Integrated double-medium heat pump temperature control system and method and planting system

Abstract

The invention provides an integrated double-medium heat pump temperature control system and method and a planting system, and the system comprises a refrigerant loop which is arranged in an indoor unit and comprises a compressor, a condenser module, a throttling device and an evaporator module which are connected in sequence; the heat dissipation unit is arranged in the indoor unit and is in heat exchange connection with the condenser module and the evaporator module; an outdoor heat exchange module; the first heat exchange medium loop is in heat exchange connection with the condenser module and the outdoor heat exchange module; the second heat exchange medium loop is in heat exchange connection with the evaporator module and the outdoor heat exchange module; and the valve assembly is used for switching on and off of internal pipelines of the condenser module and the evaporator module. The complete refrigerant loop is integrally packaged in advance, the leakage risk caused by field installation is completely eradicated, meanwhile, mode switching is achieved by changing a refrigerant flow path, a four-way reversing valve serving as a core fault source is omitted, pressure impact during reversing is avoided, and the reliability of long-term operation of the system is greatly improved.

Description

Technical Field

[0001] This invention relates to the field of heat pump technology, specifically to an integrated dual-medium heat pump temperature control system, method, and planting system. Background Technology

[0002] Heat pump systems, as highly efficient energy transport devices, are widely used in air conditioning, heating, and other fields. Existing split-type heat pump systems typically consist of an outdoor unit and an indoor unit, connected via a refrigerant loop. This structure requires a series of complex operations on-site, including wall penetration, welding, vacuuming, and refrigerant charging, resulting in high installation costs and requiring specialized personnel. More importantly, on-site welding points and connections are major potential sources of refrigerant leakage, severely impacting the long-term operational reliability of the system.

[0003] To simplify installation, some existing technologies integrate the refrigerant circuit into a single unit, exchanging energy with terminal devices via secondary media such as water. However, these systems still generally rely on traditional four-way reversing valves to switch between cooling and heating modes. A four-way reversing valve is a complex mechanical moving part that generates severe pressure shocks when switching refrigerant flow. This not only easily damages itself and pipe welds, shortening system lifespan, but is also another major source of system failure and refrigerant leakage. Furthermore, to adapt to different ambient temperatures and load requirements, existing technologies typically use electronic expansion valves in conjunction with pressure sensors to achieve precise refrigerant flow regulation, but this significantly increases system hardware costs and the complexity of control logic.

[0004] Furthermore, during winter heating operation, frost easily forms on the surface of the outdoor heat exchanger, severely impacting heat exchange efficiency. Traditional systems often employ reverse circulation defrosting, which involves briefly switching the system to cooling mode and using high-temperature refrigerant to defrost the outdoor unit. This method is not only inefficient and time-consuming, but it also interrupts heating to the indoor unit, potentially causing a temporary drop in indoor temperature, affecting system stability and user comfort. Summary of the Invention

[0005] To address the shortcomings of existing technologies, the purpose of this invention is to provide an integrated dual-medium heat pump temperature control system, method, and planting system.

[0006] The integrated dual-medium heat pump temperature control system provided by the present invention includes:

[0007] A pre-packaged refrigerant circuit, the entire refrigerant circuit being set at indoor temperature, includes a compressor, a condenser module, a throttling device, and an evaporator module connected in sequence; A heat dissipation unit is installed in the indoor unit to regulate the indoor temperature. The heat dissipation unit is also connected to the condenser module and the evaporator module for heat exchange. Outdoor heat exchange module; The first heat exchange medium circuit is simultaneously connected to the condenser module and the outdoor heat exchange module for heat exchange. The second heat exchange medium circuit is simultaneously connected to the evaporator module and the outdoor heat exchange module for heat exchange. The valve assembly is used to switch the on / off state of the internal piping of the condenser module and the evaporator module, so that the condenser module can be selectively connected to the heat dissipation unit and the first heat exchange medium circuit, and the evaporator module can be selectively connected to the heat dissipation unit and the second heat exchange medium circuit.

[0008] Preferably, the condenser module is internally provided with: A first heat exchange pipe for heat exchange connection with the heat dissipation unit and a second heat exchange pipe for heat exchange connection with the first heat exchange medium circuit.

[0009] Preferably, the evaporator module is internally provided with: A third heat exchange pipe for heat exchange connection with the heat dissipation unit and a fourth heat exchange pipe for heat exchange connection with the second heat exchange medium circuit.

[0010] Preferably, the throttling device comprises a capillary tube or at least two capillary tubes of different diameters arranged in parallel.

[0011] Preferably, the throttling device consists of a thin tube and a thick tube connected in parallel, and is controlled by a solenoid valve to achieve three throttling levels.

[0012] Preferably, the throttling device consists of three capillary tubes of different diameters connected in parallel and controlled by a combination of solenoid valves to achieve seven throttling levels.

[0013] Preferably, the heat dissipation unit includes an energy storage unit, which internally has a first heat exchange pipeline of the condenser module and a third heat exchange pipeline of the evaporator module.

[0014] Preferably, the energy storage unit includes an energy storage tank with a volume of 10-2000 liters.

[0015] Preferably, the energy storage unit is a phase change energy storage unit containing phase change energy storage material.

[0016] Preferably, antifreeze flows through both the first heat exchange medium circuit and the second heat exchange medium circuit; The first heat exchange medium circuit includes a first antifreeze tank and a second heat exchange pipeline with a condenser module inside. The second heat exchange medium pipeline includes a second antifreeze tank and a fourth heat exchange pipeline with an evaporator module inside.

[0017] Preferably, the second antifreeze housing comprises a metal housing.

