Heat pump system and control method of heat pump system

Abstract

The invention relates to a heat pump system, in particular to a heat pump system and a control method of the heat pump system, and aims at solving the problems that an existing steam heat pump system is complex in structure and low in efficiency. In order to achieve the purpose, the heat pump system comprises a refrigerant loop, and a compressor, a condenser, a throttling device, an evaporator and a heat exchange passage structure are sequentially arranged on the refrigerant loop; the system further comprises a water inlet passage structure, a flash evaporation device, a water return passage structure, a heat source passage structure, a first water replenishing passage structure and a second water replenishing passage structure, a water inlet of the flash evaporation device communicates with the water inlet passage structure, and a hot water outlet of the flash evaporation device communicates with the water return passage structure; according to the heat pump system, the water inlet channel structure can exchange heat with the water return channel structure and the condenser, and the heat exchange channel structure can exchange heat with the condenser. The first water supplementing channel structure and the second water supplementing channel structure both communicate with the water inlet channel structure, and the first water supplementing channel structure and the evaporator can exchange heat with the heat source channel structure.

Description

Technical Field

[0001] The present invention relates to the field of heat pump systems, and in particular provides a heat pump system and a control method for the heat pump system. Background Art

[0002] Heat pump technology, as an energy-saving and environmentally friendly method of heat conversion, is gaining increasing attention in industrial steam production. Traditional electric boilers convert electricity into heat to heat water, but this process typically has a low cost-of-performance ratio (COP), resulting in high energy consumption. In contrast, heat pump systems utilize a small amount of electricity to drive a compressor, upgrading the thermal energy to supply industrial steam. Their COP can reach approximately 2, potentially saving up to 50%.

[0003] However, traditional heat pump systems face many challenges in providing high-temperature steam, especially when the system needs to produce steam close to or exceeding 120°C, which is usually achieved through multi-stage heat pump systems. These systems consist of multiple refrigeration circuits, each of which requires an independent compressor, condenser, throttling device, and evaporator. This multi-stage cascade configuration not only increases the complexity of the design, but also introduces additional maintenance requirements, higher initial investment costs, and potential reliability risks during operation. In addition, system efficiency is also limited because the multi-stage system will have significant heat losses during the heat exchange process of the water replenishment link, which further reduces the thermal efficiency and economy of the entire system.

[0004] Accordingly, the art needs a new heat pump system to solve the above problems. Summary of the Invention

[0005] The present invention aims to solve the above technical problem, that is, to solve the problem that the existing steam heat pump system has a complex structure and low efficiency.

[0006] In a first aspect, the present invention provides a heat pump system, characterized in that the heat pump system includes: a refrigerant circuit, on which a compressor, a condenser, a throttling device, an evaporator and a heat exchange path structure are sequentially provided; a water inlet path structure, a flash evaporation device and a return water path structure, the water inlet of the flash evaporation device is connected to the water inlet path structure, and the hot water outlet of the flash evaporation device is connected to the return water path structure; the heat pump system is configured so that the water inlet path structure can exchange heat with the return water path structure and the condenser, and the heat exchange path structure can exchange heat with the condenser; the heat pump system also includes a heat source path structure, a first water replenishment path structure and a second water replenishment path structure, the first water replenishment path structure and the second water replenishment path structure are both connected to the water inlet path structure, and the first water replenishment path structure and the evaporator can exchange heat with the heat source path structure.

[0007] In an optional technical solution of the above-mentioned heat pump system, the heat pump system also includes a first temperature sensor and a valve body, the valve body is used to connect with the water source, the first temperature sensor is used to detect the heat source temperature in the heat source passage structure, and the valve body can be connected with one of the first water replenishment passage structure and the second water replenishment passage structure.

[0008] In an optional technical solution of the above heat pump system, the heat pump system further includes a main water pipe, the water outlet of the main water pipe is connected to the water inlet of the valve body, and the main water pipe is provided with a second temperature sensor and an on-off valve.

[0009] In an optional technical solution of the above-mentioned heat pump system, the heat pump system also includes a return water pipe and a water storage device, the water inlet passage structure, the flash evaporation device and the return water passage structure are arranged on the return water pipe, and the water storage device is arranged on the return water pipe between the water inlet end of the water inlet passage structure and the water outlet end of the return water passage structure.

[0010] In an optional technical solution of the above-mentioned heat pump system, a water level sensor is provided on the water storage device, and the water level sensor is used to detect the water level value in the water storage device.

[0011] On the other hand, the present invention also provides a control method for a heat pump system, wherein the heat pump system includes: a refrigerant circuit, wherein the refrigerant circuit is sequentially provided with a compressor, a condenser, a throttling device, an evaporator and a heat exchange path structure; a water inlet path structure, a flash evaporation device and a return water path structure, the water inlet of the flash evaporation device is connected to the water inlet path structure, and the hot water outlet of the flash evaporation device is connected to the return water path structure; the heat pump system is configured so that the water inlet path structure can exchange heat with the return water path structure and the condenser, and the heat exchange path structure can exchange heat with the condenser; it also includes a heat source path structure, a first water supply path structure and a second water supply path structure, The first water replenishment passage structure and the second water replenishment passage structure are both connected to the water inlet passage structure, and the first water replenishment passage structure and the evaporator can exchange heat with the heat source passage structure; the heat pump system also includes a first temperature sensor and a valve body, the valve body is used to communicate with the water source, the first temperature sensor is used to detect the heat source temperature in the heat source passage structure, and the valve body can be connected to one of the first water replenishment passage structure and the second water replenishment passage structure; the control method includes: obtaining the heat source temperature; based on the heat source temperature, controlling the valve body to move, so that the water source is connected to one of the first water replenishment passage structure and the second water replenishment passage structure.

[0012] In an optional technical solution of the control method of the above-mentioned heat pump system, the heat pump system also includes a main water pipe, the water outlet end of the main water pipe is connected to the water inlet of the valve body, and a second temperature sensor is provided on the main water pipe, and the second temperature sensor is used to detect the inlet water temperature; the control method also includes: obtaining the inlet water temperature; the step of "controlling the valve body action based on the heat source temperature" further includes: controlling the valve body action based on the heat source temperature and the inlet water temperature.

[0013] In the optional technical solution of the control method of the above-mentioned heat pump system, the step of "controlling the valve body action based on the heat source temperature and the water inlet temperature" further includes: when the difference between the heat source temperature and the water inlet temperature is greater than or equal to a preset temperature value, controlling the valve body to perform a first action to connect the main water pipe with the first water supply passage structure; and / or when the difference between the heat source temperature and the water inlet temperature is less than a preset temperature value, controlling the valve body to perform a second action to connect the main water pipe with the second water supply passage structure.

[0014] In an optional technical solution of the control method of the above-mentioned heat pump system, an on-off valve is also provided on the main water pipe, and the heat pump system also includes a return water pipe and a water storage device. The water inlet passage structure, the flash evaporation device and the return water passage structure are arranged on the return water pipe, and the water storage device is arranged on the return water pipe between the water inlet end of the water inlet passage structure and the water outlet end of the return water passage structure. A water level sensor is provided on the water storage device, and the water level sensor is used to detect the water level value in the water storage device; before the step of "controlling the valve body action based on the heat source temperature and the water inlet temperature", the control method also includes: obtaining the water level value; when the water level value is less than the preset water level threshold, controlling the on-off valve to open.

[0015] In an optional technical solution of the control method of the above heat pump system, the control method further includes: when the water level value is greater than or equal to a preset water level threshold, controlling the on-off valve to close.

