A split-structure air source heat pump and phase change energy storage floor radiant system

Abstract

This invention belongs to the field of floor radiant floor technology, and particularly relates to a split-structure air source heat pump and phase change energy storage floor radiant floor system, including an outdoor unit, an indoor unit, and an energy-consuming unit. The outdoor unit is integrated with several finned heat exchangers and an electric regulating valve for refrigerant. The indoor unit is integrated with several compressors, one-way valves, four-way reversing valves, electronic expansion valves, refrigerant bypass solenoid valves, dehumidifying electronic expansion valves, dehumidifying shell-and-tube heat exchangers, dehumidifying circulating pumps, electric three-way valves, cooling and heating solenoid valves, cooling and heating shell-and-tube heat exchangers, cooling and heating circulating pumps, and gas-liquid separators. The energy-consuming unit is integrated with several dehumidifying terminal devices and several phase change energy storage floor tiles. The system is provided with a refrigerant flow pipeline and a circulating water flow pipeline. The refrigerant flow pipeline realizes the circulation of refrigerant between the outdoor unit and the indoor unit, and the circulating water flow pipeline realizes water circulation heat exchange between the indoor unit and the energy-consuming unit.

Description

Technical Field

[0001] This invention belongs to the technical field of air source heat pumps and phase change energy storage floor radiant systems, and particularly relates to a split-structure air source heat pump and phase change energy storage floor radiant system. Background Technology

[0002] Air source heat pump floor radiant systems are widely used in the building HVAC field due to their energy-saving and environmental protection advantages. In the existing technology, most of these systems adopt an integrated structural design, integrating core components such as compressors, heat exchangers, and energy storage components into the same box. This not only results in large equipment size and limited installation and maintenance space, but also has problems such as poor linkage between outdoor and indoor components and low spatial adaptability. It is difficult to flexibly arrange them in different house types and building scenarios. At the same time, the fixed piping layout of the integrated structure makes subsequent commissioning and component replacement difficult, increasing the cost of use and operation and maintenance.

[0003] Currently, conventional air-source heat pump phase change energy storage floor radiant systems still suffer from drawbacks such as limited functional modes and poor coordination of temperature and humidity control. Most systems cannot achieve independent operation and flexible switching between cooling, dehumidification, and heating modes. Even some systems that can achieve multiple modes have problems such as high energy consumption when dehumidification and cooling are coupled, low energy storage and release efficiency of the phase change energy storage floor, and a lack of precise flow regulation components, making it difficult to dynamically regulate the flow of refrigerant and circulating water according to indoor environmental needs. This results in insufficient accuracy in indoor temperature and humidity control, failing to meet users' needs for comfortable and energy-saving HVAC systems. Summary of the Invention

[0004] The purpose of this invention is to address the aforementioned technical problems by providing a split-structure air source heat pump and phase change energy storage floor radiant system.

[0005] In view of this, the present invention provides a split-structure air source heat pump and phase change energy storage floor radiant system, including an outdoor unit, an indoor unit and an energy-consuming unit; The outdoor unit is integrated with several finned heat exchangers and an electric regulating valve for the refrigerant. The indoor unit is composed of several compressors, one-way valves, four-way reversing valves, electronic expansion valves, refrigerant bypass solenoid valves, dehumidifying electronic expansion valves, dehumidifying shell-and-tube heat exchangers, dehumidifying circulating pumps, electric three-way valves, refrigeration and heating solenoid valves, refrigeration and heating shell-and-tube heat exchangers, refrigeration and heating circulating pumps, and gas-liquid separators. The energy-consuming unit is integrated from several dehumidification terminal devices and several phase change energy storage floor tiles; The system is equipped with a refrigerant flow pipeline and a circulating water flow pipeline. The refrigerant flow pipeline enables refrigerant circulation between the outdoor unit and the indoor unit, while the circulating water flow pipeline enables water circulation heat exchange between the indoor unit and the energy-consuming unit.

