An air source heat pump and control method

Abstract

The application discloses an air source heat pump and a control method. The heat pump comprises a body, a driving plate, a heat dissipation piece and an air duct shell. The body is internally provided with a relatively independent compressor cavity and a fan cavity. The fan cavity is provided with a first fan. The driving plate is mounted in the body. The heat dissipation piece is arranged on one side of the driving plate. The air duct shell is arranged in the body. The air duct shell is internally formed with a heat dissipation channel. The heat dissipation piece is arranged in the heat dissipation channel. One end of the heat dissipation channel is communicated with the compressor cavity, and the other end is communicated with the fan cavity. The heat dissipation channel is provided with a second fan. The air duct shell is provided with the independent heat dissipation channel. The second fan is arranged in the air duct shell to change the air flow state of the heat dissipation channel, so that the air flow state is diversified, and the heat dissipation efficiency of the air-cooled heat dissipation driving plate is effectively improved.

Description

Technical Field

[0001] This application relates to the technical field of heat pumps, and more particularly to an air source heat pump and its control method. Background Technology

[0002] Air source heat pumps, as highly efficient energy conversion devices, are widely used in modern refrigeration and heating. One of their core components, the drive plate, plays a crucial role in controlling the operation of the heat pump system and generates a significant amount of heat in the process. To effectively remove this heat, air-cooled drive plates have become a common choice. These drive plates typically employ natural air cooling, relying on natural airflow to remove heat. In this natural air cooling mechanism, the heat generated by the drive plate heats the surrounding air, causing the hot air to rise naturally due to its lower density. This rising process creates a localized low-pressure area, which in turn attracts cooler surrounding air, creating natural convection that effectively removes heat from the drive plate surface. However, natural air cooling also has some inherent drawbacks.

[0003] First, its heat dissipation efficiency is relatively low, mainly due to the slow and unpredictable nature of natural airflow. Especially in high-temperature environments or under conditions of poor air circulation, the heat dissipation effect decreases significantly. This is because high temperatures raise the initial temperature of the air, thus reducing its ability to absorb heat; while poor air circulation reduces the frequency of exchange between hot and cold air, further affecting the heat dissipation effect.

[0004] Secondly, natural air cooling is significantly affected by ambient temperature and airflow speed. When the ambient temperature is too high or the airflow speed is too slow, the heat dissipation efficiency will drop sharply, causing the IPM (Intelligent Power Module) on the driver board to overheat. This situation will not only limit the increase of compressor frequency, but may also cause a series of safety hazards, such as overheat protection activation and system performance degradation.

[0005] To overcome the limitations of air-cooled heat dissipation, fluoropolymer (FRP) refrigerant cooling plates have been gradually introduced into air-source heat pump systems as a heat dissipation method. FRP refrigerant cooling plates utilize refrigerant (cooling medium) circulating within the plate, carrying away heat from the drive plate through heat exchange and releasing it into the external environment. However, FRP refrigerant cooling plate systems require complex piping designs to transport the refrigerant. These piping systems not only increase the system's complexity but also raise the difficulty of installation and maintenance. During design and installation, precise calculations of refrigerant flow rate and pressure are necessary to ensure efficient system operation. Simultaneously, the complex piping also increases the risk of system leaks; refrigerant leaks directly affect the system's heat dissipation and energy efficiency. Furthermore, FRP refrigerant cooling plates are prone to condensation during operation. As the refrigerant absorbs and releases heat during circulation, the surface temperature of the plate decreases. When water vapor in the surrounding air encounters the low-temperature plate, it condenses into water droplets, forming condensation. Condensation not only affects the electrical performance of the drive plate but can also pose safety hazards such as corrosion and short circuits to the system. Therefore, when designing and using fluoropolymer cold plates, effective anti-condensation measures need to be taken, such as adding insulation layers and optimizing refrigerant circulation methods.

[0006] Therefore, under natural air cooling, how to effectively improve heat dissipation efficiency, reduce driver board temperature, and ensure stable operation of the heat pump system has become an urgent technical problem to be solved. Summary of the Invention

[0007] The purpose of this application is to provide an air source heat pump and control method. By reasonably setting a duct shell with an independent heat dissipation channel and setting a second fan in the duct shell to change the air flow state of the heat dissipation channel, the air flow state is diversified, which effectively improves the heat dissipation efficiency of the air-cooled heat dissipation drive board. Moreover, the control logic of the second fan is optimized so that the operation of the second fan can be accurately controlled under different load conditions, ensuring that the IPM temperature of the drive board is within a suitable range, increasing the compressor frequency, and thus improving the energy efficiency of the heat pump.

