Multi-split air conditioner

Abstract

This application designs and provides a multi-split air conditioner, including: a refrigerant heat dissipation path, with the inlet located between the subcooler and the outdoor throttling element, and the refrigerant entering the heat dissipation module via a refrigerant regulating element; the heat dissipation module includes: a microchannel unit, comprising multiple parallel and nested microchannel pipes; and a control module configured to: calculate the target evaporation temperature and the drive module temperature for the current control cycle; obtain a gain opening coefficient based on the transient deviation and the rate of change of the transient deviation of the current evaporation temperature; calculate the heat load control deviation of the current drive module temperature based on the target drive module temperature; calculate the reference opening of the refrigerant regulating element for the current control cycle based on the heat load control deviation; calculate the dynamic gain opening based on the target opening and the gain opening coefficient of the refrigerant regulating element for the previous control cycle; and calculate the target opening of the refrigerant regulating element for the current control cycle based on the reference opening and the dynamic gain opening. This application is applicable to harsh operating conditions.

Description

Technical Field

[0001] This invention relates to the field of air conditioning equipment technology, and in particular to a multi-split air conditioner. Background Technology

[0002] Multi-split air conditioners achieve cooling or heating by connecting different types and numbers of indoor units. Existing multi-split air conditioners typically employ an inverter design, where the drive module that powers the compressor and fan motor generates significant heat. To prevent the electrical components from malfunctioning due to high temperatures, effective heat dissipation for the drive module is essential.

[0003] Currently, common heat dissipation methods include air cooling, heat pipe cooling, and refrigerant cooling.

[0004] Air cooling typically involves installing heat sinks on the back of the electrical control box to increase the heat conduction area, allowing heat exchange between the air and the heat sinks. However, under harsh operating conditions, the cooling effect will significantly decrease. Refrigerant cooling mainly uses two methods. The first is to divert refrigerant from the main liquid line before the subcooler to cool the electrical control box, but this method is relatively ineffective under high-temperature cooling conditions, potentially limiting the normal operation of the entire unit. The second method is to divert refrigerant from the main liquid line after the subcooler to cool the electrical control box, but this method is easily affected by the subcooler. Under high-temperature and high-humidity conditions, condensation is prone to occur on the surface of the electrical control box, posing a risk of damage to electrical components.

[0005] Furthermore, in scenarios involving long piping and low loads, or in high-temperature hot water production, the aforementioned two types of refrigerants are prone to reduced heat dissipation due to the small volume of refrigerant circulating in the internal system, potentially triggering high-temperature alarms. This is especially true during cooling operations with long piping, low loads, and extremely high ambient temperatures (above 60 degrees Celsius). During startup, the refrigerant in the outdoor heat exchanger is in a two-phase state with a small circulating volume, causing a rapid increase in heat generation in the drive circuit, which can prevent the compressor from starting or operating normally.

[0006] The information disclosed in this background section is only intended to enhance the understanding of the background technology of this application, and therefore may include prior art that is not known to those skilled in the art. Summary of the Invention

[0007] This application designs and provides a multi-split air conditioner, including: a refrigerant heat dissipation path, the inlet of which is located between the subcooler and the outdoor throttling element, and includes: a refrigerant regulating element, through which the refrigerant enters the heat dissipation module;

[0008] In some embodiments of this application, the heat dissipation module includes: a microchannel unit, which includes multiple microchannel pipes arranged in parallel and nested arrangement;

[0009] In some embodiments of this application, the multi-split air conditioner further includes: a control module configured to: calculate the target evaporation temperature and the target drive module temperature for the current control cycle based on real-time environmental state parameters; calculate the transient deviation of the current evaporation temperature of the heat dissipation module based on the target evaporation temperature; obtain the gain opening coefficient based on the transient deviation and the rate of change of the transient deviation; calculate the heat load control deviation of the current drive module temperature based on the target drive module temperature; calculate the reference opening of the refrigerant regulating element for the current control cycle based on the heat load control deviation; calculate the dynamic gain opening based on the target opening and the gain opening coefficient of the refrigerant regulating element for the previous control cycle; and calculate the target opening of the refrigerant regulating element for the current control cycle based on the reference opening and the dynamic gain opening.