[0006] Preferably, the connection relationship of the refrigerant flow pipeline is as follows: The outlets of several compressors in the indoor unit are connected to the first port of a four-way reversing valve through pipes. The second port of the four-way reversing valve is connected to the first port of the refrigerant electric regulating valve of the outdoor unit branch pipe through pipes. The second port of the refrigerant electric regulating valve is connected to the first port of the finned heat exchanger. The second ports of several finned heat exchangers are connected to the first port of the electronic expansion valve through parallel pipes. The second port of the electronic expansion valve is connected to the first port of the electric three-way valve. The second and third ports of the electric three-way valve are respectively connected to the first port of the dehumidification electronic expansion valve and the first port of the cooling and heating solenoid valve. The second port of the dehumidifying electronic expansion valve is connected in parallel with the first ports of several dehumidifying shell-and-tube heat exchangers through a pipe. After the flow from the second ports of several dehumidifying shell-and-tube heat exchangers converges, it flows into the third port of the four-way reversing valve. The second port of the refrigeration and heating solenoid valve is connected in parallel with the first ports of several refrigeration and heating shell-and-tube heat exchangers through a pipeline. After the flow from the second ports of several refrigeration and heating shell-and-tube heat exchangers converges, it flows into the third port of the four-way reversing valve. The fourth port of the four-way reversing valve is connected to the first port of the gas-liquid separator via a pipe, and the second port of the gas-liquid separator is connected to the inlet of several compressors.

[0007] Preferably, the outlets of several compressors are also connected to a refrigerant bypass solenoid valve via pipes and the second interface of a four-way reversing valve, and the output end of the refrigerant bypass solenoid valve merges or splits with the second interface of the electronic expansion valve.

[0008] Preferably, the refrigerant is a coolant that completes a cycle of compression, condensation / evaporation, and throttling in the refrigerant flow pipeline.

[0009] Preferably, the circulating water flow pipeline is divided into a dehumidification water circulation branch and a cooling and hot water circulation branch. The dehumidification water circulation branch realizes the water circulation between the dehumidification shell-and-tube heat exchanger and the dehumidification terminal equipment, while the cooling and hot water circulation branch realizes the water circulation between the cooling and heating shell-and-tube heat exchanger and the phase change energy storage floor tiles.

[0010] Preferably, the connection relationship of the dehumidification water circulation branches is as follows: The first interface on the circulating water side of the dehumidifying shell-and-tube heat exchanger is connected in parallel with several dehumidifying terminal devices through a pipeline. The water circulation outlets of the several dehumidifying terminal devices converge and are then transported back to the second interface on the circulating water side of the dehumidifying shell-and-tube heat exchanger through a dehumidifying circulation pump.

[0011] Preferably, the connection relationship of the cooling and hot water circulation branch is as follows: The first interface on the circulating water side of the cooling and heating shell-and-tube heat exchanger exchanges heat with several phase change energy storage floor tiles through a pipe. The circulating water after exchanging heat with the phase change energy storage floor tiles is collected and then transported back to the second interface on the circulating water side of the cooling and heating shell-and-tube heat exchanger through a cooling and heating circulating pump.

[0012] Preferably, the system can realize independent cooling mode, dehumidification mode and heating mode, and the cooling mode and dehumidification mode can operate simultaneously.

[0013] Preferably, in the cooling mode, the refrigerant is condensed by the finned heat exchanger and throttled by the electronic expansion valve. Then, it enters the cooling and heating shell-and-tube heat exchanger through the electric three-way valve and the cooling and heating solenoid valve to exchange heat with the circulating water. The medium-temperature chilled water output from the cooling and heating shell-and-tube heat exchanger is used to store cold water for the phase change energy storage floor tiles and releases cold water to the room through radiation from the phase change energy storage floor tiles.