[0018] The integrated dual-medium heat pump temperature control method provided by the present invention is used to achieve cooling and is applied to the integrated dual-medium heat pump temperature control system, comprising the following steps: The control valve assembly causes the first heat exchange medium circuit to exchange heat with the condenser module and be heated. The outdoor heat exchange module is activated to exchange heat with the outdoor environment, and the first heat exchange medium circuit releases heat to the outside. The refrigerant flows out from the condenser module and enters the evaporator module after passing through the throttling device. The control valve assembly enables the heat dissipation unit to exchange heat with the evaporator module, thereby achieving the cooling of the indoor unit. The compressor operates, causing the refrigerant to flow back to the compressor and enter the next cycle.

[0019] Preferably, it further includes a dehumidification step: After the refrigerant enters the evaporator module, the control valve assembly cools down the second heat exchange medium chamber in the second heat exchange medium circuit. When the temperature of the second heat exchange medium box drops below the dew point, the ventilation fan outside the outer shell of the second heat exchange medium box is turned on. When the humid air flows through the outer shell of the second heat exchange medium box, it condenses into water, thereby reducing the relative humidity of the air. When the temperature of the second heat exchange medium chamber reaches the temperature corresponding to the set relative humidity, the control valve assembly or the compressor is stopped to cease cooling the second heat exchange medium chamber.

[0020] The integrated dual-medium heat pump temperature control method provided by the present invention is used to achieve temperature rise and is applied to the integrated dual-medium heat pump temperature control system, comprising the following steps: The control valve assembly allows the heat dissipation unit to exchange heat with the condenser module and be heated, thereby raising the temperature of the internal heat unit. The refrigerant flows out from the condenser module and enters the evaporator module after passing through the throttling device. Control the valve assembly to enable heat exchange between the second heat exchange medium circuit and the evaporator module, so that the refrigerant absorbs heat from the second heat exchange medium circuit; The outdoor heat exchange module is activated to exchange heat with the outdoor environment, and the second heat exchange medium circuit absorbs heat from the outdoor environment. The compressor operates, causing the refrigerant to flow back to the compressor and enter the next cycle.

[0021] Preferably, it also includes a defrosting step: In heating mode, monitor the frosting status of the outdoor heat exchange module; When it is determined that the outdoor heat exchange module is frosted, the heat exchange between the second heat exchange medium circuit and the outdoor heat exchange module is stopped, and the valve assembly is controlled to allow the condenser module to exchange heat with the first heat exchange medium circuit and circulate it to the outdoor heat exchange module to heat and defrost the outdoor heat exchange module.

[0022] Preferably, it further includes a dehumidification step: After the refrigerant enters the evaporator module, the control valve assembly cools down the second heat exchange medium chamber in the second heat exchange medium circuit. When the temperature of the second heat exchange medium chamber drops below the dew point, the ventilation fan outside the outer shell of the second heat exchange medium chamber is turned on. When the humid air flows through the outer shell of the second heat exchange medium chamber, it condenses into water, thereby reducing the relative humidity of the air.

[0023] The indoor planting system provided by the present invention includes the integrated dual-medium heat pump temperature control system, wherein the heat dissipation unit adopts an energy storage water tank.

[0024] Compared with the prior art, the present invention has the following beneficial effects: 1. This invention is easy to install and highly reliable. By encapsulating and sealing the complete refrigerant circuit in the factory, users do not need to perform any operations on the refrigerant pipeline during on-site installation, fundamentally eliminating the risk of leakage introduced by on-site installation. At the same time, mode switching is achieved by changing the refrigerant flow path, eliminating the four-way reversing valve, which is the core source of failure, avoiding pressure shock during reversal, and greatly improving the long-term reliability of the system.

[0025] 2. This invention is cost-effective and has a simplified structure. By using a multi-stage parallel capillary tube to replace the expensive and complex electronic expansion valve, and eliminating the four-way valve and the corresponding pressure sensor, it significantly reduces hardware manufacturing costs and the complexity of the control system.

[0026] 3. This invention is highly efficient and energy-saving, and maintains a constant temperature. By using an energy storage unit as an energy buffer, it can achieve "peak shaving and valley filling" and output a constant temperature to the load end, avoiding temperature fluctuations caused by the start and stop of traditional air conditioners.

[0027] 4. The defrosting of this invention is highly efficient and reliable. The non-reversing defrosting method adopted utilizes the heat generated by the system itself to heat and defrost the outdoor heat exchanger without changing the refrigerant flow direction. Compared with the traditional reverse circulation defrosting method, it is more efficient, and the defrosting process does not affect the indoor heating, thus improving system stability and user comfort.

[0028] 5. This invention can be applied to indoor planting systems and has the following functions: In summer, it cools the indoor energy storage water tank and exhausts heat to the outside, while simultaneously dehumidifying and exhausting heat indoors; in winter, it heats the indoor energy storage water tank and exhausts cold air to the outside, while simultaneously recovering heat from dehumidification to heat the water tank. This invention can flexibly choose to exhaust heat to the outside (summer) or heat the water tank (winter) while dehumidifying, achieving efficient energy utilization and meeting the planting needs throughout the year. Attached Figure Description

[0029] Other features, objects, and advantages of the present invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings: Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0030] The diagram shows: Detailed Implementation

[0031] The present invention will now be described in detail with reference to specific embodiments. These embodiments will help those skilled in the art to further understand the present invention, but do not limit the invention in any way. It should be noted that those skilled in the art can make several changes and improvements without departing from the concept of the present invention. These all fall within the protection scope of the present invention.

[0032] Example 1 This embodiment discloses an integrated dual-medium heat pump temperature control system. The technical concept involves pre-integrating and sealing a complete refrigerant vapor compression cycle system (i.e., refrigerant circuit 1) within an indoor unit. Energy exchange is then conducted with refrigerant circuit 1 and the outdoor environment through two independent heat exchange medium circuits, respectively. The system switches between cooling and heating modes by changing the refrigerant circulation path. This design not only avoids on-site operation of the refrigerant piping but also eliminates the need for traditional four-way reversing valves, thus significantly improving the system's installation convenience, operational reliability, and reducing manufacturing costs.