[0010] The above technical solution has the following advantages or beneficial effects: This application maps the target evaporation temperature and the target drive module temperature of the current control cycle through real-time environmental state parameters, thereby separating heat absorption and heat generation as two dimensions; then, it further calculates the reference opening degree of the refrigerant regulating element based on the target drive module temperature, and calculates the dynamic gain opening degree of the refrigerant regulating element based on the target evaporation temperature. In the transient stage when the heat generation of the drive module suddenly increases, a rapid response can be achieved, while in the steady-state condition, the risk of condensation and system pressure oscillation can be suppressed.

[0011] In some embodiments of this application, the control module is configured to perform the following steps to calculate the target evaporation temperature for the current control cycle based on real-time environmental state parameters: obtaining the current internal dew point temperature; obtaining a preset physical safety temperature margin; generating a first constraint target temperature based on the current internal dew point temperature and the preset safety temperature margin; obtaining the current drive module temperature; obtaining a preset design convective heat transfer temperature difference; generating a second constraint target temperature based on the current drive module temperature and the design convective heat transfer temperature difference; and selecting the larger of the first constraint target temperature and the second constraint target temperature as the target evaporation temperature of the refrigerant in the heat dissipation module for the current control cycle.

[0012] The above technical solution has the following advantages or beneficial effects: In this application, if the first constraint target temperature is higher than the second constraint target temperature within a certain control cycle, the control module uses the first constraint target temperature as the target evaporation temperature and automatically raises the target evaporation temperature from the execution perspective to ensure electrical safety. Conversely, if the second constraint target temperature is higher than the first constraint target temperature within a certain control cycle, it indicates that the environment is relatively dry. Using the second constraint target temperature as the target evaporation temperature fully releases the heat exchange potential of the refrigerant under low refrigerant pressure and fully utilizes the heat dissipation capacity of the heat dissipation module.

[0013] In some embodiments of this application, the control module is configured to perform the following steps to calculate the target drive module temperature for the current control cycle based on real-time environmental state parameters: obtaining the current internal dew point temperature; obtaining a preset physical safety temperature margin; obtaining a preset comprehensive heat transfer margin; generating an adaptive evaporation temperature based on the current internal dew point temperature, physical safety temperature margin, and comprehensive heat transfer margin; obtaining a preset lower efficiency limit temperature; obtaining a preset upper safety limit temperature; selecting the larger of the adaptive evaporation temperature and the lower efficiency limit temperature as the efficiency target temperature; and selecting the smaller of the efficiency target temperature and the upper safety limit temperature as the target drive module temperature for the current control cycle.

[0014] The above technical solution has the following advantages or beneficial effects: Through the above control process, under normal or relatively dry operating conditions, the temperature of the target drive module within the corresponding control cycle will be automatically anchored at the lower efficiency limit temperature (e.g., When humidity is high, the target evaporation temperature will rise, and correspondingly, the control module will automatically raise the target drive module temperature to maintain the target drive module temperature. to The temperature fluctuations within the range are smooth, allowing the heat dissipation module to operate normally with a normal temperature difference, maintaining a balance between heat dissipation efficiency and anti-condensation safety boundaries.

[0015] In some embodiments of this application, the control module is configured to: acquire the current drive module temperature; calculate the temperature difference between the target drive module temperature and the current drive module temperature as the heat load control deviation; and, based on the heat load control deviation, call a preset PID negative feedback model to calculate the reference opening degree of the refrigerant regulating element in the current control cycle.

[0016] The above technical solution has the following advantages or beneficial effects: This application can avoid the problem of alternating hot and cold temperatures on the surface of the heat dissipation module caused by vibration, resulting in a transient temperature lower than the dew point temperature, which leads to the failure of the anti-condensation mechanism.

[0017] In some embodiments of this application, the control module is configured to: perform a two-dimensional search in a preset two-dimensional nonlinear correction matrix based on the transient deviation and the rate of change of the transient deviation to obtain the corresponding gain opening coefficient; and use the product of the target opening of the refrigerant regulating element in the previous control cycle and the gain opening coefficient as the dynamic gain opening.

[0018] The above technical solution has the following advantages or beneficial effects: the dynamic gain opening can add a response quantity on the basis of traditional PID control, ensuring a balance between heat dissipation and anti-condensation.

[0019] In some embodiments of this application, the heat dissipation module includes: a fluid inlet, through which refrigerant flowing through the refrigerant regulating element enters the heat dissipation module and is distributed into multiple microchannels; a fluid outlet, located on the same side as the fluid inlet, through which the refrigerant in the multiple microchannels converges and flows out; and multiple parallel microchannels arranged in multiple layers from the inside to the outside with the geometric axis of the heat dissipation module as the center.

