Heat pump driven coolant carrier pipe network type high and large space thermal management system and control method thereof

Abstract

This invention relates to a heat pump-driven refrigerant piping network-type thermal management system for large spaces and its control method. The thermal management system includes a refrigerant loop and a refrigerant loop connected via heat exchangers. The refrigerant loop includes an outdoor heat source refrigerant loop and an indoor heat source refrigerant loop. The refrigerant loop includes a bottom working refrigerant loop and a top heat recovery refrigerant loop. The bottom working refrigerant loop includes a refrigerant channel of a first heat exchanger and a first indoor unit. The top heat recovery refrigerant loop includes a refrigerant channel of a third heat exchanger and a second indoor unit. Compared with existing technologies, this invention provides reliable technical solutions in both structural configuration and control methods, considering the energy quality improvement characteristics, energy recovery characteristics, energy cascade utilization characteristics of heat pumps, and the physical characteristics of air density changing with temperature, across both spatial and temporal scales.

Description

Technical Field

[0001] This invention relates to a heat pump system, and more particularly to a heat pump-driven refrigerant piping network type high-rise space thermal management system and its control method. Background Technology

[0002] With the rapid development of China's urban economy and people's consumption levels, the demand for tall, spacious buildings with large spans and high-scale functional spaces is becoming increasingly strong, such as airports, train stations, large conference halls, and tall factories. These buildings are characterized by their height and large spans, with the activity areas often located at the bottom, while the top typically does not have strict temperature requirements. However, these buildings exhibit unique thermophysical properties, namely the chimney effect. During the use of tall, spacious buildings, the indoor hot air, due to its lower density, rises continuously, easily creating a large longitudinal temperature gradient. This results in higher temperatures at the top and lower temperatures in the activity areas at the bottom, further increasing the temperature and pressure difference between the top and the outdoor environment, causing extremely adverse natural outward convection. This poses a significant challenge to the energy-efficient and high-performance design of air conditioning systems for tall, spacious buildings.

[0003] In terms of indoor heating, air conditioners typically deliver hot air from the bottom of the building, allowing the air to rise naturally throughout the space for slow heating. However, in tall buildings, the chimney effect causes hot air to rapidly accumulate at the top, with a large amount of unused heat leaking out through the ceiling or skylights. This results in significant heat loss and energy waste, and the large vertical temperature gradient within the building also drastically reduces thermal comfort, creating a "hotter at the top, colder at the bottom" phenomenon, leading to excessively low temperatures in areas near the ground where people are active. In contrast, for indoor cooling, the cold air delivered by the air conditioner naturally sinks to the bottom of the building, so the focus is primarily on covering the lower areas where people are active. The chimney effect has a relatively minor impact on cooling performance, and cooling can even be enhanced by accelerating heat dissipation. Therefore, the design of air conditioning systems to address these issues in tall spaces, especially for heating in cold and frigid regions, is crucial.

[0004] Patent CN 218469179 U discloses a tiered air conditioning system for large-span, high-ceilinged spaces. This system utilizes air conditioning ducts with lifting mechanisms installed on both sides of the long side of the high-ceilinged space to allow for free adjustment of the air supply height and angle. The technology employs a position-adjustable, non-isothermal, high-speed jet airflow. In summer cooling conditions, energy savings can be achieved by dividing the entire high-ceilinged space into air-conditioned and non-air-conditioned zones. However, in winter heating conditions, this technology does not consider the significant heat accumulation and outward heat dissipation in the non-air-conditioned area at the top due to the chimney effect, resulting in substantial waste of heat transferred to the upper space.

[0005] Patent CN 211854195 U discloses an environmental system for large spaces. By installing insulated return air ducts in the upper and lower parts of the space and connecting them to an air conditioning unit, and using a fan and supply / return air louvers to switch between supply and return air modes, it can ultimately achieve summer cooling (supplying cold air from the top) and winter heating (supplying hot air from the bottom). However, due to the low density of hot air and the fact that people's activity areas in large spaces are often located at lower levels, the fixed installation of the top air vents in this technology must consider both the high ground clearance for absorbing hot air in winter and the low ground clearance for delivering cold air in summer. It cannot be adjusted in height according to usage patterns, significantly reducing the energy-saving performance of the environmental control system in large spaces.

[0006] In summary, most existing technological innovations aimed at improving energy consumption in temperature control of large spaces focus on the division between air-conditioned and non-air-conditioned areas and the optimization of circulating air composition and workflow. They have not considered starting from the structure of the heat pump air conditioning system itself, adding indoor coils to promptly recover and utilize waste heat from the building's roof. This would mitigate the chimney effect and allow the heat pump system to simultaneously utilize both outdoor ambient air and indoor roof hot air as heat sources, significantly reducing external energy consumption. Furthermore, due to the varying functions of temperature-controlled areas at different heights in large buildings, the temperature requirements of each area differ. When the function of a particular area changes, its temperature requirements (i.e., heat load requirements) also change. Therefore, the development of waste heat recovery technology for the roofs of large buildings and thermal management technologies capable of meeting the differentiated dynamic temperature requirements of different temperature zones at different heights in large buildings is urgently needed. Summary of the Invention

[0007] The purpose of this invention is to overcome the shortcomings of existing technologies by providing a heat pump-driven refrigerant piping network-based thermal management system and its control method for large spaces. By combining the energy quality enhancement characteristics, energy recyclability, and energy cascade utilization characteristics of heat pumps with the physical characteristics of air density changing with temperature across both spatial and temporal scales, reliable technical solutions are provided from both structural configuration and control method perspectives. In terms of structural configuration, building upon the traditional heat pump system that only uses ambient air as a heat source, this invention addresses the chimney effect characteristics of large spaces by adding an indoor heat exchange coil that uses the large amount of hot air accumulated at the top as a second heat source, proposing a dual-heat-source heat pump system and constructing a complete refrigerant piping network. Regarding the control method, since the actual temperature and thermal comfort requirements of different areas within a large space vary at different stages of its use, this invention proposes a full-cycle operation phase control method. This method uses valve opening and closing control to switch between different operational phases under varying needs. Ultimately, this invention enables refined, layered, and dynamic thermal management of large spaces while maintaining optimal energy efficiency.

[0008] The objective of this invention can be achieved through the following technical solutions: This invention primarily protects a heat pump-driven refrigerant piping network-type thermal management system for tall spaces. Due to the unique chimney effect of tall buildings, a large amount of hot air rapidly accumulates at the top of the space during use, resulting in a persistently high temperature at the top and a low temperature at the bottom. This significant longitudinal temperature gradient leads to extremely poor thermal comfort. Therefore, this invention designs a heat pump structure that can simultaneously utilize indoor and outdoor coils. It can use both outdoor ambient air and hot air from the top of the space as heat sources, recovering waste heat from the top to control the temperature of the lower activity areas where temperature is required. Furthermore, by using the hot air from the top as one of the heat sources, the longitudinal temperature gradient within tall buildings can be improved, mitigating the significant heat loss caused by the chimney effect.

[0009] Furthermore, the thermal management system comprises two parts in terms of system composition: a refrigerant loop and a secondary refrigerant loop. In terms of spatial arrangement, the thermal management system includes both outdoor and indoor installation components.

[0010] Furthermore, in terms of system composition, the refrigerant loop and the secondary refrigerant loop are connected by a heat exchanger. The secondary refrigerant loop is connected to the interior of tall, spacious buildings by the secondary refrigerant coils of the indoor unit.

[0011] Furthermore, in terms of system composition, the refrigerant loop includes an outdoor heat source refrigerant loop and an indoor heat source refrigerant loop.

[0012] The outdoor heat source refrigerant loop includes a first heat exchanger refrigerant passage, a first throttling valve, a second shut-off valve, a second heat exchanger refrigerant passage, a first compressor, a four-way reversing valve, and a sixth shut-off valve, all connected sequentially by copper pipes. Specifically, the left port A of the four-way reversing valve is connected to the sixth shut-off valve. The upper port B of the four-way reversing valve is connected to the discharge port of the first compressor. The right port C of the four-way reversing valve is connected to the refrigerant passage of the second heat exchanger. The lower port D of the four-way reversing valve is connected to the suction port of the first compressor.

