Heat pump system

Abstract

A heat pump system, comprising a refrigerant loop, and a first water tank and a second water tank which are arranged independent of each other. The refrigerant loop comprises a compressor, a first heat exchanger, a first throttling component, a second heat exchanger, a second throttling component, and a third heat exchanger which are communicated in sequence. The first water tank is communicated with the first heat exchanger, and the second water tank is communicated with the second heat exchanger. The first heat exchanger is configured as one of the following: the first heat exchanger can perform heat exchange between a refrigerant which is provided by the compressor and generates a phase change from a gas phase to a liquid phase and water in the first water tank; and the first heat exchanger can perform heat exchange between a gas-phase refrigerant provided by the compressor and the water in the first water tank.

Description

heat pump system

[0001] This application claims priority to Chinese patent application No. 202420153889.6 filed on January 22, 2024, priority to Chinese patent application No. 202420155142.4 filed on January 22, 2024, and priority to Chinese patent application No. 202410088993.6 filed on January 22, 2024, the entire contents of which are incorporated herein by reference. Technical Field

[0002] The present disclosure relates to the technical field of air conditioning, and in particular to a heat pump system. Background Art

[0003] Heat pump systems can be installed in buildings such as apartments, hotels, office buildings, and residences. Air-source heat pumps (ATW), as energy-efficient and environmentally friendly heat pump systems, are attracting increasing consumer interest. Consumers desire a wider range of ATW outlet water temperatures to meet the needs of different water users connected to the heat pump system. For example, lower outlet water temperatures can be used for fan coil cooling, medium outlet water temperatures can be used for floor heating, and higher outlet water temperatures can be used for heating or providing domestic hot water.

[0004] Summary of the Invention

[0005] The heat pump system proposed in the present disclosure is intended to provide water outlet covering different temperature ranges under the condition of only setting up one compressor, so as to meet the needs of different terminals of the heat pump system.

[0006] The present disclosure provides a heat pump system including a first water tank and a second water tank that are independently arranged from each other.

[0007] The heat pump system further includes a refrigerant circuit including a compressor, a first heat exchanger, a first throttling component, a second heat exchanger, a second throttling component, and a third heat exchanger connected in sequence. The first water tank is connected to the first heat exchanger, and the second water tank is connected to the second heat exchanger.

[0008] The first heat exchanger is connected to the compressor. The first throttle component is disposed between the first heat exchanger and the second heat exchanger. The second throttle component is disposed between the second heat exchanger and the third heat exchanger. A first end of the third heat exchanger is connected to the second throttle component, and a second end of the third heat exchanger is connected to the compressor.

[0009] The first heat exchanger is constructed as one of the following: the first heat exchanger is capable of performing heat exchange between the refrigerant provided by the compressor that produces a phase change from gas phase to liquid phase and the water in the first water tank; and the first heat exchanger is capable of performing one of heat exchange between the gas-phase refrigerant provided by the compressor and the water in the first water tank.

[0010] The present invention can achieve a flexible and wide range of water outlet temperature through one compressor and two water tanks, thereby expanding the range of water outlet temperature of the heat pump system under the condition of using only one compressor, overcoming the limitation of the physical properties of the refrigerant, and increasing the upper limit of the water outlet temperature of the heat pump system. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] FIG1 is a structural diagram of a heat pump system in the related art;

[0012] FIG2 is a block diagram of a heat pump system according to some embodiments;

[0013] FIG3 is a block diagram of a heat pump system according to some embodiments;

[0014] FIG4 is a block diagram of a heat pump system according to some embodiments;

[0015] FIG5 is a block diagram of a heat pump system according to some embodiments;

[0016] FIG6 is a block diagram of a heat pump system according to some embodiments;

[0017] FIG7 is a block diagram of a heat pump system according to some embodiments;

[0018] FIG8 is a block diagram of a heat pump system according to some embodiments;

[0019] FIG9 is a block diagram of a heat pump system according to some embodiments;

[0020] FIG10 is a block diagram of a heat pump system according to some embodiments;

[0021] FIG11 is a block diagram of a heat pump system according to some embodiments;

[0022] FIG12 is a block diagram of a heat pump system according to some embodiments;

[0023] FIG13 is a block diagram of a heat pump system according to some embodiments;

[0024] FIG14 is a schematic diagram of a heat pump system according to some embodiments;

[0025] FIG15 is a circuit block diagram of a heat pump system according to some embodiments;

[0026] FIG16 is a circuit block diagram of a heat pump system according to some embodiments;

[0027] FIG17 is a circuit block diagram of a heat pump system according to some embodiments;

[0028] FIG18 is a circuit block diagram of a heat pump system according to some embodiments;

[0029] FIG19 is a block diagram of a heat pump system according to some embodiments;

[0030] FIG20 is a flow chart of a heat pump system according to some embodiments;

[0031] FIG21 is a flow chart of a heat pump system according to some embodiments;

[0032] FIG22 is a flow chart of a heat pump system according to some embodiments;

[0033] FIG23 is a flow chart of a heat pump system according to some embodiments;

[0034] FIG24 is a flow chart of a heat pump system according to some embodiments;

[0035] FIG25 is a flow chart of a heat pump system according to some embodiments;

[0036] FIG26 is a flow chart of a heat pump system according to some embodiments;

[0037] FIG27 is a flow chart of a heat pump system according to some embodiments;

[0038] FIG28 is a flow chart of a heat pump system according to some embodiments;

[0039] FIG29 is a block diagram of a heat pump system according to some embodiments; and

[0040] FIG30 is a control schematic diagram of a heat pump system according to some embodiments. DETAILED DESCRIPTION

[0041] The following will be combined with the accompanying drawings to clearly and completely describe some embodiments of the present disclosure. Obviously, the embodiments described are only some embodiments of the present disclosure, not all embodiments. Based on the embodiments provided by the present disclosure, all other embodiments obtained by ordinary technicians in this field are within the scope of protection of the present disclosure.

[0042] Unless the context requires otherwise, throughout the specification and claims, the term "comprise" and its other forms, such as the third person singular form "comprises" and the present participle form "comprising", are to be interpreted as open and inclusive, that is, "including, but not limited to". In the description of the specification, the terms "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific example" or "some examples" are intended to indicate that the particular features, structures, materials or characteristics associated with the embodiment or example are included in at least one embodiment or example of the present disclosure. The schematic representation of the above terms does not necessarily refer to the same embodiment or example. In addition, the particular features, structures, materials or characteristics may be included in any one or more embodiments or examples in any appropriate manner.

[0043] In the following, the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.

[0044] When describing some embodiments, the expressions "coupled" and "connected" and their derivatives may be used. The term "connected" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. The term "coupled" indicates that two or more components are in direct physical or electrical contact. The term "coupled" or "communicatively coupled" may also refer to two or more components that are not in direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the contents of this document.

[0045] “At least one of A, B and C” has the same meaning as “at least one of A, B or C” and both include the following combinations of A, B and C: A only, B only, C only, the combination of A and B, the combination of A and C, the combination of B and C, and the combination of A, B and C.

[0046] “A and / or B” includes the following three combinations: A only, B only, and a combination of A and B.

[0047] The use of "adapted to" or "configured to" herein is intended to be open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.

[0048] As used herein, "about," "substantially," or "approximately" includes the stated value and an average value that is within an acceptable range of deviation from the particular value as determined by one of ordinary skill in the art taking into account the measurements in question and the errors associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0049] As used herein, "parallel", "perpendicular", and "equal" include the situations described and situations similar to the situations described, and the range of the similar situations is within an acceptable deviation range, wherein the acceptable deviation range is as determined by a person of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of the specific quantity (i.e., the limitations of the measurement system). For example, "parallel" includes absolute parallelism and approximate parallelism, wherein the acceptable deviation range of approximate parallelism can be, for example, a deviation within 5°; "perpendicular" includes absolute perpendicularity and approximate perpendicularity, wherein the acceptable deviation range of approximate perpendicularity can also be, for example, a deviation within 5°. "Equal" includes absolute equality and approximate equality, wherein the acceptable deviation range of approximate equality can be, for example, that the difference between the two equals is less than or equal to 5% of either one.

[0050] As the global greenhouse effect becomes increasingly serious, the public's requirements for the environmental performance of refrigerants are becoming increasingly higher.

[0051] Typically, heat pump systems use refrigerants such as R410A, difluoromethane (chemical formula CH2F2, abbreviated as R32), and propane (chemical formula CH3CH2CH3, abbreviated as R290).

[0052] R410A refrigerant is a quasi-azeotropic mixture of two elements, primarily hydrogen, fluorine, and carbon (referred to as HFC). It is stable, non-toxic, and offers superior performance. Furthermore, because it contains no chlorine, R410A has an ozone depletion potential (ODP) of 0. This means that R410A does not react with ozone and therefore does not damage the ozone layer. R410A has a global warming potential (GWP) of 2100 (for comparison, CO2 has a GWP of 1), significantly contributing to global warming.

[0053] R32's cooling performance is similar to R410A, but its thermal conductivity is higher. With an ODP of 0 and a GWP of 675, R32 is energy-efficient, environmentally friendly, and non-toxic.

[0054] The natural refrigerant R290 does not contain chlorine atoms in its molecules, so its ODP is 0 and it does not damage the ozone layer. R290 has a GWP of 20 and has a very small impact on the greenhouse effect.

[0055] Due to the physical properties of the refrigerant, the maximum outlet water temperature for heat pump systems using R410A can reach 55°C. For heat pump systems using R32, the maximum outlet water temperature can reach 60°C. For heat pump systems using R290, the maximum outlet water temperature can reach 80°C. Due to the maximum saturation pressure of different refrigerants, further increases in outlet water temperature may trigger the heat pump system's high-pressure protection mechanism.

[0056] If you want to further increase the outlet water temperature, the relevant technology usually uses electric heating to continue heating the water in the water tank. The main disadvantage of electric heating is high energy consumption. Alternatively, a cascade heat recovery system is used. In the cascade heat recovery system, the first-level system uses R410A (critical temperature 72.5°C) or R32 (critical temperature 78.4°C) refrigerant with a relatively low critical temperature, and the second-level system uses tetrafluoroethane (CH2FCF3, abbreviated as R134a, critical temperature 101.1°C) refrigerant with a higher critical temperature. It should be noted that the critical temperature is the highest temperature at which an object changes from gas to liquid.

[0057] Referring to Figure 1, the related art discloses an energy-saving air-conditioning system with dual recovery of sensible heat and latent heat. Under refrigeration conditions, after the refrigerant comes out of the compressor 1, it enters the sensible heat recovery device 8 to heat the hot water. Then the refrigerant flows to the evaporator 9 through the four-way valve 3, and exchanges heat with the heat transfer medium in the latent heat recovery device 8. After the heat transfer medium absorbs heat and evaporates, it enters the compressor 2 11, and is compressed by the compressor 2 11 to become a high-temperature and high-pressure heat transfer medium. The high-temperature and high-pressure heat transfer medium transfers heat to the hot water in the condenser 12 to increase the temperature of the hot water. After the refrigerant flows out of the evaporator 9, it passes through the throttling effect of the throttling device 7 and flows to the indoor heat exchanger 4 for indoor cooling. Finally, the refrigerant returns to the compressor 1 through the gas-liquid separator 2.

[0058] However, using two compressors (compressor 1 and compressor 2 11, refer to FIG1 ) to perform two-stage compression on the refrigerant will significantly increase the complexity and cost of the heat pump system.

[0059] Some embodiments of the present disclosure provide a heat pump system 1000, which includes a compressor and two water tanks. The two water tanks are a first water tank and a second water tank, respectively. The first water tank is connected to a first heat exchanger, and the second water tank is connected to a second heat exchanger. The refrigerant provided by the compressor can use sensible heat or latent heat, or first use latent heat and then use sensible heat to increase the water temperature in the first water tank through the first heat exchanger. The refrigerant provided by the compressor can also exchange heat with water through the second heat exchanger 103 after heat exchange with the first heat exchanger 102 or before heat exchange with the first heat exchanger 102 to increase the water temperature in the second water tank 108, thereby expanding the range of the outlet water temperature of the heat pump system 1000 while using only one compressor, overcoming the limitations of the physical properties of the refrigerant, and increasing the upper limit of the outlet water temperature of the heat pump system 1000.

[0060] It's important to note that sensible heat refers to the amount of heat added or removed that causes a change in a substance's temperature without a phase change. The product of the substance's molar mass, molar heat capacity, and temperature difference is called sensible heat. In other words, the heat required to increase or decrease the temperature of an object without undergoing a chemical or phase change is called sensible heat.