[0020] The above technical solution has the following advantages or beneficial effects: This application enables the microchannels to be nested outward with the geometric axis as the center, so that heat is symmetrically conducted on the plane, avoiding uneven surface temperature.

[0021] In some embodiments of this application, the microchannel pipeline includes: a forward pipe section, which is fluidly connected to a fluid inlet and extends away from the fluid inlet in a direction parallel to the geometric axis; a diversion pipe section, which is fluidly connected to the forward pipe section to change the refrigerant flow direction of the forward pipe section; and a return pipe section, which is fluidly connected to the diversion pipe section and extends towards the fluid outlet in a direction parallel to the geometric axis; the forward and return pipe sections of multiple microchannel pipelines are arranged alternately, and in any two adjacent microchannel pipelines, one is the forward pipe section and the other is the return pipe section.

[0022] The above technical solution has the following advantages or beneficial effects: through multiple parallel microchannel pipes, the refrigerant of the heat dissipation module enters and exits on the same side, and the outgoing pipe section and the return pipe section are intertwined. Through the heat transfer between the outgoing pipe section and the return pipe section, the heat load gradient is avoided, thereby making the surface temperature of the heat dissipation module highly uniform.

[0023] In some embodiments of this application, the design length of the microchannel pipeline is calculated based on the effective heat exchange area of ​​the microchannel pipeline, the design inner diameter of the microchannel pipeline, and the design wall thickness of the microchannel pipeline.

[0024] The above technical solution has the following advantages or beneficial effects: This application combines the design inner diameter that determines the refrigerant flow rate and the contact surface, the design pipe wall thickness that determines the heat transfer rate, and the design effective heat exchange area. Through the mutual constraints between the parameters, a reasonable microchannel pipeline design length is obtained, which reduces the friction resistance and optimizes the energy consumption of the multi-split system while meeting the heat load requirements of the heat dissipation module.

[0025] In some embodiments of this application, the effective heat exchange area of ​​the microchannel pipeline is calculated based on the transient heat generation threshold of the drive module, the heat transfer coefficient, the design drive module temperature, and the design evaporation temperature.

[0026] The above technical solution has the following advantages or beneficial effects: This application is designed based on extreme working conditions, introduces a transient heat generation threshold for the drive module design, and combines it with the inherent heat transfer coefficient of the structure, so that the heat dissipation module can cope with the most severe heat generation scenarios of the drive module, while still retaining a reasonable safety margin, thereby providing a stable hardware foundation for the subsequent control process.

[0027] In some embodiments of this application, the transient heat generation threshold of the drive module is calculated based on the upper limit operating frequency of the compressor, a first correction coefficient, and a second correction coefficient. The first correction coefficient is obtained based on the real-time operating current of the compressor and the ambient temperature, and the second correction coefficient is obtained based on the reference heat generation.

[0028] The above technical solution has the following advantages or beneficial effects: When measuring extreme operating conditions, based on the upper limit operating frequency of the compressor, a first correction factor that can evaluate the actual load of the compressor and the external heat load is further introduced, and a second correction factor that can evaluate the physical benchmark is also introduced, so that the final structural design of the heat dissipation module can fully cope with the harsh operating conditions, while avoiding hardware waste caused by blindly setting the safety factor.

[0029] Other features and advantages of the present invention will become clearer after reading the detailed embodiments of the invention in conjunction with the accompanying drawings. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0031] Figure 1 This is a schematic diagram of the refrigerant circulation system of a multi-split air conditioner provided in some embodiments of the present invention;

[0032] Figure 2 This is a schematic diagram of the refrigerant heat dissipation path in a multi-split air conditioner provided in some embodiments of the present invention;

[0033] Figure 3 This is a schematic diagram of the refrigerant circulation system of a multi-split air conditioner provided in some embodiments of the present invention;

[0034] Figure 4 This is a schematic diagram of the microchannel unit in a multi-split air conditioner provided in some embodiments of the present invention;

[0035] Figure 5 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0036] Figure 6 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0037] Figure 7 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0038] Figure 8 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0039] Figure 9 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0040] Figure 10 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0041] Figure 11 Examples of two-dimensional nonlinear correction matrices provided in some embodiments of the present invention;