[0014] Preferably, the refrigerant bypass solenoid valve can adjust the refrigerant flow rate in cooling mode, dehumidification mode, and heating mode, thereby adjusting the cooling, dehumidification, and heating effects of the system. In the heating mode, after being compressed by the compressor, the refrigerant directly enters the cooling and heating shell-and-tube heat exchanger through the four-way reversing valve to exchange heat with the circulating water. The low-temperature hot water output by the cooling and heating shell-and-tube heat exchanger stores heat in the phase change energy storage floor tiles and releases heat to the room through radiation from the phase change energy storage floor tiles. After completing the heat exchange, the refrigerant enters the finned heat exchanger to absorb heat from the outdoor air after being throttled by the electronic expansion valve, and then flows back to the compressor through the four-way reversing valve and the gas-liquid separator. In the dehumidification mode, the refrigerant is condensed by the finned heat exchanger and throttled by the electronic expansion valve. Then, it enters the dehumidification shell-and-tube heat exchanger through the electric three-way valve and the dehumidification electronic expansion valve to exchange heat with the circulating water. The low-temperature chilled water output from the dehumidification shell-and-tube heat exchanger enters the dehumidification terminal equipment to exchange heat with the indoor air, thereby achieving indoor cooling and dehumidification.

[0015] The beneficial effects of this invention are as follows: This invention adopts a split structure to divide the system into outdoor units, indoor units and energy-consuming units and carries out modular integrated design, which eliminates the layout defects of traditional integral structures, greatly reduces the volume of a single unit, and allows each unit to be flexibly arranged according to the building type and installation scenario, significantly improving spatial adaptability. At the same time, the modular component integration makes the system installation, commissioning and subsequent maintenance and repair more convenient, reducing the difficulty and cost of operation and maintenance. In addition, the pipeline connection between each unit is simple, improving the stability of the component linkage operation.

[0016] This invention, through the rational design of the refrigerant flow pipeline and the dual circulation branch on the circulating water side, combined with the coordinated control of a four-way reversing valve, an electric three-way valve, various solenoid valves, and flow regulation components, achieves independent operation and flexible switching of three modes: cooling, dehumidification, and heating. Furthermore, cooling and dehumidification modes can operate simultaneously, effectively solving the problems of single functional modes and poor temperature and humidity control coordination in traditional systems. The refrigerant bypass solenoid valve allows for precise dynamic adjustment of the refrigerant flow in each mode. Combined with the radiative heat exchange and energy storage / release characteristics of phase change energy storage floor tiles, this not only improves the accuracy of indoor temperature and humidity control, making the heat exchange process more uniform and indoor comfort better, but also avoids the high energy consumption problem of multi-mode coupled operation in traditional systems. This improves the overall heat exchange efficiency and energy storage utilization rate of the system, achieving energy saving and consumption reduction. At the same time, the parallel configuration of core components such as heat exchangers and compressors allows for flexible adjustment of the number of operating components according to the actual indoor energy load, further optimizing system energy consumption and meeting the comfort and energy-saving HVAC needs of different scenarios. Attached Figure Description

[0017] Figure 1 A schematic diagram of a split-structure air-source heat pump and phase change energy storage floor radiant system according to the present invention; Figure 2 This invention provides a cooling mode for a split-structure air-source heat pump and phase change energy storage floor radiant system. Figure 3 This invention relates to a dehumidification mode for a split-structure air-source heat pump and phase change energy storage floor radiant system. Figure 4 This invention discloses a split-structure air-source heat pump and phase change energy storage floor radiant heating system.

[0018] In the picture: 1. Outdoor unit; 2. Indoor unit; 3. Energy consumption unit; 4. Compressor; 5. Check valve; 6. Four-way directional valve; 7. Electric regulating valve for refrigerant; 8. Finned heat exchanger; 9. Electronic expansion valve; 10. Refrigerant bypass solenoid valve; 11. Dehumidifying electronic expansion valve; 12. Dehumidifying shell-and-tube heat exchanger; 13. Dehumidification terminal equipment; 14. Dehumidification circulation pump; 15. Electric three-way valve; 16. Refrigeration and heating solenoid valve; 17. Shell-and-tube heat exchangers for refrigeration and heating; 18. Phase change energy storage floor tiles; 19. Refrigeration and heating circulation pump; 20. Gas-liquid separator. Detailed Implementation

[0019] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application are within the scope of protection of this application.

