sixth refrigerant port.

[0029] In some embodiments, the air source heat pump system further includes:

[0030] A third throttling device is provided for each indoor unit, and the third refrigerant port is connected to the fifth refrigerant port and one end of the first throttling device via the third throttling device.

[0031] In some embodiments, the air source heat pump system further includes at least two indoor units, gas pipes, and liquid pipes;

[0032] In each of the indoor units, the fourth refrigerant port is connected to the corresponding branch port in the gas pipe, and the third refrigerant port is connected to the corresponding branch port in the liquid pipe.

[0033] The main interface end of the liquid pipe is connected to the fifth refrigerant port and one end of the first throttling device, respectively;

[0034] The main inlet of the air pipe is connected to the outlet and inlet of the compressor, respectively.

[0035] By implementing this utility model, the following beneficial effects can be achieved:

[0036] This utility model's air source heat pump system, by installing the heat exchanger and the first throttling device at the outlet of the outdoor heat exchanger, allows the refrigerant from the outdoor heat exchanger to enter the indoor unit via one path through the enthalpy-increasing main path (i.e., the sixth and fifth refrigerant ports), and another path through the enthalpy-increasing auxiliary path (i.e., the first throttling device, the seventh and eighth refrigerant ports) to enter the compressor inlet. After being throttled and cooled by the first throttling device in the enthalpy-increasing auxiliary path, the refrigerant can more efficiently absorb heat from the refrigerant in the enthalpy-increasing main path in the heat exchanger. After absorbing heat, the refrigerant vaporizes and enters the compressor inlet. At the same time, the subcooling degree of the refrigerant after releasing heat through the enthalpy-increasing main path is increased, resulting in a lower temperature of the refrigerant entering the indoor unit, thereby improving the cooling effect in summer. Attached Figure Description

[0037] The present invention will be further described below with reference to the accompanying drawings and embodiments. In the accompanying drawings:

[0038] Figure 1 This is a schematic diagram of the air source heat pump system of this utility model;

[0039] Figure 2 This is a schematic diagram of the refrigerant flow direction in the air source heat pump system of this utility model, which produces hot water through a total heat recovery mode while cooling.

[0040] Figure 3 This is a schematic diagram of the flow direction of the first refrigerant in the air source heat pump system of this utility model, which produces hot water through waste heat recovery while cooling.

[0041] Figure 4 This is a schematic diagram of the flow direction of the second refrigerant in the air source heat pump system of this utility model, which produces hot water through waste heat recovery while cooling.

[0042] Figure 5 This is a schematic diagram of the flow direction of the first refrigerant in the air source heat pump system of this utility model, which produces hot water while heating.

[0043] Figure 6 This is a schematic diagram of the flow direction of the second refrigerant in the air source heat pump system of this utility model, which produces hot water while heating.

[0044] Figure 7 This is a schematic diagram of the refrigerant flow direction in the air source heat pump system of this utility model when it is purely preparing hot water;

[0045] Figure 8 This is a schematic diagram of the refrigerant flow direction during cooling in the air source heat pump system of this utility model;

[0046] Figure 9 This is a schematic diagram of the refrigerant flow direction during heating in the air source heat pump system of this utility model. Detailed Implementation

[0047] To provide a clearer understanding of the technical features, objectives, and effects of this utility model, the specific embodiments of this utility model will now be described in detail with reference to the accompanying drawings.

[0048] It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0049] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "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," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0050] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "connected," "linked," "located in," and "located in" 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 a chemical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between 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] It should be noted that the connections between ports, between ports and components, or between components described below are only physical structural connections and do not uniquely define the connectivity or refrigerant flow relationship.

[0052] like Figure 1As shown, some embodiments of this utility model disclose an air source heat pump system, including: a compressor 11, an outdoor heat exchanger 12, at least one indoor unit 13, a first throttling device 14, and a heat exchanger 15. It is understood that the at least one unit can be one, two, three, or any number of units. The specific details of this air source heat pump system are as follows:

[0053] The compressor 11 is used to compress the refrigerant. The outdoor heat exchanger 12 is used to realize heat exchange between the refrigerant and the outside air. The outdoor heat exchanger 12 includes a first refrigerant port 121 and a second refrigerant port 122, which are connected to each other. The indoor unit 13 is used to realize heat exchange between the refrigerant and the indoor air. The indoor unit 13 includes a third refrigerant port 131 and a fourth refrigerant port 132, which are connected to each other.

[0054] The heat exchanger 15 includes a fifth refrigerant port 151, a sixth refrigerant port 152, a seventh refrigerant port 153, and an eighth refrigerant port 154. The fifth refrigerant port 151 and the sixth refrigerant port 152 are connected to form an enthalpy-increasing main path. One end of the first throttling device 14 is connected to the pipeline between the third refrigerant port 131 and the fifth refrigerant port 151, and the other end of the first throttling device 14 is connected to the eighth refrigerant port 154 via the seventh refrigerant port 153 to form an enthalpy-increasing auxiliary path.

[0055] Specifically, the first refrigerant port 121 is connected to the outlet of the compressor 11, the sixth refrigerant port 152 is connected to the second refrigerant port 122, the eighth refrigerant port 154 is connected to the inlet of the compressor 11, and the fourth refrigerant port 132 is connected to the inlet of the compressor 11.

[0056] In this embodiment, the air source heat pump system uses a heat exchanger 15 and a first throttling device 14 installed at the outlet of the outdoor heat exchanger 12. This allows the refrigerant from the outdoor heat exchanger 12 to enter the indoor unit 13 via the enthalpy-increasing main path (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151) and the compressor 11 via the enthalpy-increasing auxiliary path (i.e., the first throttling device 14, the seventh refrigerant port 153, and the eighth refrigerant port 154). After the refrigerant is throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary path, it can more efficiently absorb heat from the refrigerant in the enthalpy-increasing main path in the heat exchanger 15. After absorbing heat, the refrigerant vaporizes and enters the compressor 11. At the same time, the subcooling of the refrigerant after releasing heat in the enthalpy-increasing main path is increased, resulting in a lower temperature of the refrigerant entering the indoor unit 13, thereby improving the cooling effect in summer.

[0057] For example, the outdoor heat exchanger 12 is a finned heat exchanger, and the indoor unit 13 is a ducted air conditioner, which includes an indoor heat exchanger (such as a finned heat exchanger) and a fan. The first throttling device 14 is an electronic expansion valve or a thermal expansion valve. The finned heat exchanger, the ducted air conditioner, the electronic expansion valve, and the thermal expansion valve mentioned here are just examples and are not intended to limit this application. They can also be other types.

[0058] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes: a first switching valve 16, and the eighth refrigerant port 154 is connected to the inlet of the compressor 11 via the first switching valve 16.

[0059] In some embodiments, such as Figure 1 As shown, the outlet of the compressor 11 is also connected to the fourth refrigerant port 132, and the first refrigerant port 121 is also connected to the inlet of the compressor 11.

[0060] The air source heat pump system further includes: a second switching valve 17, one of the eighth refrigerant ports 154 being connected to the inlet of the compressor 11 via the first switching valve 16, and the other of the eighth refrigerant ports 154 being connected to the enthalpy-increasing port 111 of the compressor 11 via the second switching valve 17.

[0061] For example, the first switching valve 16 and the second switching valve 17 are solenoid valves. The solenoid valve here is only an example and is not intended to limit this application. Other valves may also be used.

[0062] In this embodiment, the air source heat pump system, by setting the heat exchanger 15 and the first throttling device 14 at the outlet of the indoor unit 13, allows the refrigerant from the indoor unit 13 to enter the outdoor heat exchanger 12 via the enthalpy-increasing main path (i.e., the fifth refrigerant port 151 and the sixth refrigerant port 152), and via the enthalpy-increasing auxiliary path (i.e., the first throttling device 14, the seventh refrigerant port 153 and the eighth refrigerant port 154) to enter the enthalpy-increasing port 111 of the compressor 11. After the refrigerant is throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary path, it can more efficiently absorb the heat from the refrigerant in the enthalpy-increasing main path in the heat exchanger 15. After absorbing heat, the refrigerant vaporizes and enters the enthalpy-increasing port 111 of the compressor 11, thereby improving the performance of the compressor 11. Meanwhile, the subcooling of the refrigerant after the heat release through the enthalpy-increasing main circuit is increased, and the temperature of the refrigerant entering the outdoor heat exchanger 12 is lower. Especially in cold winters, the temperature of the refrigerant can be lower than the outdoor temperature, thereby improving the heat absorption performance of the outdoor heat exchanger 12 in low-temperature environments and enhancing the subsequent heating effect.

