Operation control method and device of fresh air equipment, fresh air equipment and storage medium

Abstract

The invention relates to the technical field of fresh air machines, in particular to an operation control method and device of fresh air equipment, the fresh air equipment and a storage medium. The temperature of the coil pipe of the indoor heat exchanger arranged in the air supply duct in the second heat pump system is obtained, and the running state of the first heat pump system and / or the second heat pump system is correspondingly adjusted according to the temperature of the coil pipe in different running modes, so that the mutual influence of the two heat pump systems in the running process is reduced; the technical problem that in the prior art, faults are prone to occurring in the operation process of fresh air equipment is solved, and the use stability of the fresh air machine is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of fresh air fans, and particularly to an operation control method and device for fresh air equipment, fresh air equipment, and a storage medium. Background Art

[0002] During the operation of a fresh air fan with a dual system, air will flow through multiple heat exchangers in sequence for heat exchange. Taking the primary heat pump system and the secondary heat pump system as an example, if the fresh air fan operates in the heating mode, after the air is heated by the primary heat pump system, it then flows through the secondary heat pump system. At this time, the temperature difference between the heated air and the heat exchanger of the secondary heat pump system is relatively small, resulting in the refrigerant of the secondary heat pump system still being in a high-temperature and high-pressure state, which easily causes the compressor of the secondary heat pump system to be overloaded, damage the compressor, and reduce the reliability of the whole machine. If the fresh air fan operates in the cooling mode, after the air is cooled by the primary heat pump system and remains in a low-temperature state, when it passes through the indoor heat exchanger of the secondary heat pump system, it is easy to make the evaporation pressure of the secondary heat pump system too low, frequently trigger the separate low-pressure protection program of the secondary heat pump system, and then reduce the frequency or stop the machine.

[0003] The above content is only used to assist in understanding the technical solution of the present invention and does not represent an admission that the above content is prior art. Summary of the Invention

[0004] The main purpose of the present invention is to provide an operation control method and device for fresh air equipment, fresh air equipment, and a storage medium, aiming to solve the technical problem that the fresh air equipment is prone to failures during operation in the prior art.

[0005] To achieve the above purpose, the present invention provides an operation control method for fresh air equipment. The operation control method for fresh air equipment is applied to fresh air equipment. The fresh air equipment includes a primary heat pump system and a secondary heat pump system. The primary heat pump system includes a primary indoor heat exchanger, and the secondary heat pump system includes a secondary indoor heat exchanger. Both the primary indoor heat exchanger and the secondary indoor heat exchanger are arranged in the air supply duct. The distance between the primary indoor heat exchanger and the fresh air inlet of the air supply duct is less than the distance between the secondary indoor heat exchanger and the fresh air inlet of the air supply duct.

[0006] The method includes the following steps:

[0007] Obtain the current operation mode of the fresh air equipment and the coil temperature of the indoor heat exchanger arranged in the air supply duct in the secondary heat pump system; and

[0008] Adjust the operation state of the primary heat pump system and / or the secondary heat pump system according to the current operation mode and the coil temperature.

[0009] Optionally, obtaining the coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system includes:

[0010] Obtaining the heat exchanger temperatures of all the indoor heat exchangers disposed in the air supply duct of the second heat pump system;

[0011] Determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures.

[0012] Optionally, determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures includes:

[0013] If all the indoor heat exchangers disposed in the air supply duct of the second heat pump system are second indoor heat exchangers, the heat exchanger temperature of the second indoor heat exchanger is the coil temperature;

[0014] If all the indoor heat exchangers disposed in the air supply duct of the second heat pump system are second indoor heat exchangers and third indoor heat exchangers, the maximum or minimum value of the heat exchanger temperature of the second indoor heat exchanger and the heat exchanger temperature of the third indoor heat exchanger is the coil temperature.

[0015] Optionally, the first heat pump system includes a first compressor, and the second heat pump system includes a second compressor;

[0016] Adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes:

[0017] When the current operating mode is the heating mode and the coil temperature is in the first temperature range, reducing the operating frequency of the first compressor and / or the operating frequency of the second compressor;

[0018] Wherein, when the current operating mode is the heating mode, both the first heat pump system and the second heat pump system operate in the heating mode.

[0019] Optionally, after reducing the operating frequency of the first compressor and / or the operating frequency of the second compressor, the method for controlling the operation of the fresh air device further includes:

[0020] If, after the operating frequency of the first compressor is reduced to the minimum operating frequency, the current coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system is still in the first temperature range, controlling the first heat pump system to stop operating.

[0021] Optionally, after controlling the first heat pump system to stop operating, the method for controlling the operation of the fresh air device further includes:

[0022] When the current coil temperature is less than the preset temperature, control the first heat pump system to start heating operation.

[0023] Optionally, the operation control method of the fresh air device further includes:

[0024] Count the current shutdown times of the first heat pump system; and

[0025] Adjust the first temperature range according to the current shutdown times and the preset temperature adjustment value.

[0026] Optionally, the operation control method of the fresh air device further includes:

[0027] Determine the target shutdown duration of the first heat pump system according to the current shutdown times; and

[0028] When the current shutdown times is greater than the preset times, control the first heat pump system to shutdown within the target shutdown duration.

[0029] Optionally, the operation control method of the fresh air device further includes:

[0030] At intervals of the target shutdown duration, obtain the outdoor ambient temperature of the area where the fresh air device is located; and

[0031] When the outdoor ambient temperature is less than the fourth temperature, or the coil temperature is less than the third temperature, restart the first heat pump system.

[0032] Optionally, the first heat pump system includes a first compressor, and the second heat pump system includes a second compressor;

[0033] Adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes:

[0034] When the current operating mode is the heating mode and the coil temperature is in the second temperature range, limit the maximum operating frequency of the first compressor to be less than or equal to the current operating frequency of the first compressor, and control the second compressor to maintain the current operating frequency;

[0035] Wherein, the maximum temperature of the second temperature range is less than the minimum temperature of the first temperature range.

[0036] Optionally, adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes:

[0037] When the current operating mode is the cooling mode and the coil temperature is in the third temperature range, reduce the operating frequency of the first compressor and / or the operating frequency of the second compressor;

[0038] Wherein, when the current operation mode is the refrigeration mode, both the first heat pump system and the second heat pump system operate in the refrigeration mode.

[0039] In addition, to achieve the above object, the present invention further provides an operation control device for a fresh air device, and the operation control device for the fresh air device includes:

[0040] An acquisition module, configured to acquire the current operation mode of the fresh air device and the coil temperature of the indoor heat exchanger provided in the air supply duct in the second heat pump system; and

[0041] An adjustment module, configured to adjust the operation states of the first heat pump system and / or the second heat pump system according to the current operation mode and the coil temperature.