[0016] Because the water inlet passage structure can exchange heat with the return water passage structure and the condenser, and the heat exchange passage structure can exchange heat with the condenser, the refrigerant on the compressor suction side is preheated, increasing the condenser heating temperature. While the cold water in the water inlet passage structure is heated by the condenser, it also captures excess heat in the return water passage structure, ensuring system efficiency while also ensuring the system can reach the required flash evaporation temperature. To further improve the efficiency of the heat pump system, the present invention introduces a heat source passage structure. When a heat source is available, heat is introduced into the heat source passage structure. At this time, water can be replenished to the water inlet passage structure through a first water replenishment passage structure. Because the first water replenishment structure and the evaporator can exchange heat with the heat source passage structure, the system can use this heat source to preheat the incoming water and improve the heat exchange efficiency of the evaporator. It also reduces the energy required for refrigerant evaporation in the evaporator, and the required evaporation temperature is relatively low, thereby reducing heat loss in the system. A higher inlet water temperature also helps reach the flash evaporation temperature more quickly, thereby improving flash evaporation efficiency. When the external heat source is unavailable, the system can instead use the second water replenishment path structure to replenish water to the water inlet path structure, thereby avoiding affecting the heat exchange efficiency of the evaporator and ensuring normal system operation. The heat pump system of the present invention dynamically adjusts its operating path based on the availability of the external heat source, thereby maximizing energy efficiency under different operating conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

[0018] Figure 1 is a structural schematic diagram of a heat pump system according to a first embodiment of the present invention;

[0019] Figure 2 is a schematic structural diagram of a first possible implementation of a first heat exchanger of a heat pump system of the present invention;

[0020] Figure 3 1 is a schematic structural diagram of a second possible embodiment of the first heat exchanger of the heat pump system of the present invention (I);

[0021] Figure 4 2 is a schematic structural diagram of a second possible embodiment of the first heat exchanger of the heat pump system of the present invention;

[0022] Figure 5 is a schematic structural diagram of a third possible implementation of the first heat exchanger of the heat pump system of the present invention;

[0023] Figure 6 is a structural schematic diagram of a second embodiment of a heat pump system of the present invention;

[0024] Figure 7 is a schematic structural diagram of a first possible implementation of the second heat exchanger of the heat pump system of the present invention;

[0025] Figure 8 is a schematic structural diagram of a second possible implementation of the second heat exchanger of the heat pump system of the present invention;

[0026] Figure 9 is a partial structural diagram of a third embodiment of a heat pump system of the present invention;

[0027] Figure 10 is a schematic structural diagram of a first possible implementation of the fourth heat exchanger of the heat pump system of the present invention;

[0028] Figure 11 is a schematic structural diagram of a second possible implementation of the fourth heat exchanger of the heat pump system of the present invention;

[0029] Figure 12 is a schematic structural diagram of a third possible implementation of the fourth heat exchanger of the heat pump system of the present invention;

[0030] Figure 13 is a main flow chart of the control method of the heat pump system of the present invention;

[0031] Figure 14 It is a possible logic diagram of the control method of the heat pump system of the present invention.

[0032] Description of reference numerals:

[0033] 10-refrigerant circuit; 11-first branch; 12-second branch; 13-compressor; 14-condenser; 141-first condenser; 142-second condenser; 15-throttling device; 16-evaporator; 17-heat exchange path structure; 20-return water pipe; 21-water inlet path structure; 211-first water inlet path structure; 212-second water inlet path structure; 22-flash evaporation device; 221-water inlet; 222-hot water outlet; 23-return water path structure; 24-water storage device; 25-water pump; 26-pressure reducing device; 27-first water supply path structure; 28 -Second water supply passage structure; 30-heat source passage structure; 301-heat exchange cavity; 3011-heat source inlet; 3012-heat source outlet; 40-first water supply branch pipe; 41-second water supply branch pipe; 50-first water inlet pipe; 51-second water inlet pipe; 52-first return water pipe; 53-second return water pipe; 60-first heat exchanger; 61-regenerator; 62-second heat exchanger; 63-third heat exchanger; 64-fourth heat exchanger; 70-valve body; 71-main water pipe; 72-on-off valve; 80-first temperature sensor; 81-second temperature sensor; 90-water level sensor. DETAILED DESCRIPTION

[0034] Preferred embodiments of the present invention are described below with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely intended to illustrate the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. Those skilled in the art may adjust these embodiments as needed to suit specific applications.

[0035] It should be noted that, in the description of the present invention, the terms "first", "second" and "third" are used for descriptive purposes only and should not be understood as indicating or implying relative importance.

[0036] Furthermore, it should be noted that, in the description of the present invention, unless otherwise expressly specified or limited, the terms "installed," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integral connections; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium, such as through a water pipe; and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0037] In order to solve the problem of complex structure and low efficiency of existing steam heat pump systems, the present invention provides a heat pump system, such as Figure 1 and Figure 6 As shown, the heat pump system includes a refrigerant circuit 10, a water inlet passage structure 21, a flash evaporation device 22, a return water passage structure 23, a heat source passage structure 30, a first water supply passage structure 27, and a second water supply passage structure 28. The refrigerant circuit 10 is provided with a compressor 13, a condenser 14, a throttling device 15, an evaporator 16, and a heat exchange passage structure 17 in sequence. The water inlet 221 of the flash evaporation device 22 is connected to the water inlet passage structure 21, and the hot water outlet 222 of the flash evaporation device 22 is connected to the return water passage structure 23. The heat pump system is configured so that the water inlet passage structure 21 can exchange heat with the return water passage structure 23 and the condenser 14, and the heat exchange passage structure 17 can exchange heat with the condenser 14. The first water supply passage structure 27 and the second water supply passage structure 28 are both connected to the water inlet passage structure 21. The first water supply passage structure 27 and the evaporator 16 can exchange heat with the heat source passage structure 30.

[0038] It is understood that the water inlet passage structure 21 and the water return passage structure 23 refer to passage structures having a water inlet end and a water outlet end. Water can enter the passage structure from the water inlet end and flow out from the water outlet end. The present invention does not limit the specific form of the water inlet passage structure 21 and the water return passage structure 23; as long as they can pass water, their specific form can be adjusted. In addition, the present invention does not limit the specific structure of the throttling device 15; as long as it can throttle and reduce pressure, it can be a capillary tube or an electronic expansion valve. It is understood that the flash evaporation device 22 is a process device that uses pressure reduction to partially vaporize the liquid, and can also be called a flash tank.

[0039] Since the water inlet passage structure 21 can exchange heat with the return water passage structure 23 and the condenser 14, and the heat exchange passage structure 17 can exchange heat with the condenser 14, the refrigerant on the suction side of the compressor 13 is preheated, and the heating temperature of the condenser 14 is increased. The cold water in the water inlet passage structure 21 is heated by the condenser 14 while also capturing the waste heat in the return water passage structure 23, thereby ensuring the system efficiency while also ensuring that the system can reach the required flash temperature. In order to further improve the efficiency of the heat pump system, the present invention introduces a heat source passage structure 30. When a heat source is available, a heat source will be introduced into the heat source passage structure 30. At this time, water can be replenished to the water inlet passage structure 21 through the first water replenishment passage structure 27. Since the first water replenishment passage structure 27 and the evaporator 16 can exchange heat with the heat source passage structure 30, the system can use this heat source to preheat the incoming water and improve the heat exchange efficiency of the evaporator 16. It also reduces the energy required to evaporate the refrigerant in the evaporator 16, and the required evaporation temperature is relatively low, thereby reducing heat loss in the system. A higher inlet water temperature also helps reach the flash evaporation temperature more quickly, thereby improving flash evaporation efficiency. When an external heat source is unavailable, the system can instead use the second water replenishment passage structure 28 to replenish water to the water inlet passage structure 21 to avoid affecting the heat exchange efficiency of the evaporator 16 and ensure normal operation of the system. The above-mentioned heat pump system of the present invention dynamically adjusts its operating path based on the availability of the external heat source, thereby maximizing energy efficiency under different operating conditions.