[0063] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a heat recovery heat exchanger 18. The heat recovery heat exchanger 18 is used to achieve heat exchange between the refrigerant and the heat storage medium for heat storage. In some embodiments, it is used to achieve heat exchange between the refrigerant and water to produce domestic hot water. In other embodiments, the heat recovery heat exchanger 18 is a heat storage device with heat storage material. The heat recovery heat exchanger 18 includes a first refrigerant inlet 181 and a first refrigerant outlet 182, which are connected. For example, the heat recovery heat exchanger 18 is a shell-and-tube heat exchanger. The shell-and-tube heat exchanger described here is merely an example and is not intended to limit this application; other types are also possible.

[0064] The compressor 11 is connected to the first refrigerant inlet 181, and the first refrigerant outlet 182 is connected to the first refrigerant port 121, the fourth refrigerant port 132 and the sixth refrigerant port 152 respectively.

[0065] In some embodiments, such as Figure 1 As shown, the heat recovery heat exchanger 18 further includes a first water inlet 183 and a first water outlet 184, with the first water inlet 183 and the first water outlet 184 connected together. The air source heat pump system further includes a domestic water tank 19, which includes a cold water inlet 191, a first water outlet 192, a first water return outlet 193, and a hot water outlet 194. The first water outlet 192 is connected to the first water inlet 183, and the first water outlet 184 is connected to the first water return outlet 193.

[0066] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes: a first water pump 20, which is installed in the inlet pipe (i.e., the pipe connecting the first outlet 192 and the first water inlet 183) or the outlet pipe (i.e., the pipe connecting the first water outlet 184 and the first return water inlet 193) of the heat recovery heat exchanger 18. The first water pump 20 is used to provide power for the water circulation between the heat recovery heat exchanger 18 and the domestic water tank 19.

[0067] In some embodiments, such as Figure 1 As shown, the heat recovery heat exchanger 18, the domestic water tank 19, and the first water pump 20 can be integrated into a domestic hot water module, which can be assembled by the user according to actual needs.

[0068] In some embodiments, under the cooling and total heat recovery domestic hot water production mode, the refrigerant exiting the compressor 11 passes through the first refrigerant inlet 181, the first refrigerant outlet 182, and the enthalpy-increasing main path and then splits into two paths. One path returns to the compressor 11 inlet via the third refrigerant port 131 and the fourth refrigerant port 132, while the other path returns to the compressor 11 inlet via the enthalpy-increasing auxiliary path and the first switching valve 16. Simultaneously, all the heat of the refrigerant is exchanged in the heat recovery heat exchanger 18.

[0069] In the cooling and waste heat recovery mode for domestic hot water production, the refrigerant exits from the compressor 11 and passes through the first refrigerant inlet 181, the first refrigerant outlet 182, the first refrigerant port 121, the second refrigerant port 122, and the enthalpy-increasing main path before splitting into two paths. One path returns to the compressor 11 inlet via the third refrigerant port 131 and the fourth refrigerant port 132, while the other path returns to the compressor 11 inlet via the enthalpy-increasing auxiliary path and the first switching valve 16. Simultaneously, some of the heat from the refrigerant is exchanged in the heat recovery heat exchanger 18.

[0070] In the heating and domestic hot water mode, the refrigerant exits from the compressor 11 and passes through the first refrigerant inlet 181, the first refrigerant outlet 182, the fourth refrigerant port 132, and the third refrigerant port 131 before splitting into two paths. One path passes through the enthalpy-increasing main path, the second refrigerant port 122, and the first refrigerant port 121 before returning to the compressor 11 inlet. The other path passes through the enthalpy-increasing auxiliary path and the second switching valve 17 before returning to the enthalpy-increasing port 111 of the compressor 11. Simultaneously, some of the heat from the refrigerant is exchanged in the heat recovery heat exchanger 18.

[0071] In cooling mode, the refrigerant exits from the compressor 11 and splits into two paths after passing through the first refrigerant port 121, the second refrigerant port 122, and the enthalpy-increasing main path. One path returns to the inlet of the compressor 11 via the third refrigerant port 131 and the fourth refrigerant port 132, while the other path returns to the inlet of the compressor 11 via the enthalpy-increasing auxiliary path and the first switching valve 16.

[0072] In heating mode, the refrigerant exits from the compressor 11 and splits into two paths after passing through the fourth refrigerant port 132 and the third refrigerant port 131. One path passes through the enthalpy-increasing main path, the second refrigerant port 122 and the first refrigerant port 121 and returns to the inlet of the compressor 11. The other path passes through the enthalpy-increasing auxiliary path and the second switching valve 17 and returns to the enthalpy-increasing port 111 of the compressor 11.

[0073] It should be noted that "all the heat is exchanged in the heat recovery heat exchanger 18" means that the refrigerant is completely formed into liquid refrigerant after heat exchange in the heat recovery heat exchanger 18, while "part of the heat is exchanged in the heat recovery heat exchanger 18" means that the refrigerant is formed into gaseous refrigerant after heat exchange in the heat recovery heat exchanger 18.

[0074] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a high-pressure gas-liquid separator 21. The high-pressure gas-liquid separator 21 includes a second refrigerant inlet 211, a second refrigerant outlet 212, and a third refrigerant outlet 213. The second refrigerant inlet 211 is connected to both the second refrigerant outlet 212 and the third refrigerant outlet 213. The second refrigerant outlet 212 is used to output gaseous refrigerant after gas-liquid separation, and the third refrigerant outlet 213 is used to output liquid refrigerant after gas-liquid separation.

[0075] The first refrigerant outlet 182 is connected to the second refrigerant inlet 211, the second refrigerant outlet 212 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 respectively, and the third refrigerant outlet 213 is connected to the sixth refrigerant port 152.

[0076] When the heat pump system includes the heat recovery heat exchanger 18, the system has multiple operating modes (see below for details). The high-pressure gas-liquid separator 21 can realize the automatic flow direction of refrigerant when switching between modes (mainly the cooling and total heat recovery domestic hot water mode and the cooling and waste heat recovery domestic hot water mode), thereby improving the stability of the system.

[0077] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a third switching valve 22. One outlet of the compressor 11 is connected to the first refrigerant inlet 181 via the third switching valve 22, and the other outlet of the compressor 11 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 respectively. When hot water needs to be prepared, the third switching valve 22 can be opened. For example, the third switching valve 22 is a two-way valve. This two-way valve is merely an example and is not intended to limit the scope of this application; other types are also possible.

[0078] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes: a first reversing valve 23, the second refrigerant outlet 212 being connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the first reversing valve 23, and another outlet of the compressor 11 being connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the first reversing valve 23.

[0079] The first reversing valve 23 includes a first valve port 231, a second valve port 232, and a third valve port 233. The first valve port 231 is connected to the second refrigerant outlet 212, the second valve port 232 is connected to both the first refrigerant port 121 and the fourth refrigerant port 132, and the third valve port 233 is connected to the outlet of the compressor 11. For example, the first reversing valve 23 may be a three-way valve. This three-way valve is merely an example and is not intended to limit the scope of this application; other valves may also be used.

[0080] When in the cooling and waste heat recovery domestic hot water production mode and the heating and domestic hot water production mode, the first valve port 231 is connected to the second valve port 232, that is, the second refrigerant outlet 212 is connected to the first refrigerant port 121 or the fourth refrigerant port 132.