[0008] To achieve the above objectives, this application adopts the following technical solution:

[0009] On one hand, an air source heat pump is provided, comprising: a body, a drive plate, a heat sink, and a duct shell. The body has a relatively independent compressor chamber and a fan chamber. A first fan is disposed in the fan chamber. The drive plate is installed inside the body. The heat sink is disposed on one side of the drive plate. The duct shell is disposed inside the body. A heat dissipation channel is formed inside the duct shell. The heat sink is located in the heat dissipation channel. One end of the heat dissipation channel is connected to the compressor chamber, and the other end is connected to the fan chamber. A second fan is disposed in the heat dissipation channel so that air in the compressor chamber enters from one end of the heat dissipation channel, passes through the heat sink, and is delivered to the fan chamber from the other end of the heat dissipation channel.

[0010] Furthermore, the machine body is provided with an air inlet, which connects the external environment and the compressor chamber.

[0011] Furthermore, the heat dissipation channel has a first end and a second end, the first end is connected to the compressor chamber, the second fan is disposed at the second end, and the first end is also provided with a guide to allow air from the compressor chamber to enter the heat dissipation channel upward.

[0012] Furthermore, the side of the first end is provided with a connection port that connects to the compressor chamber, and the top surface of the second end is provided with an air outlet that connects to the fan chamber.

[0013] Furthermore, the connection port is located below the heat sink.

[0014] Furthermore, the drive plate is installed inside the press cavity, and the air duct shell is located inside the fan cavity.

[0015] On the other hand, a control method for an air source heat pump is also provided, applicable to the air source heat pump as described above. The control method includes: after the air source heat pump is running, the first fan is turned on, the IPM temperature T of the drive board is monitored in real time, and when T > T1, the second fan is turned on, where T1 is a preset temperature threshold.

[0016] Furthermore, a compressor is installed inside the press chamber. When T2≤T≤T1, the compressor reduces its operating frequency, where T2 is a preset temperature threshold.

[0017] Furthermore, when T≤T3, the compressor stops reducing the frequency and maintains the current frequency, where T3 is a preset temperature threshold and T3<T2.

[0018] Furthermore, when T≤T4, the compressor removes the frequency limit and increases the operating frequency, where T4 is a preset temperature threshold and T4<T3.

[0019] Furthermore, after the second fan is turned on, when the IPM temperature T of the drive board is detected to be continuously rising, the operating frequency of the second fan is gradually increased.

[0020] Furthermore, the second fan includes at least a first operating gear, a second operating gear, and a third operating gear. When T > T1, the second fan operates according to the first operating gear; when T > T5, the second fan operates according to the second operating gear; when T > T6, the second fan operates according to the third operating gear; wherein, T6 > T5 > T1, the operating frequency of the third operating gear is greater than the operating frequency of the second operating gear, and the operating frequency of the second operating gear is greater than the operating frequency of the first operating gear.

[0021] Furthermore, after the second fan is turned on, the ambient temperature t is detected in real time, and the drop rate of the IPM temperature T of the drive board is set to F. When t > t1, T > T1 and F < F1, the operating frequency of the first fan is increased, and / or the operating frequency of the second fan is increased, where t1 is a preset ambient temperature threshold and F is a preset amplitude threshold.

[0022] Furthermore, when the air source heat pump is operating in heating mode, the outlet air temperature H of the first fan is detected in real time. When H > H1, the operating frequency of the first fan is increased, and / or the operating frequency of the second fan is increased, wherein H1 is the temperature set by the air source heat pump.