[0042] In addition, to achieve the above object, the present invention further provides a fresh air device, and the fresh air device includes: a memory, a processor, and an operation control program for the fresh air device stored on the memory and executable on the processor, and the operation control program for the fresh air device is configured to implement the steps of the operation control method for the fresh air device as described above.

[0043] In addition, to achieve the above object, the present invention further provides a storage medium, and an operation control program for a fresh air device is stored on the storage medium, and when the operation control program for the fresh air device is executed by a processor, the steps of the operation control method for the fresh air device as described above are implemented.

[0044] The present invention discloses an operation control method for a fresh air device, and the operation control method for the fresh air device includes: acquiring the current operation mode of the fresh air device and the coil temperature of the indoor heat exchanger provided in the air supply duct in the second heat pump system; adjusting the operation states of the first heat pump system and / or the second heat pump system according to the current operation mode and the coil temperature. Compared with the prior art, by acquiring the coil temperature of the indoor heat exchanger provided in the second heat pump system and correspondingly adjusting the operation states of the first heat pump system and / or the second heat pump system according to the coil temperature in different operation modes, the present invention reduces the mutual influence during the operation of the two heat pump systems, avoids the technical problem that the fresh air device is prone to failure during operation in the prior art, and improves the use stability of the fresh air fan. Description of the Drawings

[0045] Figure 1 is a schematic structural diagram of a fresh air device in a hardware operation environment related to the embodiment solution of the present invention;

[0046] Figure 2 is a schematic flowchart of the first embodiment of the operation control method for the fresh air device of the present invention;

[0047] Figure 3 Schematic diagram of a structure of an air conditioner in an embodiment of the control method of the fresh air machine of the present invention;

[0048] Figure 4 Schematic diagram of another structure of an air conditioner in an embodiment of the control method of the fresh air machine of the present invention;

[0049] Figure 5 Schematic flow chart of the second embodiment of the operation control method of the fresh air equipment of the present invention;

[0050] Figure 6 Schematic flow chart of the third embodiment of the operation control method of the fresh air equipment of the present invention;

[0051] Figure 7 Block diagram of the structure of the first embodiment of the operation control device of the fresh air equipment of the present invention.

[0052] Description of reference numerals

[0053] Label Name Label Name 100 Fresh air equipment 10 First heat pump system 20 Second heat pump system 11 First compressor 12 First heat exchange module 13 First fresh air heat exchanger 14 Second fresh air heat exchanger 15 First throttling element 16 Second throttling element 17 Third throttling element 18 First check valve 19 Second check valve 1 Third check valve 2 Fourth check valve 3 Reversing device 4 Air supply channel 5 Exhaust air channel 6 Air supply fan 7 Air supply valve 8 Exhaust fan 9 Exhaust air valve 27 Second compressor 21 Second outdoor heat exchanger 22 Third fresh air heat exchanger 23 Fourth fresh air heat exchanger 24 Fourth throttling element 25 Fifth check valve 26 Fifth throttling element 30 By-pass air valve 31 First communication port 32 Second communication port 33 Inlet 34 Outlet 35 First outdoor heat exchanger 36 Heat recovery heat exchanger 37 Outdoor fan

[0054] The realization, functional features and advantages of the object of the present invention will be further described in conjunction with the embodiments with reference to the drawings. Detailed implementation manners

[0055] It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0056] Refer to Figure 1 , Figure 1 Schematic diagram of the structure of the fresh air equipment of the hardware operating environment involved in the embodiment solution of the present invention.

[0057] Such as Figure 1As shown in the figure, the fresh air device may include: a processor 1001, such as a Central Processing Unit (CPU), a communication bus 1002, a user interface 1003, a network interface 1004, and a memory 1005. Among them, the communication bus 1002 is used to realize the connection and communication between these components. The user interface 1003 may include a display screen (Display) and an input unit such as a keyboard (Keyboard). Optionally, the user interface 1003 may further include a standard wired interface and a wireless interface. The network interface 1004 may optionally include a standard wired interface and a wireless interface (such as a Wireless-Fidelity (Wi-Fi) interface). The memory 1005 may be a high-speed Random Access Memory (RAM) or a stable Non-Volatile Memory (NVM), such as a disk memory. Optionally, the memory 1005 may also be a storage device independent of the aforementioned processor 1001.

[0058] Those skilled in the art can understand that Figure 1 the structure shown in the figure does not constitute a limitation on the fresh air device, and it may include more or fewer components than shown in the figure, or combine some components, or have different component arrangements.

[0059] As Figure 1 shown, the memory 1005, as a storage medium, may include an operating system, a network communication module, a user interface module, and a running control program for the fresh air device.

[0060] In Figure 1 the fresh air device shown in the figure, the network interface 1004 is mainly used for data communication with a network server; the user interface 1003 is mainly used for data interaction with a user; the processor 1001 and the memory 1005 in the fresh air device of the present invention may be arranged in the fresh air device. The fresh air device calls the running control program stored in the memory 1005 through the processor 1001 and executes the running control method for the fresh air device provided by the embodiments of the present invention.

[0061] The embodiments of the present invention provide a running control method for a fresh air device. Referring to Figure 2 , Figure 2 it is a schematic flowchart of the first embodiment of a running control method for a fresh air device of the present invention.

[0062] In this embodiment, the running control method for the fresh air device includes the following steps:

[0063] Step S10: Obtain the current operating mode of the fresh air device and the coil temperature of the indoor heat exchanger provided in the air supply duct of the second heat pump system.

[0064] It should be noted that the execution subject of the method in this embodiment can be a device with data acquisition or data processing functions, such as: the control device of the fresh air device or a fresh air fan equipped with a dual heat pump system, or other devices that can achieve the same or similar functions. This embodiment does not make specific limitations. In this embodiment and the following embodiments, a fresh air fan equipped with a dual heat pump system will be used as an example for illustration.