[0013] The indoor heat source refrigerant loop includes a first heat exchanger refrigerant passage, a first shut-off valve, a second throttle valve, a third heat exchanger refrigerant passage, a second compressor, and a fourth shut-off valve, all connected in sequence by copper pipes.

[0014] Furthermore, the outdoor heat source refrigerant loop and the indoor heat source refrigerant loop can be interconnected through the opening and closing actions of the third shut-off valve and the fifth shut-off valve.

[0015] Furthermore, in terms of system composition, the refrigerant loop includes a bottom working refrigerant loop and a top heat recovery refrigerant loop.

[0016] The bottom working refrigerant loop includes a first heat exchanger refrigerant channel, a first bypass valve, and a first indoor unit connected in sequence by refrigerant piping. The first bypass valve can control the flow rate of refrigerant through the internal heat exchange coil of the first indoor unit by adjusting the valve opening.

[0017] The top heat recovery refrigerant loop includes a third heat exchanger refrigerant channel, a second bypass valve, and a second indoor unit connected in sequence via refrigerant piping. The second bypass valve can control the flow rate of refrigerant through the internal heat exchange coil of the second indoor unit by adjusting the valve opening.

[0018] Furthermore, in terms of spatial arrangement, the outdoor installation includes the installation of the refrigerant loop. All equipment and pipes on the refrigerant loop are arranged in a suitable location on the exterior of a tall, spacious building to facilitate centralized management and control of the refrigerant system.

[0019] Furthermore, in terms of spatial arrangement, the indoor installation includes the installation of a refrigerant loop and indoor units connected in series. The first indoor unit and its supporting equipment are installed at the bottom of the building to control the temperature of the activity area for people at the bottom where temperature requirements are specified. The second indoor unit and its supporting equipment are installed at the top of the building to recover a large amount of excess heat accumulated in the top area where temperature requirements are not specified, reducing heat loss to the outside through the roof while also migrating the heat accumulated at the top to the bottom.

[0020] Furthermore, the number of indoor units connected in series on the refrigerant loop is unlimited; it can be a single unit or more. In terms of the overall functionality of tall, spacious buildings, the functional requirements generally differ across different height zones, thus the temperature requirements also vary. Therefore, this invention requires dividing the space by height to determine the temperature control zones based on indoor temperature requirements, establishing one indoor unit for each zone, and finally connecting the multiple indoor units in series through the refrigerant loop to achieve refined, layered thermal management covering the entire tall, spacious area.

[0021] Furthermore, water is preferably used as the refrigerant in this invention.

[0022] Furthermore, the heat pump driven piping network in the system of the present invention is not limited to the refrigerant piping network (i.e., the refrigerant system is independently set up outdoors, and the refrigerant enters the heat exchange coil in the indoor unit to exchange heat with the indoor air). In actual use, the heat pump driven refrigerant piping network (i.e., the refrigerant in the heat pump system flows directly into the heat exchange coil in the indoor unit to exchange heat with the indoor air) or the heat pump driven air piping network (i.e., both the refrigerant system and the air handling system are set up outdoors, the refrigerant enters the heat exchange coil in the air handling unit to exchange heat with the return air from the indoor unit, and the air is treated before being sent into the indoor unit) can be used to partially or completely replace the heat pump driven refrigerant-refrigerant-air mixed piping network. Ultimately, a heat pump driven refrigerant-refrigerant-air mixed piping network thermal management system can be formed.

[0023] The second objective of this invention is to protect a control method for a heat pump-driven refrigerant network-type thermal management system for large spaces. Since the internal temperature of a large space remains stable and consistent with the external environment when it is not in use for extended periods, the chimney effect has little impact. Therefore, during the initial use of the building, there is not much waste heat at the top for heat recovery, and at this time, it is not necessary to activate the top heat recovery refrigerant loop; only heating of the bottom areas with temperature requirements is needed. However, as the bottom working refrigerant loop continues to operate, a large amount of hot air will rapidly converge at the top of the space. When the heat exceeds a certain threshold, the top heat recovery refrigerant loop needs to be activated for heat recovery and area temperature control. Therefore, this invention designs a full-cycle operation control method to address the dynamic heat recovery needs of large spaces during heating.

[0024] Furthermore, the full-cycle operation phase control method controls the opening and closing actions of the shut-off valve and the bypass valve, and completes the full-cycle efficient heating of the entire tall, spacious building interior by periodically switching between the following four major operation phases: 1. External circulation heating operation phase: When a tall, spacious building has not been used for a long time and is about to start indoor heating for the first time, its initial indoor temperature is in a stable state consistent with the outside ambient temperature, that is, the indoor temperature is equal to the outside ambient temperature and lower than the thermal comfort lower limit temperature set for areas with temperature requirements. At this time, in terms of valve control, the second shut-off valve, the sixth shut-off valve, and the first bypass valve are opened, and the remaining valves are closed; the outdoor heat source refrigerant loop and the bottom working refrigerant loop are switched to the open state; the indoor heat source refrigerant loop and the top heat recovery refrigerant loop are both switched to the closed state; during this phase, the refrigerant system has only outdoor air as a heat source, and only the bottom first indoor unit in the indoor units heats the space to quickly raise the indoor temperature; 2. Synchronous Operation Stage of Internal and External Circulation Heat Recovery: After the system has been operating in the external circulation heating stage for a period of time, the indoor temperature of the high space continues to rise. Due to the chimney effect, hot air in the space rapidly gathers at the top, and the higher the location, the faster the temperature rises. Therefore, the temperature rise rate is fastest in the high-altitude areas without temperature requirements. When the temperature reaches the heat recovery set temperature, the first, second, fourth, and sixth shut-off valves, the first bypass valve, and the second bypass valve are opened, while the remaining valves are closed. The refrigerant loop and the refrigerant loop are all switched to the open state. During this stage, the refrigerant system uses both outdoor air and hot air from the top of the room as heat sources. In addition to the first indoor unit at the bottom heating the space to raise the temperature of areas with temperature requirements, the second indoor unit at the top can also recover waste heat from the top, weakening the chimney effect and reducing the energy demand from the outside. 3. Internal circulation heat recovery operation phase: Specifically, after the system has been operating in the internal and external circulation heat recovery synchronous operation phase for a period of time, the temperature of the bottom area with temperature requirements gradually rises, and the heat load demand gradually decreases. When the heat load demand of this area can be met by recovering heat from the top area without temperature requirements, the first shut-off valve, the fourth shut-off valve, the first bypass valve, and the second bypass valve are opened, and the remaining valves are closed. During this phase, the refrigerant system uses the hot air at the top of the room as the only heat source. The heat output of the first indoor unit at the bottom is the same as the heat recovered by the second indoor unit at the top. The heating demand of the bottom area with temperature requirements is met in the internal heat circulation without the need for external energy input. 4. Intermittent Operation Phase: After the system operates in the above-mentioned phase for a period of time, under the combined effect of external circulation heating and internal circulation heat recovery, the temperature of the bottom area with temperature requirements continuously rises. When it reaches the upper limit of thermal comfort temperature, the entire system shuts down until the temperature of the area with temperature requirements drops to the lower limit of thermal comfort temperature. At this point, the valve control switches to the same mode as the external circulation heating mode. The difference is that the initial temperature of the area with temperature requirements changes from the ambient temperature to the lower limit of thermal comfort temperature. During this phase, intermittent heating can be achieved for tall, spacious buildings, significantly reducing heating energy consumption while meeting thermal comfort requirements. This invention system achieves flexible matching of dynamic heat recovery needs in high-ceilinged spaces under heating mode by cyclically switching between the above-mentioned working stages. Furthermore, it should be noted that during the use of a high-ceilinged space, when the function of a certain area changes, the corresponding temperature requirement of that area will also change. To meet this change, this invention can control the opening degree of the bypass valves equipped on different indoor units in the refrigerant loop, thereby adjusting the flow rate of refrigerant flowing into the indoor units of each temperature-controlled zone to match the heat load of different areas. Finally, when the high-ceilinged space is no longer in use or there is no temporary heating demand, all valves are closed. Thus, the indoor heating of the entire high-ceilinged building throughout its entire lifecycle is completed.