[0040] Possibly, the heat pump system of the present invention further includes a return water pipe 20, which includes a first water inlet pipe 50, a second water inlet pipe 51, a first return water pipe 52, and a second return water pipe 53. The water outlet end of the first water inlet pipe 50 is connected to the water inlet end of the water inlet passage structure 21, the water outlet end of the water inlet passage structure 21 is connected to the water inlet 221 of the flash evaporation device 22 through the second water inlet pipe 51, the hot water outlet 222 of the flash evaporation device 22 is connected to the water inlet end of the return water passage structure 23 through the first return water pipe 52, the water outlet end of the return water passage structure 23 is connected to the water inlet end of the second return water pipe 53, and the water outlet end of the second return water pipe 53 is connected to the water inlet end of the first water inlet pipe 50, thereby forming a closed return water pipe 20. Among them, a water pump 25 can be set on the return water pipe 20. The water pump 25 is preferably set on the first water inlet pipe 50, but of course it can also be set at a location such as on the first return water pipe 52. In addition, a pressure reducing device 26 can be connected between the water outlet of the water inlet passage structure 21 and the water inlet 221 of the flash evaporation device 22. The pressure reducing device 26 can specifically be a pressure reducing valve, an expansion valve, or a pressure regulating valve. The pressure reducing device 26 can be installed on the second water inlet pipe 51. If the second water inlet pipe 51 is not installed, the pressure reducing device 26 can also be directly connected to the water outlet of the water inlet passage structure 21 and the water inlet 221. Under the action of the water pump 25, the water in the return pipe 20 circulates in the following order: the first water inlet pipe 50, the water inlet passage structure 21, the second water inlet pipe 51, the pressure reducing device 26, the flash evaporation device 22, the first return water pipe 52, the return water passage structure 23, and the second return water pipe 53.

[0041] As a possible embodiment, the heat pump system further includes a water storage device 24, which is disposed on the return water pipe 20 between the water inlet end of the water inlet passage structure 21 and the water outlet end of the return water passage structure 23. A water level sensor 90 may be provided on the water storage device 24 to detect the water level within the water storage device 24. Optionally, the water storage device 24 includes a water storage cavity, which is provided with a water inlet and a water outlet. Optionally, the water outlet end of the second return water pipe 53 is connected to the water inlet of the water storage cavity, and the water outlet of the water storage cavity is connected to the water inlet end of the first water inlet pipe 50. A water replenishment port may also be provided on the water storage cavity, and the water outlet end of the first replenishment water passage structure 27 and the water outlet end of the second replenishment water passage structure 28 are connected to the water replenishment port. Of course, this is not restrictive. The water outlet end of the first water replenishment passage structure 27 and the water outlet end of the second water replenishment passage structure 28 can also be directly connected to the first water inlet pipe 50. As long as the first water replenishment passage structure 27 and the second water replenishment passage structure 28 can be connected to the water inlet end of the water inlet passage structure 21, these adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0042] It is understandable that the above description is based on the example of setting water pipes to achieve indirect connection between components. Of course, at least one of the water pipes described above can be omitted to achieve direct connection between components.

[0043] Flash evaporator 22 is used to evaporate a portion of the water by rapidly reducing the water pressure, facilitating heat exchange. This process causes the water pressure in return pipe 20 to drop. Water storage device 24 replenishes the water flow after this process, ensuring stable water pressure and smooth system operation. Water storage device 24 also protects the heat pump system from potential damage caused by an unstable water supply. For example, if the water supply is suddenly interrupted, water in water storage device 24 can continue to supply the system, preventing damage caused by water shortage.

[0044] As a possible embodiment, the heat pump system of the present invention further includes a first temperature sensor 80 and a valve body 70. The valve body 70 is configured to communicate with a water source and is capable of communicating with either the first water supply passage structure 27 or the second water supply passage structure 28. The first temperature sensor 80 is configured to detect the temperature of the heat source in the heat source passage structure 30. For example, the temperature sensor is disposed at the heat source inlet 3011 of the heat source passage structure 30 or within the heat source passage structure 30. The heat pump system may further include a main water pipe 71, a first water supply branch pipe 40, and a second water supply branch pipe 41. The first water supply branch pipe 40 communicates with the second water supply branch pipe 41 via the first water supply passage structure 27. The water outlet of the second water supply branch pipe 41 is connected to the water inlet of the water inlet passage structure 21. Possibly, the valve body 70 can be a three-way valve, the water outlet of the main water pipe 71 is connected to the water inlet of the three-way valve, the first water outlet of the three-way valve is connected to the water inlet end of the first water replenishment branch pipe 40, and the second water outlet of the three-way valve is connected to the water inlet end of the second water replenishment passage structure 28, so as to realize the selective communication between the water inlet of the three-way valve and the first water outlet and the second water outlet, thereby realizing the water channel switching between the main water pipe 71 and the first water replenishment passage structure 27 and the second water replenishment passage structure 28. Of course, as long as the valve body 70 can be connected to one of the first water replenishment passage structure 27 and the second water replenishment passage structure 28, its structure can be adjusted. For example, the valve body 70 includes a first solenoid valve and a second solenoid valve, the first solenoid valve is arranged on the first water replenishment branch pipe 40, and the second solenoid valve is arranged on the second water replenishment passage structure 28; when the first solenoid valve is opened and the second solenoid valve is closed, the main water pipe 71 is connected to the first water replenishment passage structure 27, and when the first solenoid valve is closed and the second solenoid valve is opened, the main water pipe 71 is connected to the second water replenishment passage structure 28. These adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0045] As a possible embodiment, the heat pump system further includes a second temperature sensor 81 for detecting the water source temperature. For example, the second temperature sensor 81 can be located on the main water pipe 71. As long as the second temperature sensor 81 can detect the water source temperature before entering the valve body 70, its location can be adjusted, such as being located at the water inlet of the three-way valve. Furthermore, an on-off valve 72 can also be provided on the main water pipe 71. Specifically, the on-off valve 72 can be a solenoid valve, a pneumatic valve, or a mechanical valve.

[0046] It should be noted that while the above structure is described using the main water pipe 71 as an example, the main water pipe 71 can also be omitted. For example, if the valve body 70 is a three-way valve, water can be directly supplied to the water inlet of the three-way valve. If the valve body 70 is a first solenoid valve and a second solenoid valve, water can be supplied to the water inlet of the first water supply branch pipe 40 and the water inlet of the second water supply passage structure 28, respectively. Furthermore, at least one of the first water supply branch pipe 40 and the second water supply branch pipe 41 can be omitted. For example, if the first water supply branch pipe 40 is omitted, the first water supply passage structure 27 can be directly connected to the water outlet of the valve body 70.

[0047] The present invention implements heat exchange between the water inlet passage structure 21 and the return water passage structure 23 and the condenser 14, and heat exchange between the heat exchange passage structure 17 and the condenser 14. There are many specific implementation methods, which are introduced below using Example 1, Example 2 and Example 3 as examples.

[0048] As a possible implementation method, refer to Figure 1 The condenser 14 includes a first condenser 141 and a second condenser 142. The refrigerant pipe section between the exhaust side of the compressor 13 and the throttling device 15 includes a first branch 11 and a second branch 12 connected in parallel. The first condenser 141 is arranged on the first branch 11, and the second condenser 142 is arranged on the second branch 12. At least the first condenser 141, the water inlet passage structure 21 and the return water passage structure 23 together constitute a first heat exchanger 60, which means that heat can be exchanged between the first condenser 141, the water inlet passage structure 21 and the return water passage structure 23; at least the second condenser 142 and the heat exchange passage structure 17 together constitute a regenerator 61, which means that heat can be exchanged between the second condenser 142 and the heat exchange passage structure 17.

[0049] After the refrigerant in the evaporator 16 takes heat from the environment, it first passes through the regenerator 61, enters the heat exchange path structure 17 in the regenerator 61 to exchange heat with the second condenser 142, so that the refrigerant reaches a quasi-high temperature state, and then is compressed in the compressor 13 to further increase the temperature and pressure, and then flows to the first branch 11 and the second branch 12 respectively. The refrigerant on the second branch 12 flows to the regenerator 61, enters the second condenser 142 in the regenerator 61 to release heat to heat the refrigerant in the heat exchange path structure 17, thereby forming a low-temperature and high-pressure refrigerant, and then passes through the throttling device 15. The pressure is reduced to a low temperature and low pressure state, and then returns to the evaporator 16; the high-temperature refrigerant on the first branch 11 flows to the first heat exchanger 60, and enters the first condenser 141 in the first heat exchanger 60 to heat the water in the water inlet passage structure 21. The water in the water inlet passage structure 21 is also heated by the water in the return water passage structure 23. The temperature of the refrigerant after flowing out of the first heat exchanger 60 is reduced to close to the ambient temperature. The high-pressure and normal-temperature refrigerant becomes a low temperature and low pressure state after throttling and reducing the pressure through the throttling device 15, and then returns to the evaporator 16 to absorb heat, thereby completing the refrigerant cycle.