[0065] It is worth noting that the fresh air fan with a dual heat pump system in this embodiment and the following embodiments refers to such as Figure 3 and Figure 4The shown fresh air machine, the fresh air machine 100 includes a housing and a first heat pump system 10. A air supply channel 4 is provided in the housing. The first heat pump system 10 includes: a fresh air heat exchanger structure and a first switching device. The fresh air heat exchanger structure is in the air supply channel 4, and the fresh air heat exchanger structure has a refrigerant pipeline. The first switching device is communicated with the fresh air heat exchanger structure, and the first switching device is used to switch the flow direction of the refrigerant in the fresh air heat exchanger structure. In different operating modes of the first heat pump system 10, the refrigerant of the first heat pump system 10 first passes through the refrigerant pipeline located downstream of the air supply channel 4, and then passes through the refrigerant pipeline located upstream of the air supply channel 4. Wherein, the air supply channel 4 refers to the channel through which the air conditioner 100 sends outdoor fresh air into the room, and the exhaust channel 5 refers to the channel through which the air conditioner 100 discharges indoor air to the outside. The fresh air heat exchanger structure is arranged in the first refrigerant flow path. The first heat pump system 10 further includes: a first compressor 11, a first heat exchange module 12 and a reversing device 3. The first compressor 11 is arranged in the first refrigerant flow path and has a first exhaust port and a first suction port. The first heat exchange module 12 is arranged in the first refrigerant flow path and is communicated with the first switching device. The first heat exchange module 12 includes a first outdoor heat exchanger 35 and a heat recovery heat exchanger 36 connected in series. The heat recovery heat exchanger 36 is arranged in the exhaust channel 5, and the first outdoor heat exchanger 35 is arranged outside the housing (main housing). The first compressor 11 is installed in the exhaust channel 5 or outside the housing (main housing). Thus arranged, the heat recovery heat exchanger 36 is arranged in the exhaust channel 5. After the air in the exhaust channel 5 exchanges heat with the heat recovery heat exchanger 36, it is then discharged from the exhaust channel 5, so that the heat of the air discharged from the exhaust channel 5 can be recovered. The reversing device 3 communicates with the first exhaust port, the first suction port, the first heat exchange module 12 and the first switching device. The reversing device 3 is used to switch the refrigerant flow direction, so that the refrigerant first passes through the first heat exchange module 12 and then the first switching device, or so that the refrigerant first passes through the first switching device and then passes through the first heat exchange module 12. In order to realize the dehumidification and reheating function of the air conditioner 100, the fresh air heat exchanger structure includes a first fresh air heat exchanger 13 and a second fresh air heat exchanger 14 connected in series in sequence. The first fresh air heat exchanger 13 is located downstream of the air supply channel 4 relative to the second fresh air heat exchanger 14. The outlet 34 is connected to the first fresh air heat exchanger 13, and the inlet 33 is connected to the second fresh air heat exchanger 14. Thus arranged, in the dehumidification and reheating mode, the first fresh air heat exchanger 13 acts as an evaporator to cool the air, and the second fresh air heat exchanger 14 acts as a condenser to heat the air, thereby realizing the dehumidification and reheating of the air.In order to reduce the control components in the air conditioner 100 and improve the stability of the air conditioner 100, the first switching device has a first communication port 31, a second communication port 32, an inflow port 33 and an outflow port 34. The fresh air heat exchanger structure communicates the outflow port 34 and the inflow port 33. The first switching device includes: a first check valve 18, a second check valve 19, a third check valve 1 and a fourth check valve 2. The first check valve 18 is connected between the first communication port 31 and the inflow port 33, and the first check valve 18 is conductive in the direction from the inflow port 33 to the first communication port 31; the second check valve 19 is connected between the first communication port 31 and the outflow port 34, and the second check valve 19 is conductive in the direction from the first communication port 31 to the outflow port 34; the third check valve 1 is connected between the inflow port 33 and the second communication port 32, and the third check valve 1 is conductive in the direction from the inflow port 33 to the second communication port 32; the fourth check valve 2 is connected between the outflow port 34 and the second communication port 32, and the fourth check valve 2 is conductive in the direction from the second communication port 32 to the outflow port 34. With such a setting, the first switching device is entirely composed of check valves. Compared with the solutions of a four-way valve or two three-way valves, no control components are required, and the air conditioner 100 has relatively high stability.

[0066] With such a setting, for two heat pump systems, there are two indoor heat exchangers in the fresh air channel (exhaust air channel), and correspondingly two coil temperatures. In the heating mode, the coil temperature of the upstream heat exchanger is higher than that of the downstream heat exchanger. Compared with the one-stage evaporation heating solution, the energy consumption is greatly increased. However, the upstream heat pump system can preheat or precool the air first, and then exchange heat through the downstream heat pump system. At this time, it can effectively reduce the outlet air temperature in the cooling mode and increase the outlet air temperature in the heating mode.

[0067] The upstream heat exchanger in the above text refers to the heat exchanger closer to the fresh air inlet (or farther from the air supply outlet). In this embodiment and the following embodiments, it is referred to as the first indoor heat exchanger. The downstream heat exchanger refers to the heat exchanger farther from the fresh air inlet (or closer to the air supply outlet), and is also referred to as the second indoor heat exchanger. This embodiment does not make specific limitations. The first indoor heat exchanger and the second indoor heat exchanger belong to different heat pump systems respectively.

[0068] Meanwhile, due to such a setting, in the low-temperature heating scenario, when both systems of the fresh air unit are operating in heating mode, after the outdoor air is condensed and heated by the indoor heat exchanger of the first heat pump system, its temperature is relatively high. When it passes through the indoor heat exchanger of the second heat pump system again, it is likely to cause the condensation pressure of the second heat pump system to be too high, frequently triggering the separate high-pressure protection program of the second heat pump system, and then reducing the frequency or shutting down. Since the temperature of the air heated by the heat exchanger of the first heat pump system is still very high, after heat exchange with the heat exchanger of the second heat pump system, the refrigerant side of the second heat pump system continuously maintains a high-pressure state. When the second heat pump system reduces the frequency to a certain extent, it exceeds the pressure operating range of the 2-stage compressor, which is likely to cause the 2-stage compressor to be overloaded, damage the compressor, and reduce the reliability of the whole machine.

[0069] In another case, when the second heat pump system shuts down due to high-pressure protection, the first heat pump system is still operating. The air temperature passing through the heat exchanger of the second heat pump system is relatively high. When the 2-stage compressor restarts from a low frequency, the high-pressure immediately exceeds the operating range at the starting frequency, which is likely to cause the second heat pump system to be overloaded at the moment of startup, resulting in startup failure and damage to the compressor.

[0070] Similarly, in the low-temperature cooling scenario, when both systems of the fresh air unit are operating in cooling mode, after the outdoor air is evaporated and cooled by the indoor heat exchanger of the first heat pump system, its temperature is relatively low. When it passes through the indoor heat exchanger of the second heat pump system again, it is likely to cause the evaporation pressure of the second heat pump system to be too low, frequently triggering the separate low-pressure protection program of the second heat pump system, and then reducing the frequency or shutting down. Since the temperature of the air cooled by the heat exchanger of the first heat pump system is low, after heat exchange with the heat exchanger of the second heat pump system, the refrigerant side of the second heat pump system continuously maintains a low-pressure state. When the second heat pump system reduces the frequency to a certain extent, it exceeds the low-pressure operating range of the 2-stage compressor, which is likely to cause the 2-stage compressor to return liquid, damage the compressor, and reduce the reliability of the whole machine.

[0071] In another case, when the second heat pump system shuts down due to low-pressure protection, the first heat pump system is still operating. The air temperature passing through the heat exchanger of the second heat pump system is relatively low. When the 2-stage compressor restarts from a low frequency, the low-pressure immediately exceeds the operating range at the starting frequency. When the second heat pump system starts up, more liquid returns, which is likely to cause liquid hammer and damage the compressor.