[0020] like Figure 1 As shown, this invention is a split-structure air source heat pump and phase change energy storage floor radiant system. The outdoor unit 1 is integrated with several finned heat exchangers 8 and a refrigerant electric regulating valve 7. The indoor unit 2 is integrated with several compressors 4, one-way valves 5, four-way reversing valves 6, electronic expansion valves 9, refrigerant bypass solenoid valves 10, dehumidifying electronic expansion valves 11, dehumidifying shell-and-tube heat exchangers 12, dehumidifying circulating pumps 14, electric three-way valves 15, cooling and heating solenoid valves 16, cooling and heating shell-and-tube heat exchangers 17, cooling and heating circulating pumps 19, and gas-liquid separators 20. The energy-consuming unit 3 is integrated with several dehumidifying terminal devices 13 and several phase change energy storage floor tiles 18.

[0021] Refrigerant Flow Flow: The outlets of several compressors 4 in indoor unit 2 are connected to the first port of a four-way reversing valve 6 via pipes. The second port of the four-way reversing valve 6 is connected to the first port of the refrigerant electric regulating valve 7 in the branch pipe of outdoor unit 1 via pipes. The second port of the refrigerant electric regulating valve 7 is connected to the first port of a finned heat exchanger 8. The second ports of several finned heat exchangers 8 are connected to the first port of an electronic expansion valve 9 via parallel pipes. The second port of the electronic expansion valve 9 is connected to the first port of an electric three-way valve 15. The second and third ports of the electric three-way valve 15 are respectively connected to the first port of a dehumidifying electronic expansion valve 11 and a cooling / heating electronic expansion valve 15. The first port of solenoid valve 16 is connected; the second port of dehumidifying electronic expansion valve 11 is connected in parallel with the first ports of several dehumidifying shell-and-tube heat exchangers 12 via a pipe, and the flow from the second ports of several dehumidifying shell-and-tube heat exchangers 12 flows into the third port of four-way reversing valve 6; the second port of cooling / heating solenoid valve 16 is connected in parallel with the first ports of several cooling / heating shell-and-tube heat exchangers 17 via a pipe, and the flow from the second ports of several cooling / heating shell-and-tube heat exchangers 17 flows into the third port of four-way reversing valve 6; the fourth port of four-way reversing valve 6 is connected in a pipe to the first port of gas-liquid separator 20, and the second port of gas-liquid separator 20 is connected to the inlet of several compressors 4. The outlets of several compressors 4 are also connected to refrigerant bypass solenoid valve 10 via pipes and the second port of four-way reversing valve 6, and the flow converges or diverges with the second port of electronic expansion valve 9.

[0022] Circulating water flow: The first interface of the dehumidifying shell-and-tube heat exchanger 12 is connected in parallel with several dehumidifying terminal devices 13 through a pipe. After the circulating water is collected, it is pumped back to the second interface of the dehumidifying shell-and-tube heat exchanger 12 through a circulating water pump. The first interface of the cooling and heating shell-and-tube heat exchanger 17 is connected to several phase change energy storage floor tiles 18 through a pipe for heat exchange. After the heat exchange, the circulating water is collected and pumped back to the second interface of the cooling and heating shell-and-tube heat exchanger 17 through a circulating water pump.