[0033] Please see Figure 1 This figure is a schematic diagram of an integrated dual-medium heat pump temperature control system provided by an embodiment of the present invention. The system mainly includes an indoor unit and an outdoor heat exchange module 17. It should be noted that all components related to the refrigerant (hereinafter also referred to as refrigerant) are integrated into the indoor unit, forming a pre-sealed refrigerant circuit 1 that has been welded, vacuumed, charged with refrigerant, and undergone strict airtightness testing before leaving the factory. This design simplifies on-site installation to simply connecting water pipes and power supply, without the need for professional refrigeration technicians, making the installation process similar to that of ordinary household appliances, thereby effectively avoiding the risk of refrigerant leakage caused by improper on-site installation.

[0034] Specifically, the pre-sealed refrigerant circuit 1 includes a compressor 2, a condenser module 3, a throttling device 9, and an evaporator module 13 connected in sequence. As the power source for the refrigerant circuit 1, the compressor 2 is responsible for compressing the low-temperature, low-pressure gaseous refrigerant flowing from the evaporator module 13 into a high-temperature, high-pressure gaseous refrigerant. In one embodiment of the invention, a high-efficiency variable-frequency scroll compressor or rotary compressor is used to adjust the operating frequency according to the system load, achieving energy-saving operation.

[0035] The high-temperature, high-pressure gaseous refrigerant discharged from compressor 2 enters condenser module 3. As a key heat exchange component, condenser module 3, in one embodiment of the invention, has at least two independent heat exchange channels, such as a first heat exchange pipe 5 and a second heat exchange pipe 7, respectively used for heat exchange with the heat dissipation unit and the first heat exchange medium circuit 16. For example, condenser module 3 can be a plate heat exchanger or a shell-and-tube heat exchanger. Through the control of the first valve 4 and the second valve 6, the heat released by the refrigerant can be selectively transferred to the heat dissipation unit or the first heat exchange medium circuit 16.

[0036] High-temperature (or ambient temperature) high-pressure liquid refrigerant flowing from condenser module 3 enters throttling device 9. This device throttles and reduces the pressure of the high-pressure liquid refrigerant, converting it into a low-temperature, low-pressure liquid or gas-liquid mixture. Unlike the expensive and complex electronic expansion valves commonly used in the prior art, this embodiment preferably employs a simple and highly reliable multi-stage capillary throttling device. Specifically, the throttling device 9 can be composed of a thin pipe and a thick pipe connected in parallel, with a solenoid valve installed before each pipe. By controlling the opening and closing combinations of these two solenoid valves, three different throttling levels can be achieved: 1) opening only the thin pipe passage, providing the minimum refrigerant flow, suitable for low-load heating conditions in winter; 2) opening only the thick pipe passage, providing a medium refrigerant flow, suitable for normal operating conditions; 3) opening both the thin and thick pipe passages simultaneously, providing the maximum refrigerant flow, suitable for high-load cooling conditions in summer. This design achieves multi-level adjustment of refrigerant flow at a low cost, effectively matching different operating conditions while maintaining the high reliability and maintenance-free characteristics of capillary throttling.

[0037] After being depressurized by the throttling device 9, the low-temperature, low-pressure refrigerant enters the evaporator module 13. Similar to the condenser module 3, the evaporator module 13 is also a heat exchanger with multiple independent heat exchange channels, such as the third heat exchange pipe 11 and the fourth heat exchange pipe 14. The low-temperature, low-pressure refrigerant absorbs external heat and evaporates here, transforming into a low-temperature, low-pressure gaseous refrigerant, which then returns to the suction port of the compressor 2, thus completing a complete refrigeration cycle. Accordingly, through the control of the third valve 10 and the fourth valve 12, the evaporator module 13 can be selectively used to cool the heat dissipation unit or the second heat exchange medium pipe 18.

[0038] It is understood that in the entire system of this invention, the refrigerant always flows in a single direction in the above-mentioned circuit (i.e., compressor 2 → condenser module 3 → throttling device 9 → evaporator module 13 → compressor 2), and no four-way reversing valve is provided in the system to change the main flow direction of the refrigerant. Given that the four-way reversing valve is a major source of failure and leakage in traditional heat pump systems, and that its reversing action generates severe pressure shocks that affect system lifespan, this invention significantly improves the long-term operational reliability of the system by eliminating the four-way reversing valve.

[0039] The heat dissipation unit in the system can preferably be an energy storage unit, specifically an energy storage water tank in this embodiment. The volume of the energy storage water tank can be set according to the needs of the application scenario. For example, in a system for small planting boxes, a 150-liter insulated water tank can be selected. A heat exchange coil is installed inside the energy storage water tank, which forms part of the condenser module 3. The first heat exchange pipe 5 of the condenser module 3 and the third heat exchange pipe 11 of the evaporator module 13 are jointly located inside the energy storage water tank to achieve heating and heat storage or cooling and cold storage of the water tank. The presence of the energy storage water tank plays a significant energy buffering role, enabling the system to provide a very stable cold or heat source to the load end, avoiding the large temperature fluctuations caused by compressor start-stop in traditional air conditioning. Furthermore, it allows the system to adopt a peak-shaving and valley-filling operation strategy, that is, to pre-store energy during periods of low electricity prices and release it during peak periods, thereby using a smaller power compressor to meet peak load demand, reducing equipment costs and operating electricity expenses.