[0072] To solve the above problems, in this embodiment, by monitoring the coil temperature of the indoor heat exchanger in the second heat pump system, the operation of the first heat pump system and / or the second heat pump system is controlled according to the temperature range of its coil temperature, so as to avoid the temperature being too high or too low and damaging the fresh air unit.

[0073] It can be understood that in this embodiment, the operation modes of the fresh air equipment include but are not limited to the heating mode and the cooling mode. According to the refrigerant flow direction, it also includes the heating and dehumidifying mode, the defrosting mode, etc. This embodiment does not make specific limitations on this.

[0074] In a specific implementation, the first heat pump system includes a first indoor heat exchanger, and the second heat pump system includes a second indoor heat exchanger. Both the first indoor heat exchanger and the second indoor heat exchanger are arranged in the air supply duct. The distance between the first indoor heat exchanger and the fresh air inlet of the air supply duct is less than the distance between the second indoor heat exchanger and the fresh air inlet of the air supply duct.

[0075] Further, obtaining the coil temperature of the indoor heat exchanger arranged in the air supply duct in the second heat pump system includes:

[0076] Obtaining the heat exchanger temperatures of all the indoor heat exchangers arranged in the air supply duct in the second heat pump system;

[0077] Determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures.

[0078] It can be understood that there are two sets of heat pump systems in this embodiment, and multiple indoor heat exchangers may be provided in both sets of heat pump systems.

[0079] In this embodiment, referring to Figure 3 , in the second heat pump system, multiple indoor heat exchangers may be arranged in the air supply duct. To improve the efficiency and accuracy of controlling the operating state of the heat pump system, in this embodiment, the maximum or minimum value of the heat exchanger temperatures of all the indoor heat exchangers arranged in the air supply duct is taken as the final coil temperature. Among them, when the fresh air device operates in the heating mode, the maximum value of the heat exchanger temperatures of all the indoor heat exchangers is taken as the coil temperature, and when the fresh air device operates in the cooling mode, the minimum value of the heat exchanger temperatures of all the indoor heat exchangers is taken as the coil temperature.

[0080] Further, determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures includes:

[0081] If all the indoor heat exchangers arranged in the air supply duct in the second heat pump system are the second indoor heat exchangers, then the heat exchanger temperature of the second indoor heat exchanger is the coil temperature;

[0082] If all the indoor heat exchangers arranged in the air supply duct in the second heat pump system are the second indoor heat exchanger and the third indoor heat exchanger, then the maximum or minimum value of the heat exchanger temperature of the second indoor heat exchanger and the heat exchanger temperature of the third indoor heat exchanger is the coil temperature.

[0083] In a specific implementation, the third indoor heat exchanger refers to the indoor heat exchanger in the upstream part of the second heat pump system in the air supply duct, that is, the distance between the third indoor heat exchanger and the fresh air inlet of the air supply duct is greater than the distance between some of the first indoor heat exchangers of the first heat pump system and the fresh air inlet of the air supply duct. Referring toFigure 3 Or Figure 4 In the structure diagram of the fresh air fan in Figure 4 , when there are multiple indoor heat exchangers in both heat pump systems of the fresh air equipment, it is possible that the distance from a part of the indoor heat exchangers of the first heat pump system to the fresh air inlet of the air supply duct is less than the distance from the second indoor heat exchanger of the second heat pump system to the fresh air inlet of the air supply duct. It is also possible that, as in Figure 3 , the first fresh air heat exchanger 13 (the third indoor heat exchanger) is upstream of the air supply duct. At this time, in order to improve the stability of controlling the operating state of the dual heat pump system of the fresh air equipment, in this embodiment, the maximum or minimum value of the heat exchanger temperature of the second indoor heat exchanger and the heat exchanger temperature of the third indoor heat exchanger is taken as the coil temperature, reducing the temperature interference caused by the structural setting of the indoor heat exchangers in the fresh air equipment. Figure 3 In Figure 3 , the first fresh air heat exchanger 13 (the third indoor heat exchanger) is in the upstream of the air supply duct. At this time, in order to improve the stability of controlling the operating state of the dual heat pump system of the fresh air equipment, in this embodiment, the maximum or minimum value of the heat exchanger temperature of the second indoor heat exchanger and the heat exchanger temperature of the third indoor heat exchanger is taken as the coil temperature, reducing the temperature interference caused by the structural setting of the indoor heat exchangers in the fresh air equipment.

[0084] Step S20: Adjust the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature.

[0085] It should be noted that adjusting the operating states of the first heat pump system and / or the second heat pump system can be to adjust the operating frequency of the first compressor corresponding to the first heat pump system or the operating frequency of the second compressor corresponding to the second heat pump system. This embodiment does not make specific limitations on this.

[0086] Since the fresh air fan faces different fault conditions for the second indoor heat exchanger in the second heat pump system in different operating modes, it is necessary to ensure that the coil pressure of the second indoor heat exchanger cannot be too high in the heating mode and the pressure of the second indoor heat exchanger cannot be too low in the cooling mode, so as to avoid the occurrence of fresh air fan system failures.

[0087] In this embodiment, by obtaining the coil temperature of the indoor heat exchanger provided in the air supply duct of the second heat pump system and correspondingly adjusting the operating states of the first heat pump system and / or the second heat pump system according to the coil temperature in different operating modes, the mutual influence during the operation of the two heat pump systems is reduced, avoiding the technical problem of easy occurrence of failures during the operation of the fresh air equipment in the prior art, and improving the use stability of the fresh air fan.

[0088] Refer to Figure 5 , Figure 5 which is the flowchart of the second embodiment of the operating control method of a fresh air equipment according to the present invention.

[0089] Based on the above first embodiment, in this embodiment, the step S20 includes:

[0090] Step S201: When the current operating mode is the heating mode and the coil temperature is within the first temperature range, reduce the operating frequency of the first compressor and / or the operating frequency of the second compressor.

[0091] It can be understood that in this embodiment, since there may be multiple indoor heat exchangers in the heat pump system. In this embodiment, the first indoor heat exchanger generally refers to the indoor heat exchanger close to the fresh air inlet, and the second indoor heat exchanger generally refers to the indoor heat exchanger that is farther from the fresh air inlet than the first indoor heat exchanger and does not belong to the same heat pump system. For example: Figure 3 In [reference], the second fresh air heat exchanger 14 can be used as the first indoor heat exchanger, and the third fresh air heat exchanger 22 can be used as the second indoor heat exchanger.

[0092] The first temperature range refers to the temperature range where the coil temperature is greater than the first temperature. Correspondingly, when the coil temperature is greater than the first temperature, reduce the operating frequency of the first compressor and / or the second compressor according to the preset synchronous frequency reduction coefficient until the operating frequency of the first compressor is less than the minimum frequency or the coil temperature is less than the second temperature, and the second temperature is less than the first temperature.