[0023] The beneficial effects of this application are as follows: When the IPM temperature of the drive board exceeds the preset temperature threshold, the heat from the drive board is conducted to the heat sink, and the second fan in the heat dissipation channel starts, changing the airflow state within the heat dissipation channel. This continuously draws in fresh air from the compressor chamber. After entering the heat dissipation channel through one end of the duct housing, the air, driven by the second fan, flows along the heat dissipation channel, passes through the heat sink, carries away heat, and is output to the fan chamber, where it is then discharged from the machine body. In this solution, the independent heat dissipation channel formed within the duct housing accelerates the heat dissipation of the drive board, resulting in better and faster heat dissipation efficiency, thereby significantly improving the energy efficiency of the heat pump.

[0024] In addition, the operating logic of the second fan has been optimized based on the above-mentioned heat pump. By monitoring the IPM temperature of the drive board in real time, the second fan starts when the temperature exceeds the threshold. This allows the heat pump to accurately control the operation of the second fan under different load conditions, ensuring that the IPM temperature of the drive board is within a suitable range, thereby increasing the operating frequency of the compressor and ensuring the heating effect of the heat pump. Attached Figure Description

[0025] The present application will now be described in further detail with reference to the accompanying drawings and embodiments.

[0026] Figure 1 This is a schematic diagram of the internal structure of the air source heat pump described in the embodiments of this application. Figure 1 ;

[0027] Figure 2 This is a schematic diagram of the internal structure of the air source heat pump described in the embodiments of this application. Figure 2 ;

[0028] Figure 3 Examples of this application Figure 2 Enlarged view of point A in the middle;

[0029] Figure 4 This is a schematic diagram of the internal structure of the air source heat pump described in the embodiments of this application. Figure 3 (Hidden electrical box)

[0030] In the diagram: 1. Body; 101. Compressor chamber; 102. Fan chamber; 2. Drive plate; 3. Heat sink; 4. Air duct shell; 5. First fan; 6. Second fan; 7. Connection port; 8. Air guide; 9. Electrical box; 10. Middle partition; 11. Air inlet. Detailed Implementation

[0031] To make the technical problems solved by this application, the technical solutions adopted, and the technical effects achieved clearer, the technical solutions of the embodiments of this application are further described in detail below. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0032] In the description of this application, unless otherwise expressly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0033] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature being directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0034] like Figures 1-4 As shown, this embodiment provides an air source heat pump, including: a body 1, a drive plate 2, a heat sink 3, and a duct shell 4. The body 1 has a relatively independent compressor chamber 101 and a fan chamber 102. A first fan 5 is installed in the fan chamber 102. The drive plate 2 is installed inside the body 1. The heat sink 3 is disposed on one side of the drive plate 2. The duct shell 4 is disposed inside the body 1. A heat dissipation channel is formed inside the duct shell 4. The heat sink 3 is located in the heat dissipation channel. One end of the heat dissipation channel is connected to the compressor chamber 101, and the other end is connected to the fan chamber 102. A second fan 6 is disposed in the heat dissipation channel so that air in the compressor chamber 101 enters from one end of the heat dissipation channel, passes through the heat sink 3, and is delivered to the fan chamber 102 from the other end of the heat dissipation channel.

[0035] Based on the above scheme, when the temperature of the IPM (Intelligent Power Module) on the drive board 2 exceeds the preset safety threshold, a precise heat dissipation process is triggered. The core mechanism of this process is that the heat generated by the drive board 2 is first effectively conducted to the heat sink 3, which is in close contact with it. Then, the second fan 6, located inside the carefully designed air duct shell 4 within the housing 1, is activated. An independent heat dissipation channel is constructed inside the air duct shell 4, which plays a crucial role as the key path connecting the compressor chamber 101 and the fan chamber 102. When the second fan 6 starts, it significantly adjusts the airflow dynamics within the heat dissipation channel, causing fresh air from the compressor chamber 101 to be continuously drawn in. This air flows smoothly into the heat dissipation channel through one end of the air duct shell 4 and, under the powerful drive of the second fan 6, flows orderly along the channel. During this flow, the air comes into close contact with the heat sink 3, efficiently absorbing the heat from it. With the effective heat transfer, the air temperature gradually rises, and then this heat-rich air is transported into the fan chamber 102. Inside the fan chamber 102, the first fan 5 is responsible for expelling the hot air from the outside of the machine body 1, thus achieving the purpose of heat dissipation. At the same time, it can also assist in the output of heating air, thereby successfully completing the entire heat dissipation cycle.