[0040] The first heat exchange medium circuit 16 is filled with a first heat exchange medium (usually antifreeze). This circuit has a first antifreeze tank 8 equipped with a water pump M. The second heat exchange pipe 5 of the condenser module 3 is disposed in the first antifreeze tank 8 to transfer energy between the condenser module 3 and the outdoor heat exchange module 17. The second heat exchange medium circuit 16 is filled with a second heat exchange medium (usually antifreeze). This circuit has a second antifreeze tank 15 equipped with a water pump M. The fourth heat exchange pipe 14 of the evaporator module 13 is disposed in the second antifreeze tank 15 to transfer energy between the evaporator module 13 and the outdoor heat exchange module 17.

[0041] In addition, the system also includes an outdoor heat exchange module 17 for heat exchange with the outdoor ambient air, which is typically a finned coil heat exchanger with a fan. The outdoor heat exchange module 17 is connected to the indoor unit through a first heat exchange medium circuit 16 and a second heat exchange medium circuit 18.

[0042] The valve assembly is the core control component for enabling the system's multi-functional operation. It typically consists of multiple solenoid valves and is controlled by a system controller (not shown in the figure). By precisely switching the opening and closing states of each valve in the valve assembly, the flow path of the refrigerant in the condenser module 3 and the evaporator module 13 can be altered, thereby achieving different operating modes of the system, such as cooling, heating, and defrosting. It is precisely this method of changing the medium flow path rather than the refrigerant flow direction that constitutes the core technical feature of the non-reversing mode switching of this invention.

[0043] The implementation process of the main working mode of the system in this embodiment will be described in detail below.

[0044] After the system starts up, the controller first determines the operating mode set by the user or automatically selected based on environmental conditions.

[0045] In summer cooling mode (executing the cooling process steps), the system aims to cool and store cold in the energy storage tank. At this time, the controller controls the valve assembly to establish the following circulation path: In refrigerant loop 1, compressor 2, condenser module 3, throttling device 9, and evaporator module 13 operate normally. In the first heat exchange line 5, the second valve 6 opens, and the refrigerant, after passing through compressor 2, becomes a high-temperature, high-pressure gas, entering condenser module 3. The refrigerant releases heat to the first antifreeze tank 8. The first antifreeze flows to the outdoor heat exchange module 17, activating the fan and outdoor heat exchange. The cooled first antifreeze flows back to the first antifreeze tank 8. The refrigerant flows out of the condenser module 3 as a high-pressure, room-temperature (a few degrees higher than antifreeze A) liquid and enters the throttling device 9. The refrigerant pressure decreases in the capillary expander, lowering its vaporization saturation point. Thus, after flowing out of the throttling device 9, the refrigerant becomes a low-pressure, low-temperature (basically the same temperature as the front section of the evaporator module 13) gas-liquid mixture (more liquid than gas) and enters the evaporator module 13. The third valve 10 is activated to cool the energy storage tank (the refrigerant absorbs heat from the tank), causing complete vaporization. Under the suction of the compressor 2, the gaseous refrigerant returns to the compressor 2 to enter the next cycle. Through this process, the system transfers heat from the energy storage tank to the outdoor environment, achieving cooling of the tank.

[0046] In winter heating mode (executing heating process steps), the system aims to heat and store heat in the energy storage tank. At this time, the controller controls the valve assembly to create a completely different circulation path from the cooling mode: in refrigerant loop 1, each component still operates in a unidirectional flow. After passing through compressor 2, the refrigerant becomes a high-temperature, high-pressure gas and enters condenser module 3. Selecting and opening the first valve 4 allows the refrigerant to flow through the energy storage tank, heating it. After passing through condenser module 3, the refrigerant becomes a high-pressure, low-temperature (a few degrees higher than the energy storage tank) liquid and enters throttling device 9. The refrigerant exiting throttling device 9 becomes a low-pressure, low-temperature (basically the same temperature as the front section of evaporator module 13) gas-liquid mixture (more liquid than gas) and enters evaporator module 13. Selecting and opening the fourth valve 12 allows heat absorption from the second antifreeze. The water pump in the second antifreeze tank starts, and the second antifreeze flows to the outdoor heat exchange module 17. The outdoor heat exchange module 17 fan starts, exchanging heat with the outside. The second antifreeze absorbs heat from the outside (its temperature is lower than the outdoor temperature) and flows back to the indoor second antifreeze tank. When the refrigerant exits the second antifreeze tank, it is completely vaporized (its temperature is lower than the second antifreeze). Under the suction of compressor 2, the refrigerant returns to compressor 2 to begin the next cycle. Through the above process, the system transfers heat from the outdoor air to the energy storage tank, thus heating the tank.

[0047] In winter heating mode, when the outdoor unit temperature is below the outdoor dew point and the outdoor unit surface temperature is below 0 degrees Celsius, frost will form on the outdoor unit surface. After frost forms, the outdoor unit's heat exchange efficiency decreases significantly, the second antifreeze temperature drops rapidly, and the refrigerant in the evaporator module 13 may not have enough time to vaporize and enter the compressor 2, potentially damaging the compressor 2. Therefore, it is crucial to prevent frost formation on the outdoor unit surface. Normal air conditioners use a four-way valve reversal to turn the outdoor evaporator into a condenser, heating the surface frost, then reversing back to an evaporator absorbing heat from the outside. This instantaneous pressure change in the piping reduces lifespan and lowers thermal efficiency. This invention employs the following defrosting method: After detecting a sharp drop in the second antifreeze temperature, the system determines that frost has formed on the surface of the outdoor heat exchange module 17. The controller performs the following operations: the operating direction and state of the refrigerant circuit 1 remain unchanged, the compressor 2 continues to run, and the condenser module 3 continues to generate high-temperature heat. The controller temporarily stops the heat exchange between the second heat exchange medium and the evaporator module 13 (e.g., by closing relevant valves or water pumps). Turn on the ventilation fan outside the second antifreeze tank 15 to put the second antifreeze into dehumidification mode. When the humid air passes through the second antifreeze tank 15, it condenses into water on the surface of the tank due to its temperature being below the dew point. The collected water is then collected and recycled through pipes. The second antifreeze tank 15 will heat up due to the latent heat of condensation. Control valve 4 to close and valve 6 to open, heating the first antifreeze. The heated first antifreeze is then pumped to the outdoor heat exchange module 17 by water pump M, flowing directly through its internal coils. The large amount of heat carried by the antifreeze is conducted through the pipe walls to the frost on the surface, causing it to melt rapidly from the inside out. After defrosting is complete, the outdoor heat exchange module 17 will rapidly rise in temperature due to its relatively small heat capacity. Therefore, the defrosting status of the outdoor heat exchange module 17 can be determined based on the temperature recovery of the first antifreeze. After the outdoor heat exchange module 17 has been heated for a certain period of time, the system can be switched back to the energy storage water tank heating mode. At this time, since the latent heat of condensation of the condensate in the second antifreeze tank 15 has risen, when the second antifreeze exchanges heat with the outdoor heat exchange module 17, the instantaneous temperature of the outdoor heat exchange module 17 is kept above the frost point.