[0093] It should be noted that during the heating operation, when it is detected that the condensation temperature of the second indoor heat exchanger is higher than the first temperature t2_1, the compressors of the first heat pump system and the second heat pump system are synchronously frequency-reduced. Since the 1-level system also has frequency reduction, reducing the air temperature passing through the second indoor heat exchanger can effectively reduce the high-pressure of the second indoor heat exchanger, thereby reducing the possibility of high-pressure shutdown of the second heat pump system.

[0094] Among them, the preset synchronous frequency reduction coefficient can be set to 10%, that is, each time the operating frequencies of the first compressor and the second compressor are reduced, the operating frequency of the first compressor can be reduced to 90% of the current frequency, and the operating frequency of the second compressor can be reduced to 90% of the current operating frequency. This embodiment does not make specific limitations on this.

[0095] In the specific implementation, considering to ensure the normal operation of the fresh air unit, when frequency-reducing, the frequency of the compressor cannot be reduced to its minimum operating frequency to avoid the fresh air unit not meeting the user's usage requirements.

[0096] Further, after reducing the operating frequency of the first compressor and / or the operating frequency of the second compressor, the operation control method of the fresh air device further includes:

[0097] If the current coil temperature of the indoor heat exchanger provided in the air supply duct of the second heat pump system is still within the first temperature range after the operating frequency of the first compressor is reduced to the minimum operating frequency, then control the first heat pump system to stop operating:

[0098] When the temperature of the coil is greater than the rated condensation temperature and the operating frequency of the first heat pump system has not been reduced to the minimum frequency, control the first heat pump system to shut down. The rated condensation temperature is greater than the first temperature, and control the second heat pump system to maintain its current operating state or reduce the operating frequency of the second compressor according to a preset synchronous frequency reduction coefficient until the temperature of the coil is less than the third temperature.

[0099] In a specific implementation, if the condensation temperature of the two-stage heat exchanger is higher than the rated condensation temperature t2_m (t2_m > t2_1, and the rated condensation temperature can be understood as the highest condensation temperature that the first heat pump system can withstand), but the compressor frequency of the first heat pump system has not dropped to the lower limit frequency fm_1, the first heat pump system can be directly shut down at this time to avoid excessive load on the second heat pump system and damage to the compressor. At this time, the second heat pump system can maintain its current state or operate at a reduced frequency. This embodiment does not make specific restrictions on this.

[0100] It can be understood that if after a period of frequency reduction, the temperature of the coil of the second indoor heat exchanger is still higher than the second temperature, the second temperature is less than the first temperature, and at this time the operating frequency of the first compressor of the first heat pump system has been reduced to the minimum frequency, it means that there is still a situation of excessive load on the second heat pump system at this time. To avoid damaging the fresh air unit, the first heat pump system can be controlled to shut down, and heating can be achieved only through the second heat pump system.

[0101] Further, after controlling the first heat pump system to shut down, the operation control method of the fresh air device further includes:

[0102] If the current coil temperature is less than the preset temperature, control the first heat pump system to start heating operation.

[0103] If after the first heat pump system shuts down, the current coil temperature is less than the preset temperature, it means that the heating capacity of the fresh air device is insufficient at this time, and the first heat pump system needs to be restarted to start heating to increase the heating output of the fresh air device.

[0104] Further, adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes:

[0105] When the current operating mode is the heating mode and the coil temperature is in the second temperature range, limit the maximum operating frequency of the first compressor to be less than or equal to the current operating frequency of the first compressor, and control the second compressor to maintain its current operating frequency;

[0106] Among them, the maximum temperature of the second temperature range is less than the minimum temperature of the first temperature range.

[0107] If the fresh air equipment is in the heating mode, both the first heat pump system and the second heat pump system operate in the heating mode. At this time, if the coil temperature is within a relatively low temperature range, to ensure the normal operation of the fresh air equipment and avoid high-pressure protection of the first heat pump system, the maximum operating frequency of the first compressor is restricted to be less than or equal to the current operating frequency of the first compressor, reducing the heating output of the first heat pump system and the impact of high temperature and high pressure. At the same time, the second compressor is controlled to maintain the current operating frequency to ensure the normal heating output of the fresh air equipment.

[0108] Furthermore, the operation control method of the fresh air equipment further includes:

[0109] Count the current number of shutdowns of the first heat pump system;

[0110] Adjust the first temperature according to the current number of shutdowns and the preset temperature adjustment value.

[0111] In specific implementation, when the shutdown of the first heat pump system is triggered each time, the first temperature t2_1 of the second indoor heat exchanger will decrease by 2 - 3°C. For example, when the first shutdown occurs, if the initially set first temperature is 30°C, then when the first heat pump system restarts, the first temperature corresponding to the second indoor heat exchanger is 28°C. When the second shutdown occurs, if the initially set first temperature is 30°C, then when the first heat pump system restarts, the first temperature corresponding to the second indoor heat exchanger is 26°C, and so on, achieving the effect of triggering frequency reduction of the first heat pump system and the second heat pump system earlier next time and reducing the probability of subsequent shutdowns.

[0112] Furthermore, the operation control method of the fresh air equipment further includes:

[0113] Determine the target shutdown duration of the first heat pump system according to the current number of shutdowns;

[0114] When the current number of shutdowns is greater than the preset number, control the first heat pump system to shutdown within the target shutdown duration.

[0115] It should be noted that the more shutdowns there are, the greater the load of the second heat pump system. At this time, to ensure the normal operation of the fresh air blower without damage, the shutdown duration of the first heat pump system can be extended according to the current number of shutdowns of the first heat pump system. Simply put, in a non-power-off control process, the greater the number of shutdowns of the first heat pump system, the longer the subsequent shutdown duration for each time, and the more frequent the shutdowns indicate that at this working condition, even at the lowest frequency of turning on the two systems for heating, the high pressure is still too high, and only one system is needed to meet the heating demand.

[0116] Among them, for each additional current shutdown time, the target shutdown duration of the first heat pump system can be increased by 1 min, and this embodiment does not make specific limitations on this.

[0117] Further, the operation control method of the fresh air device further includes:

[0118] At intervals of the target shutdown duration, obtain the outdoor ambient temperature of the area where the fresh air device is located;

[0119] When the outdoor ambient temperature is lower than the fourth temperature or the coil temperature is lower than the third temperature, restart the first heat pump system.

[0120] After a certain time t0, detect the temperature of the heat exchanger of the secondary system. If the coil temperature of the second indoor heat exchanger is higher than the third temperature t2_3, it means that the load of the second heat pump system is still large at this time, and the first heat pump system continues to remain in the shutdown state; if the coil temperature of the second indoor heat exchanger is lower than the third temperature t2_3, the operation of the first heat pump system can be restored.

[0121] In addition, if the outdoor temperature is low, heat exchange can be carried out even if the coil temperature of the second indoor heat exchanger is high at this time. For example, when the outdoor temperature is 0°C, after heat exchange through the first indoor heat exchanger of the first heat pump system, the temperature of the air in the air supply duct will not be too high. For example, it rises to 10°C. At this time, even through the second indoor heat exchanger with a high temperature, there is still a lot of heat exchange, which can greatly reduce the pressure of the second indoor heat exchanger, and the situation of high-pressure protection will not occur.