[0061] Latent heat, short for latent heat of phase change, refers to the amount of heat absorbed or released when a substance changes from one phase to another under constant temperature and pressure. This is a characteristic of objects transitioning between solid, liquid, and gas phases, as well as between different solid phases. The latent heat between a solid and a liquid is called the heat of fusion (or solidification), the latent heat between a liquid and a gas is called the heat of vaporization (or condensation), and the latent heat between a solid and a gas is called the heat of sublimation (or condensation).

[0062] The heat pump system provided by some embodiments of the present disclosure is described below.

[0063] In some embodiments of the present disclosure, the heat pump system 1000 may be an air-source heat pump. An air-source heat pump (ASHP, also known as air to water (ATW)) is a heat pump system that uses heat from the air to heat or cool the air or water in a building. Air-source heat pumps can be used for heating and hot water. From a functional perspective, air-source heat pumps offer advantages such as energy conservation and environmental protection.

[0064] In some embodiments, the refrigerant may be R32. R32 has good heat transfer performance and a lower global warming potential (GWP) than traditional hydrochlorofluorocarbon (HCFC) and hydrofluorocarbon (HFC) refrigerants, making it a relatively environmentally friendly refrigerant option.

[0065] Of course, in some embodiments, the refrigerant may also be other refrigerants, such as R410A, R290, etc.

[0066] Due to the varying physical properties of different refrigerants, different refrigerants correspond to different refrigerant reference temperatures, i.e., the upper limit of the water outlet temperature. Taking R32 as an example, the refrigerant reference temperature may be 60°C. Referring to FIG2 , heat pump system 1000 includes a refrigerant circuit 100 . Refrigerant circuit 100 may be a vapor compression refrigerant circuit.

[0067] In some embodiments, the refrigerant circuit 100 includes a compressor 101 configured to compress refrigerant to form a high-temperature and high-pressure gaseous refrigerant.

[0068] In some embodiments, the refrigerant circuit 100 further includes a first heat exchanger 102. A first end of the first heat exchanger 102 is connected to the compressor 101. The first heat exchanger 102 is configured to further transfer the heat provided by the refrigerant in the refrigerant circuit 100 to a target medium (e.g., water).

[0069] In some embodiments, the refrigerant circuit 100 further includes a second heat exchanger 103, a first end of which can be connected to a second end of the first heat exchanger 102. The second heat exchanger 103 is configured to further transfer heat provided by the refrigerant in the refrigerant circuit 100 to a target medium (eg, water).

[0070] In some embodiments, the refrigerant circuit 100 further includes a first throttling component 105 , which is disposed at the second end of the first heat exchanger 102 .

[0071] In some embodiments, the refrigerant circuit 100 further includes a second throttling component 106 , which is disposed at the second end of the second heat exchanger 103 .

[0072] In some embodiments, the first throttling component 105 and the second throttling component 106 may be electronic expansion valves or other forms of throttling components.

[0073] In some embodiments, the refrigerant circuit 100 further includes a third heat exchanger 104, wherein a first end of the third heat exchanger 104 is connected to a second end of the second heat exchanger 103, and a second end of the third heat exchanger 104 is connected to the compressor 101. The third heat exchanger 104 is configured to absorb heat from a heat source medium (e.g., air).

[0074] In some embodiments, a vapor compression refrigerant circuit sequentially connects a compressor 101, a first heat exchanger 102, a second heat exchanger 103, a first throttling component 105, a second throttling component 106, and a third heat exchanger 104 via refrigerant piping to form a refrigeration cycle. Refrigerant flows in the refrigeration cycle.

[0075] 2 , the heat pump system 1000 further includes a first water tank 107 (eg, a first hot water storage tank), which is in communication with the first heat exchanger 102 .

[0076] In some embodiments, the heat pump system 1000 further includes a second water tank 108 (eg, a second hot water storage tank), which is in communication with the second heat exchanger 103 .

[0077] In some embodiments, the first water tank 107 and the second water tank 108 are independently provided. The first water tank 107 and the second water tank 108 can be set to different water outlet temperatures to meet different water needs of users.

[0078] For example, the first water tank 107 is configured to store high-temperature water, and the second water tank 108 is configured to store low-temperature water.

[0079] In some embodiments, the temperature of the high-temperature water provided by the first water tank 107 may be in the range of [50°C, 80°C], and the temperature of the low-temperature water provided by the second water tank 108 may be in the range of [20°C, 60°C].

[0080] In some embodiments, the temperature of the high-temperature water provided by the first water tank 107 may be in the range of [30°C, 80°C], and the temperature of the low-temperature water provided by the second water tank 108 may be in the range of [5°C, 60°C].

[0081] The first heat exchanger 102 is configured to perform heat exchange between the refrigerant provided by the compressor 101 and water, and the water after heat exchange is stored in the first water tank 107 .

[0082] The second heat exchanger 103 is configured to perform heat exchange between the refrigerant passing through the first throttle component 105 and water, or to perform heat exchange between the refrigerant provided by the compressor 101 and water, and the water after heat exchange is stored in the second water tank 108 .

[0083] In some embodiments, the heat pump system 1000 further includes a first loop 109, which can be provided in conjunction with the first water tank 107. The first loop 109 can circulate the water stored in the first water tank 107 as circulating water.

[0084] In some embodiments, the heat pump system 1000 further includes a first water pump 110, which is disposed in the first loop 109. The first water pump 110 can pump water out of the first water tank 107, guide the water in the first loop 109 to flow into the first heat exchanger 102 and participate in the heat cycle of the refrigerant loop 100 to receive heat transferred by the first heat exchanger 102 for heating.

[0085] In some embodiments, the first water pump 110 may be a centrifugal pump.

[0086] In some embodiments, the heat pump system 1000 further includes a first water replenishment pipeline 111 . The first water replenishment pipeline 111 may be provided in conjunction with the first water tank 107 . The first water replenishment pipeline 111 is configured to replenish water into the first water tank 107 .

[0087] In some embodiments, the heat pump system 1000 further includes a first water supply pipeline 113 . The first water supply pipeline 113 may be provided in conjunction with the first water tank 107 . The first water supply pipeline 113 is configured to supply water to a water user terminal.

[0088] In some embodiments, the water terminal connected to first water supply line 113 can be a heating device, that is, a radiator installed along a room wall to dissipate heat through convection and radiation. The water terminal connected to first water supply line 113 can also be a hot water distribution system that further distributes hot water to various locations where hot water is needed, such as bathrooms, kitchens, and restrooms.

[0089] In some embodiments, the heat pump system 1000 further includes a first water replenishment valve 112 . The first water replenishment valve 112 may be disposed in the first water replenishment pipeline 111 . The first water replenishment valve 112 may be operated manually or automatically (eg, opened or closed).

[0090] In some embodiments, the heat pump system 1000 further includes a first water outlet valve 114 . The first water outlet valve 114 may be disposed in the first water supply pipeline 113 . The first water outlet valve 114 may also be operated manually or automatically (eg, opened or closed).

[0091] In some embodiments of the present disclosure, the heat pump system 1000 further includes a first pressure relief valve, which can be provided in conjunction with the first water tank 107. The first pressure relief valve can ensure that the first water tank 107 operates within a preset pressure range.

[0092] Similarly, the heat pump system 1000 further includes a second loop 121, which is provided in conjunction with the second water tank 108. The second loop 121 can circulate the water stored in the second water tank 108 as circulating water.

[0093] The heat pump system 1000 also includes a second water pump 120, which is arranged on the second circuit 121. The second water pump 120 can pump water out of the second water tank 108, guide the water in the second circuit 121 to flow into the second heat exchanger 103, and participate in the thermal cycle of the refrigerant circuit 100 to transfer heat.

[0094] In some embodiments, the second water pump 120 may also be a centrifugal pump.

[0095] In some embodiments, the heat pump system 1000 further includes a second water replenishment pipeline 116 . The second water replenishment pipeline 116 may be provided in conjunction with the second water tank 108 . The second water replenishment pipeline 116 is configured to replenish water into the second water tank 108 .

[0096] Correspondingly, the heat pump system 1000 also includes a second water supply line 118, which can be provided in conjunction with the second water tank 108, and the second water supply line 118 is configured to supply water to a water terminal. The water terminal connected to the second water supply line 118 can be a floor heating device, that is, a device that transfers heat by installing a heating component (such as a water pipe) under the floor of the room. Heat rises from the floor, heating the entire room evenly. The water terminal can also be a water terminal such as a fan coil unit. For example, a fan coil unit uses water supply to heat or cool air and transfers the heated or cooled air to a specific area of ​​the building.

[0097] In some embodiments, the heat pump system 1000 further includes a second water supply valve 117 . The second water supply valve 117 is disposed in the second water supply pipeline 116 . The second water supply valve 117 can be operated manually or automatically (eg, opened or closed).

[0098] In some embodiments, the heat pump system 1000 further includes a second water outlet valve 119, which can be disposed on the second water supply line 118. The second water outlet valve 119 can be operated manually or automatically (eg, opened or closed).

[0099] In some embodiments, the heat pump system 1000 further includes a second pressure relief valve, which can be provided in conjunction with the second water tank 108. The second pressure relief valve can ensure that the second water tank 108 operates within a preset reliable range.

[0100] In some embodiments, first water tank 107 and second water tank 108 can be installed in an indoor environment, such as a machine room or machinery room. This prevents the water tanks from freezing in cold winter months or overheating in extremely hot summer months. Furthermore, first water tank 107 and second water tank 108 can continue to produce hot water during winter while the outdoor heat exchanger is defrosting.

[0101] The first water tank 107 and the second water tank 108 can also be installed in an indoor space such as a basement or laundry room of a house to provide relatively good environmental conditions for the equipment. The first water tank 107 and the second water tank 108 can be made of pressure-resistant and corrosion-resistant materials, such as stainless steel, plastic, etc., to ensure long-term stable operation of the first water tank 107 and the second water tank 108.

[0102] In some embodiments, the first heat exchanger 102 can be a water-fluorine heat exchanger. A water-fluorine heat exchanger is a common term referring to a heat exchanger between a refrigerant and water, and the refrigerant is not limited to Freon. From a structural perspective, the first heat exchanger 102 can be a plate heat exchanger or a shell and tube heat exchanger. For example, when a plate heat exchanger is selected, the first circuit 109 is connected to a flow channel in the plate heat exchanger to allow water to circulate in the flow channel. The refrigerant pipeline in the refrigerant circuit 100 is connected to another flow channel in the plate heat exchanger to allow refrigerant to circulate in the other flow channel.

[0103] Due to the thermal conductivity of the plate heat exchanger, heat can be transferred from the hot side to the cold side, thereby enabling heat exchange between two fluids (e.g., water and refrigerant). For ease of description, in the first heat exchanger 102, the flow channel through which water flows is defined as the first water flow channel, and the flow channel through which the refrigerant flows is defined as the first refrigerant flow channel.

[0104] In some embodiments, second heat exchanger 103 may be a water-fluorine heat exchanger, as defined above. Structurally, second heat exchanger 103 may be a plate heat exchanger or a shell-and-tube heat exchanger. For example, in the case of a plate heat exchanger, second circuit 121 is connected to one flow channel in the plate heat exchanger to allow water to circulate within that flow channel. The refrigerant line in refrigerant circuit 100 is connected to another flow channel in the plate heat exchanger to allow refrigerant to circulate within that other flow channel.

[0105] Due to the thermal conductivity of the plate heat exchanger, heat can be transferred from the hot side to the cold side, thereby enabling heat exchange between two fluids (e.g., water and refrigerant). For ease of description, in the second heat exchanger 103, the flow channel through which water flows is defined as the second water flow channel, and the flow channel through which refrigerant flows is defined as the second refrigerant flow channel.

[0106] Some embodiments of the present disclosure provide a dual sensible and latent heat recovery system, which uses two water-fluorine heat exchangers to recover the sensible and latent heat of the refrigerant. By providing two water tanks, different water temperature ranges can be set to meet the varying water temperature requirements of different user groups. Furthermore, sensible heat recovery can be used to increase the outlet water temperature, avoiding electrical heating and achieving energy savings. The exchange of sensible and latent heat is controlled by a first throttling device, ultimately achieving the different water temperature requirements of the two water tanks.

[0107] In some embodiments, the heat pump system 1000 further includes a fifth sensor 131 (eg, a first outlet water temperature sensor). The fifth sensor 131 is disposed at the outlet of the first water circulation channel and is configured to detect the outlet water temperature of the first water tank 107 .

[0108] In some embodiments, the heat pump system 1000 further includes a seventh sensor 132 (eg, a second outlet water temperature sensor). The seventh sensor 132 is disposed at the outlet of the second water circulation channel and is configured to detect the outlet water temperature of the second water tank 108 .