[0025] Furthermore, when the heat pump-driven refrigerant pipeline type high-rise space thermal management system of the present invention switches to the external circulation heating operation stage, its working process is as follows: When the outdoor heat source refrigerant loop is opened, the low-temperature, low-pressure refrigerant gas flowing out of the refrigerant heat exchange channel of the second heat exchanger first enters the first compressor through the four-way reversing valve. Then, the compressed high-temperature, high-pressure refrigerant gas flows into the refrigerant heat exchange channel of the first heat exchanger through the four-way reversing valve. In the first heat exchanger, the high-temperature, high-pressure refrigerant gas transfers heat to the bottom working refrigerant loop through the heat exchange coil, heating the refrigerant supplied to the first indoor unit. Next, the cooled low-temperature, high-pressure refrigerant subcooled liquid flows into the first throttling valve and is throttled and depressurized into a low-temperature, low-pressure two-phase refrigerant. Then, the low-temperature, low-pressure refrigerant enters the refrigerant heat exchange channel of the second heat exchanger, absorbs heat from the outdoor air, and evaporates into superheated refrigerant gas. Finally, the low-temperature, low-pressure refrigerant gas enters the first compressor again through the four-way reversing valve to complete the outdoor heat source refrigerant loop, realizing the absorption of heat from the outdoor air. When the bottom working refrigerant loop is opened, the high-temperature refrigerant flowing out of the refrigerant heat exchange channel of the first heat exchanger enters the heat exchange coil of the first indoor unit through the first bypass valve. The high-temperature refrigerant transfers heat to the low-temperature indoor air driven by the indoor unit fan in the refrigerant coil. Then, the cooled low-temperature refrigerant returns to the refrigerant heat exchange channel of the first heat exchanger, absorbs the heat released by the high-temperature and high-pressure refrigerant flowing in the refrigerant heat exchange channel of the first heat exchanger, and is then reheated into high-temperature refrigerant to complete the bottom working refrigerant loop. Furthermore, when the heat pump-driven refrigerant pipeline type high-rise space thermal management system of the present invention switches to the stage of simultaneous operation of internal and external circulation heat recovery, its working process is as follows: Both the outdoor heat source refrigerant loop and the bottom working refrigerant loop are open, and their working process is consistent with the external circulation heating operation stage; the difference is that during this stage, both the indoor heat source refrigerant loop and the top heat recovery refrigerant loop are switched from closed to open. When the indoor heat source refrigerant loop is opened, the low-temperature, low-pressure refrigerant gas flowing out of the refrigerant heat exchange channel of the third heat exchanger first enters the second compressor. Then, the compressed high-temperature, high-pressure refrigerant gas flows into the refrigerant heat exchange channel of the first heat exchanger through the fourth shut-off valve. In the first heat exchanger, the high-temperature, high-pressure refrigerant gas transfers heat to the bottom working refrigerant loop through the heat exchange coil, heating the refrigerant supplied to the first indoor unit. Next, the cooled low-temperature, high-pressure refrigerant subcooled liquid flows into the second throttling valve through the first shut-off valve and is throttled and depressurized into a low-temperature, low-pressure two-phase refrigerant. Then, the low-temperature, low-pressure refrigerant enters the refrigerant heat exchange channel of the third heat exchanger, absorbs heat recovered from the top of the building by the top heat recovery refrigerant loop, and evaporates into superheated refrigerant gas. Finally, the low-temperature, low-pressure refrigerant gas re-enters the second compressor to complete the indoor heat source refrigerant loop, realizing the recovery of heat from the hot air accumulated at the top of the high space. When the top heat recovery refrigerant loop is opened, the low-temperature refrigerant flowing out of the refrigerant heat exchange channel of the third heat exchanger enters the heat exchange coil of the second indoor unit through the second bypass valve. The low-temperature refrigerant absorbs the high-temperature air at the top of the room driven by the indoor unit fan in the refrigerant coil of the indoor unit. Then, the heated high-temperature refrigerant returns to the refrigerant heat exchange channel of the third heat exchanger, releasing heat to the low-temperature, low-pressure refrigerant flowing in the refrigerant heat exchange channel of the third heat exchanger, and is then cooled back to low-temperature refrigerant to complete the top heat recovery refrigerant loop. Furthermore, when the heat pump-driven refrigerant pipeline type high-rise space thermal management system of the present invention switches to the internal circulation heat recovery operation stage, its working process is as follows: The bottom working refrigerant loop, the top heat recovery refrigerant loop, and the indoor heat source refrigerant loop are all open, and their working process is consistent with the synchronous operation phase of internal and external circulation heat recovery; the difference is that during this phase, the outdoor heat source refrigerant loop is switched from open to closed. Furthermore, it should be noted that the above describes the workflow and control methods for high-ceilinged spaces in heating mode. The system of this invention can achieve flexible switching between heating and cooling modes by switching the connection states of different ports of the four-way reversing valve in the refrigerant loop and controlling the opening and closing action of the shut-off valve.

[0026] Furthermore, when the system of the present invention switches to the cooling mode, it is only necessary to open the second, third, fifth, and sixth shut-off valves and close the first and fourth shut-off valves. This allows the first and third heat exchangers to operate as evaporators while the second heat exchanger operates as a condenser. This ensures that the refrigerant entering the indoor unit to exchange heat with the indoor air is low-temperature refrigerant. The low-temperature refrigerant absorbs heat at both the top and bottom of the tall building and is finally discharged through the second heat exchanger located outdoors, which can significantly improve the indoor cooling efficiency.

[0027] This invention aims to protect a heat pump-driven refrigerant piping network-type thermal management system for large spaces and its control method. Its thermal management functions cover both spatial and temporal scales. Furthermore, under the control method of this invention, the system can also achieve both energy conservation and energy saving. To achieve the above effects, this invention has made the following designs in terms of structural configuration and control scheme, and obtained corresponding beneficial effects: 1. In terms of structural configuration, due to the unique chimney effect of tall, open-air buildings, a large amount of hot air will rapidly accumulate at the top of the space during use, resulting in a persistently high temperature at the top and a low temperature at the bottom, creating a significant longitudinal temperature gradient within the building. Therefore, this invention designs and employs a heat pump structure that can simultaneously utilize indoor and outdoor coils, proposing a dual-heat-source heat pump air conditioning system capable of using both outdoor ambient air and hot air from the top of the interior as heat sources.

[0028] On the one hand, this invention can improve the chimney effect caused by the accumulation of hot air by recovering waste heat from the top of tall spaces, reduce the ineffective loss of heat to the outside, and lower the vertical temperature gradient inside the room, thereby improving indoor thermal comfort. At the same time, it can also transfer excess heat from the upper parts of the room to the lower parts of the space where people are active, significantly reducing the energy consumption of heat pump heating and achieving the effect of increasing revenue and saving energy. On the other hand, by introducing hot air from the top of the room as a second heat source, since its temperature is higher than that of ambient air, it can significantly reduce the average compression ratio of the compressor in the entire system compared to traditional heat pump air conditioning systems that only use ambient air as the sole heat source, thereby improving the system's operating performance and achieving greater energy-saving effects.

[0029] 2. In terms of structural configuration, the functional uses of tall, spacious buildings differ across different height zones, resulting in varying optimal temperature ranges. The lower levels of the space, often designated for work and activity areas, have particularly strong heating and cooling requirements. Therefore, this invention employs a heat pump-driven refrigerant piping network for indoor thermal management. First, the space is divided vertically based on indoor temperature requirements, defining temperature control zones. One indoor unit is installed in each zone. Finally, the indoor units are connected in series via two refrigerant loops to achieve layered thermal management across the entire tall, spacious area.

[0030] On the one hand, this system can adjust the connection status of the four-way reversing valve in the refrigerant system and the opening degree of the bypass valves on different indoor unit sides of the two refrigerant loops according to the real-time temperature of each area. This satisfies the heating and cooling needs of each temperature zone while also enabling tiered energy utilization through the series-connected refrigerant loops passing through the heat exchange coils of the indoor units in different areas. This reduces the temperature difference between the air in each temperature zone and the corresponding heat exchange coil, flexibly matching the heat load required by different areas, ultimately significantly improving the overall system efficiency and reducing energy consumption. On the other hand, this invention uses a refrigerant as the heat transfer medium (preferably water), which is easier to store and transport than refrigerant or air, making the system design and installation simpler. Furthermore, the refrigerant system can be installed independently outdoors, avoiding potential problems such as refrigerant leakage or high noise pollution from the heat pump unit.