[0081] In cooling and heating modes, the third valve port 233 is connected to the second valve port 232, meaning the outlet of the compressor 11 is connected to either the first refrigerant port 121 or the fourth refrigerant port 132. Understandably, when it is necessary to regulate the amount of refrigerant entering the heat recovery heat exchanger 18 in cooling and waste heat recovery for domestic hot water production, or in heating and domestic hot water production, the third valve port 233 can also be connected to the second valve port 232.

[0082] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes: a second reversing valve 24, wherein the outlet of the compressor 11 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the second reversing valve 24, the inlet of the compressor 11 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the second reversing valve 24, and the first refrigerant outlet 182 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the second reversing valve 24.

[0083] Specifically, the outlet of the compressor 11 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the first reversing valve 23 and the second reversing valve 24, respectively. The first refrigerant outlet 182 is connected to the first refrigerant port 121 and the fourth refrigerant port 132 via the second refrigerant inlet 211, the second refrigerant outlet 212, the first reversing valve 23, and the second reversing valve 24, respectively.

[0084] The second reversing valve 24 includes a fourth valve port 241, a fifth valve port 242, a sixth valve port 243, and a seventh valve port 244. The fourth valve port 241 is connected to the compressor 11 (specifically, the second valve port 232 of the first reversing valve 23), the fifth valve port 242 is connected to the first refrigerant port 121, the sixth valve port 243 is connected to the inlet of the compressor 11, and the seventh valve port 244 is connected to the fourth refrigerant port 132. For example, the second reversing valve 24 is a four-way valve. The four-way valve mentioned here is only an example and is not intended to limit this application; other valves are also possible.

[0085] When in the cooling and total heat recovery domestic hot water mode, the seventh valve port 244 is connected to the sixth valve port 243.

[0086] When in the cooling and waste heat recovery domestic hot water mode and in the cooling mode, the fourth valve port 241 is connected to the fifth valve port 242, and the seventh valve port 244 is connected to the sixth valve port 243.

[0087] When in heating plus domestic hot water mode and in heating mode, the fourth valve port 241 is connected to the seventh valve port 244, and the fifth valve port 242 is connected to the sixth valve port 243.

[0088] When in pure hot water mode, the fifth valve port 242 is connected to the sixth valve port 243.

[0089] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a second throttling device 25, through which the third refrigerant outlet 213 is connected to the sixth refrigerant port 152. For example, the second throttling device 25 may be an electronic expansion valve or a thermal expansion valve. The electronic expansion valve and the thermal expansion valve mentioned here are merely examples and are not intended to limit this application; other types are also possible.

[0090] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a fourth throttling device 30, through which the second refrigerant port 122 is connected to the sixth refrigerant port 152. For example, the fourth throttling device 30 is an electronic expansion valve or a thermal expansion valve. The electronic expansion valve and the thermal expansion valve mentioned here are merely examples and are not intended to limit this application; other types are also possible.

[0091] The temperature of the refrigerant entering the outdoor heat exchanger 12 can be further reduced by the fourth throttling device 30.

[0092] Furthermore, the air source heat pump system also includes a one-way valve 31. One path of the second refrigerant port 122 is connected to the sixth refrigerant port 152 via the fourth throttling device 30, and the other path of the second refrigerant port 122 is connected to the sixth refrigerant port 152 via the one-way valve 31. The one-way valve 31 is oriented towards the sixth refrigerant port 152. It should be noted that the orientation of the one-way valve 31 refers to the direction of refrigerant flow, not its spatial orientation.

[0093] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a low-pressure gas-liquid separator 27, which is used to separate gaseous refrigerant and liquid refrigerant. The low-pressure gas-liquid separator 27 is located at the inlet end of the compressor 11. The eighth refrigerant port 154 is connected to the inlet of the low-pressure gas-liquid separator 27, and the outlet of the low-pressure gas-liquid separator 27 is connected to the inlet of the compressor 11.

[0094] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes an oil separator 28 and an oil return pipe 29. The oil separator 28 is located at the outlet end of the compressor 11. The oil separator 28 is used to separate the lubricating oil from the compressor 11 mixed in the refrigerant and return it to the compressor 11 through the oil return pipe 29.

[0095] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a third throttling device 26 corresponding to each indoor unit 13. The third refrigerant port 131 is connected to the fifth refrigerant port 151 and one end of the first throttling device 14 via the third throttling device 26. For example, the third throttling device 26 is an electronic expansion valve or a thermal expansion valve. The electronic expansion valve and the thermal expansion valve mentioned here are merely examples and are not intended to limit this application; other types are also possible.

[0096] In this embodiment, the subcooling of the refrigerant after the heat release through the enthalpy-increasing main circuit is improved, and the temperature of the refrigerant entering the indoor unit 13 is lower, thereby reducing the throttling noise of the third throttling device 26 during summer cooling.

[0097] In some embodiments, such as Figure 1 As shown, the air source heat pump system also includes a fresh air module (not shown in the figure), which is provided for each indoor unit 13 and is used to introduce fresh outdoor air and exhaust stale indoor air.

[0098] In some embodiments, such as Figure 1As shown, the air source heat pump system further includes at least two indoor units 13, a gas pipe 32, and a liquid pipe 33. In each indoor unit 13, the fourth refrigerant port 132 is connected to the corresponding branch port in the gas pipe 32, and the third refrigerant port 131 is connected to the corresponding branch port in the liquid pipe 33. The main port of the liquid pipe 33 is connected to the fifth refrigerant port 151 and one end of the first throttling device 14, respectively. The main port of the gas pipe 32 (specifically, the main port of the gas pipe 32 is connected to the outlet and inlet of the compressor 11 via the second reversing valve 24), respectively.

[0099] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes: a fourth switching valve 34, a fifth switching valve 35, a sixth switching valve 36, and a seventh switching valve 37. The fourth switching valve 34 is located on the pipeline between the third switching valve 22 and the first refrigerant inlet 181. The fifth switching valve 35 is located on the pipeline between the first refrigerant outlet 182 and the second refrigerant inlet 211. One end of the sixth switching valve 36 is connected to the fifth refrigerant port 151 and one end of the first throttling device 14, and the other end of the sixth switching valve 36 is connected to the main interface end of the liquid pipe 33. The seventh switching valve 37 is located on the pipeline between the main interface end of the gas pipe 32 and the second reversing valve 24 (specifically, the seventh valve port 244 of the second reversing valve).

[0100] For example, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36 and the seventh switching valve 37 are shut-off valves. The shut-off valves mentioned here are just examples and are not intended to limit this application. They can also be other types.

[0101] In some embodiments, such as Figure 1 As shown, the compressor 11, the outdoor heat exchanger 12, the first throttling device 14, the heat exchanger 15, the first switching valve 16, the second switching valve 17, the high-pressure gas-liquid separator 21, the third switching valve 22, the first reversing valve 23, the second reversing valve 24, the second throttling device 25, the fourth throttling device 30, the low-pressure gas-liquid separator 27, the oil separator 28, the oil return pipe 29, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are all integrated into the outdoor unit. It can be understood that at least one of the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 can be located inside or on the outer surface of the outdoor unit.

[0102] In some embodiments, such as Figure 1As shown, the air source heat pump system further includes: at least one heat exchanger 38, which is used to realize heat exchange between the refrigerant and the water in the terminal 40. The heat exchanger 38 includes a ninth refrigerant port 381 and a tenth refrigerant port 382, ​​which are connected to each other. The ninth refrigerant port 381 is connected to the corresponding branch end in the gas pipe 32, and the tenth refrigerant port 382 is connected to the corresponding branch end in the liquid pipe 33. It can be understood that at least one can be one, two, three, or any number.

[0103] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a fifth throttling device 39, which is used to throttle and cool the refrigerant. The tenth refrigerant port 382 is connected to the corresponding branch port in the liquid pipe 33 via the fifth throttling device 39. For example, the fifth throttling device 39 can be an electronic expansion valve or a thermostatic expansion valve. These examples are merely illustrative and not intended to limit the scope of this application; other types are also possible.