[0036] The heat dissipation channel design in this scheme not only significantly accelerates the heat dissipation speed of the driver board 2, but also greatly improves the heat dissipation efficiency. Compared with traditional heat dissipation methods, it can effectively dissipate the heat on the driver board 2 in a shorter time, thereby ensuring the stable and efficient operation of the heat pump system.

[0037] Furthermore, the solution also optimizes the operating logic of the second fan 6. By monitoring the temperature of the drive plate 2IPM in real time and with precision, the system can intelligently determine when to start the second fan 6. This precise control strategy ensures that the second fan 6 can maintain the temperature of the drive plate 2IPM within a suitable range under different load conditions. This improvement not only significantly increases the operating frequency of the compressor but also further enhances the heating performance of the heat pump, making the entire system more efficient, stable, and reliable.

[0038] Furthermore, the heat dissipation channel has a first end and a second end. The first end is connected to the compressor chamber 101, and the second fan 6 is disposed at the second end. The first end is also provided with a guide member 8 to allow air from the compressor chamber 101 to enter the heat dissipation channel upwards. The main function of the guide member 8 is to guide the air in the compressor chamber 101 into the heat dissipation channel in a specific direction (such as upwards). This design not only ensures that air can flow smoothly into the heat dissipation channel, but also further enhances the heat dissipation effect by changing the direction of airflow.

[0039] It should be noted that in heating mode, the fan chamber 102 blows hot air, which is not conducive to the effective heat dissipation of the heat sink 3. The air temperature in the compressor chamber 101 is relatively lower than that in the fan chamber 102. Therefore, introducing the cold air in the compressor chamber 101 into the heat dissipation channel can dissipate heat from the heat sink 3 and finally exhaust it from the fan chamber 102.

[0040] Furthermore, a partition 10 is provided inside the body 1, dividing the interior of the body 1 into a compressor chamber 101 and a fan chamber 102. A duct shell 4 is mounted on the partition 10 and located on one side of the fan chamber 102. The body 1 has an air inlet 11, which connects the external environment to the compressor chamber 101. The compressor chamber 101 is a relatively enclosed space, and its internal pressure differs from the external environment. A connection port 7 is provided on the side of the first end of the duct shell 4, connecting to the compressor chamber 101. To avoid interference from the partition 10, the partition 10 is perforated at the corresponding position of the connection port 7, allowing the connection port 7 to smoothly connect the compressor chamber 101 and the heat dissipation channel. When the second fan 6 starts during heat dissipation, it not only generates forced convection within the heat dissipation channel but also further promotes natural airflow through the pressure difference between the connection port 7 and the air inlet 11. This pressure differential-driven airflow, together with the forced convection generated by the second fan 6, forms a highly efficient and stable heat dissipation system.

[0041] Specifically, when the air inside the compressor chamber 101 is drawn into the heat dissipation channel by the second fan 6, the pressure at the connection port 7 decreases, while the pressure at the air inlet 11, as the connection point between the external environment and the compressor chamber 101, is relatively high. Therefore, under the action of the pressure difference, fresh air from the external environment is drawn into the compressor chamber 101 through the air inlet 11, and then enters the heat dissipation channel through the connection port 7. In this process, the fresh air not only provides a continuous source of cooling for the heat dissipation channel, but also carries away the heat from the heat sink 3 through its flow.

[0042] Meanwhile, the top surface of the second end of the duct housing 4 is provided with an air outlet that communicates with the fan cavity 102. Here, the connection port 7 and the air outlet are on different planes; that is, the connection port 7 faces horizontally, while the air outlet faces vertically. In addition, the duct housing 4 is sealed except for the connection port 7, the air outlet, and the other parts where the heat sink 3 is installed. Since the drive plate 2 is installed in the compressor cavity 101, and the duct housing 4 is installed in the fan cavity 102, the connection port 7 on the side of the first end can guide the air in the compressor cavity 101 into the heat dissipation channel. The air in the heat dissipation channel is driven upward by the second fan 6, passes through the heat sink 3, and is discharged from the top air outlet to the fan cavity 102. This achieves effective heat dissipation and also avoids the air discharged from the heat dissipation channel from disturbing the original airflow in the fan cavity 102.