[0109] In some embodiments, the heat pump system 1000 may further include a fourth sensor 130 (e.g., a first heat exchanger temperature sensor), which is configured to detect the temperature of the first heat exchanger 102. For example, the fourth sensor 130 may be disposed in the first refrigerant circulation channel, such as at the outlet of the first refrigerant circulation channel.

[0110] In some embodiments, the heat pump system 1000 may further include a sixth sensor 132 (e.g., a second heat exchanger temperature sensor), which is configured to detect the temperature of the second heat exchanger 103. For example, the sixth sensor 132 may be disposed in the second refrigerant circulation channel, for example, at the outlet of the second refrigerant circulation channel.

[0111] In some embodiments, the heat pump system 1000 further includes a first sensor 127 (e.g., a first water storage temperature sensor), which is disposed in the first water tank 107. The first sensor 127 is configured to detect the temperature of the water stored in the first water tank 107 (i.e., a first water storage temperature, denoted as T1) and generate a first water storage temperature signal.

[0112] In some embodiments, the heat pump system 1000 further includes a second sensor 128 (e.g., a second water storage temperature sensor). The second sensor 128 is disposed in the second water tank 108. The second sensor 128 is configured to detect the temperature of the water stored in the second water tank 108 (i.e., the second water storage temperature, denoted as T2) and generate a second water storage temperature signal.

[0113] The outdoor fan 135 can guide air to flow and enter the third heat exchanger 104. The third heat exchanger 104 can perform heat exchange with the air guided by the outdoor fan 135, so that the refrigerant flowing in the third heat exchanger 104 undergoes a phase change from a liquid phase to a gas phase, and then flows back to the compressor 101 after the phase change.

[0114] In some embodiments, the heat pump system 1000 further includes an eighth sensor 134 (eg, a third heat exchanger temperature sensor). The eighth sensor 134 is disposed on the third heat exchanger 104 and configured to detect the surface temperature of the third heat exchanger 104 , ie, a coil temperature sensor.

[0115] In some embodiments, the heat pump system 1000 further includes a third sensor 129 (eg, an outdoor temperature sensor) configured to detect an outdoor ambient temperature.

[0116] In some embodiments, the first heat exchanger 102 is configured to perform heat exchange between the refrigerant provided by the compressor 101 and producing a phase change from gas to liquid and water, or the first heat exchanger 102 is also configured to perform heat exchange between the gas-phase refrigerant provided by the compressor 101 and water.

[0117] In some embodiments, the heat pump system 1000 further includes a second branch 122 , which is arranged in parallel with the first throttling component 105 .

[0118] In some embodiments, the heat pump system 1000 further includes a second solenoid valve 123 , which is disposed in the second branch 122 .

[0119] In some embodiments, the first heat exchanger 102 is configured to perform heat exchange between the refrigerant provided by the compressor 101 and undergoing a phase change from gas to liquid and water. The second solenoid valve 123 keeps the second branch 122 closed, directing the refrigerant provided by the compressor 101 and undergoing a phase change from gas to liquid to enter the second heat exchanger 103 after passing through the first throttling component 105. Heat exchange occurs within the second heat exchanger 103 between the refrigerant that has undergone a phase change from gas to liquid and passed through the first throttling component 105 and water.

[0120] In some embodiments, the first heat exchanger 102 is configured to perform heat exchange between the gas-phase refrigerant provided by the compressor 101 and water. The second solenoid valve 123 maintains the second branch 122 open, guiding the gas-phase refrigerant through the second branch 122 and the first throttling component 105 before entering the second heat exchanger 103. Heat exchange between the gas-phase refrigerant and water is performed within the second heat exchanger 103 after passing through the first throttling component 105.

[0121] In some embodiments, the heat pump system 1000 further includes a first branch 124 . A first end of the first branch 124 is connected to the compressor 101 , and a second end of the first branch 124 is connected to the second heat exchanger 103 .

[0122] In some embodiments, the heat pump system 1000 further includes a first solenoid valve 125, which is disposed in the first branch 124. If the first solenoid valve 125 keeps the first branch 124 closed, the first heat exchanger 102 performs heat exchange between the refrigerant provided by the compressor 101, which undergoes a phase change from gas to liquid, and water. Alternatively, the first heat exchanger 102 may perform heat exchange between the gas-phase refrigerant provided by the compressor 101 and water. If the first solenoid valve 125 keeps the first branch 124 open, and the first throttling component 105 and the second solenoid valve 123 are closed, the second heat exchanger 103 performs heat exchange between the refrigerant provided by the compressor 101 and water.

[0123] In some embodiments, the heat pump system 1000 further includes a heating unit 126 . The heating unit 126 may be an electric heater, which may be disposed in the first water tank 107 .

[0124] In principle, the refrigerant cycle of the heat pump system 1000 includes different processes, such as compression, condensation, throttling, and evaporation.

[0125] 14 , the horizontal axis h represents the enthalpy of the refrigerant in kJ / kg, and the vertical axis p represents the pressure of the refrigerant in MPa. The first water tank 107 and the second water tank 108 can absorb the heat of the refrigerant by recovering sensible heat and latent heat separately.

[0126] For example, the first water tank 107 absorbs heat from the refrigerant through sensible heat recovery. In the first heat exchanger 102, the refrigerant remains in a high-temperature, high-pressure gas phase, releasing heat into the first water tank 107. The refrigerant temperature drops from the high temperature at the exhaust port of the compressor 101 and remains above the condensing temperature. The second water tank 108 can absorb heat from the refrigerant through latent heat recovery. In the second heat exchanger 103, the refrigerant transitions from gas to liquid. Although the refrigerant temperature remains unchanged, heat can still be released into the second water tank 108.

[0127] In some embodiments, the heat pump system 1000 further includes a reversing valve 115. Reversing valve 115 is configured to switch between a heating mode and a cooling mode of the heat pump system. For example, reversing valve 115 may be a four-way valve having four openings: port D, port E, port S, and port C. Port D connects to the first throttle component 105, port E connects to the first end of the second heat exchanger 103, port S connects to the compressor 101, and port C connects to the second end of the third heat exchanger 104.

[0128] In some embodiments of the present disclosure, the heat pump system 1000 has four operating states. The four different operating states of the heat pump system 1000 are described one by one below with reference to FIG3 to FIG6 .

[0129] It should be noted that the operating states shown in Figures 3 to 6 are described using the heating mode as an example, i.e., the reversing valve 115 (four-way valve) in the figures maintains communication between port D and port E, and between port S and port C. In Figures 3 to 6, the first water tank 107 can be a high-temperature water tank, the second water tank 108 can be a low-temperature water tank, the refrigerant used in the heat pump system 1000 can be R32, and the refrigerant reference temperature can be 60°C.

[0130] Assuming that the first set water temperature is greater than the refrigerant reference temperature, the first water tank 107 can be heated through the following first working state and second working state.

[0131] Figure 3 illustrates the first operating state of heat pump system 1000. For example, if the first condition is met: the first water storage temperature of first water tank 107 is less than the refrigerant reference temperature (e.g., 60°C), the refrigerant reference temperature is less than the first set water temperature of first water tank 107, and the second water storage temperature is less than the second set water temperature, the first operating state can achieve the first stage of heating of first water tank 107 and second water tank 108. The refrigerant circulation is shown by arrow F1 in Figure 3.

[0132] In the first operating state, the heating unit 126, the first solenoid valve 125, and the second solenoid valve 123 are closed, while the first throttle component 105, the second throttle component 106, the first water pump 110, the second water pump 120, and the outdoor fan 135 are turned on. The refrigerant first passes through the first heat exchanger 102 to heat the water in the first water tank 107, then enters the second heat exchanger 103 through the first throttle component 105 to heat the water in the second water tank 108, thereby heating the water in the first water tank 107 and the second water tank 108.

[0133] In some embodiments, low-temperature, low-pressure refrigerant enters compressor 101, which compresses the low-temperature, low-pressure refrigerant into a high-temperature, high-pressure gaseous refrigerant and discharges it. At this time, because first solenoid valve 125 keeps first branch 124 closed, the gaseous refrigerant discharged from compressor 101 is supplied to first heat exchanger 102.

[0134] The first heat exchanger 102 functions as a condenser, where the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 101 undergoes a phase change. Specifically, the first heat exchanger 102, acting as a condenser, condenses the gaseous refrigerant supplied by the compressor 101 into a liquid phase, releasing the refrigerant's heat into the first water flow channel through the condensation process. The first water pump 110 operates, causing water in the first water tank 107 to flow into the first water flow channel via the first circuit 109. The heat released by the refrigerant raises the water temperature in the first water flow channel, and the heated water then re-enters the first water tank 107 for further heating or use.

[0135] Since the second solenoid valve 123 keeps the second branch 122 closed, the refrigerant flowing out of the first heat exchanger 102 and undergoing a phase change from gas to liquid passes through the first throttle component 105. The first throttle component 105 expands the high-temperature and high-pressure liquid refrigerant condensed in the first heat exchanger 102 into a medium-temperature and medium-pressure liquid refrigerant.

[0136] The medium-temperature, medium-pressure liquid refrigerant enters the second heat exchanger 103. The second water pump 120 operates, causing the water in the second water tank 108 to flow into the second water flow channel via the second circuit 121. The heat dissipated by the refrigerant raises the temperature of the water in the second water flow channel. The heated water then re-enters the second water tank 108 for further heating or use.

[0137] As can be understood, the temperature of the liquid refrigerant in the second refrigerant circulation channel continues to drop, meaning it is subcooled in the second heat exchanger 103. The subcooled refrigerant flows into the second throttle component 106, which expands the subcooled liquid refrigerant in the second heat exchanger 103 into a low-temperature, low-pressure two-phase refrigerant. This low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 now operates as an evaporator. The outdoor fan 135 operates, causing the evaporator to evaporate the expanded refrigerant and return the low-temperature, low-pressure refrigerant to the compressor 101.

[0138] During this process, the first heat exchanger 102 utilizes the latent heat of condensation of the refrigerant to exchange heat with the water in the first water tank 107 to achieve a heating effect, while the second heat exchanger 103 utilizes the sensible heat of the refrigerant to exchange heat with the water in the second water tank 108 to achieve a heating effect. Throughout the entire cycle, the heat pump system 1000 utilizes both the sensible and latent heat of the refrigerant to provide hot water.

[0139] FIG4 illustrates the second operating state of heat pump system 1000. For example, if the second condition is met: the first water temperature of first water tank 107 is greater than the refrigerant reference temperature, the first water temperature of first water tank 107 is less than the first set water temperature, and the second water temperature of second water tank 108 is less than the second set water temperature, the second operating state can be used to achieve a second stage of heating of first water tank 107 and second water tank 108. The refrigerant circulation is shown by arrow F2 in FIG4 .

[0140] In the second operating state, heating unit 126 and first solenoid valve 125 are closed, while second solenoid valve 123, first throttle component 105, second throttle component 106, first water pump 110, second water pump 120, and outdoor fan 135 are opened. The refrigerant first passes through first heat exchanger 102, exchanging heat with the water in first water tank 107. The refrigerant then splits into two paths, passing through first throttle component 105 and second solenoid valve 123, respectively, and enters second heat exchanger 103, exchanging heat with the water in second water tank 108, thereby heating the water in first and second water tanks 107 and 108.

[0141] In some embodiments, low-temperature, low-pressure refrigerant enters compressor 101 , which compresses the low-temperature, low-pressure refrigerant into a high-temperature, high-pressure gaseous refrigerant and discharges it. Because first solenoid valve 125 keeps first branch 124 closed, the discharged gaseous refrigerant flows into first heat exchanger 102 .

[0142] First heat exchanger 102 cools the high-temperature, high-pressure gas-phase refrigerant to a high-pressure, medium-temperature gas-phase refrigerant at a high pressure but above the condensation temperature (this can be achieved by adjusting the frequency of compressor 101). The condensation temperature refers to the temperature at which the refrigerant undergoes a phase change in the condenser, from a gas phase to a liquid phase. Therefore, although the refrigerant in first heat exchanger 102 does not undergo a phase change, it still releases heat into the first water flow channel, thereby raising the water temperature therein.

[0143] Second solenoid valve 123 maintains the second branch 122 in an open state, allowing the high-pressure, medium-temperature gas-phase refrigerant flowing through second branch 122 and first throttle component 105 to remain in its gaseous state. The gas-phase refrigerant enters second heat exchanger 103, which now functions as a condenser. The high-pressure, medium-temperature gas-phase refrigerant undergoes a phase change in second heat exchanger 103. In other words, second heat exchanger 103, acting as a condenser, cools the refrigerant into a high-pressure, medium-temperature liquid-phase refrigerant and releases the refrigerant's heat into the second water flow channel, raising the water temperature therein.