[0050] As for the water flow path, the water entering the return water pipe 20 from the first water replenishment passage structure 27 or the second water replenishment passage structure 28 flows from the first water inlet pipe 50 to the first heat exchanger 60 under the action of the water pump 25, enters the water inlet passage structure 21 in the first heat exchanger 60, reaches a high temperature state through heat exchange with the high-temperature refrigerant in the first condenser 141 and the high-temperature water of the return water passage structure 23, and then is depressurized by the pressure reducing device 26, and enters the flash evaporation device 22 from the water inlet 221 for flash evaporation. After the flash evaporation process, gas-liquid flash evaporation is realized, and the obtained high-temperature steam is utilized, and the high-temperature liquid water passes through the first heat exchanger 60 from the hot water outlet 222 to complete the water heating cycle, so as to be repeatedly utilized.

[0051] The present invention does not limit the specific form of the regenerator 61, as long as it can achieve heat exchange between the heat exchange path structure 17 and the second condenser 142. For example, the heat exchange path structure 17 and the second condenser 142 are a shell and tube heat exchanger, a plate heat exchanger, a microchannel heat exchanger, or a spiral heat exchanger, or the like, or the regenerator 61 includes a regenerator cavity, the regenerator cavity being provided with a first interface, a second interface, a third interface, and a fourth interface, the second condenser 142 and the heat exchange path structure 17 are disposed in the regenerator 61 cavity, and the second condenser 142 has two ends connected to the first interface and the second interface, the first interface and the second interface are connected to the second branch 12, the heat exchange path structure 17 has two ends connected to the third interface and the fourth interface, and the third interface and the fourth interface are connected to the refrigerant pipe section between the evaporator 16 and the suction port of the compressor 13. These adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0052] The first heat exchanger 60 of the present invention can be implemented in a variety of specific forms. The structure of the first heat exchanger 60 is described below. It should be understood that while the first heat exchanger 60 of the present invention is described with the following structure, this is not intended to limit the scope of protection of the present invention. As long as the first heat exchanger 60 can enable heat exchange between the first condenser 141, the water inlet passage structure 21, and the water return passage structure 23, the specific form of the first heat exchanger 60 may be adjusted. Such adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0053] A first possible embodiment of the first heat exchanger 60, referring to Figure 2 The water inlet passage structure 21 constitutes the first outer tube shell 21, the first condenser 141 constitutes the first tube bundle 141, and the return water passage structure 23 constitutes the second tube bundle 23. At least a portion of the first tube bundle 141 and at least a portion of the second tube bundle 23 are disposed within the first outer tube shell 21. For example, the ends of the first tube bundle 141 serve as its inlet and outlet, respectively, and similarly, the ends of the second tube bundle 23 serve as its inlet and outlet, respectively. Both ends of the first tube bundle 141 and the second tube bundle 23 can be sealed and pass through the first outer tube shell 21 to facilitate connection between the pipes. The first outer tube shell 21 can be provided with an inlet and an outlet, which serve as the water inlet and outlet of the water inlet passage structure 21. The heat exchange tubes of the first tube bundle 141 and the second tube bundle 23 can be evenly distributed to achieve uniform heat exchange between the cold fluid and the two hot fluids.

[0054] By performing dual heat exchange between the cold fluid (cold water) in the first outer tube shell 21 and the hot fluid (high-temperature refrigerant and hot water) in the first tube bundle 141 and the second tube bundle 23, this configuration is more efficient in recovering condensation heat and return water heat, helping to improve the COP (coefficient of performance) of the heat pump and effectively improving the efficiency of heat exchange. When the cold fluid flows through the first outer tube shell 21, it absorbs heat from the hot fluid in the two tube bundles in turn, thereby fully utilizing the thermal energy. In a multi-tube bundle system, different temperature gradients and flow rates can be designed as needed to optimize the entire heat exchange process. For example, the higher temperature first tube bundle 141 can be used to preheat the cold fluid first, and then the second tube bundle 23 can be used for further heating. This allows for more efficient use of the thermal energy in each tube bundle.

[0055] A second possible embodiment of the first heat exchanger 60 is shown in FIG. Figure 3 and Figure 4The water inlet passage structure 21 is sleeved on the outside of the return water passage structure 23, and the first condenser 141 is sleeved on the outside of the water inlet passage structure 21. Thus, a composite concentric tube heat exchange structure is formed between the return water passage structure 23, the water inlet passage structure 21 and the first condenser 141. Among them, the opposite ends of the return water passage structure 23 (its water inlet and outlet) can be sealed to pass through the opposite ends of the water inlet passage structure 21, and the opposite ends of the water inlet passage structure 21 can be sealed to pass through the opposite ends of the first condenser 141. The sides of the water inlet passage structure 21 passing through the two ends of the first condenser 141 can be provided with an inlet and an outlet, and the inlet and outlet are also the water inlet end and the water outlet end of the water inlet passage structure 21. The first condenser 141 can also have an opening on the side as its refrigerant inlet and refrigerant outlet.

[0056] Through this concentric tube design, the hot water in the return water passage structure 23 can transfer its heat to the cold water in the water inlet passage structure 21 in the middle layer. While receiving the return water heat, the water inlet passage structure 21 in the middle layer will also receive heat from the first condenser 141 in the outer layer. In the first condenser 141, the high-temperature refrigerant discharged by the compressor 13 condenses into liquid by releasing heat, and the released heat can be used to further heat the water in the water inlet passage structure 21 on its inner side. Such a design further improves the overall thermal efficiency of the heat pump system. Among them, the heat exchange between the cold fluid in the water inlet passage structure 21 and the hot fluid in the return water passage structure 23 and the first condenser 141 can be countercurrent heat exchange (the flow directions of the cold and hot fluids are parallel and opposite), thereby further improving the heat exchange efficiency.

[0057] Alternatively, the water inlet passage structure 21 is sleeved outside the first condenser 141, and the water return passage structure 23 is sleeved outside the water inlet passage structure 21. This design also places the cold fluid in the middle and the two hot fluids on the inner and outer sides of the cold fluid. Its structure and function are similar to those described above and will not be repeated here.

[0058] A third possible embodiment of the first heat exchanger 60 is shown in FIG. Figure 5, the first heat exchanger 60 constitutes a plate heat exchanger. For example, the plate heat exchanger includes a plurality of first parts arranged in a stacked manner, the first part including a first hot layer plate (a), a cold layer plate (b), a second hot layer plate (c), and a cold layer plate (b) stacked in sequence; the cold layer plate (b) of each first part contacts the first hot layer plate (a) of its adjacent first part, thereby forming a cyclic stacking structure of the first hot layer plate, the cold layer plate, the second hot layer plate, the cold layer plate, the first hot layer plate, the cold layer plate, the second hot layer plate, and the cold layer plate, that is, a cyclic stacking structure of abcbabcb. Among them, the water inlet passage structure 21 can include a plurality of the above-mentioned cold layer plates (b) connected in parallel, the return water passage structure 23 can include a plurality of the above-mentioned first hot layer plates (a) connected in parallel, and the first condenser 141 can include a plurality of the above-mentioned second hot layer plates (c) connected in parallel. Alternatively, the return water passage structure 23 may include multiple parallel-connected second heat plates (c), and the first condenser 141 may include multiple parallel-connected first heat plates (a). This stacked structure of the plate heat exchanger (alternating hot and cold plates) provides a large surface area, allowing heat to be more efficiently transferred from the refrigerant and hot water to the cold water within a smaller volume, thereby improving heat exchange efficiency. Furthermore, fins may be added to the plate heat exchanger to enhance heat exchange.