[0048] This non-reversing defrosting method has several advantages. First, the defrosting process does not change the refrigerant flow direction, eliminating the pressure shock and noise associated with four-way valve reversals, thus ensuring stable system operation. Second, the defrosting heat source comes from the continuous condensation heat generated by the system itself, with heat directly conducted through the liquid medium, resulting in fast defrosting speed and high efficiency. Most importantly, during the entire defrosting period, heat exchange between condenser module 3 and the energy storage tank can continue or be interrupted only briefly, essentially not affecting indoor heating and thus ensuring user comfort.

[0049] In addition, the system can also conveniently achieve the dehumidification function. In the refrigeration mode, the heating mode or the independent dehumidification mode, the controller can choose to conduct the fourth valve 12, so that the refrigerant flows through the evaporator module 13 to cool the second antifreeze tank 15. The fan drives the indoor air to flow through the low-temperature outer shell of the antifreeze tank, and the water vapor in the air will condense on the surface of the tank because the temperature is lower than its dew point. The condensed water is discharged through the water collecting tray and the drain pipe, thereby reducing the indoor air humidity. Since at a certain indoor temperature, the dew point and the relative humidity have a one-to-one correspondence relationship, the relative humidity of the air can be precisely adjusted by setting the temperature of the second antifreeze tank 15. When the temperature in the second antifreeze tank 15 reaches the temperature corresponding to the set relative humidity, the cooling of the second antifreeze tank 15 can be stopped, and the valve can be switched to the third valve 10 to cool the energy storage tank or stop the operation of the compressor 2. The refrigerant is completely vaporized and returns to the compressor 2 under the suction of the compressor 2 to enter the next cycle.

[0050] In winter, the latent heat of condensation of the air recovered in this dehumidification process can ultimately be transferred to the condenser module 3 through the refrigerant cycle and used to heat the energy storage tank, thereby improving the overall energy efficiency ratio of the system. When the outdoor temperature is very low, the temperature of the second antifreeze tank 15 will also be very low. When the temperature of the second antifreeze tank 15 is lower than 0 degrees, moisture may frost on the surface of the second antifreeze tank 15 and will not affect dehumidification. When the ice layer outside the second antifreeze tank 15 thickens, the second antifreeze tank 15 can be thawed by drawing water from the water pipe of the energy storage tank, and this operation can also be carried out during the day.

[0051] Embodiment 2 Based on Embodiment 1, this embodiment further optimizes the throttling device 9, aiming to provide a more refined refrigerant flow regulation ability to adapt to a wider range of operating conditions and further improve the overall operating efficiency of the system.

[0052] Different from the solution using two capillary tubes in Embodiment 1, the throttling device 9 in this embodiment is composed of three capillary tubes with different internal diameters connected in parallel, namely a thin tube, a medium tube and a thick tube. Assume their diameters are D1, D2, D3, and D1 < D2 < D3. An independent solenoid valve is connected in series upstream of each capillary tube, namely solenoid valve 1V1, solenoid valve 2V2 and solenoid valve 3V3. The other ends of these three solenoid valves are commonly connected to the refrigerant outlet from the condenser module 3, and the outlets of the three capillary tubes are commonly converged to the refrigerant inlet leading to the evaporator module 13.

[0053] The system controller can achieve multiple throttling levels by combining and controlling solenoid valves 1V1, 2V2, and 3V3 based on real-time collected operating parameters, such as the operating frequency of compressor 2, outdoor ambient temperature, and the difference between the current water temperature and the target water temperature in the energy storage tank. Since each solenoid valve has two states, "on" and "off", theoretically, seven effective throttling levels can be combined (excluding the case where all valves are closed).

[0054] As an optional implementation, the specific control logic can be designed as follows: 1. Lowest setting (strongest throttling capability, smallest flow rate): Only solenoid valve 1V1 is open, and the refrigerant flows only through the thin pipe. This setting is suitable for situations with extremely low system load, such as in severe winter when the outdoor temperature is very low and the system only needs to operate at the lowest frequency. 2. Second setting: Only solenoid valve 2V2 is open, and the refrigerant flows only through the middle pipe. 3. Third setting: Only solenoid valve 3V3 is open, and the refrigerant flows only through the thick pipe. 4. Fourth setting: Solenoid valves 1V1 and 2V2 are opened simultaneously, and the refrigerant flows in parallel through the thin and middle pipes. 5. Fifth setting: Solenoid valves 1V1 and 3V3 are opened simultaneously, and the refrigerant flows in parallel through the thin and thick pipes. 6. Sixth setting: Solenoid valves 2V2 and 3V3 are opened simultaneously, and the refrigerant flows in parallel through the middle and thick pipes. 7. Highest setting (weakest throttling capacity, largest flow rate): Simultaneously opens solenoid valves 1V1, 2V2, and 3V3, allowing the refrigerant to flow in parallel through all three capillary tubes. This setting is suitable for situations with the highest system load, such as during hot summer months when rapid cooling of the energy storage tank is required.