[0104] In some embodiments, such as Figure 1 As shown, the heat exchanger 38 further includes a second water inlet 383 and a second water outlet 384, with the second water inlet 383 and the second water outlet 384 connected. The air source heat pump system further includes a terminal 40, which includes a second water outlet 401 and a second water return outlet 402. The second water outlet 401 is connected to the second water inlet 383, and the second water outlet 384 is connected to the second water return outlet 402. For example, the terminal 40 may be a ground pipe, achieving underfloor heating or cooling effects through heat exchange with the heat exchanger 38. If there are multiple ground pipes, a manifold can also be installed at the terminal. The ground pipe mentioned here is merely an example and is not intended to limit this application; other types are also possible.

[0105] In some embodiments, such as Figure 1 As shown, the air source heat pump system further includes a second water pump 41, which is installed in the inlet pipe (i.e., the pipe connecting the second outlet 401 and the second water inlet 383) or the outlet pipe (i.e., the pipe connecting the second water outlet 384 and the second return water inlet 402) of the terminal 40. The second water pump 41 is used to provide power for the water circulation between the heat exchanger 38 and the terminal 40.

[0106] In some embodiments, such as Figure 1As shown, the heat exchanger 38, the fifth throttling device 39, and the second water pump 41 can be integrated into a hydraulic module, which can be installed on the gas pipe 32 and the liquid pipe 33 according to the user's needs. Furthermore, the indoor unit 13 and the hydraulic module can operate independently or simultaneously.

[0107] Completely, in some embodiments, such as Figure 1 As shown, the connection relationships between the components in the air source heat pump system are as follows:

[0108] One outlet of the compressor 11 is connected to the first refrigerant inlet 181 via the third switching valve 22 and the fourth switching valve 34. The other outlet of the compressor 11 is connected to the third valve port 233 of the first reversing valve 23. The first refrigerant outlet 182 is connected to the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 via the fifth switching valve 35. The second refrigerant outlet 212 of the high-pressure gas-liquid separator 21 is connected to the first valve port 231 of the first reversing valve 23. The third refrigerant outlet 213 of the high-pressure gas-liquid separator 21 is connected to the sixth refrigerant port 152 of the heat exchanger 15 via the second throttling device 25. The second valve port 232 of the first reversing valve 23 is connected to the fourth valve port 241 of the second reversing valve 24. The fifth valve port 242 of the second reversing valve 24 is connected to the first refrigerant port 121 of the outdoor heat exchanger 12. The sixth port 243 of the second reversing valve 24 is connected to the inlet of the compressor 11 via the low-pressure gas-liquid separator 27. The seventh port 244 of the second reversing valve 24 is connected to the main interface of the gas pipe 32 via the seventh switching valve 37. The main interface of the liquid pipe 33 is connected to the fifth refrigerant port 151 of the heat exchanger 15 via the sixth switching valve 36, and another path of the main interface of the liquid pipe 33 is connected to the seventh refrigerant port 153 of the heat exchanger 15 via the first throttling device 14. The sixth refrigerant port 152 of the heat exchanger 15 is connected to the second refrigerant port 122 of the outdoor heat exchanger 12 via the fourth throttling device 30, and the other end of the sixth refrigerant port 152 is connected to the second refrigerant port 122 of the outdoor heat exchanger 12 via the one-way valve 31, with the one-way valve 31 oriented towards the sixth refrigerant port 152 of the heat exchanger 15. The eighth refrigerant port 154 of the heat exchanger 15 is connected to the inlet of the low-pressure gas-liquid separator 27 via the first switching valve 16, and the other end of the eighth refrigerant port 154 is connected to the enthalpy-increasing port 111 of the compressor 11 via the second switching valve 17, with the outlet of the low-pressure gas-liquid separator 27 connected to the inlet of the compressor 11.

[0109] The first outlet 192 of the domestic water tank 19 is connected to the first water inlet 183 of the heat recovery heat exchanger 18 via the first water pump 20, and the first water outlet 184 of the heat recovery heat exchanger 18 is connected to the first return water inlet 193 of the domestic water tank 19.

[0110] The fourth refrigerant port 132 of the indoor unit 13 is connected to the corresponding branch end in the gas pipe 32, and the third refrigerant port 131 of the indoor unit 13 is connected to the corresponding branch end in the liquid pipe 33 via the third throttling device 26.

[0111] The ninth refrigerant port 381 of the heat exchanger 38 is connected to the corresponding branch port in the gas pipe 32, and the tenth refrigerant port 382 of the heat exchanger 38 is connected to the corresponding branch port in the liquid pipe 33 via the fifth throttling device 39. The second water outlet 401 of the terminal 40 is connected to the second water inlet 383 of the heat exchanger 38 via the second water pump 41, and the second water outlet 384 of the heat exchanger 38 is connected to the second water return port 402 of the terminal 40.

[0112] Under different circumstances, the air source heat pump system will be connected to different valve ports. The following will use... Figure 1 The diagram illustrates the refrigerant flow direction for each mode of the air source heat pump system. It should be noted that components not explicitly marked as "on" are considered off, as detailed below:

[0113] like Figure 2As shown, in the cooling and total heat recovery domestic hot water mode, the second throttling device 25, the third throttling device 26, the fifth throttling device 39, the first switching valve 16, the third switching valve 22, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are open. The first valve port 231 of the first reversing valve 23 is connected to or not connected to the second valve port 232. The seventh valve port 244 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when hot water needs to be prepared quickly in cooling mode, the high-temperature gaseous refrigerant output from the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switch valve 22 and the fourth switch valve 34. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, and becomes a medium-temperature liquid refrigerant after preparing hot water. The medium-temperature liquid refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 through the fifth switch valve 35, and undergoes further gas-liquid separation in the high-pressure gas-liquid separator 21 to ensure that the refrigerant output from the third refrigerant outlet 213 is pure liquid. The medium-temperature liquid refrigerant output from the third refrigerant outlet 213 is throttled and cooled by the second throttling device 25, becoming a lower-temperature liquid refrigerant, and then enters the enthalpy-increasing main circuit (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151). One path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 via the sixth switching valve 36. Another path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit (i.e.... The first throttling device 14, the seventh refrigerant port 153, and the sixth refrigerant port 152) allow the low-temperature liquid refrigerant to be throttled and cooled in the enthalpy-increasing auxiliary circuit. After this cooling process, the refrigerant can absorb heat from the main enthalpy-increasing circuit more efficiently in the heat exchanger 15, becoming a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the inlet of the compressor 11 after passing through the first switching valve 16 and the low-pressure gas-liquid separator 27. The low-temperature liquid refrigerant in the enthalpy-increasing main circuit is cooled down by heat exchange and becomes an even lower-temperature liquid refrigerant. The low-temperature liquid refrigerant enters the third throttling device 26 in the liquid pipe 33. After being throttled and cooled by the third throttling device 26, it becomes an even lower-temperature liquid refrigerant and then enters the third refrigerant port 131 of the indoor unit 13. The low-temperature liquid refrigerant exchanges heat with the indoor air in the indoor unit 13. After absorbing the heat from the indoor air, the low-temperature liquid refrigerant evaporates and becomes a low-temperature gaseous refrigerant. The indoor unit 13 blows out cold air, and the low-temperature gaseous refrigerant output from the fourth refrigerant port 132 of the indoor unit 13 enters the gas pipe 32.Furthermore, the low-temperature liquid refrigerant enters the fifth throttling device 39 within the liquid pipe 33. After being throttled and cooled by the fifth throttling device 39, it becomes an even lower-temperature liquid refrigerant, which then enters the tenth refrigerant port 382 of the heat exchanger 38. In the heat exchanger 38, the low-temperature liquid refrigerant exchanges heat with the water in the terminal 40. The low-temperature liquid refrigerant absorbs heat from the water and evaporates into low-temperature gaseous refrigerant, turning the water in the terminal 40 into cold water. The low-temperature gaseous refrigerant output from the ninth refrigerant port 381 of the heat exchanger 38 enters the gas pipe 32. The low-temperature gaseous refrigerant output from the gas pipe 32 passes through the seventh switching valve 37, the seventh valve port 244 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle.