[0043] Specifically, the heat sink 3 includes multiple heat sink fins, and gaps are formed between adjacent heat sink fins to allow air to flow through. It can also be understood that the heat sink fins are vertically arranged in the heat dissipation channel, so that air can pass through the gaps between the heat sink fins and carry away the heat.

[0044] In addition to being finned, heat sink 3 can also be a heat pipe. It dissipates heat by having the liquid inside the pipe absorb, condense, release, and recirculate heat at high temperatures, resulting in higher heat dissipation efficiency and a smaller size compared to traditional heat sinks. Heat sink 3 can also be a heat dissipation fin, which is similar to a heat dissipation fin but is typically thinner, denser, and arranged in a fin-like structure. This structure can more effectively increase the heat dissipation area and improve heat dissipation efficiency.

[0045] It is worth mentioning that during the heat dissipation process, the airflow in the fan cavity 102 is often laminar. Therefore, in the air field of the first fan 5, the air velocity around the fan blades is the highest, and the air velocity decreases as it moves further away from the fan blades. The air duct shell 4 and the heat sink 3 are generally located far away from the first fan 5 to avoid collision damage. Therefore, the air velocity at the heat sink 3 on the drive plate 2 is almost zero, and the air field around the heat sink 3 is in a laminar flow state. The heat dissipated by the heat sink 3 cannot be effectively dissipated, resulting in a high IPM temperature on the drive plate 2. The compressor can only operate at a low frequency, resulting in very low energy efficiency of the heat pump. When the second fan 6 is started, the airflow state in the heat dissipation channel will change. At this time, the airflow state in the heat dissipation channel is often a transitional flow, which is a flow state between laminar flow and turbulent flow. When the fluid velocity and the geometry of the heat dissipation channel, the physical properties of the fluid and other factors change, the airflow state may change from laminar flow to turbulent flow. This process is often a transitional flow. Because the local area of ​​the heat dissipation channel sometimes has an orderly flow similar to laminar flow, and sometimes some small vortices are generated in other areas, it presents an unstable state. This greatly improves the heat dissipation effect of the heat sink 3 and greatly improves the energy efficiency of the heat pump.

[0046] Generally, an electrical box 9 is also installed inside the main body 1, and the drive board 2 is installed inside the electrical box 9.

[0047] As an optional real-time solution, the drive board 2 is set inside the press chamber 101, and the air duct shell 4 can also be set inside the press chamber 101. In this case, the bottom or side of the first end of the air duct shell 4 is opened with a connection port 7 so that the air in the press chamber 101 can smoothly enter the heat dissipation channel. The side of the second end is opened with an air outlet, and the partition plate 10 needs to be hollowed out according to the air outlet position so that the air in the heat dissipation channel can smoothly enter the fan chamber 102.

[0048] It should be noted that the flow guide 8 can be installed or not at the connection port 7 in this solution, depending on the situation. However, the flow guide must be installed at the air outlet, because the air outlet is horizontal. If the flow guide 8 is not installed, the air in the heat dissipation channel will be disturbed and the airflow in the fan cavity 102 will be disrupted.

[0049] As another optional real-time solution, when the air duct shell 4 is embedded in the partition plate, so that half of the air duct shell 4 is located in the compressor chamber 101 and the other half is located in the fan chamber 102, a connection port 7 is opened on the bottom surface of the first end of the air duct shell 4, and an air outlet is opened on the top surface of the second end. The connection port 7 is partially sealed in the fan chamber 102, and the air outlet is partially sealed in the compressor chamber 101.

[0050] On the other hand, a control method for an air source heat pump is also provided, applicable to the air source heat pump described above. The execution of the control method begins with the startup of the air source heat pump. Once the heat pump starts operating, the first fan 5 is immediately turned on, its function being to maintain the basic airflow circulation within the heat pump system. Simultaneously, the system begins real-time monitoring of the temperature T of the intelligent power module (IPM) on the drive board 2. When the monitored IPM temperature T exceeds a preset temperature threshold T1, the system determines that enhanced heat dissipation is needed and immediately starts the second fan 6. It is worth noting that in the initial startup phase of the second fan 6, the system sets its operating frequency at a low level to avoid excessive interference with the system's airflow. To achieve coordinated operation between the two fans, a frequency adjustment mechanism is also designed. Specifically, the system dynamically adjusts the frequency of the second fan 6 based on the real-time operating frequency of the first fan 5. For example, when the first fan 5 operates at a higher frequency, the system will choose to start the second fan 6 at a relatively lower but appropriate frequency to ensure that the airflow generated by both fans can blend together rather than interfere with each other. As the IPM temperature continues to rise, the system gradually increases the operating frequency of the second fan 6, but throughout this process, it maintains consistency with the frequency of the first fan 5. Through this precise frequency adjustment, the system can minimize turbulence, thereby ensuring maximum heat dissipation.