[0055] Through this seven-level fine-tuning of flow rate, the system can more accurately match the refrigerant circulation volume under different loads, ensuring that the inlet of evaporator module 13 and the outlet of condenser module 3 maintain optimal levels over a wider operating range, thereby significantly improving the system's overall energy efficiency ratio. Compared to the three-level adjustment in Example 1, this embodiment offers higher adjustment precision, making the system's performance closer to that of a system using an expensive electronic expansion valve. However, its hardware cost remains significantly lower than the electronic expansion valve solution, and the system composed of solenoid valves and capillary tubes offers higher reliability and a longer service life. This design achieves an effective balance between cost, performance, and reliability.

[0056] Example 3 Based on the hardware architecture of Example 1, this embodiment upgrades the control strategy for winter defrosting with intelligence, aiming to improve the accuracy of defrosting judgment, avoid ineffective or delayed defrosting due to misjudgment of a single parameter, reduce unnecessary energy consumption, and ensure the system continues to operate efficiently in severe weather.

[0057] In Example 1, defrosting is primarily triggered by monitoring the temperature of the second heat exchange medium (antifreeze). While this is an effective basic judgment method, it may have limitations under certain critical operating conditions. For example, when the outdoor temperature suddenly drops sharply, the antifreeze temperature may decrease rapidly even without frost, potentially triggering an incorrect defrosting action.

[0058] To address this issue, the controller in this embodiment integrates a more intelligent multi-dimensional fusion judgment algorithm. In addition to the existing antifreeze temperature sensor, an outdoor air humidity sensor can be added to the system. When executing the steps of monitoring frost conditions and determining whether frost conditions are met, the controller will perform logical judgments based on the following multiple pieces of information: a) Basic Environmental Condition Assessment: The controller first confirms whether the outdoor ambient temperature is within the temperature range most prone to frost formation, which is typically between -15°C and 0°C. Only when the outdoor temperature is within this range will the subsequent frost probability assessment be initiated. If the temperature is too high (e.g., above 0°C), the probability of frost formation is low; if the temperature is too low (e.g., below -15°C), the air humidity is extremely low, making it difficult for thick frost to form.

[0059] b) Core performance indicator monitoring: The controller continuously monitors the antifreeze temperature returned from the outdoor heat exchange module 17 in the second heat exchange medium loop 18. After the system has been running stably for a period of time, this temperature should be relatively stable. If the controller detects a significant and continuous downward trend in this temperature within a short period of time (e.g., within 10 minutes) (e.g., a drop of more than 3°C), it is considered a strong signal that frost formation is causing heat exchange deterioration.

[0060] c) Auxiliary humidity condition judgment: The controller simultaneously reads the value from the outdoor air humidity sensor. Only when the relative humidity of the air is higher than a preset threshold (e.g., 80%) is it considered that the humidity conditions for rapid frosting are met. Using humidity as a judgment factor can effectively eliminate false judgments caused by temperature drops due to dry and cold air.

[0061] d) Mandatory timing logic supplement: To prevent the system from not defrosting for extended periods due to insignificant temperature and humidity changes under certain slow frosting conditions, ultimately leading to a thick frost layer, the controller can also incorporate a timer. When the system meets the conditions in a) and c) above (i.e., is in a temperature and humidity environment prone to frosting) and continues to operate for more than a set cumulative time (e.g., continuous operation for 2 hours), even if no significant temperature drop as described in b) is detected, the controller will initiate a short-duration "preventative" defrosting cycle.

[0062] In summary, the defrosting startup logic of this embodiment can be summarized as follows: when (condition a is true) and (condition b is true or condition c is true), defrosting is started immediately; or, when (condition a is true) and (condition c is true) and (cumulative running time exceeds the threshold), preventive defrosting is started.

[0063] By integrating and judging information from multiple dimensions, defrosting triggering becomes more accurate and reliable. This not only effectively avoids erroneous defrosting caused by fluctuations in data from a single sensor, thus saving energy, but also ensures the system's stability and continuous heating capacity under severe weather conditions such as high humidity through preventative defrosting logic, thereby improving the overall efficiency and user experience during winter operation.

[0064] Example 4 This embodiment provides a system variant using a phase change energy storage unit, which aims to solve the problems of large energy storage tank volume and further reduce operating costs by utilizing time-of-use pricing strategies.

[0065] In Example 1, the energy storage unit uses an energy storage water tank. Although water, as an energy storage medium, has advantages such as high specific heat capacity and low cost, its energy storage method is sensible heat storage, which means that the storage of energy is accompanied by significant temperature changes, and storing a large amount of energy requires a large volume.

[0066] To store more energy within a limited volume and achieve a more constant energy release temperature, this embodiment replaces the energy storage tank in Embodiment 1 with a phase change energy storage unit. The external dimensions of this phase change energy storage unit can be designed to be smaller than the original tank, and its interior is filled with a specific phase change energy storage material. A phase change energy storage material is a substance that absorbs or releases a large amount of latent heat by undergoing a change of state (such as a solid-liquid transition) at a specific temperature.