[0114] The heat recovery heat exchanger 18 is connected to the domestic water tank 19, thereby recovering and utilizing all the condensation heat originally used for heat exchange with the air in the outdoor heat exchanger 12 during cooling. This avoids heat waste caused by heat exchange between the outdoor heat exchanger 12 and the air. The recovered heat is then exchanged with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, quickly producing hot water, improving energy efficiency and increasing the speed of hot water production. Furthermore, by configuring the heat exchanger 38 and the terminal 40, ground cooling and other effects can be achieved simultaneously, further improving energy efficiency.

[0115] like Figure 3As shown, when the domestic hot water reaches a certain temperature, it can be switched to a cooling and waste heat recovery domestic hot water mode. In the cooling and waste heat recovery domestic hot water mode, the third throttling device 26, the fifth throttling device 39, the first switching valve 16, the third switching valve 22, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are opened. The first valve port 231 of the first reversing valve 23 is connected to the second valve port 232. The fourth valve port 241 of the second reversing valve 24 is connected to the fifth valve port 242. The seventh valve port 244 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when hot water needs to be prepared in cooling mode, the high-temperature gaseous refrigerant output from the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switch valve 22 and the fourth switch valve 34. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, and becomes a medium-temperature gaseous refrigerant after preparing hot water. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 through the fifth switch valve 35, and undergoes further gas-liquid separation in the high-pressure gas-liquid separator 21 to ensure that the refrigerant output from the second refrigerant outlet 212 is pure gas. The medium-temperature gaseous refrigerant output from the second refrigerant outlet 212 enters the first refrigerant port 121 of the outdoor heat exchanger 12 after passing through the first valve port 231 and the second valve port 232 of the first reversing valve 23 and the fourth valve port 241 and the fifth valve port 242 of the second reversing valve 24. The medium-temperature gaseous refrigerant condenses and releases heat in the outdoor heat exchanger 12, becoming a medium-temperature liquid refrigerant. The medium-temperature liquid refrigerant output from the second refrigerant port 122 of the outdoor heat exchanger 12 enters the enthalpy-increasing main circuit (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151) through the one-way valve 31. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switching valve 36. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153, and the sixth refrigerant port 152) through another circuit. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the medium-temperature liquid refrigerant can absorb the refrigerant heat from the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the inlet of the compressor 11 after passing through the first switching valve 16 and the low-pressure gas-liquid separator 27.The medium-temperature liquid refrigerant in the enthalpy-increasing main circuit is cooled down by heat exchange and becomes a lower-temperature liquid refrigerant. One path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switch valve 36. Another path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit. The medium-temperature or low-temperature liquid refrigerant enters the third throttling device 26 in the liquid pipe 33. After being throttled and cooled by the third throttling device 26, it becomes a lower-temperature liquid refrigerant and then enters the third refrigerant port 131 of the indoor unit 13. The low-temperature liquid refrigerant exchanges heat with the indoor air in the indoor unit 13. After absorbing heat from the indoor air, the low-temperature liquid refrigerant evaporates and becomes a low-temperature gaseous refrigerant. The indoor unit 13 blows out cold air. The low-temperature gaseous refrigerant output from the fourth refrigerant port 132 of the indoor unit 13 enters the gas pipe 32. Furthermore, the medium-temperature or low-temperature liquid refrigerant enters the fifth throttling device 39 within the liquid pipe 33. After being throttled and cooled by the fifth throttling device 39, it becomes an even lower-temperature liquid refrigerant, which then enters the tenth refrigerant port 382 of the heat exchanger 38. The low-temperature liquid refrigerant exchanges heat with the water in the terminal 40 within the heat exchanger 38. The low-temperature liquid refrigerant absorbs heat from the water and evaporates into a low-temperature gaseous refrigerant, turning the water in the terminal 40 into cold water. The low-temperature gaseous refrigerant output from the ninth refrigerant port 381 of the heat exchanger 38 enters the gas pipe 32. The low-temperature gaseous refrigerant output from the gas pipe 32 passes through the seventh switching valve 37, the seventh valve port 244 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle.

[0116] The heat recovery heat exchanger 18 is connected to the domestic water tank 19, thereby recovering at least a portion of the condensation heat originally used for heat exchange with the air in the outdoor heat exchanger 12 during cooling. This avoids heat waste due to heat exchange between the outdoor heat exchanger 12 and the air. The recovered heat is exchanged with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, quickly producing hot water, improving energy efficiency and increasing the speed of hot water production. Furthermore, by configuring the heat exchanger 38 and the terminal 40, ground cooling and other effects can be achieved simultaneously, further improving energy efficiency.

[0117] Specifically, Figure 3 and Figure 2 The difference in the illustrated embodiment is that, Figure 3 In order to recover and reuse at least a portion of the condensation heat originally used by the outdoor heat exchanger 12 for heat exchange with the air, Figure 2 In order to recover and utilize all the condensation heat originally used by the outdoor heat exchanger 12 for heat exchange with the air.

[0118] like Figure 4As shown, in the cooling and waste heat recovery domestic hot water production mode, the third throttling device 26, the fifth throttling device 39, the first switching valve 16, the third switching valve 22, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are opened. The second valve port 232 of the first reversing valve 23 is connected to the first valve port 231 and the third valve port 233. The fourth valve port 241 of the second reversing valve 24 is connected to the fifth valve port 242. The seventh valve port 244 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when hot water needs to be prepared in cooling mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switching valve 22 and the fourth switching valve 34. The high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the first refrigerant port 121 of the outdoor heat exchanger 12 after passing through the third valve port 233 and the second valve port 232 of the first reversing valve 23 and the fourth valve port 241 and the fifth valve port 242 of the second reversing valve 24. High-temperature gaseous refrigerant exchanges heat with water in the domestic water tank 19 in the heat recovery heat exchanger 18 to produce hot water, which then becomes medium-temperature gaseous refrigerant. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 via the fifth switching valve 35, where further gas-liquid separation is performed to ensure that the refrigerant output from the second refrigerant outlet 212 is pure gas. The medium-temperature gaseous refrigerant output from the second refrigerant outlet 212 enters the first refrigerant port 121 of the outdoor heat exchanger 12 after passing through the first valve port 231 and the second valve port 232 of the first reversing valve 23 and the fourth valve port 241 and the fifth valve port 242 of the second reversing valve 24. The medium-temperature gaseous refrigerant condenses and releases heat in the outdoor heat exchanger 12, becoming medium-temperature liquid refrigerant. The medium-temperature liquid refrigerant output from the second refrigerant port 122 of the outdoor heat exchanger 12 enters the enthalpy-increasing main circuit (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151) through the one-way valve 31. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switching valve 36. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153, and the sixth refrigerant port 152) through another circuit. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the medium-temperature liquid refrigerant can absorb the refrigerant heat from the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the inlet of the compressor 11 after passing through the first switching valve 16 and the low-pressure gas-liquid separator 27.The medium-temperature liquid refrigerant in the enthalpy-increasing main circuit is cooled down by heat exchange and becomes a lower-temperature liquid refrigerant. One path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switch valve 36. Another path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit. The medium-temperature or low-temperature liquid refrigerant enters the third throttling device 26 in the liquid pipe 33. After being throttled and cooled by the third throttling device 26, it becomes a lower-temperature liquid refrigerant and then enters the third refrigerant port 131 of the indoor unit 13. The low-temperature liquid refrigerant exchanges heat with the indoor air in the indoor unit 13. After absorbing heat from the indoor air, the low-temperature liquid refrigerant evaporates and becomes a low-temperature gaseous refrigerant. The indoor unit 13 blows out cold air. The low-temperature gaseous refrigerant output from the fourth refrigerant port 132 of the indoor unit 13 enters the gas pipe 32. Furthermore, the medium-temperature or low-temperature liquid refrigerant enters the fifth throttling device 39 within the liquid pipe 33. After being throttled and cooled by the fifth throttling device 39, it becomes an even lower-temperature liquid refrigerant, which then enters the tenth refrigerant port 382 of the heat exchanger 38. The low-temperature liquid refrigerant exchanges heat with the water in the terminal 40 within the heat exchanger 38. The low-temperature liquid refrigerant absorbs heat from the water and evaporates into a low-temperature gaseous refrigerant, turning the water in the terminal 40 into cold water. The low-temperature gaseous refrigerant output from the ninth refrigerant port 381 of the heat exchanger 38 enters the gas pipe 32. The low-temperature gaseous refrigerant output from the gas pipe 32 passes through the seventh switching valve 37, the seventh valve port 244 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle.