[0023] The above technical solution can realize cooling mode, dehumidification mode, and heating mode. The working principles of different working modes are as follows: Figure 2Cooling mode: The refrigerant is compressed into a high-temperature, high-pressure gas by several compressors 4. The gas is then transported to the finned heat exchanger 8 through the path adjustment of the four-way reversing valves 6-a and 6-b. After exchanging heat with the outdoor air, the gaseous refrigerant releases heat and condenses into a medium-temperature, high-pressure liquid refrigerant. After being throttled and depressurized by the electronic expansion valve 9, it becomes a low-temperature, low-pressure liquid refrigerant. After being regulated by the electric three-way valve 15 and the cooling / heating solenoid valve 16, it enters the cooling / heating shell-and-tube heat exchanger 17, where it exchanges heat with the circulating water on the other side. The liquid refrigerant absorbs heat and vaporizes into a low-temperature, low-pressure gaseous refrigerant. After being regulated by the path adjustment of the four-way reversing valves 6-c and 6-d and separated by the gas-liquid separator 20, it is compressed again into a high-temperature, high-pressure gaseous refrigerant, continuously performing the cooling cycle. In the cooling and heating shell-and-tube heat exchanger 17, the medium on the circulating water side absorbs heat from the liquid refrigerant and cools to a medium-temperature chilled water. This medium-temperature chilled water stores and cools several phase change energy storage floor tiles 18 laid on the pipes. The chilled water then releases heat from the phase change energy storage floor tiles 18 and radiates heat with the indoor air, cooling the indoor air and achieving a cooling effect. Simultaneously, the chilled water, heated after exchanging heat with the phase change energy storage floor tiles 18, flows back to the cooling and heating shell-and-tube heat exchanger 17 via the cooling and heating circulation pump 19.

[0024] (2) Figure 3 Dehumidification mode: The refrigerant is compressed into a high-temperature, high-pressure gas by several compressors 4. The gas is then transported to the finned heat exchanger 8 through the path adjustment of the four-way reversing valves 6-a and 6-b. After exchanging heat with the outdoor air, the gaseous refrigerant releases heat and condenses into a medium-temperature, high-pressure liquid refrigerant. After being throttled and depressurized by the electronic expansion valve 9, it becomes a low-temperature, low-pressure liquid refrigerant. After being adjusted by the electric three-way valve 15 and the dehumidification electronic expansion valve 11, it enters the dehumidification shell-and-tube heat exchanger 12, where it exchanges heat with the circulating water on the other side. The liquid refrigerant absorbs heat and vaporizes into a low-temperature, low-pressure gaseous refrigerant. After being adjusted by the path adjustment of the four-way reversing valves 6-c and 6-d and separated by the gas-liquid separator 20, it is compressed again into a high-temperature, high-pressure gaseous refrigerant, continuously performing the refrigeration cycle. In the dehumidification shell-and-tube heat exchanger 12, the medium on the circulating water side absorbs heat from the liquid refrigerant and is reduced to low-temperature chilled water. After entering several dehumidification terminal devices 13, it exchanges heat with the indoor air, and the indoor air is cooled and condenses out moisture, thus achieving the effects of cooling and dehumidification.

[0025] (3) Figure 4Heating mode: The refrigerant is compressed into high-temperature and high-pressure gas by several compressors 4. The gas is then transported to the refrigeration and heating shell-and-tube heat exchanger 17 through the path adjustment of four-way reversing valves 6-a and 6-c. It exchanges heat with the circulating water medium on the other side of the refrigeration and heating shell-and-tube heat exchanger. The circulating water medium absorbs the heat released by the high-temperature and high-pressure gaseous refrigerant and heats up to become low-temperature hot water. The low-temperature hot water stores and heats several phase change energy storage floor tiles 18 laid on the pipes. The phase change energy storage floor tiles 18 release heat and exchange heat with the indoor air through radiation. The indoor air is heated to achieve the heating effect. At the same time, the hot water that has cooled down after exchanging heat with several phase change energy storage floor tiles 18 flows back to the refrigeration and heating shell-and-tube heat exchanger 17 through the refrigeration and heating circulation pump 19. Meanwhile, in the refrigeration and heating shell-and-tube heat exchanger 17, the high-temperature and high-pressure gaseous refrigerant releases heat and condenses into a medium-temperature and high-pressure liquid refrigerant. After being regulated by the refrigeration and heating solenoid valve 16 and the electric three-way valve 15, the liquid refrigerant is throttled and depressurized by the electronic expansion valve 9 into a low-temperature and low-pressure liquid refrigerant. It then enters several finned heat exchangers 8 to exchange heat with the outdoor air. After absorbing the heat from the outdoor air, the liquid refrigerant vaporizes into a low-temperature and low-pressure gaseous refrigerant. After being regulated by the four-way reversing valves 6-b and 6-d and separated by the gas-liquid separator 20, the gaseous refrigerant is drawn into several compressors 4 and recompressed into a high-temperature and high-pressure gaseous refrigerant, continuously cycling to provide heating.