[0051] Generally, a compressor is installed in the compressor chamber 101. Based on the operating state of the heat pump, there are at least three operating states: the first is the high-load operating state, the second is the low-load operating state, and the third is a special operating state (such as a fault).

[0052] Based on the high-load operation state described in the first scenario, i.e., when the heat pump is running at high load, the IPM temperature of the drive board 2 rises rapidly. The IPM temperature is monitored in real time by a temperature sensor. Initial stage: Only the first fan 5 is activated for basic heat dissipation. When the IPM temperature reaches a preset higher threshold T2, the compressor begins to reduce its operating frequency to reduce heat generation. If the IPM temperature continues to rise and exceeds a higher threshold T1, the second fan 6 is activated, and the operating frequencies of both fans are adjusted according to the previously described anti-turbulence control logic to ensure effective heat dissipation. As the second fan 6 continues to operate, when the IPM temperature drops to T3, the compressor stops reducing its frequency and maintains its current frequency. When the temperature further drops to T4, the compressor releases its frequency limit and rapidly increases to its normal operating frequency. At this point, a strong airflow is formed throughout the airflow field, achieving efficient heat dissipation. Here, T2, T3, and T4 are all preset temperature thresholds, and T4 < T3 < T2 < T1.

[0053] Based on the second low-load operating state described above, i.e., when the heat pump is running at a low load, the heat generated by the drive board 2 is relatively small. At this time, the first fan 5 operates at a low frequency to maintain basic heat dissipation. If the IPM temperature rises slightly but does not reach T1, the second fan 6 is not turned on, and heat dissipation relies solely on the first fan 5 and the heat sink 3 for natural cooling. If the IPM temperature continues to rise above T1, the control logic for the high-load operating state is followed to ensure that the IPM temperature remains stable within a reasonable range, keeping the compressor frequency stable and ensuring the normal operation of the heat pump.

[0054] Based on the special operating state described in the third scenario, after the second fan 6 is turned on, the ambient temperature t is monitored in real time. Simultaneously, the IPM temperature T drop of the drive board 2 is set to F. When the detected ambient temperature t > t1 and the heat pump is running at high load, and both the first fan 5 and the second fan 6 are turned on and running normally, the IPM temperature drops slowly but remains above the normal range (i.e., T > T1 and F < F1). At this time, the upper limit of the operating frequency of the first fan 5 and the second fan 6 can be appropriately increased to enhance heat dissipation until the IPM temperature drops to a safe range. Here, the operating frequency of either the first fan 5 or the second fan 6 can be increased individually, or the operating frequency can be increased simultaneously according to the actual situation. If abnormal heat dissipation is caused by a fault, such as a fault in the second fan 6, the compressor operation is immediately stopped, and a fault alarm signal is issued. After the second fan 6 is repaired, the system is restarted and operates according to normal control logic. Here, t1 is the preset ambient temperature threshold, and F is the preset amplitude threshold.

[0055] It is important to note that if the system detects a continuous increase in the IPM temperature T of the drive board 2 after the second fan 6 is turned on, this usually indicates that the current heat dissipation capacity is insufficient to meet the heat dissipation requirements of the heat pump system. To more effectively reduce the IPM temperature and prevent overheating, the system can prioritize gradually increasing the operating frequency of the second fan 6. Increasing the operating frequency of the second fan 6 will increase the airflow within the heat dissipation channel, thereby accelerating heat transfer and dissipation. This measure can quickly respond to the rise in IPM temperature without changing the compressor's operating frequency, helping to maintain the stable operation of the heat pump system. The "continuous increase" refers to the IPM temperature remaining in an upward phase after the second fan 6 is started, without any cooling effect.