[0067] For example, in a temperature control system for plant growth, a phase change energy storage material with a phase change temperature of around 20°C can be selected. The system operates as follows: 1. Energy Storage Process: The system can operate intelligently according to time-of-use electricity pricing strategies. For example, during nighttime hours when electricity prices are lower, the controller starts the system. *If heat needs to be stored for the daytime, the system operates in heating mode. After the refrigerant is heated in condenser module 3, it circulates through the heat exchange coils of the phase change energy storage unit. When the temperature of the phase change material reaches its melting point (e.g., 20°C), it begins to melt from a solid to a liquid state, absorbing a large amount of latent heat of phase change while its own temperature remains essentially constant. *If cooling needs to be stored for the daytime, the system operates in cooling mode. After the refrigerant is cooled in evaporator module 13, it circulates through the heat exchange coils of the phase change energy storage unit. When the temperature of the phase change material reaches its freezing point, it begins to solidify from a liquid state, releasing a large amount of latent heat, thus storing cooling capacity.

[0068] 1. Energy release process: During peak hours when electricity prices are high, or when the load side needs to adjust the temperature quickly, the system can stop the operation of compressor 2, which consumes the most power.

[0069] – If heating is required, the controller starts compressor 2, causing the refrigerant to exchange heat between the phase change energy storage unit and the condenser module 3. The liquid phase change material gradually solidifies when it releases heat. Due to the isothermal characteristics of the phase change process, the released heat can maintain the circulating water temperature at a constant temperature close to its phase change point for a long time.

[0070] - If cooling is required, compressor 2 is also started. The solid phase change material will gradually melt as it absorbs heat, providing a stable low temperature for the circulating water.

[0071] The use of phase change energy storage units (PCS) brings several beneficial effects. First, the energy storage density of PCS materials is much higher than that of water. Therefore, for storing the same amount of energy, the volume and weight of PCS units can be much smaller than that of water storage tanks, making the entire indoor unit more compact and easier to install and arrange. Second, utilizing the latent heat of phase change for energy storage and release results in a temperature plateau effect, making the temperature of the energy output to the load end more constant, which is beneficial for precise temperature control of the environment. Finally, combined with time-of-use pricing strategies, storing energy during off-peak hours and releasing it during peak hours can significantly reduce the annual operating cost of the system, resulting in outstanding economic benefits.

[0072] Example 5 This embodiment discloses an indoor planting system, the purpose of which is to illustrate the specific application of the above-mentioned integrated dual-medium heat pump temperature control system in indoor planting scenarios.

[0073] The indoor planting area is equipped with planting racks, and the energy storage unit can be an energy storage water tank, which is placed directly in the indoor planting area. The energy storage water tank adopts an insulated structure design, and its surface is preferably equipped with heat exchange fins for natural convection heat exchange with indoor air. The planting area is preferably equipped with indoor temperature and humidity sensors for real-time monitoring of environmental parameters.

[0074] During system operation, the non-reversing mode switching mechanism described in Example 1 enables precise control of the planting environment. In summer, the system stores cold in the energy storage tank, with the low-temperature tank directly absorbing sensible and latent heat from the indoor air, achieving both cooling and dehumidification effects. In winter, the system stores heat in the energy storage tank, with the high-temperature tank releasing heat to the indoor air, and the recovered condensation heat during dehumidification is used to heat the water tank.

[0075] The core advantage of placing the energy storage water tank directly in the planting area is that it eliminates the intermediate step of secondary heat exchange through fan coil units required by traditional air conditioning. The surface of the water tank directly contacts the air for heat exchange, resulting in higher heat exchange efficiency and faster temperature response. The large-capacity water tank has significant thermal inertia, which can effectively stabilize instantaneous temperature fluctuations caused by operations such as supplemental lighting and irrigation, providing a stable growth environment for plant roots and canopy.

[0076] This embodiment integrates the above temperature control system with the planting space, giving full play to the advantages of the temperature control technology described in Embodiment 1, and providing an efficient and stable temperature control solution for plant factories, home planting and other scenarios.

[0077] Those skilled in the art will understand that, besides implementing the system and its various devices, modules, and units provided by this invention in the form of purely computer-readable program code, the same functions can be achieved entirely through logical programming of the method steps, making the system and its various devices, modules, and units of this invention function in the form of logic gates, switches, application-specific integrated circuits, programmable logic controllers, and embedded microcontrollers. Therefore, the system and its various devices, modules, and units provided by this invention can be considered as a hardware component, and the devices, modules, and units included therein for implementing various functions can also be considered as structures within the hardware component; alternatively, the devices, modules, and units for implementing various functions can be considered as both software modules implementing the method and structures within the hardware component.

[0078] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0079] Specific embodiments of the present invention have been described above. It should be understood that the present invention is not limited to the specific embodiments described above, and those skilled in the art can make various changes or modifications within the scope of the claims, which do not affect the essence of the present invention. Unless otherwise specified, the embodiments and features of the present invention can be arbitrarily combined with each other.

Claims

1. An integrated dual-medium heat pump temperature control system, characterized in that, include: A pre-packaged refrigerant circuit (1) is installed in the indoor unit and includes a compressor (2), a condenser module (3), a throttling device (9) and an evaporator module (13) connected in sequence. The heat dissipation unit is located in the indoor unit and is used to regulate the indoor temperature. The heat dissipation unit is also connected to the condenser module (3) and the evaporator module (13) for heat exchange. Outdoor heat exchange module (17); The first heat exchange medium circuit (16) is simultaneously connected to the condenser module (3) and the outdoor heat exchange module (17) for heat exchange. The second heat exchange medium circuit (18) is simultaneously connected to the evaporator module (13) and the outdoor heat exchange module (17) for heat exchange. The valve assembly is used to switch the on / off state of the internal piping of the condenser module (3) and the evaporator module (13), so that the condenser module (3) is connected to the heat dissipation unit and the first heat exchange medium circuit (16) in an alternative manner, and the evaporator module (13) is connected to the heat dissipation unit and the second heat exchange medium circuit (18) in an alternative manner.

2. The integrated dual-medium heat pump temperature control system according to claim 1, characterized in that, The condenser module (3) is internally equipped with: A first heat exchange pipe (5) for heat exchange connection with the heat dissipation unit and a second heat exchange pipe (7) for heat exchange connection with the first heat exchange medium circuit (16).