[0122] In this embodiment, when the fresh air fan operates in the heating mode, the operating frequency of the first compressor is obtained, and when the coil temperature is greater than the preset first temperature, the first compressor and the second compressor are synchronously frequency-reduced to reduce the load of the second heat pump system. When the coil temperature is less than or equal to the first temperature, greater than the second temperature, and the operating frequency of the first compressor is reduced to the lowest frequency, the first heat pump system is controlled to shut down, improving the heat interaction between the second heat pump system and the outside, thereby reducing the high-pressure of the second indoor heat exchanger and avoiding the situation of damage to the fresh air fan.

[0123] Reference Figure 6 , Figure 6 is a schematic flowchart of the third embodiment of an operation control method for a fresh air device according to the present invention.

[0124] Based on the above second embodiment, in this embodiment, the step S20 further includes:

[0125] Step S201`: When the current operating mode is the refrigeration mode and the coil temperature is within the third temperature range, reduce the operating frequency of the first compressor and / or the operating frequency of the second compressor.

[0126] It should be noted that during refrigeration operation, the outdoor high-temperature fresh air is first cooled by the first indoor heat exchanger and then further cooled by the second indoor heat exchanger. The air temperature passing through the second indoor heat exchanger is low, which reduces the evaporation degree of the second indoor heat exchanger, and the pressure on the low-pressure side of the system will be on the low side, easily triggering low-temperature frequency reduction and shutdown, but the low-pressure side pressure cannot be effectively reduced.

[0127] The third temperature range refers to the temperature range less than the second temperature. Correspondingly, when the coil temperature is less than the fifth temperature, reduce the operating frequencies of the first compressor and the second compressor according to a preset synchronous frequency reduction coefficient until the operating frequency of the first compressor is less than the minimum frequency or the coil temperature is greater than the sixth temperature, and the sixth temperature is greater than the fifth temperature.

[0128] It should be noted that during refrigeration operation, when it is detected that the condensation temperature of the second indoor heat exchanger is higher than the fifth temperature t2_5, the compressors of the first heat pump system and the second heat pump system are synchronously frequency-reduced. Since the first heat pump system also has frequency reduction, increasing the air temperature passing through the second indoor heat exchanger can effectively reduce the low-pressure of the second indoor heat exchanger, thereby reducing the possibility of high-pressure shutdown of the second heat pump system.

[0129] Among them, the preset synchronous frequency reduction coefficient can be set to 10%. That is, each time the operating frequencies of the first compressor and the second compressor are reduced, the operating frequency of the first compressor can be reduced to 90% of the current frequency, and the operating frequency of the second compressor can be reduced to 90% of the current operating frequency. This embodiment does not make specific restrictions on this.

[0130] In specific implementation, considering to ensure the normal operation of the fresh air device, when frequency-reducing, the frequency of the compressor cannot be reduced to its minimum operating frequency to avoid the fresh air device not meeting the user's usage requirements.

[0131] Furthermore, the operation control method of the fresh air device further includes:

[0132] When the coil temperature is less than the minimum condensation temperature and the operating frequency of the first heat pump system has not been reduced to the minimum frequency, control the first heat pump system to stop operating, the rated condensation temperature is less than the fifth temperature, and control the second heat pump system to maintain the current operating state or reduce the operating frequency of the second compressor according to a preset synchronous frequency reduction coefficient until the coil temperature is greater than the sixth temperature.

[0133] In a specific implementation, if the condensation temperature of the second indoor heat exchanger is lower than the lowest condensation temperature t2_m (t2_m > t2_5, and the lowest condensation temperature can be understood as the lowest condensation temperature that the first heat pump system can withstand), but the compressor frequency of the first heat pump system has not dropped to the lower limit frequency fm_1, the first heat pump system can be directly shut down at this time to avoid excessive load on the second heat pump system and damage to the compressor. At this time, the second heat pump system can maintain the current state of operation or operate at a reduced frequency, and this embodiment does not make specific restrictions on this.

[0134] In addition, when the coil temperature is greater than or equal to the fifth temperature, less than the sixth temperature, and the operating frequency of the first compressor is reduced to the lowest frequency, the first heat pump system is controlled to stop until the coil temperature is greater than the seventh temperature, and the seventh temperature is greater than the sixth temperature.

[0135] It can be understood that if after a period of synchronous frequency reduction, the coil temperature of the second indoor heat exchanger is still lower than the sixth temperature, and at this time the operating frequency of the first compressor of the first heat pump system has been reduced to the lowest frequency, it means that there is still a situation of excessive load on the second heat pump system at this time. To avoid damaging the fresh air unit, the first heat pump system can be controlled to stop, and refrigeration can be achieved only through the second heat pump system.

[0136] Furthermore, the operation control method of the fresh air device further includes:

[0137] Count the current number of shutdowns of the first heat pump system;

[0138] Adjust the fifth temperature according to the current number of shutdowns and the preset temperature adjustment value.

[0139] In a specific implementation, when the first heat pump system is shut down each time, the set fifth temperature t2_5 of the second indoor heat exchanger will increase by 2 - 3 °C. For example: when shutting down for the first time, if the initially set fifth temperature is 15 °C, then when the first heat pump system restarts, the corresponding fifth temperature of the second indoor heat exchanger is 17 °C; when shutting down for the second time, if the initially set fifth temperature is 15 °C, then when the first heat pump system restarts, the corresponding fifth temperature of the second indoor heat exchanger is 19 °C, and so on, achieving the effect of triggering frequency reduction earlier for the first heat pump system and the second heat pump system next time, and reducing the probability of shutdown again.

[0140] Furthermore, the operation control method of the fresh air device further includes:

[0141] Determine the target shutdown duration of the first heat pump system according to the current number of shutdowns;

[0142] When the current number of shutdowns is greater than the preset number, control the first heat pump system to stop within the target shutdown duration.

[0143] It should be noted that the more the number of shutdowns, the greater the load on the second heat pump system. At this time, in order to ensure the normal operation of the fresh air unit without damage, the shutdown duration of the first heat pump system can be extended according to the current number of shutdowns of the first heat pump system. Simply put, in a power-on control process, the greater the number of shutdowns of the first heat pump system, the longer the shutdown duration for each subsequent shutdown, and the more frequent the shutdowns, indicating that in this operating condition, even at the lowest frequency of heating with both systems, the low pressure is still too low, and only one system is required to meet the heating demand.

[0144] Among them, for each increase in the current number of shutdowns, the target shutdown duration of the first heat pump system can be increased by 1 minute, and this embodiment does not make specific limitations on this.

[0145] Furthermore, the operation control method of the fresh air device further includes:

[0146] At intervals of the target shutdown duration, obtain the outdoor ambient temperature of the area where the fresh air device is located;

[0147] When the outdoor ambient temperature is greater than the eighth temperature or the coil temperature is greater than the sixth temperature, restart the first heat pump system.