[0144] The second throttle component 106 further expands the liquid-phase refrigerant that undergoes phase change in the second heat exchanger 103 into a low-temperature, low-pressure two-phase refrigerant. This low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 now operates as an evaporator, with the outdoor fan 135 operating. The evaporator evaporates the expanded refrigerant and returns the low-temperature, low-pressure refrigerant to the compressor 101.

[0145] In the entire cycle, the first heat exchanger 102 utilizes the sensible heat of the refrigerant to exchange heat with the water in the first water tank 107, and utilizes the latent heat of the refrigerant to exchange heat with the water in the second water tank 108, thereby achieving a heating effect.

[0146] In some embodiments, during the second phase, the first water tank 107 can recover the refrigerant's heat through pure sensible heat, thereby raising the outlet water temperature. This eliminates the need to reheat the water in the first water tank 107 using electrical heating methods, allowing the water in the first water tank 107 to reach the first set water temperature, thus avoiding energy waste.

[0147] Figure 5 shows the third operating state of heat pump system 1000. For example, if the third condition is met: the first water temperature in first water tank 107 is greater than the first set water temperature, and the water temperature in second water tank 108 is less than the second set water temperature, the third operating state can be used to heat second water tank 108. The refrigerant circulation is shown by arrow F3 in Figure 5.

[0148] In the third working state, the heating part 126 and the first water pump 110 are turned off, and the first solenoid valve 125, the second solenoid valve 123, the first throttling component 105, the second throttling component 106, the second water pump 120, and the outdoor fan 135 are turned on.

[0149] In some embodiments, low-temperature and low-pressure refrigerant enters the compressor 101 , and the compressor 101 compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure gas-phase refrigerant and discharges the compressed refrigerant.

[0150] The first solenoid valve 125 keeps the first branch 124 in a conducting state, and the gas-phase refrigerant discharged from the compressor 101 flows into the second heat exchanger 103 through the first branch 124 .

[0151] Second heat exchanger 103 functions as a condenser. The high-temperature, high-pressure refrigerant discharged from compressor 101 undergoes a phase change in second heat exchanger 103. Specifically, second heat exchanger 103, acting as a condenser, condenses the compressed refrigerant into a liquid phase. This condensation process releases heat from the refrigerant into the second water flow channel, raising the water temperature therein.

[0152] The second throttle component 106 expands the condensed refrigerant into a low-temperature, low-pressure two-phase refrigerant. The low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 now operates as an evaporator, with the outdoor fan 135 operating. The evaporator evaporates the expanded refrigerant and returns the low-temperature, low-pressure refrigerant to the compressor 101.

[0153] In this way, the refrigerant discharged from the compressor 101 enters the second heat exchanger 103 through the first solenoid valve 125 to heat the water in the second water tank 108, which is conducive to quickly increasing the water temperature in the second water tank 108 and improving the heating efficiency of the water in the second water tank 108.

[0154] In some embodiments, in operating state three, the first throttling component 105 can be closed. At this point, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 101 enters the second heat exchanger 103 through the first branch 124 to heat the water in the second water tank 108. This allows the refrigerant to enter the second heat exchanger 103 without undergoing a throttling process, which helps maintain the refrigerant at a high temperature and high pressure.

[0155] In other embodiments, in operating state three, the first throttle component 105 can be in the open state. At this point, the high-temperature, high-pressure gas-phase refrigerant discharged from the compressor 101 can be split into two paths. The first path of refrigerant enters the second heat exchanger 103 via the first branch 124, while the second path of refrigerant enters the second heat exchanger 103 via the first heat exchanger 102 and the first throttle component 105 to heat the water in the second water tank 108. This allows the refrigerant to quickly reach the second heat exchanger 103, increasing the refrigerant flow rate in the second heat exchanger 103.

[0156] FIG6 illustrates the fourth operating state of the heat pump system 1000. For example, if the fourth condition is satisfied: the first water storage temperature of the first water tank 107 has not reached the first set water temperature, but the second water storage temperature of the second water tank 108 has reached the second set water temperature, the first water tank 107 can be heated in the fourth operating state.

[0157] In the fourth operating state, the heating unit 126 and the first water pump 110 are turned on, while the compressor 101, the first solenoid valve 125, the second solenoid valve 123, the second water pump 120, and the outdoor fan 135 are turned off. Thus, the heating unit 126 heats the water in the first water tank 107. This maintains the temperature of the second water tank 108 at the second set water temperature.

[0158] In summary, in some embodiments of the present disclosure, the refrigerant provided by the compressor 101 can utilize sensible heat or latent heat, or first utilize latent heat and then utilize sensible heat to increase the water temperature in the first water tank 107 through the first heat exchanger 102, and can be operated to exchange heat with water through the second heat exchanger 103 after heat exchange with the first heat exchanger 102, or before heat exchange with the first heat exchanger 102, to increase the water temperature in the second water tank 108, thereby achieving the expansion of the outlet water temperature range under the condition of using only one compressor 101, overcoming the limitations of the physical properties of the refrigerant, and increasing the upper limit value of the outlet water temperature of the heat pump system 1000.

[0159] 7 , in other embodiments, a large-caliber, low-pressure-loss electronic expansion valve may be selected to implement the functions of the second solenoid valve 123 and the first throttling component 105 , that is, the first throttling component 105 may be used to implement both throttling and on-off control functions.

[0160] That is, the heat pump system 1000 in FIG. 7 does not include the second branch 122 and the second solenoid valve 123, but instead includes the first throttle component 105, the first branch 124, and the first solenoid valve 125 disposed in the first branch 124. In this case, the first heat exchanger 102 of the heat pump system 1000 is configured to perform heat exchange between the refrigerant provided by the compressor 101 and water, with the heat-exchanged water being stored in the first water tank 107. The second heat exchanger 103 is configured to perform heat exchange between the refrigerant passing through the first throttle component 105 and water, or between the refrigerant provided by the compressor 101 and water, with the heat-exchanged water being stored in the second water tank 108.

[0161] In yet other embodiments, referring to FIG8 , the heat pump system 1000 may include the first throttle component 105 and the second solenoid valve 123 instead of the first solenoid valve 125. In this case, the first heat exchanger 102 of the heat pump system 1000 is configured to exchange heat between the refrigerant provided by the compressor 101 and water, with the heat-exchanged water being stored in the first water tank 107. The second heat exchanger 103 is configured to exchange heat between the refrigerant passing through the first throttle component 105 and water, with the heat-exchanged water being stored in the second water tank 108.

[0162] In yet other embodiments, referring to FIG. 9 , the heat pump system 1000 may also include a first throttling component 105 instead of a first branch. In this case, the first heat exchanger 102 of the heat pump system 1000 is configured to exchange heat between the refrigerant provided by the compressor 101 and water, with the heat-exchanged water stored in a first water tank 107. The second heat exchanger 103 is configured to exchange heat between the refrigerant passing through the first throttling component 105 and water, with the heat-exchanged water stored in a second water tank 108.

[0163] The heating method of the heat pump system 1000 in Figures 7 to 9 can be referred to the description of the working state of the heat pump system in Figures 3 to 6. The heating method of the heat pump system 1000 in Figure 8 will be described below using Figure 8 as an example.

[0164] The four operating states of heat pump system 1000 in FIG8 are described one by one with reference to FIG10 through FIG13 . The operating states shown in FIG10 through FIG13 are based on the heating mode, where reversing valve 115 (a four-way valve) maintains communication between ports D and E, and between ports S and C. First water tank 107 can be a high-temperature water tank, second water tank 108 can be a low-temperature water tank, the refrigerant can be R32, and the refrigerant reference temperature can be 60°C.

[0165] Assuming that the first set water temperature is greater than the refrigerant reference temperature, the heat pump system 1000 can heat the water in the first water tank 107 through the following first working state and second working state.

[0166] Figure 10 illustrates the first operating state of heat pump system 1000. For example, if the first condition is met: the first water temperature of first water tank 107 is less than the refrigerant reference temperature, the refrigerant reference temperature is less than the first water temperature, and the second water temperature of second water tank 108 is less than the second set water temperature, the first operating state can achieve the first stage of heating of first water tank 107 and second water tank 108. The refrigerant circulation is shown by arrow F1 in Figure 10.

[0167] In the first working state, the heating part 126 and the second solenoid valve 123 are closed, and the first throttle component 105, the second throttle component 106, the first water pump 110, the second water pump 120, and the outdoor fan 135 are turned on.

[0168] In some embodiments, low-temperature, low-pressure refrigerant enters the compressor 101 , which compresses the refrigerant into a high-temperature, high-pressure gaseous refrigerant and discharges the compressed gaseous refrigerant. The gaseous refrigerant discharged from the compressor 101 is supplied to the first heat exchanger 102 .

[0169] At this point, the first heat exchanger 102 functions as a condenser. The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 101 undergoes a phase change in the first heat exchanger 102. In other words, the first heat exchanger 102, acting as a condenser, condenses the gaseous refrigerant supplied by the compressor 101 into a liquid phase. The refrigerant's heat is released into the first water flow channel through the condensation process. The first water pump 110 operates, causing water in the first water tank 107 to flow into the first water flow channel via the first circuit 109. The refrigerant dissipates heat, raising the water temperature in the first water flow channel. The heated water then enters the first water tank 107.

[0170] The second solenoid valve 123 keeps the second branch 122 closed, and the refrigerant flowing out of the first heat exchanger 102 and undergoing a phase change from gas to liquid passes through the first throttle component 105. The first throttle component 105 expands the high-temperature and high-pressure liquid refrigerant condensed in the first heat exchanger 102 into a medium-temperature and medium-pressure liquid refrigerant.

[0171] The medium-temperature, medium-pressure liquid refrigerant enters the second heat exchanger 103. The second water pump 120 operates, causing the water in the second water tank 108 to flow into the second water flow channel via the second circuit 121. The refrigerant dissipates heat, raising the temperature of the water in the second water flow channel. The heated water then enters the second water tank 108 again.

[0172] The temperature of the liquid refrigerant continues to drop in the second refrigerant circulation channel, resulting in subcooling in the second heat exchanger 103. The subcooled refrigerant flows into the second throttle component 106, which expands the subcooled liquid refrigerant in the second heat exchanger 103 into a low-temperature, low-pressure two-phase refrigerant. This low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 now operates as an evaporator, with the outdoor fan 135 operating. The evaporator evaporates the expanded refrigerant, returning the low-temperature, low-pressure refrigerant to the compressor 101.

[0173] During this process, the first heat exchanger 102 utilizes the latent heat of condensation of the refrigerant to exchange heat with the water in the first water tank 107 to achieve a heating effect, while the second heat exchanger 103 utilizes the sensible heat of the refrigerant to exchange heat with the water in the second water tank 108 to achieve a heating effect. Throughout the entire cycle, the heat pump system 1000 utilizes both sensible and latent heat to provide hot water.

[0174] Figure 11 shows the second operating state of heat pump system 1000. For example, if the second condition is met: the first water temperature of first water tank 107 is greater than the refrigerant reference temperature, the first water temperature is less than the first set water temperature, and the second water temperature of second water tank 108 is less than the second set water temperature, heating of first water tank 107 and second water tank 108 can be achieved in the second operating state. The refrigerant circulation is shown by arrow F2 in Figure 11.

[0175] In the second working state, the heating part 126 is closed, and the second solenoid valve 123, the first throttle component 105, the second throttle component 106, the first water pump 110, the second water pump 120, and the outdoor fan 135 are opened.

[0176] In some embodiments, low-temperature and low-pressure refrigerant enters the compressor 101 , and the compressor 101 compresses the refrigerant into a high-temperature and high-pressure gas-phase refrigerant and discharges the compressed gas-phase refrigerant.

[0177] The gaseous refrigerant discharged from compressor 101 flows into first heat exchanger 102, which cools the high-temperature, high-pressure gaseous refrigerant to a high-pressure, medium-temperature gaseous refrigerant at a higher temperature than the condensing temperature. The condensing temperature refers to the temperature at which the refrigerant undergoes a phase change in the condenser, from gas to liquid. Although the refrigerant does not undergo a phase change during this process, heat is still released into the first water flow channel, raising the water temperature therein.

[0178] Second solenoid valve 123 maintains the second branch 122 in an open state, allowing the high-pressure, medium-temperature gas-phase refrigerant flowing through second branch 122 and first throttle component 105 to remain in its gaseous state. The gas-phase refrigerant enters second heat exchanger 103, which now functions as a condenser. The high-pressure, medium-temperature gas-phase refrigerant undergoes a phase change in second heat exchanger 103. In other words, second heat exchanger 103, acting as a condenser, cools the refrigerant into a high-pressure, medium-temperature liquid-phase refrigerant and releases the refrigerant's heat into the second water flow channel, raising the water temperature therein.