[0031] 3. Regarding the control method, since the internal temperature of a large space remains stable and consistent with the outside temperature when it is not used for a long time, the chimney effect has little impact. Therefore, in the initial stage of building use, there is not much waste heat at the top for heat recovery, so there is no need to activate the top heat recovery refrigerant loop; only heating / cooling of the bottom area is required. As the bottom refrigerant loop continues to operate, a large amount of hot air will rapidly gather at the top of the space. When the heat exceeds a certain threshold, the top refrigerant loop needs to be activated for heat recovery and zone temperature control. Therefore, this invention designs and adopts a full-cycle operation phase control method to address the dynamic heat recovery needs during the use of large spaces. Under the control method of this invention, the opening and closing actions of the indoor units in the refrigerant loop and the refrigerant loop can cycle through four operation phases according to the real-time temperature of each area of ​​the building, instantly matching the heat recovery state under different environments to maintain the balance of the indoor temperature gradient, thereby completing the dynamic and efficient thermal management of the entire large space.

[0032] 4. Regarding control methods, in tall, spacious buildings, the temperature requirements of temperature-controlled zones at different heights vary due to differences in their functions. Furthermore, when the function of a particular zone changes, its temperature requirements also change. Therefore, this invention addresses the randomly changing temperature requirements of temperature-controlled zones at different heights in tall spaces by equipping each indoor unit with a dedicated bypass valve. By controlling the opening of the bypass valves of different indoor units in the refrigerant loop, the flow rate of refrigerant flowing into the indoor units of each temperature-controlled zone can be adjusted to match the heat load of different zones, ultimately achieving layered, differentiated, and dynamic thermal management for each temperature-controlled zone. Attached Figure Description

[0033] Figure 1 This is a schematic diagram of the structural principle of a heat pump-driven refrigerant pipeline type high-rise space thermal management system according to Embodiment 1 of the present invention.

[0034] Figure 2 This is a schematic diagram of the operating principle of a heat pump driven refrigerant pipeline type high-rise space thermal management system in Embodiment 1 of the present invention (heating mode - external circulation heating operation stage).

[0035] Figure 3 This is a schematic diagram of the operating principle of a heat pump driven refrigerant pipeline type high-rise space thermal management system in Embodiment 1 of the present invention (heating mode - internal and external circulation heat recovery synchronous operation stage).

[0036] Figure 4 This is a schematic diagram of the operating principle of a heat pump driven refrigerant pipeline type high-rise space thermal management system in Embodiment 1 of the present invention (heating mode - internal circulation heat recovery operation stage).

[0037] Figure 5This is a schematic diagram (cooling mode) illustrating the operating principle of a heat pump-driven refrigerant pipeline type high-rise space thermal management system according to Embodiment 1 of the present invention.

[0038] Figure 6 This is a schematic diagram of the structural principle of a heat pump-driven refrigerant pipeline network type high-space multi-temperature stratified thermal management system according to Embodiment 2 of the present invention.

[0039] Figure 7 This is a schematic diagram (heating mode) of the operation principle of a heat pump driven refrigerant pipeline network type high-ceiling multi-temperature stratified thermal management system in Embodiment 2 of the present invention.

[0040] Figure 8 This is a schematic diagram of the structural principle of a heat pump driven hybrid pipe network type high-space multi-temperature stratified thermal management system in Embodiment 3 of the present invention.

[0041] Figure 9 This is a schematic diagram (heating mode) of the operating principle of a heat pump driven hybrid pipe network type high-ceiling multi-temperature stratified thermal management system in Embodiment 3 of the present invention.

[0042] Figures 1 to 5 In the diagram, 1 represents the first heat exchanger; 2 represents the second heat exchanger; 3 represents the third heat exchanger; 4 represents the first compressor; 5 represents the second compressor; 6 represents the four-way reversing valve; 7 represents the first throttle valve; 8 represents the second throttle valve; 9 represents the first shut-off valve; 10 represents the second shut-off valve; 11 represents the third shut-off valve; 12 represents the fourth shut-off valve; 13 represents the fifth shut-off valve; 14 represents the sixth shut-off valve; 15 represents the first indoor unit; 16 represents the second indoor unit; 17 represents the first bypass valve; and 18 represents the second bypass valve. Figures 6 to 7 In the diagram, 1 represents the first heat exchanger; 2 represents the second heat exchanger; 3 represents the third heat exchanger; 4 represents the first compressor; 5 represents the second compressor; 6 represents the four-way reversing valve; 7 represents the first throttle valve; 8 represents the second throttle valve; 9 represents the first shut-off valve; 10 represents the second shut-off valve; 11 represents the third shut-off valve; 12 represents the fourth shut-off valve; 13 represents the fifth shut-off valve; 14 represents the sixth shut-off valve; 15 represents the first indoor unit; 16 represents the second indoor unit; 17 represents the third indoor unit; 18 represents the fourth indoor unit; 19 represents the fifth indoor unit; 20 represents the sixth indoor unit; 21 represents the first bypass valve; 22 represents the second bypass valve; 23 represents the third bypass valve; 24 represents the fourth bypass valve; 25 represents the fifth bypass valve; 26 represents the sixth bypass valve; 27 represents the seventh bypass valve; 28 represents the eighth bypass valve; 29 represents the ninth bypass valve; 30 represents the tenth bypass valve; 31 represents the eleventh bypass valve; and 32 represents the twelfth bypass valve. Figures 8 to 9In this diagram, 1 is a variable refrigerant flow heat pump box; 2 is a refrigerant pipe; 3 is a second refrigerant coil indoor unit; 4 is a refrigerant pipe; 5 is a first refrigerant coil indoor unit; 6 is a variable refrigerant flow heat pump box; 7 is a refrigerant copper pipe; 8 is a second refrigerant coil indoor unit; 9 is a refrigerant copper pipe; 10 is a first refrigerant coil indoor unit; 11 is a variable air volume heat pump box; 12 is a refrigerant copper pipe; 13 is a second air handling unit; 14 is a top air inlet duct; 15 is a top air inlet; 16 is a top return air inlet; 17 is a top return air duct; 18 is a refrigerant copper pipe; 19 is a first air handling unit; 20 is a bottom air inlet duct; 21 is a bottom air inlet; 22 is a bottom return air inlet; and 23 is a bottom return air duct. Detailed Implementation

[0043] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments. Component models, material names, connection structures, control methods, algorithms, and other features not explicitly described in this technical solution are considered common technical features disclosed in the prior art.

[0044] Example 1 See Figure 1 This embodiment describes a heat pump-driven refrigerant pipeline type high-rise space thermal management system, which includes two parts in terms of system composition: a refrigerant loop and a refrigerant pipeline, and two parts in terms of spatial arrangement: outdoor installation and indoor installation. In terms of system composition, the refrigerant loop and the secondary refrigerant loop are connected by a heat exchanger; the air inside the tall building and the secondary refrigerant loop are connected by a heat exchanger through the secondary refrigerant coil of the indoor unit. In terms of system composition, the refrigerant loop includes an outdoor heat source refrigerant loop and an indoor heat source refrigerant loop; The outdoor heat source refrigerant loop includes a first heat exchanger 1 refrigerant passage, a first throttling valve 7, a second shut-off valve 10, a second heat exchanger 2 refrigerant passage, a first compressor 4, a four-way reversing valve 6, and a sixth shut-off valve 14, connected in sequence by copper pipes. The lower port of the four-way reversing valve 6 is connected to the inlet of the first compressor 4; the upper port of the four-way reversing valve 6 is connected to the outlet of the first compressor 4; the left port of the four-way reversing valve 6 is connected to one end of the refrigerant heat exchange passage of the first heat exchanger 1; and the right port of the four-way reversing valve 6 is connected to one end of the refrigerant heat exchange passage of the second heat exchanger 2. The indoor heat source refrigerant loop includes a first heat exchanger 1 refrigerant passage, a first shut-off valve 9, a second throttle valve 8, a third heat exchanger 3 refrigerant passage, a second compressor 5, and a fourth shut-off valve 12, which are connected in sequence by copper pipes. The outdoor heat source refrigerant loop and the indoor heat source refrigerant loop can be interconnected through the opening and closing actions of the third shut-off valve 11 and the fifth shut-off valve 13. In terms of system composition, the refrigerant loop includes a bottom working refrigerant loop and a top heat recovery refrigerant loop; The bottom working refrigerant loop includes a refrigerant channel for a first heat exchanger 1, a first bypass valve 17, and a first indoor unit 15 connected in sequence by a refrigerant pipe; the first bypass valve 17 can control the flow rate of refrigerant through the internal heat exchange coil of the first indoor unit 15 by adjusting the valve opening. The top heat recovery refrigerant loop includes a third heat exchanger 3 refrigerant channel, a second bypass valve 18 and a second indoor unit 16 connected in sequence by a refrigerant pipe; the second bypass valve 18 can control the flow rate of refrigerant through the internal heat exchange coil of the second indoor unit 16 by adjusting the valve opening.