[0059] Example 2:

[0060] Reference Figure 6 At least the water inlet passage structure 21 , the water return passage structure 23 , the condenser 14 and the heat exchange passage structure 17 together constitute the second heat exchanger 62 .

[0061] After the refrigerant in the evaporator 16 takes heat from the environment, it passes through the second heat exchanger 62, and enters the heat exchange path structure 17 in the second heat exchanger 62 to absorb the heat of the refrigerant in the condenser 14 and the heat of the water in the return water path structure 23, so that the refrigerant reaches a quasi-high temperature state, and then is compressed in the compressor 13 to further increase the temperature and pressure, and then flows to the second heat exchanger 62, and enters the condenser 14 in the second heat exchanger 62 to exchange heat with the refrigerant in the heat exchange path structure 17 and the water in the water inlet path structure 21, thereby forming a low-temperature and high-pressure refrigerant, and then is reduced in pressure to a low-temperature and low-pressure state through the throttling device 15, and then returns to the evaporator 16, thereby completing the refrigerant cycle.

[0062] As for the water flow path, the water entering the return water pipe 20 from the first water replenishment passage structure 27 or the second water replenishment passage structure 28 flows from the first water inlet pipe 50 to the second heat exchanger 62 under the action of the water pump 25, and enters the water inlet passage structure 21 in the second heat exchanger 62. It reaches a high temperature state through heat exchange with the high-temperature refrigerant in the condenser 14 and the high-temperature water of the return water passage structure 23, and then reduces the pressure through the pressure reducing device 26, and enters the flash evaporation device 22 from the water inlet 221 for flash evaporation. After the flash evaporation process, gas-liquid flash evaporation is realized, and the obtained high-temperature steam is utilized, and the high-temperature liquid water completes the water heating cycle after passing through the second heat exchanger 62 from the hot water outlet 222, so as to be repeatedly utilized.

[0063] Compared to traditional heat pump systems, only one compressor 13 is required to achieve the function of extracting heat from the environment to produce steam, eliminating the need for a cascade heat pump system, simplifying the system structure and improving efficiency. The heat pump system utilizes a second heat exchanger 62 to preheat the refrigerant, reducing the load on the compressor 13 and improving the overall COP (coefficient of performance) of the system. The design of the second heat exchanger 62 enables the refrigerant to effectively transfer heat to the water circulation system while capturing waste heat in the return water passage structure 23, reducing heat energy loss, improving the system's heat recovery capacity, and improving the system's operating efficiency and economy.

[0064] The second heat exchanger 62 of the present invention can be implemented in a variety of specific forms. The structure of the second heat exchanger 62 is described below. It should be understood that while the second heat exchanger 62 of the present invention is described with the following structure, this is not intended to limit the scope of protection of the present invention. As long as the second heat exchanger 62 can facilitate heat exchange between the water inlet passage structure 21, the water return passage structure 23, the condenser 14, and the heat exchange passage structure 17, the specific form of the second heat exchanger 62 may be adjusted. Such adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0065] A first possible embodiment of the second heat exchanger 62 is shown in FIG. Figure 7 The condenser 14 is constructed as a second outer tube shell 14, the heat exchange passage structure 17 is constructed as a third tube bundle 17, at least part of the third tube bundle 17 is arranged in the second outer tube shell 14, the water inlet passage structure 21 and the return water passage structure 23 constitute a first sleeve-tube structure, the water inlet passage structure 21 is arranged outside the return water passage structure 23, and at least part of the first sleeve-tube structure is arranged in the second outer tube shell 14.

[0066] The water inlet passage structure 21 can be sealed at both ends and pass through the second outer tube shell 14. The return water passage structure 23 is formed into a tube bundle, and its two ends are sealed and pass through the water inlet passage structure 21. The two ends of the return water passage structure 23 respectively serve as the water inlet and outlet. The side of the portion of the water inlet passage structure 21 that passes through the second outer tube shell 14 is provided with an inlet and an outlet, which serve as the water inlet and outlet of the water inlet passage structure 21. The two ends of the third tube bundle 17 can be sealed and pass through the second outer tube shell 14. The two ends of the third tube bundle 17 serve as the refrigerant inlet and refrigerant outlet of the heat exchange passage structure 17 respectively. The side wall of the second outer tube shell 14 can be provided with an inlet and an outlet to serve as the refrigerant inlet and refrigerant outlet of the condenser 14.

[0067] The above arrangement allows the high-temperature refrigerant to release heat in the second outer tube shell 14, while the low-temperature refrigerant absorbs heat through the third tube bundle 17. This convection and conduction improve heat exchange efficiency. The inlet passage structure 21, which circulates cold water, is nested outside the return passage structure 23, which circulates hot water. This structure is placed inside the second outer tube shell 14, i.e., within the high-temperature refrigerant. This overall reduces heat loss during transfer because heat is transferred and reused over a shorter distance. This evenly distributes heat across all components, reduces thermal stress caused by temperature differences, and improves system stability and service life.

[0068] Alternatively, the inlet passage structure 21 can be constructed as a second outer tube shell, and the return passage structure 23 can be constructed as a third tube bundle, with at least a portion of the third tube bundle located within the second outer tube shell. The condenser 14 and the heat exchange passage structure 17 can form a first telescopic structure, with the condenser 14 nested outside the heat exchange passage structure 17, and at least a portion of the first telescopic structure located within the second outer tube shell. This structure is similar to that described above and will not be further described. This structure can also improve heat exchange efficiency, ensuring even heat distribution across all components, reducing thermal stress caused by temperature differences, and improving system stability and service life.

[0069] A second possible embodiment of the second heat exchanger 62 is shown in FIG. Figure 8The second heat exchanger 62 constitutes a plate heat exchanger, which includes a plurality of second parts stacked in layers, and the second parts include a first hot plate (d), a first cold plate (e), a second hot plate (f) and a second cold plate (g) stacked in sequence, and the second cold plate (g) of at least one second part is adjacent to the first hot plate (d) of the adjacent second part, and further, the second cold plate of each second part is adjacent to the first hot plate of the adjacent second part; thereby forming a cyclic stacking structure of the first hot plate, the first cold plate, the second hot plate, the second cold plate, the first hot plate, the first cold plate, the second hot plate and the second cold plate, that is, a cyclic stacking form of defgdefg. The first hot plate (d) is one of the return water passage structure 23 and the condenser 14, and the second hot plate (f) is the other of the return water passage structure 23 and the condenser 14; the first cold plate (e) is one of the inlet water passage structure 21 and the heat exchange passage structure 17, and the second cold plate (g) is the other of the inlet water passage structure 21 and the heat exchange passage structure 17; the outlets of each first hot plate can be converged by a first header, and the inlets of each first hot plate can be distributed by a second header. The inlets and outlets of each second hot plate, first cold plate, and second cold plate can also be converged and distributed by corresponding headers. Furthermore, fins can be added to the plate heat exchanger to enhance heat exchange.

[0070] Plate heat exchangers employ a specific stacking method, alternating hot and cold plates. This stacking design provides a large heat exchange area within a small volume, enabling efficient heat transfer within limited space. Because the plates in the second heat exchanger 62 are closely spaced, heat loss is minimized as the fluid flows between them, improving the thermal efficiency of the entire system.

[0071] Example 3:

[0072] Reference Figure 9 The water inlet passage structure 21 includes a first water inlet passage structure 211 and a second water inlet passage structure 212 arranged in parallel on the return water pipe 20. At least the first water inlet passage structure 211 and the return water passage structure 23 constitute a third heat exchanger 63, and at least the second water inlet passage structure 212, the condenser 14 and the heat exchange passage structure 17 constitute a fourth heat exchanger 64.