3. The integrated dual-medium heat pump temperature control system according to claim 2, characterized in that, The evaporator module (13) is internally equipped with: The third heat exchange pipe (11) is used for heat exchange connection with the heat dissipation unit and the fourth heat exchange pipe (14) is used for heat exchange connection with the second heat exchange medium circuit (18).

4. The integrated dual-medium heat pump temperature control system according to claim 1, characterized in that, The throttling device (9) includes a capillary tube or at least two capillary tubes of different diameters arranged in parallel.

5. The integrated dual-medium heat pump temperature control system according to claim 4, characterized in that, The throttling device (9) consists of a thin tube and a thick tube connected in parallel and is controlled by a solenoid valve to achieve three throttling levels.

6. The integrated dual-medium heat pump temperature control system according to claim 4, characterized in that, The throttling device (9) consists of three capillary tubes of different diameters connected in parallel and controlled by a combination of solenoid valves to achieve seven throttling levels.

7. The integrated dual-medium heat pump temperature control system according to claim 3, characterized in that, The heat dissipation unit includes an energy storage unit, which is internally equipped with a first heat exchange pipe (5) of the condenser module (3) and a third heat exchange pipe (14) of the evaporator module (13).

8. The integrated dual-medium heat pump temperature control system according to claim 7, characterized in that, The energy storage unit includes an energy storage tank with a volume of 10-2000 liters.

9. The integrated dual-medium heat pump temperature control system according to claim 3, characterized in that, The energy storage unit is a phase change energy storage unit containing phase change energy storage materials.

10. The integrated dual-medium heat pump temperature control system according to claim 3, characterized in that, Antifreeze flows through both the first heat exchange medium circuit (16) and the second heat exchange medium circuit (18); The first heat exchange medium circuit (16) includes a first antifreeze tank (8) and a second heat exchange pipeline (7) with a condenser module (3) inside. The second heat exchange medium pipeline (17) includes a second antifreeze tank (15) and a fourth heat exchange pipeline (14) with an evaporator module (13) inside.

11. The integrated dual-medium heat pump temperature control system according to claim 10, characterized in that, The second antifreeze tank (15) includes a metal casing.

12. An integrated dual-medium heat pump temperature control method for achieving cooling, characterized in that, The integrated dual-medium heat pump temperature control system according to any one of claims 1-11 includes the following steps: Control the valve assembly to heat the first heat exchange medium circuit (16) by exchanging heat with the condenser module (3); The outdoor heat exchange module (17) is started to exchange heat with the outside, and the first heat exchange medium circuit (16) releases heat to the outside. The refrigerant flows out from the condenser module (3) and enters the evaporator module (13) after passing through the throttling device (9). The control valve assembly enables the heat dissipation unit to exchange heat with the evaporator module (13), thereby achieving the cooling of the indoor unit. The compressor (2) operates, causing the refrigerant to flow back to the compressor (2) and enter the next cycle.

13. The integrated dual-medium heat pump temperature control method according to claim 12, characterized in that, It also includes a dehumidification step: After the refrigerant enters the evaporator module (13), it controls the valve assembly to cool down the second heat exchange medium box in the second heat exchange medium circuit (18). When the temperature of the second heat exchange medium box drops below the dew point, the ventilation fan outside the outer shell of the second heat exchange medium box is turned on. When the humid air flows through the outer shell of the second heat exchange medium box, it condenses into water, thereby reducing the relative humidity of the air. When the temperature of the second heat exchange medium box reaches the temperature corresponding to the set relative humidity, control the valve assembly or stop the operation of the compressor (2) to stop cooling the second heat exchange medium box.

14. An integrated dual-medium heat pump temperature control method for achieving temperature rise, characterized in that, The integrated dual-medium heat pump temperature control system according to any one of claims 1-11 includes the following steps: Control the valve assembly to heat the heat dissipation unit and the condenser module (3) by exchanging heat, thereby raising the temperature of the internal heat unit. The refrigerant flows out from the condenser module (3) and enters the evaporator module (13) after passing through the throttling device (9). Control the valve assembly to allow the second heat exchange medium circuit (18) to exchange heat with the evaporator module (13), so that the refrigerant absorbs heat from the second heat exchange medium circuit (18); The outdoor heat exchange module (17) is started to exchange heat with the outside, and the second heat exchange medium circuit (18) absorbs heat from the outside. The compressor (2) operates, causing the refrigerant to flow back to the compressor (2) and enter the next cycle.

15. The integrated dual-medium heat pump temperature control method according to claim 14, characterized in that, It also includes a defrosting step: In heating mode, monitor the frosting status of the outdoor heat exchange module (17); When it is determined that the outdoor heat exchange module (17) is frosted, the heat exchange between the second heat exchange medium circuit (18) and the outdoor heat exchange module (17) is stopped, and the valve assembly is controlled to make the condenser module (3) exchange heat with the first heat exchange medium circuit (16) and circulate to the outdoor heat exchange module (17) to heat and defrost the outdoor heat exchange module (17).

16. The integrated dual-medium heat pump temperature control method according to claim 14, characterized in that, It also includes a dehumidification step: After the refrigerant enters the evaporator module (13), it controls the valve assembly to cool down the second heat exchange medium box in the second heat exchange medium circuit (18). When the temperature of the second heat exchange medium chamber drops below the dew point, the ventilation fan outside the outer shell of the second heat exchange medium chamber is turned on. When the humid air flows through the outer shell of the second heat exchange medium chamber, it condenses into water, thereby reducing the relative humidity of the air.

17. An indoor planting system, characterized in that, The integrated dual-medium heat pump temperature control system according to any one of claims 1-11, wherein the heat dissipation unit adopts an energy storage water tank.

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