[0179] The second throttle component 106 further expands the liquid-phase refrigerant that undergoes phase change in the second heat exchanger 103 into a low-temperature, low-pressure two-phase refrigerant. This low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 is now operating in the evaporator mode, with the outdoor fan 135 in operation. The evaporator evaporates the expanded refrigerant and returns the low-temperature, low-pressure refrigerant to the compressor 101.

[0180] In this process, the first heat exchanger 102 utilizes the sensible heat of the refrigerant to exchange heat with the water in the first water tank 107 , and utilizes the latent heat of the refrigerant to exchange heat with the water in the second water tank 108 , thereby achieving a heating effect.

[0181] Figure 12 shows the third operating state of heat pump system 1000. For example, if the third condition is met: the first water temperature of first water tank 107 reaches the first set water temperature, and the second water temperature of second water tank 108 is less than the second set water temperature, the third operating state can be used to heat second water tank 108. The refrigerant circulation is shown by arrow F3 in Figure 12.

[0182] In the third working state, the heating unit 126 and the first water pump 110 are turned off, and the second solenoid valve 123, the first throttling component 105, the second throttling component 106, the second water pump 120, and the outdoor fan 135 are turned on.

[0183] In some embodiments, low-temperature, low-pressure refrigerant enters compressor 101, which compresses it into a high-temperature, high-pressure gas-phase refrigerant and discharges the compressed gas-phase refrigerant. The gas-phase refrigerant then passes through first heat exchanger 102. Since first water pump 110 is stopped at this point, it does not cause significant fluctuations in the water temperature in first water tank 107.

[0184] At this point, first solenoid valve 125 maintains first branch 124 in an open state, allowing the discharged gaseous refrigerant to flow into second heat exchanger 103. Second heat exchanger 103 now functions as a condenser, and the high-temperature, high-pressure refrigerant discharged from compressor 101 undergoes a phase change in second heat exchanger 103. In other words, second heat exchanger 103, acting as a condenser, condenses the compressed refrigerant into a liquid phase. The refrigerant's heat is released into the second water flow channel through the condensation process, raising the water temperature therein.

[0185] The second throttle component 106 expands the condensed refrigerant into a low-temperature, low-pressure two-phase refrigerant. The low-temperature, low-pressure two-phase refrigerant then enters the third heat exchanger 104. The third heat exchanger 104 is now operating in the evaporator mode, with the outdoor fan 135 in operation. The evaporator evaporates the expanded refrigerant and returns the low-temperature, low-pressure refrigerant to the compressor 101.

[0186] In the entire cycle, the heat pump system 1000 heats the second water tank 108 through the latent heat of the refrigerant.

[0187] In some embodiments, referring to FIG. 12 , the first throttle component 105 may be at a maximum opening to ensure that the refrigerant can flow smoothly to the second heat exchanger 103 .

[0188] Referring to Figure 12 , the first heat exchanger 102 in the heat pump system 1000 is configured to allow the gas-phase refrigerant provided by the compressor 101 to flow therethrough. The second heat exchanger 103 is configured to exchange heat between the refrigerant, which has passed through the first throttle component 105 at its maximum opening, and water. The water after heat exchange is stored in the second water tank 108. The third heat exchanger 104 is configured to exchange heat between the refrigerant, which has passed through the second throttle component 106, and a heat source. The refrigerant after heat exchange flows back to the compressor 101. The gas-phase refrigerant provided by the compressor 101 flows through the first heat exchanger 102, and the first water pump 110 stops operating.

[0189] FIG13 illustrates the fourth operating state of the heat pump system 1000. For example, if the fourth condition is satisfied: the first water storage temperature of the first water tank 107 has not reached the first set water level, but the second water storage temperature of the second water tank 108 has reached the second set water temperature, the fourth operating state can be used to heat the first water tank 107.

[0190] In the fourth working state, the heating unit 126 and the first water pump 110 are turned on, and the compressor 101, the first throttle member 105, the second throttle member 106, the second solenoid valve 123, the second water pump 120, and the outdoor fan 135 are turned off. In this way, the water in the first water tank 107 is heated by the heating unit 126.

[0191] In summary, in some embodiments of the present disclosure, the refrigerant provided by the compressor 101 can utilize sensible heat or latent heat, or first utilize latent heat and then utilize sensible heat to increase the water temperature in the first water tank 107 through the first heat exchanger 102, and operationally, the refrigerant can enter the second heat exchanger 103 after passing through the first heat exchanger 102, exchange heat with water through the second heat exchanger 103, and increase the water temperature in the second water tank 108, thereby achieving the expansion of the outlet water temperature range under the condition of using only one compressor 101, overcoming the limitations of the physical properties of the refrigerant, and increasing the upper limit value of the outlet water temperature of the heat pump system 1000.

[0192] In some embodiments, referring to FIG2 , the heat pump system 1000 further includes a controller 20 , which is disposed in an electrical box having good sealing performance and heat dissipation function. The controller 20 may include components such as a processor, a memory, an input / output interface, and a communication interface. The processor may be an application-specific integrated circuit (ASIC), a microprocessor, a general-purpose central processing unit (CPU), or the like. The processor may access the memory to execute instructions or applications stored in the memory to implement related functions, such as adjusting the speed of the motor driving the compressor 101 (i.e., adjusting the frequency of the compressor 101) through a program.

[0193] The instructions or applications stored in the memory are programs disclosed in the relevant technology or programs compiled based on algorithms disclosed in the relevant technology. They are not protected by this disclosure and will not be described in detail here. The storage unit may include volatile memory and / or non-volatile memory. The input / output interface can be connected to the various sensors mentioned above to receive detection values ​​from various sensors. The input / output interface is also connected to devices such as the compressor 101 and the outdoor fan 135 to output control instructions generated by the processor.

[0194] The communication interface can support different wireless communication protocols, such as Wi-Fi, Bluetooth, near-field communication, narrowband Internet of Things (NB-IoT), etc., to communicate with other electronic devices, including but not limited to cloud servers, computers (host computers), smart phones, tablets, intelligent control tools, wearable devices and vehicle-mounted devices, etc.

[0195] The controller 20 may also be a chip or a programmable device, including a complex programmable logic device (CPLD), an erasable programmable logic device (EPLD), or a field programmable gate array (FPGA). The chip may be an integrated circuit (IC).

[0196] 2 , the controller 20 is coupled to the compressor 101 , the first throttling component 105 , the second throttling component 106 , the second solenoid valve 123 , the first solenoid valve 125 , the first water pump 110 , the second water pump 120 , the heating unit 126 , the four-way valve 115 , and the outdoor fan 135 to control the operation of the above components.

[0197] In some embodiments, the heat pump system 1000 further includes a control terminal 30, which is in communication with the controller 20. The control terminal 30 has a user-friendly interface, and the user can operate it through a touch screen, a remote control, or other means. For example, the control terminal 30 allows the user to input a first set water temperature T of the first water tank 107 according to demand. set1 , the second set water temperature T of the second water tank 108 set2 Afterwards, the control terminal 30 may generate a first water tank set water temperature signal according to the first set water temperature, and generate a second water tank set water temperature signal according to the second set water temperature.

[0198] The control terminal 30 can be a centralized controller, a combination of a centralized controller and a wired controller, or a computer, a tablet computer, a smart phone, a wearable device, etc.

[0199] 15 , in some embodiments, the heat pump system 1000 further includes a control circuit 40 .

[0200] In some embodiments of the present disclosure, the control circuit 40 is further configured to control the opening and closing of the first solenoid valve 125 , thereby controlling the on-off state of the first branch 124 .

[0201] 15 , the control circuit 40 is configured to receive a first water tank set water temperature signal, a second water tank set water temperature signal, a first water storage temperature signal, and a second water storage temperature signal, and generate a first drive signal to the first solenoid valve 125, so that the first solenoid valve 125 keeps the first branch 124 closed, so as to perform heat exchange between the refrigerant provided by the compressor 101 and water in the first heat exchanger 102, and the water after heat exchange is stored in the first water tank 107, and perform heat exchange between the refrigerant and water passing through the first throttling component 105 in the second heat exchanger 103, and the water after heat exchange is stored in the second water tank 108.

[0202] For example, when the first stored water temperature is lower than the first set water temperature and the second stored water temperature is lower than the second set water temperature, the control circuit 40 generates a first drive signal to the first solenoid valve 125 to keep the first branch 124 closed. That is, in either the first operating state or the second operating state, the control circuit 40 generates the first drive signal to control the first solenoid valve 125 to close.

[0203] The control circuit 40 can be implemented by a controller. The principle of a processor implementing comparison of digital signals and generating a driving signal is common knowledge and will not be elaborated here.

[0204] The control circuit 40 can also be implemented using a combination of comparators and logic gate circuits. For example, the control circuit 40 includes two comparators. The first water tank set water temperature signal can be connected to the inverting input of one comparator circuit (using an operational amplifier, for example), and the first storage water temperature signal can be connected to the non-inverting input. The second water tank set water temperature signal can be connected to the inverting input of another comparator circuit (using an operational amplifier, for example), and the second storage water temperature signal can be connected to the non-inverting input. The power pins of the comparator circuits can be connected to a power supply.

[0205] The outputs of the two operational amplifiers can be connected to the input of an AND gate circuit. In this way, when the first water storage temperature is lower than the first set water temperature and the second water storage temperature is lower than the second set water temperature, the output of the AND gate circuit can output a level signal (e.g., a low or high level signal), namely, the first drive signal. The first drive signal can further be output to the first solenoid valve 125, causing it to close, thereby keeping the first branch closed.

[0206] 15 , the control circuit 40 is further configured to receive a first water tank set water temperature signal, a second water tank set water temperature signal, a first water storage temperature signal, and a second water storage temperature signal, and generate a second drive signal to the first solenoid valve to keep the first branch conductive, so as to perform heat exchange between the refrigerant provided by the compressor and water in the second heat exchanger, and the water after heat exchange is stored in the second water tank 108 .

[0207] For example, when the first stored water temperature is greater than the first set water temperature and the second stored water temperature is less than the second set water temperature, the control circuit 40 generates a second drive signal to the first solenoid valve 125 to cause the first solenoid valve 125 to maintain the first branch 124 conductive. That is, in the third operating state, the control circuit 40 sends the second drive signal to control the first solenoid valve 125 to open.

[0208] The control circuit 40 can be implemented by a controller. It can also be implemented by comparators and logic gates. For example, the output of the first comparator can indicate whether the first water storage temperature is greater than a first set water temperature, and the output of the second comparator can indicate whether the second water storage temperature is greater than a second set water temperature. The outputs of the two comparators are connected to an AND gate circuit. If the first water storage temperature is greater than the first set water temperature and the second water storage temperature is less than the second set water temperature, the output of the AND gate circuit becomes the second drive signal.

[0209] In some embodiments of the present disclosure, the control circuit 40 is further configured to control the opening and closing of the second solenoid valve 123 , thereby controlling the on-off of the second branch 122 .

[0210] 16 , the control circuit 40 is further configured to: receive a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, a first water storage temperature signal, and a second water storage temperature signal, and generate a third drive signal to the second solenoid valve 123 to keep the second branch 122 closed, so as to perform heat exchange between the refrigerant provided by the compressor 101 and producing a phase change from gas phase to liquid phase and water in the first heat exchanger 102; or receive the reference temperature signal, the first water tank set water temperature signal, the second water tank set water temperature signal, the first water storage temperature signal, and the second water storage temperature signal, and generate a fourth drive signal to the second solenoid valve 123 to keep the second branch 122 open, so as to perform heat exchange between the gas-phase refrigerant provided by the compressor 101 and water in the first heat exchanger 102.

[0211] In some embodiments, the control circuit 40 may generate a third drive signal to the second solenoid valve 123 to keep the second branch 122 closed when the first water storage temperature is lower than the refrigerant reference temperature, the refrigerant reference temperature is lower than the first set water temperature, and the second water storage temperature is lower than the second set water temperature. That is, the control circuit 40 may control the second solenoid valve 123 to be closed in the first working state.

[0212] For example, the control circuit 40 may also generate a fourth drive signal to the second solenoid valve to maintain conduction of the second branch 122 when the first storage water temperature is greater than the refrigerant reference temperature, but less than the first set water temperature, and the second storage water temperature is less than the second set water temperature. The refrigerant reference temperature can be generated by detecting the temperature of a reference heat source via a temperature sensor. That is, the control circuit 40 may control the second solenoid valve 123 to open in the second operating state.