[0073] After the refrigerant in the evaporator 16 takes heat from the environment, it first passes through the fourth heat exchanger 64, enters the heat exchange path structure 17 in the fourth heat exchanger 64 to exchange heat with the condenser 14, so that the refrigerant reaches a quasi-high temperature state, and then is compressed in the compressor 13 to further increase the temperature and pressure, and then flows to the fourth heat exchanger 64, enters the condenser 14 in the fourth heat exchanger 64 to release heat to heat the refrigerant in the heat exchange path structure 17 and the water in the second water inlet path structure 212, thereby forming a low-temperature and high-pressure refrigerant, and then is reduced in pressure to a low-temperature and low-pressure state through the throttling device 15, and then returns to the evaporator 16, thereby completing the refrigerant cycle.

[0074] Regarding the water flow path, water entering the return pipe 20 through the first water supply passage structure 27 or the second water supply passage structure 28 is driven by the water pump 25 and flows from the first water inlet pipe 50 to the third heat exchanger 63 and the fourth heat exchanger 64, respectively. In the fourth heat exchanger 64, water enters the second water supply passage structure 212, where it is heated by heat exchange with the high-temperature refrigerant in the condenser 14. In the third heat exchanger 63, water enters the first water supply passage structure 211, where it is heated by heat exchange with the high-temperature hot water in the return water supply passage structure 23. The water in the first and second water supply passage structures 211 and 212 is heated and then merged. The water is then reduced in pressure by the pressure reducing device 26 and enters the flash evaporation device 22 through its water inlet 221 for flash evaporation. This flash evaporation process achieves gas-liquid flash evaporation, resulting in high-temperature steam that is then utilized. The high-temperature liquid water then enters the return water supply passage structure 23 of the third heat exchanger 63 through the hot water outlet 222, completing the water heating cycle and being reused repeatedly.

[0075] Since only one compressor 13 is required, the complexity of the system is lower than that of a traditional cascade heat pump system. This simplification not only reduces equipment costs, but also reduces the complexity of operation and maintenance. Among them, the heat pump system utilizes the fourth heat exchanger 64, so that the refrigerant can exchange heat with the condenser 14 before entering the compressor 13 after absorbing heat in the evaporator 16. This process preheats the refrigerant, reduces the load of the compressor 13, and improves the overall COP (coefficient of performance) of the system. The fourth heat exchanger 64 also preheats the incoming water, reducing the energy that may be required for subsequent heating links, further improving energy efficiency, while also speeding up the production of hot water and improving response speed. The third heat exchanger 63 allows cold water to capture waste heat in the return water passage structure 23, reducing the loss of heat energy, improving the heat recovery capacity of the system, and improving the operating efficiency and economy of the system. In short, the above-mentioned setting method can simplify the structure and improve thermal efficiency.

[0076] The present invention does not limit the specific form of the third heat exchanger 63, as long as it can achieve heat exchange between the first water inlet passage structure 211 and the return water passage structure 23. For example, the first water inlet passage structure 211 and the return water passage structure 23 are shell and tube heat exchangers, plate heat exchangers, microchannel heat exchangers or spiral heat exchangers, etc. These adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0077] The fourth heat exchanger 64 of the present invention can be implemented in a variety of specific forms. The structure of the fourth heat exchanger 64 is described below. It should be understood that while the fourth heat exchanger 64 of the present invention is described with the following structure, this is not intended to limit the scope of protection of the present invention. As long as the fourth heat exchanger 64 can facilitate heat exchange between the second water inlet passage structure 212, the condenser 14, and the heat exchange passage structure 17, the specific form of the fourth heat exchanger 64 may be adjusted. Such adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0078] A first possible embodiment of the fourth heat exchanger 64 is described with reference to Figure 10 The condenser 14 constitutes a third outer tube shell, the heat exchange path structure 17 constitutes a fourth tube bundle, and the second water inlet path structure 212 constitutes a fifth tube bundle. At least part of the fourth tube bundle and at least part of the fifth tube bundle are arranged in the third outer tube shell. For example, the two ends of the fourth tube bundle serve as its inlet and outlet respectively, and similarly, the two ends of the fifth tube bundle serve as its inlet and outlet respectively. Both ends of the fourth tube bundle and the two ends of the fifth tube bundle can be sealed and pass through the third outer tube shell to facilitate the connection between the pipelines. The third outer tube shell can be provided with an inlet and an outlet, which are also the refrigerant inlet and refrigerant outlet of the condenser 14. Among them, the heat exchange tubes of the fourth tube bundle and the fifth tube bundle can be evenly distributed to achieve uniform heat exchange between the hot fluid and the two cold fluids.

[0079] Two cold fluids (the fourth and fifth tube bundles) simultaneously exchange heat with the hot fluid within the same third outer tube shell, increasing the heat exchange area and efficiency, allowing for more efficient heat utilization. The volume or flow rate of the fluids passing through the fourth and fifth tube bundles can be adjusted as needed to control the heat exchange rate between the different fluids, providing greater operational flexibility. This design also more effectively recovers the heat released during the condensation process. Some of this heat is used to preheat the water in the second water inlet passage structure 212, while the remaining heat is used to increase the temperature of the refrigerant, reducing the system's reliance on external energy.

[0080] A second possible embodiment of the fourth heat exchanger 64 is described with reference to Figure 11The condenser 14 is sleeved outside the heat exchange passage structure 17, and the second water inlet passage structure 212 is sleeved outside the condenser 14. Thus, a composite concentric tube heat exchange structure is formed between the heat exchange passage structure 17, the condenser 14 and the second water inlet passage structure 212. Among them, the opposite ends of the heat exchange passage structure 17 (the two ends are its inlet and outlet) can be sealed to pass through the opposite ends of the condenser 14, and the opposite ends of the condenser 14 can be sealed to pass through the opposite ends of the second water inlet passage structure 212. The sides of the condenser 14 passing through the two ends of the second water inlet passage structure 212 can be provided with an inlet and an outlet, which are also the refrigerant inlet and refrigerant outlet of the condenser 14. The second water inlet passage structure 212 can also have openings on the side as its water inlet and outlet.

[0081] This structure enables heat to be absorbed by the refrigerant in the heat exchange path structure 17 when released by the condenser 14, and then absorbed by the cold water in the second water inlet path structure 212. Such cascade heat utilization improves the overall energy utilization efficiency. It also reduces the heat loss caused by heat transfer, and the heat retention effect of the entire system is better. It can maintain stable heat exchange performance under different working conditions and has good adaptability to changes in flow rate and heat load. Among them, the heat exchange between the hot fluid in the condenser 14 and the cold fluid in the heat exchange path structure 17 and the second water inlet path structure 212 can be countercurrent heat exchange (the flow directions of the hot and cold fluids are parallel and opposite), thereby further improving the heat exchange efficiency.

[0082] Alternatively, the condenser 14 is sleeved outside the second water inlet passage structure 212, and the heat exchange passage structure 17 is sleeved outside the condenser 14. This design also places the hot fluid in the middle and the two cold fluids on the inner and outer sides of the hot fluid. Its structure and function are similar to those described above and will not be repeated here.

[0083] A third possible embodiment of the fourth heat exchanger 64 is described with reference to Figure 12, the fourth heat exchanger 64 constitutes a plate heat exchanger. For example, the plate heat exchanger includes a plurality of stacked third sections, each of which includes a first cold plate (h), a hot plate (i), a second cold plate (g), and a hot plate (i) stacked in sequence; the hot plate (i) of each third section contacts the first cold plate (h) of its adjacent third section, thereby forming a cyclic stacking structure of the first cold plate, the hot plate, the second cold plate, the hot plate, the first cold plate, the hot plate, the second cold plate, and the hot plate, i.e., a higihigi stacking structure. The condenser 14 may include a plurality of the aforementioned hot plates (i) connected in parallel, the second water inlet passage structure 212 may include a plurality of the aforementioned first cold plates (h) connected in parallel, and the heat exchange passage structure 17 may include a plurality of the aforementioned second cold plates (g) connected in parallel. Alternatively, the second water inlet passage structure 212 may include a plurality of the aforementioned second cold plates (g) connected in parallel, and the heat exchange passage structure 17 may include a plurality of the aforementioned first cold plates (h) connected in parallel. The stacked structure of this plate heat exchanger (alternating hot and cold plates) provides a large surface area, allowing heat to be transferred more efficiently from the refrigerant to the water within a smaller volume, thereby improving heat transfer efficiency. Furthermore, fins can be added to the plate heat exchanger to enhance heat transfer.