[0045] In terms of spatial layout, outdoor installation includes the installation of the refrigerant loop; all equipment and pipes on the refrigerant loop are arranged in a suitable location on the outside of the tall building to facilitate centralized management and control of the refrigerant system.

[0046] In terms of spatial arrangement, the indoor installation includes the installation of the refrigerant loop and the indoor units connected in series; the first indoor unit 15 and its supporting equipment are installed at the bottom of the building to complete the temperature control of the bottom activity area where temperature requirements are required; the second indoor unit 16 and its supporting equipment are installed at the top of the building to recover a large amount of excess heat accumulated in the top area where there are no temperature requirements, reduce the heat loss to the outside through the roof, and also complete the transfer of heat accumulated at the top to the bottom.

[0047] Because the internal temperature of a tall, spacious space remains stable and consistent with the outside temperature when it is not in use for extended periods, the chimney effect has little impact. Therefore, during the initial stages of building use, there is not much waste heat at the top for heat recovery, and it is not necessary to activate the top heat recovery refrigerant loop; only heating of the areas at the bottom with temperature requirements is needed. However, as the bottom refrigerant loop continues to operate, a large amount of hot air will rapidly accumulate at the top of the space. When the heat exceeds a certain threshold, the top heat recovery refrigerant loop must be activated for heat recovery and area temperature control. Therefore, this embodiment designs a full-cycle operation phase control method to address the dynamic heat recovery needs of tall, spacious spaces during heating.

[0048] See Figures 2 to 4 In this embodiment, the full-cycle operation control method of a heat pump-driven refrigerant pipeline type high-rise space thermal management system is to control the opening and closing actions of the shut-off valve and the bypass valve, and to complete the full-cycle efficient heating of the entire high-rise space building interior by periodically switching between the following four major operation stages: 1. External circulation heating operation phase: See Figure 2When a tall, spacious building has not been used for a long time and is about to be heated for the first time, its initial indoor temperature is in a stable state that is consistent with the outside ambient temperature. That is, the indoor temperature is equal to the outside ambient temperature and lower than the thermal comfort lower limit temperature set for areas with temperature requirements. At this time, in terms of valve control, the second shut-off valve 10, the sixth shut-off valve 14 and the first bypass valve 17 are opened, and the remaining valves 9, 11, 12, 13 and 18 are closed. The outdoor heat source refrigerant loop and the bottom working refrigerant loop are switched to the open state. The indoor heat source refrigerant loop and the top heat recovery refrigerant loop are both switched to the closed state. During this stage, the refrigerant system has only one heat source, the outdoor air, and only the bottom first indoor unit 15 in the indoor units heats the space to quickly raise the indoor temperature. 2. Synchronous operation phase of internal and external circulation heat recovery: See Figure 3 After the system has been operating in the external circulation heating phase for a period of time, the indoor temperature of the high space continues to rise. Due to the chimney effect, the hot air in the space quickly gathers at the top, and the higher the position, the faster the temperature rises. Therefore, the temperature rise rate is fastest in the high-altitude areas without temperature requirements. When the temperature reaches the heat recovery set temperature, the first shut-off valve 9, the second shut-off valve 10, the fourth shut-off valve 12, the sixth shut-off valve 14, the first bypass valve 17, and the second bypass valve 18 are opened, while the remaining valves 11 and 13 are closed. The refrigerant loop and the refrigerant loop are all switched to the open state. During this phase, the refrigerant system uses both outdoor air and hot air at the top of the room as heat sources. In addition to the first indoor unit 15 at the bottom heating the space to raise the temperature of the areas with temperature requirements, the second indoor unit 16 at the top can also recover waste heat from the top, weakening the chimney effect and reducing the energy demand from the outside. 3. Internal circulation heat recovery operation phase: Specifically, see Figure 4 When the system operates in the synchronous internal and external heat recovery phase for a period of time, the temperature of the area with temperature requirements at the bottom gradually rises, and the heat load demand gradually decreases. When the heat load demand of this area can be met by recovering heat from the area without temperature requirements at the top, the first shut-off valve 9, the fourth shut-off valve 12, the first bypass valve 17, and the second bypass valve 18 are opened, while the remaining valves 10, 11, 13, and 14 are closed. During this phase, the refrigerant system uses the hot air at the top of the room as the only heat source. The heat output of the first indoor unit 15 at the bottom is the same as the heat recovered by the second indoor unit 16 at the top. The heating demand of the area with temperature requirements at the bottom of the room is met in the internal heat cycle without the need for external energy input. 4. Intermittent Operation Phase: After the system operates in the above phase for a period of time, under the combined effect of external circulation heating and internal circulation heat recovery, the temperature of the area with temperature requirements at the bottom continuously rises. When it reaches the upper limit of thermal comfort temperature, the entire system shuts down until the temperature of the area with temperature requirements drops to the lower limit of thermal comfort temperature. The valve control then switches to the same operation mode as external circulation heating. The difference is that the initial temperature of the area with temperature requirements changes from ambient temperature to the lower limit of thermal comfort temperature. During this phase, intermittent heating can be achieved for tall, spacious buildings, significantly reducing heating energy consumption while meeting thermal comfort requirements. In this embodiment, the system can flexibly match the dynamic heat recovery needs of large spaces under heating mode by cyclically switching between the above-mentioned working stages. In addition, it should be noted that during the use of large spaces, when the function of a certain area changes, the corresponding temperature requirement of that area will also change. To meet this change, this embodiment can control the opening of the bypass valves equipped with different indoor units on the refrigerant loop, thereby adjusting the flow rate of refrigerant flowing into the indoor units of each temperature control zone to match the heat load of different areas. Finally, when the large space is no longer in use or there is no heating demand, all valves are closed. Thus, the indoor heating of the entire large space building throughout the entire cycle is completed.