[0119] Specifically, Figure 4 and Figure 3 The difference in the illustrated embodiment is that, Figure 4 In the illustrated embodiment, an additional refrigerant path enters the outdoor heat exchanger 12 via the third valve port 233 and the second valve port 232 of the first reversing valve 23, and the fourth valve port 241 and the fifth valve port 242 of the second reversing valve 24. This allows for better control of the amount of refrigerant entering the heat recovery heat exchanger 18. Furthermore, the path where the refrigerant from the compressor 11 directly reaches the second reversing valve 24 is more likely to be pure gaseous refrigerant. Pure gaseous refrigerant ensures that the second reversing valve 24 has sufficient pressure differential for reversing, thus reducing pressure loss in the refrigerant pipeline.

[0120] like Figure 5As shown, in the heating and domestic hot water mode, the first throttling device 14, the third throttling device 26, the fourth throttling device 30, the fifth throttling device 39, the second switching valve 17, the third switching valve 22, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are open. The first valve port 231 of the first reversing valve 23 is connected to the second valve port 232. The fourth valve port 241 of the second reversing valve 24 is connected to the seventh valve port 244. The fifth valve port 242 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when hot water needs to be prepared in heating mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switch valve 22 and the fourth switch valve 34. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, and becomes medium-temperature gaseous refrigerant after preparing hot water. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 through the fifth switch valve 35, and undergoes further gas-liquid separation in the high-pressure gas-liquid separator 21 to ensure that the refrigerant output from the second refrigerant outlet 212 is pure gas. The medium-temperature gaseous refrigerant output from the second refrigerant outlet 212 enters the gas pipe 32 via the first valve port 231 and the second valve port 232 of the first reversing valve 23, the fourth valve port 241 and the seventh valve port 244 of the second reversing valve 24, and the seventh switching valve 37. The medium-temperature gaseous refrigerant enters the fourth refrigerant port 132 of the indoor unit 13 within the gas pipe 32. The medium-temperature gaseous refrigerant exchanges heat with the indoor air in the indoor unit 13. After releasing heat into the indoor air, the medium-temperature gaseous refrigerant condenses into medium-temperature liquid refrigerant. The indoor unit 13 blows out hot air. The medium-temperature liquid refrigerant output from the third refrigerant port 131 of the indoor unit 13 is throttled and cooled by the third throttling device 26, becoming low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the third throttling device 26 enters the liquid pipe 33. Furthermore, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 381 of the heat exchanger 38 through the gas pipe 32. After heat exchange with the water in the terminal 40 in the heat exchanger 38, the medium-temperature gaseous refrigerant becomes a medium-temperature liquid refrigerant, while the water in the terminal 40 becomes hot water. The medium-temperature liquid refrigerant output from the tenth refrigerant port 382 of the heat exchanger 38 is throttled and cooled by the fifth throttling device 39, becoming a low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the fifth throttling device 39 enters the liquid pipe 33.The low-temperature liquid refrigerant output from the liquid pipe 33 enters the enthalpy-increasing main circuit (i.e., the fifth refrigerant port 151 and the sixth refrigerant port 152) through the sixth switching valve 36, and enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153 and the sixth refrigerant port 152) through the sixth switching valve 36. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the low-temperature liquid refrigerant can absorb heat from the refrigerant in the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the enthalpy-increasing port 111 of the compressor 11 through the second switching valve 17. The low-temperature liquid refrigerant in the enthalpy-increasing main path, after heat exchange to lower its temperature, becomes an even lower-temperature liquid refrigerant. It then enters the fourth throttling device 30 for further throttling and cooling, becoming an even lower-temperature liquid refrigerant before entering the second refrigerant port 122 of the outdoor heat exchanger 12. In the outdoor heat exchanger 12, the low-temperature liquid refrigerant evaporates and absorbs heat, becoming a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the first refrigerant port 121 of the outdoor heat exchanger 12 passes through the fifth valve port 242 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle. This air-source heat pump system can produce hot water and provide underfloor heating while simultaneously providing heating, thus improving energy efficiency.

[0121] like Figure 6As shown, in the heating and domestic hot water mode, the first throttling device 14, the second throttling device 25, the third throttling device 26, the fourth throttling device 30, the fifth throttling device 39, the second switching valve 17, the third switching valve 22, the fourth switching valve 34, the fifth switching valve 35, the sixth switching valve 36, and the seventh switching valve 37 are open. The second valve port 232 of the first reversing valve 23 is connected to the first valve port 231 and the third valve port 233. The fourth valve port 241 of the second reversing valve 24 is connected to the seventh valve port 244. The fifth valve port 242 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when hot water needs to be prepared in heating mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switching valve 22 and the fourth switching valve 34. The high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the gas pipe 32 through the third valve port 233 and the second valve port 232 of the first reversing valve 23, the fourth valve port 241 and the seventh valve port 244 of the second reversing valve 24, and the seventh switching valve 37. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 19 in the heat recovery heat exchanger 18 to prepare hot water, and then becomes a medium-temperature gaseous refrigerant. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 through the fifth switching valve 35, where it undergoes further gas-liquid separation to ensure that the refrigerant output from the second refrigerant outlet 212 is pure gas. The medium-temperature gaseous refrigerant output from the second refrigerant outlet 212 enters the gas pipe 32 via the first valve port 231 and the second valve port 232 of the first reversing valve 23, the fourth valve port 241 and the seventh valve port 244 of the second reversing valve 24, and the seventh switching valve 37. The medium-temperature gaseous refrigerant enters the fourth refrigerant port 132 of the indoor unit 13 within the gas pipe 32. The medium-temperature gaseous refrigerant exchanges heat with the indoor air in the indoor unit 13. After releasing heat into the indoor air, the medium-temperature gaseous refrigerant condenses into medium-temperature liquid refrigerant. The indoor unit 13 blows out hot air. The medium-temperature liquid refrigerant output from the third refrigerant port 131 of the indoor unit 13 is throttled and cooled by the third throttling device 26, becoming low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the third throttling device 26 enters the liquid pipe 33.Furthermore, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 381 of the heat exchanger 38 through the gas pipe 32. After heat exchange with the water in the terminal 40 in the heat exchanger 38, the medium-temperature gaseous refrigerant becomes a medium-temperature liquid refrigerant, while the water in the terminal 40 becomes hot water. The medium-temperature liquid refrigerant output from the tenth refrigerant port 382 of the heat exchanger 38 is throttled and cooled by the fifth throttling device 39, becoming a low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the fifth throttling device 39 enters the liquid pipe 33. The low-temperature liquid refrigerant output from the liquid pipe 33 enters the enthalpy-increasing main circuit (i.e., the fifth refrigerant port 151 and the sixth refrigerant port 152) through the sixth switching valve 36, and enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153 and the sixth refrigerant port 152) through the sixth switching valve 36. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the low-temperature liquid refrigerant can absorb heat from the refrigerant in the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the enthalpy-increasing port 111 of the compressor 11 through the second switching valve 17. The low-temperature liquid refrigerant in the enthalpy-increasing main circuit is cooled down by heat exchange and becomes an even lower-temperature liquid refrigerant. It then enters the fourth throttling device 30 for throttling and cooling, becoming an even lower-temperature liquid refrigerant. It then enters the second refrigerant port 122 of the outdoor heat exchanger 12. The low-temperature liquid refrigerant evaporates and absorbs heat in the outdoor heat exchanger 12, becoming a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the first refrigerant port 121 of the outdoor heat exchanger 12 passes through the fifth valve port 242 and the sixth valve port 243 of the second reversing valve 24 and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, repeating the cycle.