[0084] As a possible embodiment, the heat source passage structure 30 includes a heat exchange cavity 301, which is provided with a heat source inlet 3011 and a heat source outlet 3012. The evaporator 16 and the water supply passage structure 27 are provided in the heat exchange cavity 301. If the heat exchange cavity 301 is also provided with a first interface, a second interface, a third interface and a fourth interface, the two ends of the evaporator 16 are respectively connected to the first interface and the second interface, the two ends of the water supply passage structure 27 are respectively connected to the third interface and the fourth interface, the first interface and the second interface are also connected to the refrigerant circuit 10, and the fourth interface is connected to the water supply port. Of course, the above is not restrictive, and the arrangement can be adjusted. For example, the two ends of the evaporator 16 and the water supply passage structure 27 extend from the heat source inlet and the heat source outlet 3012 to achieve connection with the refrigerant circuit 10 and the water supply port, etc. These adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0085] Since the evaporator 16 and the water supply passage structure 27 are located in the same heat exchange cavity 301, a more direct heat exchange process can be achieved, heat loss can be reduced, and thus the efficiency of heat exchange can be improved. As an integrated unit, the heat exchange cavity 301 facilitates the management and optimization of heat flow and distribution, and thermal efficiency and system response speed can be further improved through design optimization. Because the heat exchange between the evaporator 16 and the water supply passage structure 27 is carried out in the same closed environment, flow control valves can be respectively provided at the heat source inlet 3011 and the heat source outlet 3012 to precisely control the heat source heat entering the heat exchange cavity 301, ensuring that the temperature within the heat exchange cavity 301 meets the requirements and is neither too high nor too low. In addition, the design located in the heat exchange cavity 301 allows the evaporator 16 and the water supply passage structure 27 to adapt to different heat source changes, because the internal components can be more easily reconfigured or adjusted as needed to best utilize the different heat source characteristics.

[0086] As another possible embodiment, the heat source passage structure 30 is arranged outside the water supply passage structure 27, and the evaporator 16 is arranged outside the heat source passage structure 30. Or the heat source passage structure 30 is arranged outside the evaporator 16, and the water supply passage structure 27 is arranged outside the heat source passage structure 30. As a result, the water supply passage structure 27, the heat source passage structure 30 and the evaporator 16 form a composite concentric tube heat exchange structure. The concentric tube design allows heat to be efficiently transferred between fluids because the contact area between the heat source passage structure 30 and the water supply passage structure 27 and the evaporator 16 passage is large, which helps to improve the efficiency of energy transfer. In addition, the loss of heat energy during the transfer process can be minimized, especially the radiation and convection losses during the transfer process.

[0087] It can be understood that the heat exchanger structure composed of the above-mentioned heat source passage structure 30, water supply passage structure 27 and evaporator 16 is not restrictive. As long as heat exchange between them can be achieved, its specific form can be adjusted. For example, a plate heat exchanger can be formed, etc. These adjustments do not deviate from the principles of the present invention and are within the scope of protection of the present invention.

[0088] As a possible embodiment, the refrigerant in the refrigerant circuit of the present invention is a transcritical refrigerant or a mixed refrigerant. Specifically, it can be a refrigerant that can achieve a transcritical cycle, such as CO2, R290, R32, R410a, R32, R410a, NH3, R152a, R600a, R600, R601a, R601 (n-pentane), cyclopentane, n-hexane, R134a, R1234yf, R1234ze, R245fa, R365mfc, R4310mee, R1224yd(Z), R1234ze(Z), R1233zd(E), R1336mzz(Z), H2O. The mixed refrigerant capable of having a large boiling point difference is preferably a high-temperature refrigerant having a normal pressure boiling point greater than 50°C, such as n-hexane and water. For low-temperature working fluids, when no heat source is available, working fluids with a normal pressure boiling point below -20°C are preferred, such as R290, R32, etc. When a heat source is available, the normal pressure boiling point can be selected between 30°C and -80°C depending on the temperature of the heat source.

[0089] The control method of the heat pump system of the present invention is introduced below. Figure 13 As shown, the control method of the present invention includes the following steps:

[0090] Step S100: Acquire the temperature of the heat source.

[0091] Step S200: Based on the temperature of the heat source, the valve body is controlled to operate so that the water source is connected to one of the first water supply passage structure and the second water supply passage structure.

[0092] Among them, the heat source temperature of the present invention is obtained by the first temperature sensor. According to the size of the heat source temperature, it can be judged whether a heat source is available, so that when a heat source is available, the water source is connected to the first water supply passage structure through the action of the valve body, so that the system can use this heat source to preheat the incoming water and improve the heat exchange efficiency of the evaporator. It can also reduce the energy required for the evaporation of the refrigerant inside the evaporator, and the required evaporation temperature is relatively low, thereby reducing the heat loss of the system; the higher inlet water temperature also helps to reach the flash temperature faster, so it can also improve the flash evaporation efficiency. When it is judged that no heat source is available according to the size of the heat source temperature, the water source is connected to the second water supply passage structure through the action of the valve body to avoid affecting the heat exchange efficiency of the evaporator and ensure the normal operation of the system. The above-mentioned heat pump system of the present invention dynamically adjusts the operation path according to the availability of the external heat source, thereby maximizing energy efficiency under different operating conditions.

[0093] Furthermore, the control method of the present invention further includes obtaining the inlet water temperature, and step S200 further includes: controlling the valve body action based on the heat source temperature and the inlet water temperature.

[0094] The inlet water temperature of the present invention is obtained by a second temperature sensor. When the difference between the heat source temperature and the inlet water temperature is greater than or equal to a preset temperature value, the control valve body performs a first action, connecting the main water pipe with the first water supply passage structure. When the difference between the heat source temperature and the inlet water temperature is less than the preset temperature value, the control valve body performs a second action, connecting the main water pipe with the second water supply passage structure.

[0095] It can be understood that when the valve body is a three-way valve, the control valve body performs a first action, that is, the water inlet of the three-way valve is connected to its first water outlet and blocked from the second water outlet, thereby connecting the main water pipe to the first water supply passage structure. The control valve body performs a second action, that is, the water inlet of the three-way valve is connected to its second water outlet and blocked from the first water outlet, thereby connecting the main water pipe to the second water supply passage structure. When the valve body includes a first solenoid valve and a second solenoid valve, the control valve body performs a first action, that is, controls the first solenoid valve on the first water supply branch to open and controls the second solenoid valve on the second water supply passage structure to close. The control valve body performs a second action, that is, controls the first solenoid valve on the first water supply branch to close and controls the second solenoid valve on the second water supply passage structure to open.

[0096] Among them, the preset temperature value can be determined based on experiments or experience. For example, before the system is put into use, the system performance under different preset temperature values ​​can be predicted through simulation and experimental data to determine the optimal preset temperature value. Possibly, the preset temperature value is 10°C. By setting a preset temperature value, the control system can automatically determine when to connect to the first water supply passage structure and when to connect to the second water supply passage structure. This allows the system to automatically adjust the working mode to maintain optimal heat energy transfer efficiency and minimize energy waste. When the difference between the heat source temperature and the inlet water temperature is large, if the second water supply passage structure is used, the system requires more heat energy exchange. Therefore, the main water pipe is connected to the first water supply passage structure by controlling the valve body to provide higher heat output or meet higher heat loads. On the contrary, when the temperature difference is small, the system switches to the second water supply passage structure through the second action, thereby saving energy.

[0097] As a possible implementation, before step S100, the control method of the present invention further includes: obtaining a water level value, and when the water level value is less than a preset water level threshold, controlling the on-off valve to open, and then starting to execute step S100.

[0098] The water level is acquired via a water level sensor. The total capacity of the water storage device determines the maximum and minimum water levels, and the threshold should be set within this range to avoid overload or dry running. The water level threshold should ensure sufficient water for efficient system operation in all modes. For example, the water level threshold should be greater than or equal to half the total water level, and the lower limit should be less than or equal to one-quarter of the total water level.