[0049] See Figure 2 In this embodiment, when a heat pump-driven refrigerant pipeline type high-rise space thermal management system switches to the external circulation heating operation stage, its workflow is as follows: When the outdoor heat source refrigerant loop is opened, the low-temperature, low-pressure refrigerant gas flowing out of the refrigerant heat exchange channel of the second heat exchanger 2 first enters the first compressor 4 through the four-way reversing valve 6; then, the compressed high-temperature, high-pressure refrigerant gas flows into the refrigerant heat exchange channel of the first heat exchanger 1 through the four-way reversing valve 6; the high-temperature, high-pressure refrigerant gas transfers heat to the bottom working refrigerant loop through the heat exchange coil in the first heat exchanger 1 to heat the refrigerant supplied to the first indoor unit 15; immediately afterward, the cooled low-temperature, high-pressure refrigerant subcooled liquid flows into the first throttling valve 7 and is throttled and depressurized into a low-temperature, low-pressure two-phase refrigerant; then, the low-temperature, low-pressure refrigerant enters the refrigerant heat exchange channel of the second heat exchanger 2, absorbs heat from the outdoor air and evaporates into superheated refrigerant gas; finally, the low-temperature, low-pressure refrigerant gas enters the first compressor 4 again through the four-way reversing valve 6 to complete the outdoor heat source refrigerant loop, realizing the absorption of heat from the outdoor air; The bottom working refrigerant loop is opened. The high-temperature refrigerant flowing out of the refrigerant heat exchange channel of the first heat exchanger 1 enters the heat exchange coil of the first indoor unit 15 through the first bypass valve 17. The high-temperature refrigerant transfers heat to the low-temperature indoor air driven by the fan in the first indoor unit 15 in the refrigerant coil. Then, the cooled low-temperature refrigerant returns to the refrigerant heat exchange channel of the first heat exchanger 1, absorbs the heat released by the high-temperature and high-pressure refrigerant flowing in the refrigerant heat exchange channel of the first heat exchanger 1, and is then reheated into high-temperature refrigerant to complete the bottom working refrigerant loop. See Figure 3 In this embodiment, when a heat pump-driven refrigerant pipeline type high-rise space thermal management system switches to the stage of simultaneous operation of internal and external circulation heat recovery, its workflow is as follows: Both the outdoor heat source refrigerant loop and the bottom working refrigerant loop are open, and their working process is consistent with the internal circulation heating operation stage; the difference is that during this stage, both the indoor heat source refrigerant loop and the top heat recovery refrigerant loop are switched from closed to open. When the indoor heat source refrigerant loop is opened, the low-temperature, low-pressure refrigerant gas flowing out of the refrigerant heat exchange channel of the third heat exchanger 3 first enters the second compressor 5; then, the compressed high-temperature, high-pressure refrigerant gas flows into the refrigerant heat exchange channel of the first heat exchanger 1 through the fourth shut-off valve 12; the high-temperature, high-pressure refrigerant gas in the first heat exchanger 1 transfers heat to the bottom working refrigerant loop through the heat exchange coil, heating the refrigerant supplied to the first indoor unit 15; immediately afterward, the cooled low-temperature, high-pressure refrigerant subcooled liquid flows into the second throttling valve 8 through the first shut-off valve 9 and is throttled and depressurized into a low-temperature, low-pressure two-phase refrigerant; then, the low-temperature, low-pressure refrigerant enters the refrigerant heat exchange channel of the third heat exchanger 3, absorbs heat recovered from the top of the building by the top heat recovery refrigerant loop, and evaporates into superheated refrigerant gas; finally, the low-temperature, low-pressure refrigerant gas re-enters the second compressor 5 to complete the indoor heat source refrigerant loop, realizing the recovery of heat from the hot air accumulated at the top of the high space; The top heat recovery refrigerant loop is activated. The low-temperature refrigerant flowing out of the refrigerant heat exchange channel of the third heat exchanger 3 enters the heat exchange coil of the second indoor unit 16 through the second bypass valve 18. The low-temperature refrigerant absorbs the high-temperature air at the top of the room driven by the fan in the second indoor unit 16 in the refrigerant coil of the indoor unit. Then, the heated high-temperature refrigerant returns to the refrigerant heat exchange channel of the third heat exchanger 3, releasing heat to the low-temperature, low-pressure refrigerant flowing in the refrigerant heat exchange channel of the third heat exchanger 3, and is then cooled back to low-temperature refrigerant to complete the top heat recovery refrigerant loop.

[0050] See Figure 4 In this embodiment, when a heat pump-driven refrigerant pipeline type high-rise space thermal management system switches to the internal circulation heat recovery operation stage, its workflow is as follows: The bottom working refrigerant loop, the top heat recovery refrigerant loop, and the indoor heat source refrigerant loop are all open, and their working process is consistent with the synchronous operation phase of internal and external circulation heat recovery; the difference is that during this phase, the outdoor heat source refrigerant loop is switched from open to closed.

[0051] It should be noted that the above describes the workflow and control methods for large spaces in heating mode. In this embodiment, the thermal management system can achieve flexible switching between heating and cooling modes by switching the connection states of different ports of the four-way reversing valve 6 in the refrigerant loop and controlling the opening and closing of the shut-off valve.

[0052] See Figure 5 When the heat pump-driven refrigerant pipeline type high-rise space thermal management system in this embodiment switches to cooling mode, it is only necessary to open the second shut-off valve 10, the third shut-off valve 11, the fifth shut-off valve 13 and the sixth shut-off valve 14, and close the first shut-off valve 9 and the fourth shut-off valve 12. This allows the first heat exchanger 1 and the third heat exchanger 3 to operate as evaporators while the second heat exchanger 2 operates as a condenser. This ensures that the refrigerant entering the first indoor unit 15 and the second indoor unit 16 to exchange heat with the indoor air is low-temperature refrigerant. The low-temperature refrigerant absorbs heat at both the top and bottom of the high-rise space building and is finally discharged by the second heat exchanger 2 located outdoors, which can significantly improve indoor cooling efficiency.

[0053] Example 2 This embodiment describes the system composition of a heat pump-driven refrigerant network-type multi-temperature stratified thermal management system (see [link]). Figure 6 ) and basic principles (see Figure 7 Similar to Example 1, but with some differences: Firstly, to adapt to the more complex functions of tall, spacious buildings (i.e., different temperature requirements within different height ranges), the areas with temperature requirements need to be divided according to height range. In this example, the areas with temperature requirements are divided into three zones: Zone 1 with temperature requirements, Zone 2 with temperature requirements, and Zone 3 with temperature requirements. Customized energy supply is provided to different zones to match different heat load demands. Secondly, due to the chimney effect in tall spaces, there is a large vertical temperature gradient indoors. The air temperature in areas without temperature requirements changes drastically with height. To make the temperature change more uniform when heat recovery is carried out in areas without temperature requirements and to reduce the impact on adjacent areas with temperature requirements, this example divides the areas without temperature requirements into three zones: Zone 1 without temperature requirements, Zone 2 without temperature requirements, and Zone 3 without temperature requirements according to height range. This expands the location and temperature range for heat recovery to balance temperature gradient changes. Therefore, in order to achieve differentiated thermal management for different temperature requirements in different areas of the aforementioned high-ceilinged space, in this embodiment of a heat pump-driven refrigerant network type multi-temperature stratified thermal management system, the number of indoor units connected in series in both the bottom working refrigerant loop and the top heat recovery refrigerant loop is increased from one to three. At the same time, in addition to equipping each indoor unit with a corresponding bypass valve to control its opening and closing action, since the refrigerant will always rise or fall to a certain extent when it enters the heat exchange coil of each indoor unit, this embodiment also sets a bypass valve in parallel for each indoor unit to control the amount of refrigerant flowing into the indoor unit, so as to match the temperature requirements of each area. The full-cycle control method of the heat pump-driven refrigerant network type multi-temperature stratified thermal management system in this embodiment is basically the same as that in Embodiment 1. Since the internal temperature of a tall space is in a stable state consistent with the outside when it is not used for a long time, the chimney effect has no significant impact on it. Therefore, there is not much waste heat at the top for heat recovery in the early stage of building use. At this time, it is not necessary to open the top heat recovery refrigerant loop, and only heating is needed for the bottom area with temperature requirements. However, as the bottom working refrigerant loop continues to work, a large amount of hot air will quickly gather at the top of the space. When the heat exceeds a certain threshold, the top heat recovery refrigerant loop needs to be opened for heat recovery and area temperature control. Therefore, in order to meet the dynamic heat recovery needs of tall spaces during heating, this embodiment also needs to adopt a full-cycle operation stage control method similar to that in Embodiment 1.

[0054] The difference lies in the fact that, under the full-cycle operation control method in this embodiment, the temperature requirements of different areas in a tall, spacious building vary due to differences in their functions during use. Furthermore, when the function of a certain area changes, its temperature requirements also change. Therefore, this embodiment further incorporates a refined, layered dynamic thermal management control method to address the randomly changing temperature requirements of different areas within a tall, spacious building. Under this control method, by controlling the opening of the bypass valves corresponding to different indoor units in the refrigerant circuit, the flow rate and temperature of the refrigerant flowing into the indoor units of each temperature-controlled area can be adjusted to match the heat load of different areas, ultimately achieving layered, differentiated dynamic thermal management for each temperature-controlled area.