[0122] Specifically, Figure 6 and Figure 5 The difference in the illustrated embodiment is that, Figure 6 In the illustrated embodiment, an additional path leads from the third valve port 233 and the second valve port 232 of the first reversing valve 23, the fourth valve port 241 and the seventh valve port 244 of the second reversing valve 24, and the sixth switching valve 36 into the gas pipe 32. This allows for better control of the amount of refrigerant entering the heat recovery heat exchanger 18. Furthermore, the path from the compressed refrigerant directly to the second reversing valve 24 ensures that the refrigerant is in a gaseous state. The pure gaseous refrigerant further ensures that the second reversing valve 24 has sufficient pressure differential for reversing, thus minimizing pressure loss in the refrigerant pipeline.

[0123] like Figure 7As shown, in pure hot water mode, the second throttling device 25, the fourth throttling device 30, the third switching valve 22, the fourth switching valve 34 and the fifth switching valve 35 are open, the first valve port 231 of the first reversing valve 23 is connected to or not connected to the second valve port 232, and the fifth valve port 242 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when only hot water needs to be produced, the high-temperature gaseous refrigerant output from the outlet of the compressor 11 enters the first refrigerant inlet 181 of the heat recovery heat exchanger 18 after passing through the third switch valve 22 and the fourth switch valve 34. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 19 in the heat recovery heat exchanger 18, and becomes a medium-temperature liquid refrigerant after producing hot water. The medium-temperature liquid refrigerant output from the first refrigerant outlet 182 of the heat recovery heat exchanger 18 enters the second refrigerant inlet 211 of the high-pressure gas-liquid separator 21 through the fifth switch valve 35, and undergoes further gas-liquid separation in the high-pressure gas-liquid separator 21 to ensure that the refrigerant output from the third refrigerant outlet 213 is pure liquid. The medium-temperature liquid refrigerant output from the third refrigerant outlet 213 is throttled and cooled by the second throttling device 25, becoming a lower-temperature liquid refrigerant. It then enters the fourth throttling device 30 for further throttling and cooling, becoming an even lower-temperature liquid refrigerant. It then enters the second refrigerant port 122 of the outdoor heat exchanger 12. The low-temperature liquid refrigerant evaporates and absorbs heat in the outdoor heat exchanger 12, becoming a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the first refrigerant port 121 of the outdoor heat exchanger 12 passes through the fifth valve port 242 and the sixth valve port 243 of the second reversing valve 24 and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, repeating the cycle.

[0124] like Figure 8As shown, in cooling mode, the first throttling device 14, the third throttling device 26, the fifth throttling device 39, the first switching valve 16, the sixth switching valve 36, and the seventh switching valve 37 are open. The third valve port 233 of the first reversing valve 23 is connected to the second valve port 232, the fourth valve port 241 of the second reversing valve 24 is connected to the fifth valve port 242, and the seventh valve port 244 of the second reversing valve 24 is connected to the sixth valve port 243. That is, during summer cooling, the high-temperature gaseous refrigerant output from the compressor 11 enters the first refrigerant port 121 of the outdoor heat exchanger 12 after passing through the third valve port 233 and the second valve port 232 of the first reversing valve 23, and the fourth valve port 241 and the fifth valve port 242 of the second reversing valve 24. The medium-temperature gaseous refrigerant condenses and releases heat in the outdoor heat exchanger 12, becoming a medium-temperature liquid refrigerant. The medium-temperature liquid refrigerant output from the second refrigerant port 122 of the outdoor heat exchanger 12 enters the enthalpy-increasing main circuit (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151) through the one-way valve 31. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switching valve 36. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153, and the sixth refrigerant port 152) through another circuit. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the medium-temperature liquid refrigerant can absorb the refrigerant heat from the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the inlet of the compressor 11 after passing through the first switching valve 16 and the low-pressure gas-liquid separator 27. The medium-temperature liquid refrigerant in the enthalpy-increasing main circuit is cooled down by heat exchange and becomes a lower-temperature liquid refrigerant. One path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 33 through the sixth switch valve 36. Another path of the low-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the heat exchanger 15 enters the enthalpy-increasing auxiliary circuit. The medium-temperature or low-temperature liquid refrigerant enters the third throttling device 26 in the liquid pipe 33. After being throttled and cooled by the third throttling device 26, it becomes a lower-temperature liquid refrigerant and then enters the third refrigerant port 131 of the indoor unit 13. The low-temperature liquid refrigerant exchanges heat with the indoor air in the indoor unit 13. After absorbing heat from the indoor air, the low-temperature liquid refrigerant evaporates and becomes a low-temperature gaseous refrigerant. The indoor unit 13 blows out cold air. The low-temperature gaseous refrigerant output from the fourth refrigerant port 132 of the indoor unit 13 enters the gas pipe 32.Furthermore, the medium-temperature or low-temperature liquid refrigerant enters the fifth throttling device 39 within the liquid pipe 33. After being throttled and cooled by the fifth throttling device 39, it becomes an even lower-temperature liquid refrigerant, which then enters the tenth refrigerant port 382 of the heat exchanger 38. In the heat exchanger 38, the low-temperature liquid refrigerant exchanges heat with the water in the terminal 40. The low-temperature liquid refrigerant absorbs heat from the water and evaporates into a low-temperature gaseous refrigerant, turning the water in the terminal 40 into cold water. The low-temperature gaseous refrigerant output from the ninth refrigerant port 381 of the heat exchanger 38 enters the gas pipe 32. The low-temperature gaseous refrigerant output from the gas pipe 32 passes through the seventh switching valve 37, the seventh valve port 244 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle. This air-source heat pump system can achieve both cooling and ground cooling effects, improving energy efficiency.

[0125] like Figure 9As shown, in heating mode, the first throttling device 14, the third throttling device 26, the fourth throttling device 30, the fifth throttling device 39, the second switching valve 17, the sixth switching valve 36, and the seventh switching valve 37 are open. The second valve port 232 of the first reversing valve 23 is connected to the third valve port 233. The fourth valve port 241 of the second reversing valve 24 is connected to the seventh valve port 244. The fifth valve port 242 of the second reversing valve 24 is connected to the sixth valve port 243. That is, when heating is required in winter, the high-temperature gaseous refrigerant output from the compressor 11 enters the gas pipe 32 through the third valve port 233 and the second valve port 232 of the first reversing valve 23, the fourth valve port 241 and the seventh valve port 244 of the second reversing valve 24, and the seventh switching valve 37. The medium-temperature gaseous refrigerant enters the fourth refrigerant port 132 of the indoor unit 13 in the gas pipe 32. The medium-temperature gaseous refrigerant exchanges heat with the indoor air in the indoor unit 13. After releasing heat into the indoor air, the medium-temperature gaseous refrigerant condenses into medium-temperature liquid refrigerant. The indoor unit 13 blows out hot air. The medium-temperature liquid refrigerant output from the third refrigerant port 131 of the indoor unit 13 is throttled and cooled by the third throttling device 26 and becomes low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the third throttling device 26 enters the liquid pipe 33. Furthermore, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 381 of the heat exchanger 38 through the gas pipe 32. After heat exchange with the water in the terminal 40 in the heat exchanger 38, the medium-temperature gaseous refrigerant becomes a medium-temperature liquid refrigerant, while the water in the terminal 40 becomes hot water. The medium-temperature liquid refrigerant output from the tenth refrigerant port 382 of the heat exchanger 38 is throttled and cooled by the fifth throttling device 39, becoming a low-temperature liquid refrigerant. Then, the low-temperature liquid refrigerant output from the fifth throttling device 39 enters the liquid pipe 33. The low-temperature liquid refrigerant output from the liquid pipe 33 enters the enthalpy-increasing main circuit (i.e., the fifth refrigerant port 151 and the sixth refrigerant port 152) through the sixth switching valve 36, and enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 14, the seventh refrigerant port 153 and the sixth refrigerant port 152) through the sixth switching valve 36. After being throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary circuit, the low-temperature liquid refrigerant can absorb heat from the refrigerant in the enthalpy-increasing main circuit more efficiently in the heat exchanger 15 and become low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the enthalpy-increasing port 111 of the compressor 11 through the second switching valve 17.The low-temperature liquid refrigerant in the enthalpy-increasing main circuit, after heat exchange to lower its temperature, becomes an even lower-temperature liquid refrigerant. It then enters the fourth throttling device 30 for further throttling and cooling, becoming an even lower-temperature liquid refrigerant before entering the second refrigerant port 122 of the outdoor heat exchanger 12. In the outdoor heat exchanger 12, the low-temperature liquid refrigerant evaporates and absorbs heat, becoming a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the first refrigerant port 121 of the outdoor heat exchanger 12 passes through the fifth valve port 242 and the sixth valve port 243 of the second reversing valve 24, and the low-pressure gas-liquid separator 27 before returning to the inlet of the compressor 11, in a continuous cycle. This air-source heat pump system can achieve effects such as underfloor heating while providing heating, thus improving energy efficiency.