[0148] After a certain time t0, detect the temperature of the heat exchanger of the second-level system. If the coil temperature of the second indoor heat exchanger is lower than the sixth temperature t2_3, it means that the load of the second heat pump system is still large at this time, and the first heat pump system continues to maintain the shutdown state; if the coil temperature of the second indoor heat exchanger is higher than the sixth temperature t2_3, the operation of the first heat pump system can be restored.

[0149] In addition, if the outdoor temperature is relatively high, even if the coil temperature of the second indoor heat exchanger is relatively low at this time, heat exchange can still be carried out. For example, when the outdoor temperature is 30°C, after heat exchange through the first indoor heat exchanger of the first heat pump system, the air temperature in the air supply duct will not be too low. For example, it is cooled to 20°C. At this time, even through the second indoor heat exchanger with a relatively low temperature, there is still a lot of heat exchange, which can greatly reduce the pressure of the second indoor heat exchanger, and the situation of low pressure protection will not occur.

[0150] In this embodiment, when the fresh air unit operates in the heating mode, the operating frequency of the first compressor is obtained, and when the coil temperature is lower than the preset fifth temperature, the first compressor and the second compressor are synchronously frequency-reduced to reduce the load of the second heat pump system. When the coil temperature is greater than or equal to the fifth temperature, less than the sixth temperature, and the operating frequency of the first compressor is reduced to the lowest frequency, the first heat pump system is controlled to shut down, improving the heat interaction between the second heat pump system and the outside, thereby reducing the low pressure of the second indoor heat exchanger and avoiding the situation of damage to the fresh air unit.

[0151] In addition, an embodiment of the present invention further provides a storage medium, on which a running control program of a fresh air device is stored. When the running control program of the fresh air device is executed by a processor, the steps of the running control method of the fresh air device as described above are implemented.

[0152] Since this storage medium adopts all the technical solutions of the above-mentioned all embodiments, it has at least all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, and will not be elaborated one by one here.

[0153] Refer to Figure 7 , Figure 7 which is a structural block diagram of the first embodiment of the running control device of the fresh air device of the present invention.

[0154] As Figure 7 shown, the running control device of the fresh air device proposed by the embodiment of the present invention includes:

[0155] An acquisition module 10, configured to acquire the current running mode of the fresh air device and the coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system.

[0156] An adjustment module 20, configured to adjust the running states of the first heat pump system and / or the second heat pump system according to the current running mode and the coil temperature.

[0157] In one embodiment, the acquisition module 10 is further configured to acquire the heat exchanger temperatures of all the indoor heat exchangers disposed in the air supply duct of the second heat pump system; and determine the coil temperature according to the maximum or minimum value of the heat exchanger temperatures.

[0158] In one embodiment, the acquisition module 10 is further configured to, if all the indoor heat exchangers disposed in the air supply duct of the second heat pump system are second indoor heat exchangers, the heat exchanger temperature of the second indoor heat exchanger is the coil temperature; if all the indoor heat exchangers disposed in the air supply duct of the second heat pump system are second indoor heat exchangers and third indoor heat exchangers, the maximum or minimum value of the heat exchanger temperatures of the second indoor heat exchanger and the third indoor heat exchanger is the coil temperature.

[0159] In one embodiment, the adjustment module 20 is further configured to, when the current running mode is a heating mode and the coil temperature is within a first temperature range, reduce the running frequency of the first compressor and / or the running frequency of the second compressor; wherein, when the current running mode is a heating mode, both the first heat pump system and the second heat pump system operate in a heating mode.

[0160] In one embodiment, the adjustment module 20 is further configured to control the first heat pump system to shut down if the current coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system is still within the first temperature range after the operating frequency of the first compressor is reduced to the minimum operating frequency.

[0161] In one embodiment, the adjustment module 20 is further configured to control the first heat pump system to start heating operation if the current coil temperature is less than a preset temperature.

[0162] In one embodiment, the adjustment module 20 is further configured to count the current shutdown times of the first heat pump system; and adjust the first temperature range according to the current shutdown times and a preset temperature adjustment value.

[0163] In one embodiment, the adjustment module 20 is further configured to determine a target shutdown duration of the first heat pump system according to the current shutdown times; and control the first heat pump system to shut down within the target shutdown duration when the current shutdown times are greater than a preset number of times.

[0164] In one embodiment, the adjustment module 20 is further configured to obtain the outdoor ambient temperature of the area where the fresh air device is located at intervals of the target shutdown duration; and

[0165] restart the first heat pump system when the outdoor ambient temperature is less than a fourth temperature or the coil temperature is less than a third temperature.

[0166] In one embodiment, the adjustment module 20 is further configured to limit the maximum operating frequency of the first compressor to be less than or equal to the current operating frequency of the first compressor and control the second compressor to maintain the current operating frequency when the current operating mode is the heating mode and the coil temperature is within the second temperature range; wherein, the maximum temperature of the second temperature range is less than the minimum temperature of the first temperature range.

[0167] In one embodiment, the adjustment module 20 is further configured to reduce the operating frequency of the first compressor and / or the operating frequency of the second compressor when the current operating mode is the cooling mode and the coil temperature is within the third temperature range; wherein, when the current operating mode is the cooling mode, both the first heat pump system and the second heat pump system operate in the cooling mode.

[0168] In this embodiment, the coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system is obtained, and the operating states of the first heat pump system and / or the second heat pump system are correspondingly adjusted according to the coil temperature in different operating modes, so as to reduce the mutual influence during the operation of the two heat pump systems, avoid the technical problem of easy failure during the operation of the fresh air equipment in the prior art, and improve the use stability of the fresh air machine.

[0169] It should be understood that although the steps in the flowcharts in the embodiments of the present application are sequentially shown according to the indication of the arrows, these steps do not necessarily execute in the order indicated by the arrows. Unless there is a clear description in this article, the execution of these steps has no strict order limit, and they can be executed in other orders. Moreover, at least a part of the steps in the figure may include multiple sub-steps or multiple stages. These sub-steps or stages do not necessarily execute at the same moment, but can execute at different moments, and their execution order is not necessarily sequential, but can be executed alternately or alternately with at least a part of other steps or sub-steps or stages of other steps.

[0170] It should be understood that the above is only for illustration and does not constitute any limitation to the technical solution of the present invention. In specific applications, those skilled in the art can set according to needs, and the present invention does not limit this.

[0171] It should be noted that the above-described work process is only illustrative and does not limit the protection scope of the present invention. In actual applications, those skilled in the art can select some or all of them according to actual needs to achieve the purpose of the solution of this embodiment, and there is no limitation here.

[0172] In addition, for the technical details not described in detail in this embodiment, reference can be made to the operation control method of the fresh air equipment provided in any embodiment of the present invention, which will not be elaborated here.