[0213] The control circuit 40 may be implemented by a controller.

[0214] The control circuit 40 can also be implemented using a combination of comparators and logic gates. For example, the output of the first comparator can indicate whether the first water storage temperature is less than the first set water temperature, while the output of the second comparator can indicate whether the second water storage temperature is less than the second set water temperature. These two outputs can be connected to the two inputs of an AND gate circuit. If the first water storage temperature is less than the first set water temperature and the second water storage temperature is less than the second set water temperature, the output of the AND gate circuit becomes the third drive signal, which can be used to activate the second solenoid valve, keeping the second branch 122 closed.

[0215] For example, the output of a third comparator can be used to indicate whether the first stored water temperature is greater than the refrigerant reference temperature. The output of the third comparator and the output of the aforementioned AND gate circuit can be connected to two inputs of another AND gate circuit. If the first stored water temperature is less than the first set water temperature but greater than the refrigerant reference temperature, and the second stored water temperature is less than the second set water temperature, the output of the other AND gate circuit becomes the fourth drive signal. This fourth drive signal can be used to activate the second solenoid valve, maintaining conduction of the second branch 122.

[0216] In some embodiments of the present disclosure, the control circuit 40 is further configured to control the start and stop of the heating portion 126 .

[0217] 17 , the control circuit 40 is further configured to receive the first water tank set water temperature signal, the second water tank set water temperature signal, the first water storage temperature signal, and the second water storage temperature signal, and generate a fifth drive signal to the heating unit 126 to drive the heating unit 126 to operate.

[0218] For example, when the first stored water temperature is lower than the first set water temperature and the second stored water temperature is higher than the second set water temperature, the control circuit 40 generates a fifth drive signal to the heating unit 126 to drive the heating unit 126. That is, the control circuit 40 can control the heating unit 126 to be turned on in the fourth operating state.

[0219] The control circuit 40 can be implemented by a controller. It can also be implemented by comparators and logic gates. For example, the control circuit 40 may include two comparators. The output of the first comparator can indicate whether the first storage water temperature is greater than the first set water temperature, and the output of the second comparator can indicate whether the second storage water temperature is greater than the second set water temperature. The outputs of the two comparators are connected to an AND gate circuit. When the first storage water temperature is less than the first set water temperature and the second storage water temperature is greater than the second set water temperature, the output of the AND gate circuit becomes the fifth drive signal.

[0220] In some embodiments of the present disclosure, the control circuit 40 is further configured to control the start and stop of the first water pump 110. Referring to FIG. 18 , from a circuit design perspective, the control circuit 40 is configured to receive a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, a first water storage temperature signal, and a second water storage temperature signal, and generate a shutdown drive signal to the first water pump to stop the first water pump, thereby allowing the gaseous refrigerant provided by the compressor to pass through the first heat exchanger 102 or the first branch 124 and exchange heat with water in the second heat exchanger. The heat-exchanged water is then stored in the second water tank.

[0221] For example, when the first storage water temperature is greater than the first set water temperature, the control circuit 40 generates a shutdown drive signal to the first water pump 110 to stop the first water pump 110. That is, the control circuit 40 can control the first water pump 110 to stop in the third working state.

[0222] The control circuit 40 may be implemented by a controller.

[0223] The control circuit 40 may also be implemented by a comparator and a logic gate circuit.

[0224] For example, the output of one comparator can indicate whether the first water storage temperature is greater than a first set temperature, while the output of another comparator can indicate whether the second water storage temperature is greater than a second set temperature. The outputs of the two comparators are connected to an AND gate circuit. When the first water storage temperature is greater than the first set temperature and the second water storage temperature is less than the second set temperature, the output of the AND gate circuit serves as a shutdown drive signal. This shutdown drive signal is further used to stop the first water pump.

[0225] 18 , the control circuit 40 is further configured to receive a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, a first water storage temperature signal, and a second water storage temperature signal, and generate a working drive signal to the first water pump to keep the first water pump running, so that the first heat exchanger can perform heat exchange between the refrigerant provided by the compressor that produces a phase change from gas to liquid and water, or can perform heat exchange between the gas-phase refrigerant provided by the compressor and water.

[0226] For example, when the first stored water temperature is lower than the first set water temperature, the control circuit 40 generates an operating drive signal to the first water pump to keep the first water pump running. That is, the control circuit 40 can control the first water pump 110 to start running in the first operating state, the second operating state, or the fourth operating state.

[0227] The control circuit 40 may be implemented by a controller.

[0228] The control circuit 40 can also be implemented using comparators and logic gates. For example, the output of the first comparator can indicate whether the first water storage temperature is greater than a first set water temperature, while the output of the second comparator can indicate whether the second water storage temperature is greater than a second set water temperature. The outputs of the two comparators are connected to an AND gate circuit. If the first water storage temperature is less than the first set water temperature and the second water storage temperature is less than the second set water temperature, the output of the AND gate circuit becomes the operating drive signal. The operating drive signal is further used to maintain the operation of the first water pump.

[0229] It is understandable that, in the first working state, the control circuit 40 may send a first drive signal to the first solenoid valve 125 , send a third drive signal to the second solenoid valve 123 , and send a working drive signal to the first water pump 110 .

[0230] In the second working state, the control circuit 40 may send a first driving signal to the first solenoid valve 125 , send a fourth driving signal to the second solenoid valve 123 , and send a working driving signal to the first water pump 110 .

[0231] In the third working state, the control circuit 40 may send a second driving signal to the first solenoid valve 125 , send a third driving signal to the second solenoid valve 123 , and send a shutdown driving signal to the first water pump 110 .

[0232] In the fourth working state, the control circuit 40 can send a first drive signal to the first solenoid valve 125 , a third drive signal to the second solenoid valve 123 , a shutdown drive signal to the first water pump 110 , and a fifth drive signal to the heating unit 126 .

[0233] 19 , the heat pump system 1000 further includes a ninth sensor 136 (e.g., a first heat exchanger pressure sensor) configured to detect the pressure of the first heat exchanger 102. The ninth sensor 136 may be disposed in the first refrigerant flow passage, for example, the ninth sensor 137 may be disposed at the outlet of the first refrigerant flow passage.

[0234] In some embodiments, referring to FIG. 19 , the heat pump system 1000 further includes a control unit. The control unit can control the opening of the first throttle component 105. The control unit can be implemented by a controller 20. Alternatively, the control unit can be a microprocessor including a CPU and memory, independent of the controller 20. In some embodiments of the present disclosure, the controller 20 is used as an example.

[0235] In some embodiments, the controller 20 is further configured to adjust the opening of the first throttling component 105 according to the degree of subcooling or superheating at the outlet of the first heat exchanger 102 .

[0236] In some embodiments, different refrigerants correspond to different refrigerant reference temperatures. The refrigerant reference temperature can be obtained in an experimental environment and is an upper limit for the water temperature. For example, it can be the temperature that the water in the first water tank 107 can reach when the compressor raises the refrigerant to the ultimate saturation pressure, with both the first water supply line and the first water supply line closed and the water in the first water tank 107 at an ideal level.

[0237] For example, the saturation pressure of R32 refrigerant at 60°C is 3.83 MPa. If the water temperature is expected to be above 60°C, the refrigerant's condensing temperature must be above 60°C, meaning the saturation pressure must be above 3.83 MPa. If operated under these conditions, the refrigerant circuit pressure will approach the design pressure, leaving insufficient design margin to further increase the refrigerant's saturation pressure. Different refrigerants have corresponding refrigerant reference temperatures. For example, the refrigerant reference temperature for R32 is 60°C, the refrigerant reference temperature for R410A is 55°C, and the refrigerant reference temperature for R290 is 80°C.

[0238] In some embodiments, the refrigerant reference temperature is set according to the type of refrigerant used, and the refrigerant reference temperature is stored in the memory of the controller 20 in the form of a set value for later use.

[0239] In some embodiments, referring to Figure 20, the controller 20 is configured to: when the first water storage temperature is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature of the first water tank 107, control the opening of the first throttling component 105 so that the outlet subcooling of the first heat exchanger 102 meets the set subcooling condition, thereby realizing heat exchange using the latent heat and sensible heat of the refrigerant in the first heat exchanger 102.

[0240] It should be noted that the subcooling condition can be set to correspond to the ideal heat recovery condition. By adjusting the subcooling at the outlet of the first heat exchanger 102, the gas-phase refrigerant in the first heat exchanger 102, which serves as a condenser, can be condensed into a saturated liquid-phase refrigerant. Further cooling can then subcool the saturated liquid-phase refrigerant, thereby increasing the heat energy recovered from the first heat exchanger 102, improving energy utilization efficiency and reducing heat energy waste. While maintaining the same heat exchange area, the amount of heat transferred from the refrigerant to the water is increased.

[0241] In some embodiments, referring to Figure 21, the controller 20 is further configured to: when the first water storage temperature is greater than the refrigerant reference temperature but less than the first set water temperature, control the opening of the first throttling component 105 so that the outlet superheat of the first heat exchanger 102 meets the set superheat condition, so that the sensible heat of the refrigerant can be used in the first heat exchanger 102 for heat exchange until the first water storage temperature reaches the first set water temperature.

[0242] It should be noted that by setting the superheat condition, the refrigerant in the first heat exchanger 102 is kept in a gas phase, thereby fully utilizing the heat transfer surface of the first heat exchanger 102 to transfer heat to water, thereby improving the heat exchange efficiency and further increasing the water temperature.

[0243] In this way, the heat pump system 1000 can continue to use the sensible heat of the refrigerant for heat exchange until the first storage water temperature reaches the first set water temperature. Thus, under the premise of using only one compressor, the limitation of the physical properties of the refrigerant on the maximum water temperature is overcome, and the water output range of the heat pump system 1000 is expanded.

[0244] In summary, in the heat pump system 1000 provided in some embodiments of the present disclosure, the controller 20 can control the outlet subcooling or outlet superheating of the first heat exchanger 102 by controlling the opening of the first throttling component 105 .

[0245] In some embodiments, the set subcooling condition is defined by a set subcooling upper threshold and a set subcooling lower threshold, that is, the outlet subcooling of the first heat exchanger 102 needs to be maintained within the range defined by the set subcooling upper threshold and the set subcooling lower threshold.

[0246] Referring to FIG. 20 , in some embodiments, the controller 20 is further configured to: when the first water storage temperature is less than the refrigerant reference temperature and the refrigerant reference temperature is less than the first set water temperature (i.e., when both S101 and S102 are determined to be yes), determine whether the outlet subcooling of the first heat exchanger 102 is greater than a set upper subcooling threshold ( S103 ). If the outlet subcooling of the first heat exchanger 102 is greater than the set upper subcooling threshold, increase the opening of the first throttle component 105 until the outlet subcooling of the first heat exchanger 102 is less than or equal to the set upper subcooling threshold ( S104 ). It is understood that when the first water storage temperature is less than the refrigerant reference temperature and the refrigerant reference temperature is less than the first set water temperature, the deviation between the first water storage temperature and the first set water temperature is significant. In this case, the opening of the first throttle component 105 is increased to reduce the outlet subcooling of the first heat exchanger 102, thereby improving the sensible and latent heat recovery efficiency of the first heat exchanger 102.

[0247] The controller 20 obtains the temperature detection value T of the fourth sensor 130 c1 And the pressure detection value of the ninth sensor 136. Then, the pressure detection value of the ninth sensor 136 is converted into the saturated condensing temperature T e1 , and calculate the temperature detection value T c1 and saturated condensation temperature T e1 The difference between the two is taken as the outlet subcooling degree T of the first heat exchanger 102. e1SC , T e1SC =T c1 -T e1 .

[0248] The controller 20 further determines the outlet subcooling degree T of the first heat exchanger 102 e1SC Is it greater than the set upper limit threshold of supercooling T? e1SC_max If the outlet subcooling degree T of the first heat exchanger 102 is determined e1SC >T e1SC_max , it means that the opening of the first throttling component 105 is too small and the subcooling degree of the refrigerant in the first heat exchanger 102 is too large. At this time, the controller 20 executes the control of increasing the opening of the first throttling component 105 until the subcooling degree at the outlet of the first heat exchanger 102 is less than or equal to the set subcooling upper limit threshold.