[0126] It should be noted that the terms high, medium, and low temperatures mentioned above are only relative descriptions, and gaseous refrigerant can also refer to a two-phase state of gas and liquid or a gaseous state, which is not limited here.

[0127] By implementing this utility model, the following beneficial effects can be achieved:

[0128] The air source heat pump system of this utility model, by setting the heat exchanger 15 and the first throttling device 14 at the outlet of the outdoor heat exchanger 12, allows the refrigerant from the outdoor heat exchanger 12 to enter the indoor unit 13 through the enthalpy-increasing main path (i.e., the sixth refrigerant port 152 and the fifth refrigerant port 151), and enter the inlet of the compressor 11 through the enthalpy-increasing auxiliary path (i.e., the first throttling device 14, the seventh refrigerant port 153 and the eighth refrigerant port 154). After the refrigerant is throttled and cooled by the first throttling device 14 in the enthalpy-increasing auxiliary path, it can more efficiently absorb the heat from the refrigerant in the enthalpy-increasing main path in the heat exchanger 15. After absorbing heat, the refrigerant vaporizes and enters the inlet of the compressor 11. At the same time, the subcooling degree of the refrigerant after releasing heat through the enthalpy-increasing main path is increased, and the temperature of the refrigerant entering the indoor unit 13 is lower, thereby improving the cooling effect in summer.

[0129] It is understood that the above embodiments only illustrate some implementation methods of this utility model, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can freely combine the above embodiments or technical features without departing from the concept of this utility model, and can also make several modifications and improvements, all of which fall within the protection scope of this utility model. That is, the embodiments described "in some embodiments" can be freely combined with any of the preceding and following embodiments. Therefore, all equivalent transformations and modifications made within the scope of the claims of this utility model should fall within the coverage of the claims of this utility model.

Claims

1. An air source heat pump system, characterized in that, include: The compressor is used to compress refrigerant; An outdoor heat exchanger, the outdoor heat exchanger including a first refrigerant port and a second refrigerant port, the first refrigerant port being connected to the second refrigerant port; At least one indoor unit, the indoor unit including a third refrigerant port and a fourth refrigerant port, the third refrigerant port being connected to the fourth refrigerant port; First throttling device; as well as, A heat exchanger includes a fifth refrigerant port, a sixth refrigerant port, a seventh refrigerant port, and an eighth refrigerant port; the fifth refrigerant port and the sixth refrigerant port are connected to form an enthalpy-increasing main path; one end of a first throttling device is connected to the pipeline between the third refrigerant port and the fifth refrigerant port, and the other end of the first throttling device is connected to the eighth refrigerant port via the seventh refrigerant port to form an enthalpy-increasing auxiliary path; The first refrigerant port is connected to the outlet of the compressor, the sixth refrigerant port is connected to the second refrigerant port, the eighth refrigerant port is connected to the inlet of the compressor, and the fourth refrigerant port is connected to the inlet of the compressor.

2. The air source heat pump system according to claim 1, characterized in that, The compressor outlet is also connected to the fourth refrigerant port, and the first refrigerant port is also connected to the compressor inlet; The air source heat pump system also includes: The first switching valve and the second switching valve, the eighth refrigerant port is connected to the compressor inlet via the first switching valve, and the other end of the eighth refrigerant port is connected to the compressor enthalpy-increasing port via the second switching valve.

3. The air source heat pump system according to claim 2, characterized in that, The air source heat pump system also includes: A heat recovery heat exchanger is used to realize heat exchange between refrigerant and heat storage medium for heat storage. The heat recovery heat exchanger includes a first refrigerant inlet and a first refrigerant outlet, and the first refrigerant inlet and the first refrigerant outlet are connected. The compressor outlet is connected to the first refrigerant inlet, and the first refrigerant outlet is connected to the first refrigerant port, the fourth refrigerant port, and the sixth refrigerant port.

4. The air source heat pump system according to claim 3, characterized in that, In the cooling and total heat recovery domestic hot water mode, the refrigerant exits from the compressor outlet and, after passing through the first refrigerant inlet, the first refrigerant outlet, and the enthalpy-increasing main circuit, splits into two paths. One path returns to the compressor inlet via the third and fourth refrigerant ports, while the other path returns to the compressor inlet via the enthalpy-increasing auxiliary circuit and the first switching valve. Simultaneously, all the heat of the refrigerant is exchanged in the heat recovery heat exchanger. In the cooling and waste heat recovery mode for domestic hot water production, the refrigerant exits from the compressor outlet and, after passing through the first refrigerant inlet, the first refrigerant outlet, the first refrigerant port, the second refrigerant port, and the enthalpy-increasing main path, splits into two paths. One path returns to the compressor inlet via the third and fourth refrigerant ports, while the other path returns to the compressor inlet via the enthalpy-increasing auxiliary path and the first switching valve. Simultaneously, some of the heat from the refrigerant is exchanged in the heat recovery heat exchanger. In the heating and domestic hot water mode, the refrigerant exits from the compressor outlet and splits into two paths after passing through the first refrigerant inlet, the first refrigerant outlet, the fourth refrigerant port, and the third refrigerant port. One path passes through the enthalpy-increasing main path, the second refrigerant port, and the first refrigerant port before returning to the compressor inlet. The other path passes through the enthalpy-increasing auxiliary path and the second switching valve before returning to the compressor's enthalpy-increasing port. Simultaneously, some of the refrigerant's heat is exchanged in the heat recovery heat exchanger.

5. The air source heat pump system according to claim 3, characterized in that, The air source heat pump system also includes: A high-pressure gas-liquid separator includes a second refrigerant inlet, a second refrigerant outlet, and a third refrigerant outlet. The second refrigerant inlet is connected to both the second and third refrigerant outlets. The second refrigerant outlet is used to output gaseous refrigerant after gas-liquid separation, and the third refrigerant outlet is used to output liquid refrigerant after gas-liquid separation. The first refrigerant outlet is connected to the second refrigerant inlet, the second refrigerant outlet is connected to both the first refrigerant port and the fourth refrigerant port, and the third refrigerant outlet is connected to the sixth refrigerant port.

6. The air source heat pump system according to claim 3, characterized in that, The air source heat pump system also includes: The third switching valve connects one outlet of the compressor to the first refrigerant inlet, and the other outlet of the compressor is connected to both the first refrigerant port and the fourth refrigerant port.

7. The air source heat pump system according to claim 5, characterized in that, The air source heat pump system also includes: The first reversing valve connects the second refrigerant outlet to the first refrigerant port and the fourth refrigerant port, respectively.

8. The air source heat pump system according to claim 5, characterized in that, The air source heat pump system also includes: The second throttling device connects the third refrigerant outlet to the sixth refrigerant port.

9. The air source heat pump system according to claim 2, characterized in that, The air source heat pump system also includes: A third throttling device is provided for each indoor unit, and the third refrigerant port is connected to the fifth refrigerant port and one end of the first throttling device via the third throttling device.

10. The air source heat pump system according to claim 2, characterized in that, The air source heat pump system also includes at least two indoor units, gas pipes, and liquid pipes; In each of the indoor units, the fourth refrigerant port is connected to the corresponding branch port in the gas pipe, and the third refrigerant port is connected to the corresponding branch port in the liquid pipe. The main interface end of the liquid pipe is connected to the fifth refrigerant port and one end of the first throttling device, respectively; The main inlet of the air pipe is connected to the outlet and inlet of the compressor, respectively.

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