[0173] In addition, it should be noted that in this article, the term "comprising", "including" or any other variant thereof is intended to cover a non-exclusive inclusion, so that a process, method, article or system including a series of elements not only includes those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, method, article or system. Without more limitations, the element defined by the statement "including one..." does not exclude the existence of another identical element in the process, method, article or system including the element.

[0174] The serial numbers of the above embodiments of the present invention are only for description and do not represent the advantages and disadvantages of the embodiments.

[0175] Through the description of the above embodiments, those skilled in the art can clearly understand that the above-described example methods can be implemented by means of software plus a necessary general hardware platform. Of course, they can also be implemented by hardware, but in many cases the former is a better implementation. Based on such an understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art can be embodied in the form of a software product. This computer software product is stored in a storage medium (such as a read-only memory (ROM) / RAM, magnetic disk, optical disk), and includes several instructions for causing a terminal device (which can be a mobile phone, computer, server, or network device, etc.) to execute the methods described in various embodiments of the present invention.

[0176] The above are only the preferred embodiments of the present invention, and do not limit the patent scope of the present invention accordingly. Any equivalent structure or equivalent process transformation made by using the content of the specification and drawings of the present invention, or directly or indirectly applied in other related technical fields, shall be equally included in the patent protection scope of the present invention.

Claims

1. A method for controlling the operation of a fresh air device, characterized in that, the method for controlling the operation of the fresh air device is applied to the fresh air device, the fresh air device includes a first heat pump system and a second heat pump system, the first heat pump system includes a first indoor heat exchanger, the second heat pump system includes a second indoor heat exchanger, both the first indoor heat exchanger and the second indoor heat exchanger are arranged in the air supply duct, and the distance between the first indoor heat exchanger and the fresh air inlet of the air supply duct is less than the distance between the second indoor heat exchanger and the fresh air inlet of the air supply duct; the method for controlling the operation of the fresh air device includes: obtaining the current operation mode of the fresh air device and the coil temperature of the indoor heat exchanger arranged in the air supply duct in the second heat pump system; and adjusting the operation states of the first heat pump system and / or the second heat pump system according to the current operation mode and the coil temperature.

2. The method for controlling the operation of the fresh air device according to claim 1, characterized in that, the obtaining the coil temperature of the indoor heat exchanger arranged in the air supply duct in the second heat pump system includes: obtaining the heat exchanger temperatures of all the indoor heat exchangers arranged in the air supply duct in the second heat pump system; determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures.

3. The method for controlling the operation of the fresh air device according to claim 2, characterized in that, the determining the coil temperature according to the maximum or minimum value of the heat exchanger temperatures includes: if all the indoor heat exchangers arranged in the air supply duct in the second heat pump system are the second indoor heat exchanger, then the heat exchanger temperature of the second indoor heat exchanger is the coil temperature; if all the indoor heat exchangers arranged in the air supply duct in the second heat pump system are the second indoor heat exchanger and the third indoor heat exchanger, then the maximum or minimum value of the heat exchanger temperature of the second indoor heat exchanger and the heat exchanger temperature of the third indoor heat exchanger is the coil temperature.

4. The method for controlling the operation of the fresh air device according to any one of claims 1-3, characterized in that, the first heat pump system includes a first compressor, and the second heat pump system includes a second compressor; the adjusting the operation states of the first heat pump system and / or the second heat pump system according to the current operation mode and the coil temperature includes: when the current operation mode is the heating mode and the coil temperature is in the first temperature range, reducing the operation frequency of the first compressor and / or the operation frequency of the second compressor; wherein, when the current operation mode is the heating mode, both the first heat pump system and the second heat pump system operate in the heating mode.

5. The method for controlling the operation of the fresh air device according to claim 4, characterized in that, after reducing the operation frequency of the first compressor and / or the operation frequency of the second compressor, the method for controlling the operation of the fresh air device further includes: If the operating frequency of the first compressor is reduced to the minimum operating frequency and the current coil temperature of the indoor heat exchanger disposed in the air supply duct of the second heat pump system is still within the first temperature range, control the first heat pump system to shut down.

6. The operation control method of the fresh air device according to claim 5, wherein, after controlling the first heat pump system to shut down, the operation control method of the fresh air device further includes: If the current coil temperature is less than the preset temperature, control the first heat pump system to start heating operation.

7. The operation control method of the fresh air device according to claim 6, wherein, the operation control method of the fresh air device further includes: Count the current shutdown times of the first heat pump system; and Adjust the first temperature range according to the current shutdown times and the preset temperature adjustment value.

8. The operation control method of the fresh air device according to claim 7, wherein, the operation control method of the fresh air device further includes: Determine the target shutdown duration of the first heat pump system according to the current shutdown times; and When the current shutdown times are greater than the preset times, control the first heat pump system to shut down within the target shutdown duration.

9. The operation control method of the fresh air device according to claim 8, wherein, the operation control method of the fresh air device further includes: At intervals of the target shutdown duration, obtain the outdoor ambient temperature of the area where the fresh air device is located; and When the outdoor ambient temperature is less than the fourth temperature or the coil temperature is less than the third temperature, restart the first heat pump system.

10. The operation control method of the fresh air device according to any one of claims 1-3, wherein, the first heat pump system includes a first compressor, and the second heat pump system includes a second compressor; The adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes: When the current operating mode is the heating mode and the coil temperature is within the second temperature range, limit the maximum operating frequency of the first compressor to be less than or equal to the current operating frequency of the first compressor, and control the second compressor to maintain the current operating frequency; wherein, the maximum temperature of the second temperature range is less than the minimum temperature of the first temperature range.

11. The operation control method of the fresh air device according to claim 1, wherein, The adjusting the operating states of the first heat pump system and / or the second heat pump system according to the current operating mode and the coil temperature includes: When the current operating mode is the cooling mode and the coil temperature is within the third temperature range, reduce the operating frequency of the first compressor and / or the operating frequency of the second compressor; wherein, when the current operating mode is the cooling mode, both the first heat pump system and the second heat pump system operate in the cooling mode.

12. An operation control device for a fresh air device, wherein, the operation control device for the fresh air device includes: An acquisition module, configured to acquire the current operation mode of the fresh air device and the coil temperature of the indoor heat exchanger disposed in the air supply duct in the second heat pump system; and An adjustment module, configured to adjust the operation states of the first heat pump system and / or the second heat pump system according to the current operation mode and the coil temperature.

13. A fresh air device characterized in that the fresh air device includes a memory, a processor, and an operation control program of the fresh air device stored on the memory and executable on the processor, and the operation control program of the fresh air device is configured to implement the operation control method of the fresh air device according to any one of claims 1 to 11.

14. A storage medium characterized in that the storage medium stores an operation control program of the fresh air device, and when the operation control program of the fresh air device is executed by a processor, it implements the operation control method of the fresh air device according to any one of claims 1 to 11.

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