[0056] Specifically, the second fan 6 includes at least a first operating gear, a second operating gear, and a third operating gear. When T > T1, the second fan 6 operates according to the first operating gear; when T > T5, the second fan 6 operates according to the second operating gear; when T > T6, the second fan 6 operates according to the third operating gear; wherein, T6 > T5 > T1, the operating frequency of the third operating gear is greater than the operating frequency of the second operating gear, and the operating frequency of the second operating gear is greater than the operating frequency of the first operating gear.

[0057] When the IPM temperature T exceeds the preset threshold T1, the second fan 6 starts at the first operating level. This level is the initial operating level of the second fan 6, and its operating frequency is relatively low, but sufficient to provide the necessary heat dissipation capacity when the heat pump system is under low load or in the initial heating stage.

[0058] As the IPM temperature rises further, when T exceeds a higher threshold T5, the system will activate the second fan 6 to its second operating level. In this level, the second fan 6 operates at a higher frequency, thereby increasing airflow and heat dissipation efficiency within the heat dissipation channels. This measure helps maintain stable system operation when the heat pump system is under high load or when the IPM temperature rises rapidly.

[0059] If the IPM temperature continues to rise and exceeds the highest threshold T6, the second fan 6 will enter the third operating mode. In this mode, the second fan 6 operates at its highest frequency, providing the strongest heat dissipation capacity. This measure is an emergency cooling measure taken when the heat pump system is under extreme load or the IPM temperature is extremely high, to ensure the safe and stable operation of the system.

[0060] However, while increasing the operating frequency of the second fan 6, the system also needs to continue monitoring changes in IPM temperature and adjust the operating parameters of the first fan 5 and the second fan 6 according to the actual situation. If increasing the frequency of the second fan 6 alone is insufficient to effectively control the rise in IPM temperature, the system may need to take further measures, such as reducing the operating frequency of the compressor or activating other backup cooling mechanisms.

[0061] Furthermore, to avoid excessive energy consumption and noise, the upper limit of the operating frequency of the second fan 6 must be considered. If the IPM temperature continues to rise when the operating frequency of the second fan 6 reaches the preset maximum value, the system may need to take more urgent cooling measures or issue a fault alarm.

[0062] In some embodiments, when the air source heat pump operates in heating mode, the outlet air temperature H of the first fan 5 is monitored in real time. When H > H1, the operating frequency of the first fan 5 and / or the operating frequency of the second fan 6 are increased, where H1 is the set temperature of the air source heat pump. During heating operation, the outlet air temperature of the first fan 5 is monitored. When a higher temperature is detected, it indicates that a significant amount of heat is not being fully utilized. In this case, depending on usage requirements, if rapid heating is needed, the system can adjust the fan operation strategy, converting the energy consumption originally used for frequency conversion into increased fan speed. This allows the hot air to better participate in the heat pump's heating cycle, improving energy efficiency and achieving energy savings. For example, when the temperature of the air carried out by the vortex (i.e., the outlet air of the first fan 5) is detected to be higher than the set temperature H1, the speed of the first fan 5 or the second fan 6 is appropriately increased, allowing more heat to be delivered to the indoor side, reducing additional heating energy consumption and improving the overall energy efficiency of the heat pump system during heating operation.

[0063] Furthermore, this solution primarily employs air cooling for heat dissipation. Unlike refrigerant-cooled systems, air cooling prevents water vapor in the air from condensing into droplets on the surfaces of low-temperature components. During operation, if the refrigerant temperature is low, the refrigerant in the refrigerant plate is prone to condensation when it comes into contact with outside air, causing water vapor in the air to reach its dew point. However, the air cooling structure in this solution relies on airflow to remove heat, resulting in a relatively stable air temperature and preventing localized low temperatures that could lead to condensation. This effectively avoids the risk of condensation on the refrigerant plate. This not only protects the drive board 2 and related components from damage such as short circuits and corrosion caused by condensation but also ensures stable system operation, reduces equipment failures and maintenance costs due to condensation, and extends the equipment's lifespan.

[0064] In the description herein, it should be understood that the terms "upper," "lower," "left," "right," and other orientations or positional relationships are used only for ease of description and simplification of operation, 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, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first" and "second" are used merely for descriptive distinction and have no special meaning.