[0055] In heating mode, for the indoor unit that provides heating in the bottom working refrigerant loop, the more refrigerant flows into the indoor unit, the more heat is delivered to the corresponding area, and the greater the temperature rise rate. For the indoor unit that provides heat recovery in the top heat recovery refrigerant loop, the more refrigerant flows into the indoor unit, the more heat is absorbed from the corresponding area, and the greater the temperature drop rate. This embodiment provides the following four typical control cases to illustrate how to achieve differentiated dynamic thermal management for each temperature control zone under the refined stratified dynamic thermal management control method: 1. Increased temperature demand in area 1 with temperature requirements: Under this temperature control requirement, the system only needs to increase the opening of the first bypass valve 21 and decrease the opening of the second bypass valve 22 to increase the flow rate of refrigerant into the heat exchange coil of the first indoor unit 15. 2. Temperature requirement of area 1 is reduced: Under this temperature control requirement, the system only needs to reduce the opening of the first bypass valve 21 and increase the opening of the second bypass valve 22, so that the flow rate of refrigerant entering the heat exchange coil of the first indoor unit 15 is reduced. 3. Increased heat recovery demand in area 1 without temperature requirements: Under this temperature control requirement, the system control only needs to increase the opening of the seventh bypass valve 27 and decrease the opening of the eighth bypass valve 28, so that the flow rate of the refrigerant entering the heat exchange coil of the fourth indoor unit 18 increases. 4. Reduced heat recovery requirements in area 1 without temperature requirements: Under this temperature control requirement, the system only needs to reduce the opening of the seventh bypass valve 27 and increase the opening of the eighth bypass valve 28, so that the flow rate of refrigerant entering the heat exchange coil of the fourth indoor unit 18 is reduced.

[0056] In summary, this embodiment demonstrates that the number of indoor units connected in series in the refrigerant loop of the present invention is unlimited; there can be only one, or more than one depending on the actual situation. Furthermore, by varying the number of indoor units connected in series, the present invention can also meet the needs of flexible matching of differentiated thermal management across all areas in large spaces with varying heights and temperature requirements due to differences in usage functions.

[0057] Example 3 The basic principle of the heat pump-driven hybrid pipe network type high-ceiling multi-temperature stratified thermal management system in this embodiment is basically similar to that in Embodiment 2 (see [link]). Figures 8 to 9 In this embodiment, the high-rise building is also divided into multiple areas with temperature requirements and multiple areas without temperature requirements to achieve differentiated thermal management of different temperature requirements in different areas of the high-rise building. The difference from embodiment 2 is that this embodiment not only uses a heat pump-driven refrigerant pipeline network for indoor thermal management (i.e., the refrigerant system is independently set up outdoors, and the refrigerant enters the heat exchange coil in the indoor unit to exchange heat with the indoor air), but also adds a refrigerant pipeline network (i.e., the refrigerant in the heat pump system flows directly into the heat exchange coil in the indoor unit to exchange heat with the indoor air) and an air pipeline network (i.e., both the refrigerant system and the air handling system are set up outdoors, the refrigerant enters the heat exchange coil in the air handling unit to exchange heat with the return air from the indoor unit, and the air is treated before being sent into the indoor unit) to work together to complete the thermal management of different areas of the indoor space.

[0058] See Figure 9In this embodiment, a heat pump-driven hybrid pipe network type high-ceiling multi-temperature stratified thermal management system can be divided into three main parts, including a heat pump-driven refrigerant pipe network, a refrigerant pipe network, and an air pipe network.

[0059] In heating mode, the workflow of the heat management loop in the heat pump-driven refrigerant network is as follows: the low-temperature refrigerant from the outlet of the variable refrigerant flow heat pump box 1 enters the second refrigerant coil indoor unit 3 through the refrigerant pipe 2. The low-temperature refrigerant absorbs the heat from the hot air in the temperature-unrequired zone 3, which is delivered by the fan in the second refrigerant coil indoor unit 3. While being heated, the low-temperature refrigerant also recovers the waste heat from the temperature-unrequired zone 3. Afterward, the heated refrigerant returns to the variable refrigerant flow heat pump box 1 through the refrigerant pipe 2, and the heat is transferred to the refrigerant coil indoor unit 3. The heat is transferred to the high-temperature refrigerant at the outlet of the variable refrigerant flow heat pump box 1; the high-temperature refrigerant enters the first refrigerant coil indoor unit 5 through the refrigerant pipe 4, and delivers heat to the cold air in the temperature-required zone 3, which is supplied by the fan in the first refrigerant coil indoor unit 5. The high-temperature refrigerant is cooled while the heating effect of the temperature-required zone 3 is achieved; finally, the low-temperature refrigerant, after releasing heat, returns to the variable refrigerant flow heat pump box 1 through the refrigerant pipe 4; at this point, the thermal management loop of the heat pump-driven refrigerant piping network is completed.

[0060] In heating mode, the workflow of the heat management loop of the heat pump-driven refrigerant piping network is as follows: The low-temperature, low-pressure refrigerant from the outlet of the variable refrigerant flow heat pump box 6 enters the second refrigerant coil indoor unit 8 through the refrigerant copper pipe 7. The second refrigerant coil indoor unit 8 operates as an evaporator. The low-temperature, low-pressure refrigerant absorbs the heat from the hot air in the temperature-unrequired zone 2, which is transported by the fan in the second refrigerant coil indoor unit 8. The refrigerant absorbs heat and evaporates into superheated vapor, simultaneously recovering the waste heat of the temperature-unrequired zone 2. Then, the superheated vapor returns to the variable refrigerant flow heat pump box 6 through the refrigerant copper pipe 9 and enters the compressor. After compression, the high-temperature, high-pressure refrigerant... Refrigerant vapor flows out from the variable refrigerant flow rate heat pump box 6, enters the first refrigerant coil indoor unit 10 through the refrigerant copper pipe 9, and operates as a condenser. The high-temperature and high-pressure refrigerant transfers heat to the cold air in the temperature-required zone 2, which is supplied by the fan in the first refrigerant coil indoor unit 10. The high-temperature and high-pressure refrigerant is condensed, and the heating effect of the temperature-required zone 2 is achieved at the same time. Finally, the two-phase refrigerant liquid returns to the variable refrigerant flow rate heat pump box 6 through the refrigerant copper pipe 9. After being throttled and depressurized by the internal throttling valve, it becomes a low-temperature and low-pressure refrigerant again. Thus, the thermal management loop of the heat pump-driven refrigerant pipeline network is completed.

[0061] In heating mode, the thermal management loop of the heat pump driven air duct network is similar to that of the aforementioned heat pump driven refrigerant duct network; the difference is that the low-temperature, low-pressure refrigerant and the high-temperature, high-pressure refrigerant from the outlet of the variable air volume heat pump box 11 enter the second air handling unit 13 and the first air handling unit 19 respectively through refrigerant copper pipes 12 and 18, instead of directly entering the interior of the tall building to exchange heat with the air; the outdoor second air handling unit 13 can use a fan to draw hot air from the area without temperature requirements from the top return air inlet 16 and send it into the second air handling unit 13 through the top return air duct 17, where it is heated by the low-temperature, low-pressure refrigerant flowing in the heat exchange coil. The cooled, low-temperature air is then sent back to the temperature-required area 1 via the top air supply duct 14 and the top air inlet 15 by a fan, completing the heat recovery of the temperature-required area 1. At the same time, the outdoor first air handling unit 19 can draw the cold air from the temperature-required area 1 through the bottom return air inlet 22 and send it into the first air handling unit 19 via the bottom return air duct 23, where it is heated by the high-temperature, high-pressure refrigerant flowing in the heat exchange coil. Then, the heated, high-temperature air is sent back to the temperature-required area 1 via the bottom air supply duct 20 and the bottom air inlet 21 by a fan, completing the heating effect of the temperature-required area 1. Thus, the heat management loop of the heat pump-driven air duct network is completed.

[0062] In summary, this embodiment demonstrates that the form of heat exchange with indoor air in this invention is not limited to the refrigerant network. Depending on the actual site conditions, the refrigerant network or air network can be partially or completely replaced, ultimately forming a heat pump-driven refrigerant-refrigerant-air mixed network thermal management system.

[0063] It should be noted that relational terms such as "first" and "second" in the above embodiments are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Meanwhile, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion.

[0064] The above embodiments do not fully demonstrate all components of the refrigerant cycle. During implementation, the addition of common refrigeration accessories such as high-pressure liquid receivers, gas-liquid separators, filters, and dryers to the refrigerant circuit, or the addition of heat exchangers without departing from the spirit of the technical solution of this invention, shall not be regarded as a substantial improvement to this invention and shall fall within the protection scope of this invention.

[0065] The above description of the embodiments is provided to enable those skilled in the art to understand and use the invention. It will be apparent to those skilled in the art that various modifications can be made to these embodiments, and the general principles described herein can be applied to other embodiments without inventive effort. Therefore, the present invention is not limited to the above embodiments, and any improvements and modifications made by those skilled in the art based on the disclosure of the present invention without departing from the scope of the invention should be within the protection scope of the present invention.