[0026] (4) Figure 2 Cooling mode Figure 3 The dehumidification mode can be run simultaneously or independently.

[0027] (5) Figure 2 Cooling mode Figure 3 Dehumidification mode Figure 4 The flow rate of the heating mode can be adjusted by the refrigerant bypass solenoid valve 10, thereby adjusting the cooling, dehumidification and heating effects.

[0028] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. An air source heat pump, phase change energy storage floor radiation system of split structure type, characterized in that: comprising an outdoor unit (1), an indoor unit (2) and an energy using unit (3); the outdoor unit (1) is integrated by a plurality of finned heat exchangers (8), a refrigerant electric regulating valve (7); the indoor unit (2) is integrated by a plurality of compressors (4), a one-way valve (5), a four-way reversing valve (6), an electronic expansion valve (9), a refrigerant bypass solenoid valve (10), a dehumidification electronic expansion valve (11), a dehumidification shell-and-tube heat exchanger (12), a dehumidification circulating pump (14), an electric three-way valve (15), a refrigeration and heating solenoid valve (16), a refrigeration and heating shell-and-tube heat exchanger (17), a refrigeration and heating circulating pump (19), a gas-liquid separator (20); the energy using unit (3) is integrated by a plurality of dehumidification terminal devices (13), a plurality of phase change energy storage floor tiles (18); the system is provided with a refrigerant flow pipeline and a circulating water side flow pipeline, the refrigerant flow pipeline realizes refrigerant circulation between the outdoor unit (1) and the indoor unit (2), and the circulating water side flow pipeline realizes water circulation heat exchange between the indoor unit (2) and the energy using unit (3). The connection relationship of the refrigerant flow pipeline is that: the outlets of the plurality of compressors (4) of the indoor unit (2) are connected to the first interface of the four-way reversing valve (6) through a pipeline, the second interface of the four-way reversing valve (6) is connected to the first interface of the refrigerant electric regulating valve (7) of the outdoor unit (1) branch pipeline through a pipeline, the second interface of the refrigerant electric regulating valve (7) is connected to the first interface of the finned heat exchanger (8), the second interfaces of the plurality of finned heat exchangers (8) are connected to the first interface of the electronic expansion valve (9) through parallel pipelines, the second interface of the electronic expansion valve (9) is connected to the first interface of the electric three-way valve (15), the second and third interfaces of the electric three-way valve (15) are respectively connected to the first interfaces of the dehumidification electronic expansion valve (11) and the refrigeration and heating solenoid valve (16); the second interface of the dehumidification electronic expansion valve (11) is connected to the first interfaces of the plurality of dehumidification shell-and-tube heat exchangers (12) through a pipeline in parallel, the second interfaces of the plurality of dehumidification shell-and-tube heat exchangers (12) are converged and then flow into the third interface of the four-way reversing valve (6); the second interface of the refrigeration and heating solenoid valve (16) is connected to the first interfaces of the plurality of refrigeration and heating shell-and-tube heat exchangers (17) through a pipeline in parallel, the second interfaces of the plurality of refrigeration and heating shell-and-tube heat exchangers (17) are converged and then flow into the third interface of the four-way reversing valve (6); The fourth interface of the four-way reversing valve (6) is connected to the first interface of the gas-liquid separator (20) through a pipeline, and the second interface of the gas-liquid separator (20) is connected to the inlets of the plurality of compressors (4). The outlets of the plurality of compressors (4) are also connected to the refrigerant bypass solenoid valve (10) through a pipeline and the second interface of the four-way reversing valve (6), and the output end of the refrigerant bypass solenoid valve (10) is converged or diverged with the second interface of the electronic expansion valve (9).

2. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 1, characterized in that: The refrigerant is a refrigerant, which completes the cycle process of compression, condensation / evaporation and throttling in the refrigerant flow pipeline. ​ ​ ​ ​ 3. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 2, characterized in that: ​ 4. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 2, characterized in that: ​ 5. An air source heat pump, phase change thermal storage, floor radiation system of split construction as defined in claim 1, wherein: The circulating water side flow pipeline is divided into a dehumidification water circulation branch and a cooling and hot water circulation branch. The dehumidification water circulation branch realizes the water circulation between the dehumidification shell-and-tube heat exchanger (12) and the dehumidification terminal equipment (13). The cooling and hot water circulation branch realizes the water circulation between the cooling and heating shell-and-tube heat exchanger (17) and the phase change energy storage floor tile (18).

6. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 5, characterized in that: The connection relationship of the dehumidification water circulation branch is as follows: The first interface of the dehumidifying shell-and-tube heat exchanger (12) on the circulating water side is connected in parallel with several dehumidifying terminal devices (13) through a pipeline. The water circulation outlets of several dehumidifying terminal devices (13) converge and are then transported back to the second interface of the dehumidifying shell-and-tube heat exchanger (12) on the circulating water side through the dehumidifying circulation pump (14).

7. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 5, characterized in that: The connection relationship of the cooling and hot water circulation branch is as follows: The first interface of the cooling and heating shell-and-tube heat exchanger (17) on the circulating water side exchanges heat with several phase change energy storage floor tiles (18) through a pipe. The circulating water after exchanging heat with the phase change energy storage floor tiles (18) is collected and then transported back to the second interface of the cooling and heating shell-and-tube heat exchanger (17) on the circulating water side through the cooling and heating circulating pump (19).

8. An air source heat pump, phase change thermal storage, floor radiation system of split construction as defined in claim 1, wherein: The system can achieve independent cooling mode, dehumidification mode, and heating mode, and the cooling mode and dehumidification mode can operate simultaneously.

9. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 8, characterized in that: In the cooling mode, the refrigerant is condensed by the finned heat exchanger (8), throttled by the electronic expansion valve (9), and then enters the cooling and heating shell-and-tube heat exchanger (17) through the electric three-way valve (15) and the cooling and heating solenoid valve (16) to exchange heat with the circulating water. The medium-temperature chilled water output by the cooling and heating shell-and-tube heat exchanger (17) is used to store cold for the phase change energy storage floor tiles (18) and releases cold through radiation to the room through the phase change energy storage floor tiles (18).

10. An air source heat pump, phase change thermal storage floor radiation system of split structure type according to claim 8, characterized in that: The refrigerant bypass solenoid valve (10) can adjust the refrigerant flow rate in cooling mode, dehumidification mode and heating mode, thereby adjusting the cooling, dehumidification and heating effects of the system. In the heating mode, after being compressed by the compressor (4), the refrigerant directly enters the cooling and heating shell-and-tube heat exchanger (17) through the four-way reversing valve (6) to exchange heat with the circulating water. The low-temperature hot water output by the cooling and heating shell-and-tube heat exchanger (17) stores heat in the phase change energy storage floor tile (18) and radiates heat to the room through the phase change energy storage floor tile (18). After completing the heat exchange, the refrigerant enters the finned heat exchanger (8) after being throttled by the electronic expansion valve (9) to absorb heat from the outdoor air, and then flows back to the compressor (4) through the four-way reversing valve (6) and the gas-liquid separator (20). In the dehumidification mode, the refrigerant is condensed by the finned heat exchanger (8) and throttled by the electronic expansion valve (9). It then enters the dehumidification shell-and-tube heat exchanger (12) through the electric three-way valve (15) and the dehumidification electronic expansion valve (11) to exchange heat with the circulating water. The low-temperature chilled water output by the dehumidification shell-and-tube heat exchanger (12) enters the dehumidification terminal equipment (13) to exchange heat with the indoor air, thereby achieving indoor cooling and dehumidification.

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