[0249] In some embodiments, referring to FIG21 , the controller 20 is further configured to: when the first water storage temperature is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature (i.e., when S201 and S202 are judged to be yes), determine whether the outlet subcooling of the first heat exchanger 102 is lower than the set subcooling lower limit threshold (S203); if it is determined that the outlet subcooling of the first heat exchanger 102 is lower than the set subcooling lower limit threshold, execute the control of reducing the opening of the first throttling component 105 until the outlet subcooling of the first heat exchanger 102 is greater than or equal to the set subcooling lower limit threshold (S204). The controller 20 obtains the outlet subcooling T of the first heat exchanger 102. e1SC After that, the outlet subcooling degree T of the first heat exchanger 102 is further determined. e1SC Is it less than the set subcooling lower limit threshold T e1SC_min If the outlet subcooling degree T of the first heat exchanger 102 is determined e1SC <T e1SC_min , it means that the opening of the first throttling component 105 is too large and the subcooling degree of the refrigerant in the first heat exchanger 102 is too small. At this time, the controller 20 executes the control to reduce the opening of the first throttling component 105 until the subcooling degree at the outlet of the first heat exchanger 102 is greater than or equal to the set subcooling lower limit threshold.

[0250] In some embodiments, the subcooling degree at the outlet of the first heat exchanger 102 satisfies the set subcooling degree condition, for example, T e1SC It needs to be in the range of [1K, 6K], that is, T e1SC_max 6K, T e1SC_min is 1K.

[0251] In some embodiments, the set superheat condition is defined by a set superheat upper threshold and a set superheat lower threshold, that is, the outlet superheat of the first heat exchanger 102 is maintained within the range defined by the set superheat upper threshold and the set superheat lower threshold.

[0252] In some embodiments, referring to FIG. 22 , the controller 20 is further configured to: when the first water storage temperature is greater than the refrigerant reference temperature and less than the first set water temperature (i.e., if both S301 and S302 are determined to be yes), determine whether the outlet superheat of the first heat exchanger 102 is greater than a set upper superheat threshold (S303). If the outlet superheat of the first heat exchanger 102 is greater than the set upper superheat threshold, control is executed to reduce the opening of the first throttle component 105 until the outlet superheat of the first heat exchanger 102 is less than or equal to the set upper superheat threshold (S304). It is understood that when the first water storage temperature is greater than the refrigerant reference temperature but less than the first set water temperature, the heat pump system 1000 recovers pure sensible heat from the first heat exchanger 102 to increase the outlet water temperature.

[0253] The controller 20 obtains the temperature detection value T of the fourth sensor 130 c1 After the pressure detection value of the ninth sensor 136 is converted into the saturated condensing temperature T e1 , and calculate the temperature detection value T c1 and saturated condensation temperature T e1 The difference between the two is taken as the outlet superheat degree T of the first heat exchanger 102 e1SH , T e1SH =T e1 -T c1 .

[0254] The controller 20 further determines the outlet superheat degree T of the first heat exchanger 102 e1SH Is it greater than the set upper limit threshold T of superheat? e1SH_max If the outlet superheat degree T of the first heat exchanger 102 is determined e1SH >T e1SH_max , it indicates that the opening of the first throttle component 105 is too large, and the refrigerant superheat in the first heat exchanger 102 is too high. In this case, the controller 20 controls the opening of the first throttle component 105 to reduce the opening until the superheat at the outlet of the first heat exchanger 102 is less than or equal to the set superheat upper threshold.

[0255] In some embodiments, referring to FIG. 23 , the controller 20 is further configured to: when the first water storage temperature is greater than the refrigerant reference temperature but less than the first set water temperature (i.e., when S401 and S402 are judged to be yes), determine whether the outlet superheat of the first heat exchanger 102 is lower than the set superheat lower limit threshold (S403). If it is determined that the outlet superheat of the first heat exchanger 102 is less than the set superheat lower limit threshold, the control of increasing the opening of the first throttling component 105 is executed until the outlet superheat of the first heat exchanger 102 is greater than or equal to the set superheat lower limit threshold (S404). The controller 20 obtains the outlet superheat T of the first heat exchanger 102. e1SH Then, the outlet superheat degree T of the first heat exchanger 102 is further estimated. e1SH Is it less than the set superheat lower limit threshold T e1SH_min If the outlet superheat degree T of the first heat exchanger 102 is determined e1SH <T e1SH_min , this indicates that the opening of the first throttle component 105 is too small, and the refrigerant superheat in the first heat exchanger 102 is too low. It is necessary to adjust the opening of the first throttle component 105 to prevent the high-temperature and high-pressure gas-phase refrigerant from undergoing phase change in the first heat exchanger 102. Specifically, the opening of the first throttle component 105 is increased until the superheat at the outlet of the first heat exchanger 102 is greater than or equal to the set lower superheat threshold.

[0256] In some embodiments, the outlet superheat of the first heat exchanger 102 satisfies the set superheat condition, for example, T e1SH It needs to be in the range of [1K, 4K], that is, T e1SH_max For 4K,T e1SH_min is 1K.

[0257] In some embodiments, referring to FIG. 24 , the controller 20 is further configured to control the second solenoid valve 123 to keep closing the second branch 122 ( S501 ) when the first water storage temperature is lower than the refrigerant reference temperature and the refrigerant reference temperature is lower than the first set water temperature.

[0258] In some embodiments, referring to FIG. 25 , the controller 20 is further configured to control the second solenoid valve 123 to keep the second branch 122 open when the first water storage temperature is greater than the refrigerant reference temperature but less than the first set water temperature ( S601 ).

[0259] In some embodiments, referring to Figure 26, the controller 20 is further configured to: when the first water storage temperature is greater than or equal to the first set water temperature, and the second water storage temperature of the second water tank 108 is less than the second set water temperature of the second water tank 108 (that is, when S701 and S702 are judged as yes), the first throttling component 105 can be controlled to be at a preset opening (S703), and the second solenoid valve 123 can be controlled to keep the second branch 122 open (S704).

[0260] In some embodiments, the preset opening degree may be the maximum opening degree of the first throttle component 105 .

[0261] In some embodiments, referring to FIG. 27 , the controller 20 is further configured to control the first water pump 110 to stop running ( S801 ) when the first storage water temperature is greater than or equal to the first set water temperature and the second storage water temperature is less than the second set water temperature.

[0262] In some embodiments, when a heating unit 126 is provided in the first water tank 107, referring to FIG28 , the controller 20 is further configured to: when the first water storage temperature is lower than the first set water temperature and the second water storage temperature is greater than or equal to the second set water temperature (i.e., when S901 and S902 are judged as yes), the heating unit 126 can be controlled to operate (S903), the compressor 101 can be controlled to stop (S904), the second solenoid valve 123 can be controlled to keep the second branch 122 closed (S905), the first throttling component 105 can be controlled to be in a closed valve state (S906), the second throttling component 106 can be controlled to be in a closed valve state (S907), the first water pump 110 can be controlled to operate (S908), and the second water pump 120 can be controlled to stop operating (S909).

[0263] In some embodiments, referring to FIG. 29 , the heat pump system 1000 further includes a first sub-controller 21 and a second sub-controller 22 .

[0264] In some embodiments, the first sub-controller 21 is configured to: when the first water storage temperature of the first water tank 107 is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature of the first water tank 107, first control the opening of the first throttling component 105 so that the outlet subcooling of the first heat exchanger 102 meets the set subcooling condition, so that the latent heat and sensible heat of the refrigerant can be utilized in the first heat exchanger 102 for heat exchange; and when the first water storage temperature is higher than the refrigerant reference temperature but lower than the first set water temperature, then control the opening of the first throttling component 105 so that the outlet superheat of the first heat exchanger 102 meets the set superheat condition, so that the sensible heat of the refrigerant can be utilized in the first heat exchanger 102 for heat exchange.

[0265] In some embodiments, the second sub-controller 22 is configured to: when the first water storage temperature is greater than the hysteresis control reference water temperature but less than the first set water temperature, first control the opening of the first throttling component 105 so that the outlet superheat of the first heat exchanger 102 meets the set superheat condition, so that the sensible heat of the refrigerant can be utilized in the first heat exchanger 102 for heat exchange; and when the first water storage temperature is less than the hysteresis control reference water temperature and less than the first set water temperature, then control the opening of the first throttling component 105 so that the outlet subcooling of the first heat exchanger 102 meets the set subcooling condition, so that the latent heat and sensible heat of the refrigerant can be utilized in the first heat exchanger 102 for heat exchange.

[0266] The refrigerant reference temperature is set according to the type of refrigerant used, and the hysteresis control reference water temperature is lower than the refrigerant reference temperature. For example, referring to Figure 30, if the refrigerant reference temperature is 60°C, the hysteresis control reference water temperature can be 57°C, and the hysteresis is designed to be 3°C.

[0267] Hysteresis control is introduced through the first sub-controller 21 and the second sub-controller 22, so that different corresponding refrigerant reference temperatures and hysteresis control reference water temperatures are given in sequence based on the direction of water temperature change in the first water tank 107 and the second water tank 108. If the water temperature changes from low to high, the controller 20 uses the refrigerant reference temperature as the control point. If the water temperature changes from high to low, the controller 20 uses the hysteresis control reference water temperature as the control point. In this way, the control point is turned into an interval to avoid the controller 20 frequently switching between different control strategies when the water temperature fluctuates around a certain value, thereby maintaining the stable operation of the heat pump system 1000.

[0268] In some embodiments, the first sub-controller 21 is further configured to: when the first water storage temperature is less than the refrigerant reference temperature and the refrigerant reference temperature is less than the first set water temperature, if it is determined that the degree of subcooling at the first heat exchanger outlet is greater than a set upper subcooling threshold, then control is executed to increase the opening of the first throttling component 105 until the degree of subcooling at the first heat exchanger outlet is less than or equal to the set upper subcooling threshold. If it is determined that the degree of subcooling at the first heat exchanger outlet is less than a set lower subcooling threshold, then control is executed to decrease the opening of the first throttling component 105 until the degree of subcooling at the first heat exchanger outlet is greater than or equal to the set lower subcooling threshold.

[0269] In some embodiments, the second sub-controller 22 is further configured to: when the first storage water temperature is less than the hysteresis control reference water temperature and the refrigerant reference temperature is less than the first set water temperature, if it is determined that the first heat exchanger outlet subcooling is greater than a set subcooling upper limit threshold, then control is executed to increase the opening of the first throttle component 105 until the first heat exchanger outlet subcooling is less than or equal to the set subcooling upper limit threshold. If it is determined that the first heat exchanger outlet subcooling is less than a set subcooling lower limit threshold, then control is executed to decrease the opening of the first throttle component 105 until the first heat exchanger outlet subcooling is greater than or equal to the set subcooling lower limit threshold.

[0270] In some embodiments, the first sub-controller 21 is further configured to: when the first storage water temperature is greater than the refrigerant reference temperature and less than the first set water temperature, if it is determined that the superheat at the first heat exchanger outlet is greater than a set superheat upper threshold, execute control to reduce the opening of the first throttle component until the superheat at the first heat exchanger outlet is less than or equal to the set superheat upper threshold. If it is determined that the superheat at the first heat exchanger outlet is less than a set superheat lower threshold, execute control to increase the opening of the first throttle component until the superheat at the first heat exchanger outlet is greater than or equal to the set superheat lower threshold.

[0271] In some embodiments, the second sub-controller 22 is further configured to: when the first storage water temperature is greater than the hysteresis control reference water temperature and the first storage water temperature is less than the first set water temperature, if it is determined that the superheat at the first heat exchanger outlet is greater than a set superheat upper threshold, then control is executed to reduce the opening of the first throttle component until the superheat at the first heat exchanger outlet is less than or equal to the set superheat upper threshold. If it is determined that the superheat at the first heat exchanger outlet is less than a set superheat lower threshold, then control is executed to increase the opening of the first throttle component until the superheat at the first heat exchanger outlet is greater than or equal to the set superheat lower threshold.

[0272] It should be noted that any one of the technical solutions disclosed in the present disclosure can, to a certain extent, solve one or more of the above-mentioned technical problems and achieve certain disclosure purposes; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve certain disclosure purposes; some of the technical disclosures can also be selected to be combined into an overall solution, while adopting related technologies and inferior solutions, but the inferior trend can be compensated by the means disclosed in this technology, and the above-mentioned one or more technical problems can be solved to a certain extent as a whole and certain disclosure purposes can be achieved; each technical disclosure combined into a complete technical solution constitutes an organic and inseparable overall solution, which solves technical problems as a whole and achieves certain disclosure purposes.

[0273] Any technical disclosure in this disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and can solve one or more of the above-mentioned technical problems and achieve the purpose of disclosure. They all belong to the content of this disclosure and are the content that is directly and unambiguously determined based on the content of this disclosure.

[0274] Those skilled in the art will understand that the scope of the present disclosure is not limited to the above specific embodiments, and that certain elements of the embodiments may be modified and replaced without departing from the spirit of the present disclosure. The scope of the present disclosure is limited by the appended claims.