Claims

1. A heat pump-driven refrigerant piping network type thermal management system for large spaces, characterized in that, The thermal management system comprises a refrigerant loop and a secondary refrigerant loop; the refrigerant loop and the secondary refrigerant loop are connected by a heat exchanger; the refrigerant loop includes an outdoor heat source refrigerant loop and an indoor heat source refrigerant loop; the outdoor heat source refrigerant loop includes, in sequence, a refrigerant passage of a first heat exchanger, a first throttling valve, a second shut-off valve, a refrigerant passage of a second heat exchanger, a first compressor, a four-way reversing valve, and a sixth shut-off valve; the indoor heat source refrigerant loop includes, in sequence, a refrigerant passage of a first heat exchanger, a first shut-off valve, a second throttling valve, a refrigerant passage of a third heat exchanger, a second compressor, and a fourth shut-off valve; the secondary refrigerant loop includes a bottom working secondary refrigerant loop and a top heat recovery secondary refrigerant loop; the bottom working secondary refrigerant loop includes, in sequence, a secondary refrigerant passage of a first heat exchanger, a first bypass valve, and a first indoor unit; The top heat recovery refrigerant loop includes a refrigerant channel for a third heat exchanger, a second bypass valve, and a second indoor unit connected in sequence. The number of first indoor units is multiple units connected in series in the bottom working refrigerant loop. These multiple first indoor units are distributed along the height direction in the temperature-required areas of the lower space of the tall building. The temperature-required areas include multiple tiered temperature-controlled zones, with one first indoor unit installed in each tiered zone. The number of second indoor units is multiple units connected in series in the top heat recovery refrigerant loop. These multiple second indoor units are distributed along the height direction in the top space of the tall building. The top space includes multiple tiered zones, with one second indoor unit installed in each tiered zone. The refrigerant loop connects multiple first indoor units and multiple second indoor units in series to achieve refined tiered thermal management covering the entire area of ​​the tall building.

2. The heat pump-driven refrigerant piping network type high-rise space thermal management system according to claim 1, characterized in that, The four-way reversing valve includes four ports: port A is connected to the sixth shut-off valve, port B is connected to the exhaust port of the first compressor, port C is connected to the refrigerant passage of the second heat exchanger, and port D is connected to the suction port of the first compressor.

3. The heat pump-driven refrigerant pipeline type high-rise space thermal management system according to claim 1, characterized in that, The outdoor heat source refrigerant loop and the indoor heat source refrigerant loop can be interconnected through the opening and closing of the third and fifth shut-off valves; the flow rate of refrigerant in the internal heat exchange coil of the first indoor unit can be controlled by adjusting the valve opening of the first bypass valve; the flow rate of refrigerant in the internal heat exchange coil of the second indoor unit can be controlled by adjusting the valve opening of the second bypass valve.

4. The heat pump-driven refrigerant piping network type high-rise space thermal management system according to claim 1, characterized in that, The refrigerant loop is installed outdoors in the tall building, and the refrigerant loop and its series-connected indoor units are installed indoors in the tall building; the refrigerant loop and the interior of the tall building are connected by heat exchange through the refrigerant coils of the indoor units; the first indoor unit and its supporting equipment are installed at the bottom of the tall building for temperature control in the lower part of the interior space of the tall building; the second indoor unit and its supporting equipment are installed in the upper part of the interior space of the tall building.

5. A heat pump-driven refrigerant piping network type high-rise space thermal management system according to claim 1, characterized in that, Water is used as the refrigerant.

6. A heat pump-driven refrigerant piping network type high-rise space thermal management system according to claim 1, characterized in that, The thermal management system includes the installation of a refrigerant piping network and an air piping network.

7. A control method for a heat pump-driven refrigerant piping network type high-rise space thermal management system as described in any one of claims 1 to 6, characterized in that, The control method includes the following steps: It addresses the dynamic heat recovery needs of large spaces during heating, achieving full-cycle operation control. Specifically, it involves periodic switching between an external circulation heating operation phase, a synchronous operation phase of internal and external circulation heat recovery, an internal circulation heat recovery operation phase, and an intermittent operation phase, thereby achieving efficient full-cycle heating of the entire large space building. During the external circulation heating operation phase, when the large space building has not been used for a long time and is about to begin indoor heating for the first time, the initial indoor temperature of the large space building is in a stable state consistent with the external ambient temperature, i.e., the indoor temperature is equal to the external ambient temperature and lower than the thermal comfort lower limit temperature set for areas with temperature requirements. At this time, the second shut-off valve, the sixth shut-off valve, and the first bypass valve are opened, while the remaining valves are closed. During the external circulation heating operation phase, the refrigerant system has only outdoor air as a heat source, and only the bottom first indoor unit heats the space to quickly raise the indoor temperature. During the synchronous operation of the internal and external circulation heat recovery, after the system has been in the external circulation heating operation for a preset time, the indoor temperature of the high space continues to rise. The chimney effect causes the hot air in the space to quickly gather at the top. The higher the location, the faster the temperature rises. The temperature rise rate is fastest in the high space area without temperature requirements. When the temperature reaches the heat recovery set temperature, the first shut-off valve, the second shut-off valve, the fourth shut-off valve, the sixth shut-off valve, the first bypass valve, and the second bypass valve are opened, and the remaining valves are closed. During the synchronous operation phase of internal and external circulation heat recovery, the refrigerant system uses both outdoor air and hot air from the top of the room as heat sources. In addition to the first indoor unit at the bottom heating the space to raise the temperature of areas with temperature requirements, the second indoor unit at the top recovers waste heat from the top, reducing the chimney effect and lowering the energy demand from external sources. During the internal circulation heat recovery operation phase, after a preset time in the synchronous operation phase, the temperature of the area with temperature requirements at the bottom gradually rises, and the heat load demand gradually decreases. When the heat load demand of this area can be met solely by recovering heat from the area without temperature requirements at the top, the first shut-off valve, the fourth shut-off valve, the first bypass valve, and the second bypass valve are opened, while the remaining valves are closed. During the internal circulation heat recovery operation phase, the refrigerant system uses only hot air from the top of the room as a heat source. Using air as the sole heat source, the heat output of the first indoor unit at the bottom is the same as the heat recovered by the second indoor unit at the top. This internal heat circulation, requiring no external energy input, satisfies the heating needs of the temperature-required area at the bottom of the building. During intermittent operation, after the system has been in other operating phases for a preset time, the temperature of the temperature-required area at the bottom continuously rises under the combined effect of external circulation heating and internal circulation heat recovery. When it reaches the upper limit of thermal comfort temperature, the entire system shuts down until the temperature of the temperature-required area drops to the lower limit of thermal comfort temperature. At this point, the valve control switches to the same mode as the external circulation heating operation, and the initial temperature of the temperature-required area changes from ambient temperature to the lower limit of thermal comfort temperature. During intermittent operation, intermittent heating can be achieved in large, spacious buildings, significantly reducing heating energy consumption while meeting thermal comfort requirements.

8. The control method according to claim 7, characterized in that, Under the full-cycle operation phase control method, since the temperature requirements of different areas of a tall, spacious building vary during its use due to differences in their functions, the temperature requirements of that area will also change when the function of a certain area changes. To address the randomly changing temperature requirements in different areas of a large space, the flow rate and temperature of the refrigerant flowing into the indoor units of each temperature-controlled zone can be adjusted by controlling the opening of the bypass valves corresponding to the indoor units in the refrigerant loop, thereby matching the heat load of different areas and ultimately achieving layered and differentiated dynamic thermal management for each temperature-controlled zone.

9. The control method according to claim 7, characterized in that, When the thermal management system switches to cooling mode, simply opening the second, third, fifth, and sixth shut-off valves and closing the first and fourth shut-off valves allows the second heat exchanger to operate as a condenser while the first and third heat exchangers function as evaporators. This ensures that the refrigerant entering the indoor unit for heat exchange with the indoor air is low-temperature refrigerant. The low-temperature refrigerant absorbs heat at both the top and bottom of tall buildings and is ultimately discharged through the second heat exchanger located outdoors, significantly improving indoor cooling efficiency.

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