[0099] When the water level falls below the preset threshold, the on-off valve is controlled to open to replenish water. This ensures the water level never falls below the minimum threshold, preventing damage to pumps and other related equipment due to water shortages. Operating at the proper water level maintains system thermal efficiency and performance, avoiding efficiency drops caused by water level fluctuations.

[0100] Possibly, the control method of the present invention further comprises: controlling the on-off valve to close when the water level value is greater than or equal to a preset water level threshold.

[0101] like Figure 14 As shown, a possible control method of the heat pump system of the present invention is introduced below. The possible control method includes the following steps:

[0102] Step S300: Obtain the water level value.

[0103] Step S301: Determine whether the water level is less than a preset water level threshold. If yes, execute step S303; if no, execute step S302.

[0104] Step S302: Control the on-off valve to close.

[0105] Step S303: Control the on-off valve to open.

[0106] Step S304: Obtain the water inlet temperature and the heat source temperature.

[0107] Step S305: Determine whether the difference between the heat source temperature and the inlet water temperature is greater than or equal to a preset temperature value. If so, execute step S306; if not, execute step S307.

[0108] Step S306: controlling the valve body to perform a first action to connect the main water pipe with the first water supply passage structure.

[0109] Step S307: controlling the valve body to perform a second action, so that the main water pipe is connected to the second water supply passage structure.

[0110] Alternatively, although the present invention is described by controlling the valve body's action based on the heat source temperature and the inlet water temperature, this is not intended to limit the scope of protection of the present invention. For example, the inlet water temperature may not be obtained. In this case, when the heat source temperature is greater than a preset heat source temperature value, the control valve body performs a first action to connect the main water pipe with the first water supply passage structure. When the heat source temperature is less than or equal to the preset heat source temperature value, the control valve body performs a second action to connect the main water pipe with the second water supply passage structure. These adjustments do not deviate from the principles of the present invention and are all within the scope of protection of the present invention.

[0111] Those skilled in the art will appreciate that the heat pump system described above also includes some other well-known structures, such as a processor, a controller, and a memory. Memory includes, but is not limited to, random access memory, flash memory, read-only memory, programmable read-only memory, volatile memory, non-volatile memory, serial memory, parallel memory, or registers. Processors include, but are not limited to, CPLD / FPGA, DSP, ARM processor, MIPS processor, etc. To unnecessarily obscure the embodiments of the present disclosure, these well-known structures are not shown in the drawings.

[0112] Although the various steps in the above embodiment are described in the above order, those skilled in the art will understand that in order to achieve the effect of this embodiment, different steps do not have to be executed in such an order. They can be executed simultaneously (in parallel) or in a reversed order. For example, obtaining the heat source temperature and obtaining the water inlet temperature can be executed in reverse or in parallel. These simple changes are within the scope of protection of the present invention.

[0113] Thus far, the technical solutions of the present invention have been described in conjunction with the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art may make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will fall within the scope of protection of the present invention.

Claims

1. A heat pump system, characterized in that: The heat pump system comprises: A refrigerant circuit, wherein the refrigerant circuit is provided with a compressor, a condenser, a throttling device, an evaporator and a heat exchange path structure in sequence; A water inlet passage structure, a flash evaporation device and a return water passage structure, wherein the water inlet of the flash evaporation device is connected to the water inlet passage structure, and the hot water outlet of the flash evaporation device is connected to the return water passage structure; The heat pump system is configured such that the water inlet passage structure can exchange heat with the water return passage structure and the condenser, and the heat exchange passage structure can exchange heat with the condenser; The heat pump system also includes a heat source passage structure, a first water replenishment passage structure and a second water replenishment passage structure. The first water replenishment passage structure and the second water replenishment passage structure are both connected to the water inlet passage structure. The first water replenishment passage structure and the evaporator can exchange heat with the heat source passage structure.

2. The heat pump system according to claim 1, characterized in that The heat pump system also includes a first temperature sensor and a valve body, the valve body is used to communicate with the water source, the first temperature sensor is used to detect the heat source temperature in the heat source passage structure, and the valve body can be connected to one of the first water replenishment passage structure and the second water replenishment passage structure.

3. The heat pump system according to claim 2, characterized in that The heat pump system further comprises a main water pipe, the water outlet end of the main water pipe is connected to the water inlet of the valve body, and the main water pipe is provided with a second temperature sensor and an on-off valve.

4. The heat pump system according to claim 1, characterized in that The heat pump system also includes a return water pipe and a water storage device. The water inlet passage structure, the flash evaporation device and the return water passage structure are arranged on the return water pipe. The water storage device is arranged on the return water pipe between the water inlet end of the water inlet passage structure and the water outlet end of the return water passage structure.

5. The heat pump system according to claim 4, characterized in that The water storage device is provided with a water level sensor, and the water level sensor is used to detect the water level value in the water storage device.

6. A control method for a heat pump system, characterized in that: The heat pump system comprises: A refrigerant circuit, wherein the refrigerant circuit is provided with a compressor, a condenser, a throttling device, an evaporator and a heat exchange path structure in sequence; A water inlet passage structure, a flash evaporation device and a return water passage structure, wherein the water inlet of the flash evaporation device is connected to the water inlet passage structure, and the hot water outlet of the flash evaporation device is connected to the return water passage structure; The heat pump system is configured such that the water inlet passage structure can exchange heat with the water return passage structure and the condenser, and the heat exchange passage structure can exchange heat with the condenser; The invention also includes a heat source passage structure, a first water replenishment passage structure and a second water replenishment passage structure, wherein the first water replenishment passage structure and the second water replenishment passage structure are both connected to the water inlet passage structure, and the first water replenishment passage structure and the evaporator can exchange heat with the heat source passage structure; The heat pump system further includes a first temperature sensor and a valve body, wherein the valve body is used to communicate with a water source, the first temperature sensor is used to detect the temperature of the heat source in the heat source passage structure, and the valve body can be communicated with one of the first water replenishment passage structure and the second water replenishment passage structure; The control method includes: Obtaining the temperature of the heat source; Based on the temperature of the heat source, the valve body is controlled to operate so that the water source is connected to one of the first water replenishment passage structure and the second water replenishment passage structure.

7. The control method of the heat pump system according to claim 6, characterized in that: The heat pump system further comprises a main water pipe, the water outlet end of the main water pipe is connected to the water inlet of the valve body, and a second temperature sensor is provided on the main water pipe, and the second temperature sensor is used to detect the inlet water temperature; The control method further includes: obtaining the inlet water temperature; The step of “controlling the valve body movement based on the heat source temperature” further includes: The valve body is controlled to operate based on the heat source temperature and the inlet water temperature.

8. The control method of the heat pump system according to claim 7, characterized in that: The step of “controlling the valve body movement based on the heat source temperature and the inlet water temperature” further includes: When the difference between the heat source temperature and the water inlet temperature is greater than or equal to a preset temperature value, controlling the valve body to perform a first action to connect the main water pipe with the first water supply passage structure; and / or When the difference between the heat source temperature and the water inlet temperature is less than a preset temperature value, the valve body is controlled to perform a second action to connect the main water pipe with the second water supply passage structure.

9. The control method of the heat pump system according to claim 7, characterized in that: The main water pipe is further provided with an on-off valve, and the heat pump system further comprises a return water pipe and a water storage device, wherein the water inlet passage structure, the flash evaporation device and the return water passage structure are provided on the return water pipe, and the water storage device is provided on the return water pipe between the water inlet end of the water inlet passage structure and the water outlet end of the return water passage structure, and the water storage device is provided with a water level sensor, and the water level sensor is used to detect the water level value in the water storage device; Before the step of “controlling the valve body movement based on the heat source temperature and the inlet water temperature”, the control method further includes: Obtaining the water level value; When the water level value is less than a preset water level threshold, the on-off valve is controlled to open.

10. The control method of the heat pump system according to claim 9, characterized in that: The control method further includes: When the water level value is greater than or equal to a preset water level threshold, the on-off valve is controlled to close.

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