Claims

1. A heat pump system comprising: First water tank; A second water tank is provided independently of the first water tank; as well as Refrigerant circuit, including: compressor; a first heat exchanger, connected to the compressor; and the first water tank is connected to the first heat exchanger; a first throttling component, connected to the first heat exchanger; a second heat exchanger connected to the first throttling component; and a second water tank connected to the second heat exchanger; a second throttling component in communication with the second heat exchanger; and a third heat exchanger, wherein a first end of the third heat exchanger is connected to the second throttling component, and a second end of the third heat exchanger is connected to the compressor; The first heat exchanger is configured as one of the following: The first heat exchanger is capable of exchanging heat between the refrigerant provided by the compressor and undergoing a phase change from gas to liquid and the water in the first water tank; and The first heat exchanger is capable of performing one of heat exchange between gas-phase refrigerant provided by the compressor and water in the first water tank.

2. The heat pump system according to claim 1, further comprising: a first sensor, disposed in the first water tank, capable of detecting the water temperature in the first water tank and generating a first water storage temperature signal; a second sensor, disposed in the second water tank, capable of detecting the water temperature in the second water tank and generating a second water storage temperature signal; A control terminal capable of generating a first water tank set water temperature signal and a second water tank set water temperature signal; as well as A controller is coupled to the first sensor, the second sensor, and the control terminal.

3. The heat pump system according to claim 2, further comprising: a first branch, wherein a first end of the first branch is connected to the compressor, and a second end of the first branch is connected to the second heat exchanger; as well as a first solenoid valve, disposed in the first branch; Wherein, the controller is further configured to: receiving the first water tank set water temperature signal, the second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a first driving signal to the first solenoid valve to control the first solenoid valve to keep the first branch closed; as well as Heat exchange is performed in the first heat exchanger between the refrigerant provided by the compressor and the water in the first water tank, and the water after heat exchange is stored in the first water tank. Heat exchange is performed in the second heat exchanger between the refrigerant passing through the first throttling component and the water in the second water tank, and the water after heat exchange is stored in the second water tank.

4. The heat pump system according to claim 3, wherein: The controller is further configured to: receiving the first water tank set water temperature signal, the second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a second driving signal to the first solenoid valve to control the first solenoid valve to keep the first branch open; Heat exchange is performed between the refrigerant provided by the compressor and the water in the second water tank in the second heat exchanger, and the water after heat exchange is stored in the second water tank.

5. The heat pump system according to any one of claims 2 to 4, wherein: The first heat exchanger has: a first refrigerant flow passage configured to allow refrigerant to flow therein; and A first water circulation channel is configured to allow water in the first water tank to flow therein, the first water circulation channel being connected to the first water tank; The second heat exchanger has: a second refrigerant flow passage configured to allow refrigerant to flow therein; and a second water circulation channel configured to allow water in the second water tank to flow therethrough, the second water circulation channel being connected to the second water tank; The heat pump system further comprises: a second branch, a first end of the second branch communicating with the first refrigerant circulation channel, a second end of the second branch communicating with the second refrigerant circulation channel; the second branch being arranged in parallel with the first throttling component; and The second solenoid valve is arranged in the second branch.

6. The heat pump system according to claim 5, wherein: The controller is further configured to: receiving a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a third driving signal to the second solenoid valve, wherein the second solenoid valve is capable of keeping the second branch closed; as well as performing heat exchange in the first heat exchanger between the refrigerant provided by the compressor and undergoing a phase change from gas to liquid and the water in the first water tank; The reference temperature signal is generated according to a refrigerant reference temperature, and the refrigerant reference temperature is set according to the type of refrigerant used.

7. The heat pump system according to claim 5, wherein: The controller is further configured to: receiving a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a fourth driving signal to the second solenoid valve, so that the second solenoid valve keeps the second branch circuit conductive; and performing heat exchange between the gas-phase refrigerant provided by the compressor and the water in the first water tank in the first heat exchanger; The reference temperature signal is generated according to a refrigerant reference temperature, and the refrigerant reference temperature is set according to the type of refrigerant used.

8. The heat pump system according to any one of claims 2 to 7, further comprising a heating unit, wherein the heating unit is disposed in the first water tank; The controller is further configured to: receive the first water tank set water temperature signal, the second water tank set water temperature signal, the first water storage temperature signal, and the second water storage temperature signal; and generate a fifth driving signal to the heating unit.

9. The heat pump system according to any one of claims 2 to 8, further comprising: a first circuit, connected to the first heat exchanger and the first water tank; as well as a first water pump, disposed in the first circuit; the first water pump is capable of guiding water in the first circuit to flow into the first heat exchanger; Wherein, the controller is further configured to: receiving a reference temperature signal, a first water tank set water temperature signal, a second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a shutdown drive signal to the first water pump to control the first water pump to stop running; The gas-phase refrigerant provided by the compressor enters the second heat exchanger and exchanges heat with the water in the second water tank in the second heat exchanger. The water after heat exchange is stored in the second water tank.

10. The heat pump system according to claim 9, wherein: The controller is also capable of: receiving the reference temperature signal, the first water tank set water temperature signal, the second water tank set water temperature signal, the first storage water temperature signal, and the second storage water temperature signal; generating a working drive signal to the first water pump to control the first water pump to keep running; The first heat exchanger performs one of heat exchange between the refrigerant provided by the compressor that undergoes a phase change from gas to liquid and the water in the first water tank, and heat exchange between the gas-phase refrigerant provided by the compressor and the water in the first water tank.

11. The heat pump system according to any one of claims 1 to 10, further comprising a controller, wherein the controller is configured to: When the first water storage temperature of the first water tank is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature of the first water tank, controlling the opening of the first throttle component until the outlet subcooling degree of the first heat exchanger meets the set subcooling degree condition; When the first water storage temperature is greater than the refrigerant reference temperature and less than the first set water temperature, controlling the opening of the first throttling component until the superheat at the outlet of the first heat exchanger meets a set superheat condition; in, The refrigerant reference temperature is set according to the type of refrigerant used.

12. The heat pump system according to claim 11, wherein: The controller is further configured to: When the first water storage temperature is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature, if it is determined that the outlet subcooling degree of the first heat exchanger is greater than a set subcooling degree upper limit threshold, controlling the opening degree of the first throttle component to increase until the outlet subcooling degree of the first heat exchanger is less than or equal to the set subcooling degree upper limit threshold; as well as If it is determined that the subcooling degree at the outlet of the first heat exchanger is less than the set subcooling degree lower limit threshold, the opening of the first throttling component is controlled to decrease until the subcooling degree at the outlet of the first heat exchanger is greater than or equal to the set subcooling degree lower limit threshold.

13. The heat pump system according to claim 12, wherein: The controller is further configured to: When the first storage water temperature is greater than the refrigerant reference temperature and the first storage water temperature is less than the first set water temperature, if it is determined that the superheat at the outlet of the first heat exchanger is greater than a set superheat upper limit threshold, controlling the opening of the first throttle component to decrease until the superheat at the outlet of the first heat exchanger is less than or equal to the set superheat upper limit threshold; as well as If it is determined that the superheat at the outlet of the first heat exchanger is less than the set superheat lower limit threshold, the opening of the first throttling component is controlled to increase until the superheat at the outlet of the first heat exchanger is greater than or equal to the set superheat lower limit threshold.

14. The heat pump system according to claim 13, further comprising: a second branch, the second branch being arranged in parallel with the first throttling component; as well as a second solenoid valve, disposed in the second branch; The controller is further configured to: control the second solenoid valve to keep the second branch closed when the first water storage temperature is lower than the refrigerant reference temperature and the refrigerant reference temperature is lower than the first set water temperature; and control the second solenoid valve to keep the second branch open when the first water storage temperature is higher than the refrigerant reference temperature but lower than the first set water temperature.

15. The heat pump system according to claim 14, wherein: The controller is further configured to: When the first water storage temperature is greater than or equal to the first set water temperature and the second water storage temperature of the second water tank is lower than the second set water temperature of the second water tank, the first throttling component is controlled to be at a preset opening, and the second solenoid valve is controlled to keep the second branch open.

16. The heat pump system according to claim 15, further comprising: a first circuit, connected to the first heat exchanger and the first water tank; as well as a first water pump, disposed in the first circuit; the first water pump is capable of guiding water in the first circuit to flow into the first heat exchanger; The controller is further configured to control the first water pump to stop running when the first water storage temperature is greater than or equal to the first set water temperature and the second water storage temperature is less than the second set water temperature.

17. The heat pump system according to claim 16, further comprising: a heating unit, the heating unit being disposed in the first water tank; a second circuit, communicating with the second heat exchanger and the second water tank; as well as a second water pump, disposed in the second circuit; the second water pump is capable of guiding water in the second circuit to flow into the second heat exchanger; The controller is further configured to: when the first water storage temperature is lower than the first set water temperature and the second water storage temperature is higher than or equal to the second set water temperature, control the heating unit to operate, control the compressor to stop, and control the second electromagnetic The valve keeps the second branch closed, controls the first throttling component to be in a closed state, controls the second throttling component to be in a closed state, controls the first water pump to operate, and controls the second water pump to stop operating.

18. The heat pump system according to any one of claims 11 to 17, wherein: The controller includes: a first sub-controller, the first sub-controller being configured to: when a first water storage temperature of the first water tank is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature of the first water tank, first control the opening of the first throttling component until the outlet subcooling of the first heat exchanger meets a set subcooling condition; and when the first water storage temperature is higher than the refrigerant reference temperature but lower than the first set water temperature, further control the opening of the first throttling component until the outlet superheat of the first heat exchanger meets the set superheat condition; and a second sub-controller configured to: when the first storage water temperature is greater than the hysteresis control reference water temperature and less than a first set water temperature, first control the opening of the first throttling component until the outlet superheat of the first heat exchanger meets a set superheat condition; and when the first storage water temperature is less than the hysteresis control reference water temperature and less than the first set water temperature, further control the opening of the first throttling component until the outlet subcooling of the first heat exchanger meets the set subcooling condition; Wherein, the hysteresis control reference water temperature is lower than the refrigerant reference temperature.

19. The heat pump system according to claim 18, wherein: The first sub-controller is further configured to: when the first water storage temperature is lower than the refrigerant reference temperature, and the refrigerant reference temperature is lower than the first set water temperature, if it is determined that the subcooling degree at the first heat exchanger outlet is greater than a set subcooling degree upper limit threshold, control the opening degree of the first throttling component to increase until the subcooling degree at the first heat exchanger outlet is less than or equal to the set subcooling degree upper limit threshold; if it is determined that the subcooling degree at the first heat exchanger outlet is less than a set subcooling degree lower limit threshold, control the opening degree of the first throttling component to decrease until the subcooling degree at the first heat exchanger outlet is greater than or equal to the set subcooling degree lower limit threshold; The second sub-controller is further configured to: when the first water storage temperature is lower than the hysteresis control reference water temperature and the refrigerant reference temperature is lower than the first set water temperature, if it is determined that the subcooling degree at the first heat exchanger outlet is greater than the set subcooling degree upper limit threshold, control the opening of the first throttling component to increase until the subcooling degree at the first heat exchanger outlet is less than or equal to the set subcooling degree upper limit threshold; if it is determined that the subcooling degree at the first heat exchanger outlet is less than the set subcooling degree lower limit threshold, control the opening of the first throttling component to decrease until the subcooling degree at the first heat exchanger outlet is greater than or equal to the set subcooling degree lower limit threshold.

20. The heat pump system according to claim 19, wherein: The first sub-controller is further configured to: when the first water storage temperature is greater than the refrigerant reference temperature and the first water storage temperature is less than the first set water temperature, if it is determined that the superheat at the first heat exchanger outlet is greater than a set superheat upper limit threshold, control the opening of the first throttling component to decrease until the superheat at the first heat exchanger outlet is less than or equal to the set superheat upper limit threshold; if it is determined that the superheat at the first heat exchanger outlet is less than a set superheat lower limit threshold, control the opening of the first throttling component to increase until the superheat at the first heat exchanger outlet is greater than or equal to the set superheat lower limit threshold; The second sub-controller is further configured to: when the first water storage temperature is greater than the hysteresis control reference water temperature and the first water storage temperature is less than the first set water temperature, if it is determined that the superheat at the first heat exchanger outlet is greater than a set superheat upper limit threshold, control the opening of the first throttling component to decrease until the superheat at the first heat exchanger outlet is less than or equal to the set superheat upper limit threshold; if it is determined that the superheat at the first heat exchanger outlet is less than the set superheat lower limit threshold, control the opening of the first throttling component to increase until the superheat at the first heat exchanger outlet is greater than or equal to the set superheat lower limit threshold.

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