[0065] In the description of this specification, references to terms such as "an embodiment," "example," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0066] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style of the specification is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0067] The technical principles of this application have been described above with reference to specific embodiments. These descriptions are merely for explaining the principles of this application and should not be construed as limiting the scope of protection of this application in any way. Based on this explanation, those skilled in the art can readily conceive of other specific embodiments of this application without inventive effort, and these embodiments will all fall within the scope of protection of this application.

Claims

1. A control method for an air source heat pump, applied to an air source heat pump, characterized in that, The air source heat pump includes: a body (1), a drive plate (2), a heat sink (3), and a duct shell (4). The body (1) has a relatively independent compressor chamber (101) and a fan chamber (102). A first fan (5) is installed in the fan chamber (102). The drive plate (2) is installed inside the body (1). The heat sink (3) is located on one side of the drive plate (2). The duct shell (4) is located inside the body (1). A heat dissipation channel is formed inside the duct shell (4). The heat sink (3) is located in the heat dissipation channel. One end of the heat dissipation channel is connected to the compressor chamber (101), and the other end is connected to the fan chamber (102). A second fan (6) is installed in the heat dissipation channel so that the air in the compressor chamber (101) enters from one end of the heat dissipation channel, passes through the heat sink (3), and is delivered to the fan chamber (102) from the other end of the heat dissipation channel. The heat dissipation channel has a first end and a second end. The first end is connected to the compressor chamber (101), and the second fan (6) is disposed at the second end. The first end is also provided with a guide (8) so that the air in the compressor chamber (101) enters the heat dissipation channel upward. The control method includes the following steps: after the air source heat pump is running, the first fan (5) is turned on, and the IPM temperature T of the drive board (2) is monitored in real time. When T > T1, the second fan (6) is turned on, where T1 is a preset temperature threshold. After the second fan (6) is turned on, when the IPM temperature T of the drive board (2) is detected to be continuously rising, the operating frequency of the second fan (6) is gradually increased; the second fan (6) includes at least a first operating gear, a second operating gear and a third operating gear. When T > T1, the second fan (6) operates according to the first operating gear; when T > T5, the second fan (6) operates according to the second operating gear; when T > T6, the second fan (6) operates according to the third operating gear; wherein, T6 > T5 > T1, the operating frequency of the third operating gear is greater than the operating frequency of the second operating gear, and the operating frequency of the second operating gear is greater than the operating frequency of the first operating gear; After the second fan (6) is turned on, the ambient temperature t is detected in real time, and the IPM temperature T of the drive board (2) is set to decrease by F. When t > t1, T > T1 and F < F1, the operating frequency of the first fan (5) and the operating frequency of the second fan (6) are increased, where t1 is a preset ambient temperature threshold and F is a preset amplitude threshold. When the air source heat pump is in heating mode, the outlet temperature H of the first fan (5) is detected in real time. When H > H1, the operating frequency of the first fan (5) and the operating frequency of the second fan (6) are increased, where H1 is the temperature set by the air source heat pump.

2. The control method for an air source heat pump according to claim 1, characterized in that, The machine body (1) is provided with an air inlet (11), which connects the external environment and the compressor chamber (101).

3. The control method for an air source heat pump according to claim 1, characterized in that, The side of the first end is provided with a connection port (7) that connects to the compressor chamber (101), and the top surface of the second end is provided with an air outlet that connects to the fan chamber (102).

4. The control method for an air source heat pump according to claim 3, characterized in that, The connection port (7) is located below the heat sink (3).

5. The control method for an air source heat pump according to claim 1, characterized in that, The drive plate (2) is installed in the press chamber (101), and the air duct shell (4) is located in the fan chamber (102).

6. The control method for an air source heat pump according to claim 1, characterized in that, A compressor is installed in the compressor chamber (101). When T2≤T≤T1, the compressor reduces its operating frequency, where T2 is a preset temperature threshold.

7. The control method for an air source heat pump according to claim 6, characterized in that, When T≤T3, the compressor stops reducing the frequency and maintains the current frequency, where T3 is a preset temperature threshold and T3<T2.

8. The control method for an air source heat pump according to claim 7, characterized in that, When T≤T4, the compressor releases the frequency limit and increases the operating frequency, where T4 is a preset temperature threshold and T4<T3.

Images