[0042] In the picture:

[0043] 1. Compressor; 2. First protection element; 3. Oil separator; 4. Check valve; 5. First pressure sensor; 6. Evaporator temperature sensor; 7. Switching valve; 8. Outdoor throttling element; 9. Subcooler; 10. Subcooling throttling element; 11. Refrigerant regulating element; 12. Second pressure sensor; 13. Gas-liquid separator; 14. Heat dissipation module; 16. Outdoor heat exchanger; 17. Outdoor fan; 18. Liquid pipe; 19. Gas pipe; 20. High-pressure pipe; 30. Control module;

[0044] 141. Microchannel unit; 142. Fluid inlet; 143. Fluid outlet; 144. Outbound pipe section; 145. Diverting pipe section; 146. Return pipe section. Detailed Implementation

[0045] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0046] From a thermodynamic perspective, the refrigerant circulation system of a multi-split air conditioner includes an evaporator, compressor, condenser, and throttling device connected in sequence. The refrigerant circulation system involves a series of processes, including compression, condensation, expansion, and evaporation, to cool and heat the indoor space.

[0047] Specifically, the low-temperature, low-pressure refrigerant enters the compressor, which compresses it into a high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0048] The throttling device causes the high-temperature, high-pressure liquid refrigerant condensed in the condenser to expand into a low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant in the throttling device and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves its cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled.

[0049] Figure 1 This is a schematic diagram of a portion of the refrigerant circulation system of a multi-split air conditioner provided in some embodiments of this application.

[0050] In the refrigerant circulation system, compressor 1 is the core component. Compressor 1 is used to compress the refrigerant, changing it from a low-pressure state to a high-pressure state, enabling the refrigerant to effectively transfer heat within the refrigerant circulation system. The discharge side of compressor 1 is equipped with a first protection element 2, a first pressure sensor 5, and a one-way valve 4. The first protection element 2 detects the pressure on the discharge side of compressor 1 and automatically cuts off the circuit of compressor 1 when the pressure exceeds a safety threshold, preventing damage due to overpressure. The first pressure sensor 5 monitors the pressure of the high-pressure gaseous refrigerant discharged by compressor 1 in real time, providing pressure feedback for the control of the multi-split air conditioner. The one-way valve 4 ensures that the high-pressure gaseous refrigerant flows only unidirectionally to the condenser, preventing refrigerant or lubricating oil from flowing back to compressor 1 when the system stops. The suction side of compressor 1 is equipped with a second pressure sensor 12, which monitors the suction side pressure in real time and provides pressure feedback for the control of the multi-split air conditioner. Compressor 1 is driven by a drive module.

[0051] like Figure 1 As shown, the outdoor unit of a multi-split air conditioner refers to the part of the refrigerant circulation system that includes compressor 1.

[0052] An oil separator 3 is also installed in the outdoor unit.

[0053] Oil separator 3 separates lubricating oil droplets carried by the refrigerant from the exhaust of compressor 1, causing them to collect and flow back to compressor 1 in a directional manner. This prevents the lubricating oil from migrating with the refrigerant to other parts of the refrigerant circulation system, ensuring that compressor 1 has a sufficient amount of lubricating oil. Oil separator 3 can achieve separation using principles such as gravity settling, inertial separation, and / or centrifugal separation. A one-way valve 4 is installed downstream of oil separator 3 to guide the flow of refrigerant.

[0054] The outdoor unit also includes an outdoor heat exchanger 16. An outdoor fan 17 is located near the outdoor heat exchanger 16. The outdoor fan 17 is used to achieve forced convection heat transfer, improving the heat exchange efficiency of the outdoor heat exchanger 16. The outdoor fan 17 can be an axial flow fan, a cross flow fan, or other optional fan types. The outdoor fan 17 is driven by a variable frequency motor, and the air volume is adjusted according to the load.

[0055] The outdoor unit also includes a switching valve 7. The switching valve 7 is used to control the flow direction of the refrigerant to switch between heating and cooling modes. For example, in some embodiments of this application, the switching valve 7 is a four-way valve. The switching valve 7 can direct the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 to the outdoor heat exchanger 16 so that the outdoor heat exchanger 16 operates in condensing mode; or, the outdoor heat exchanger 16 can be connected to the suction side of the compressor 1 so that the outdoor heat exchanger 16 operates in evaporating mode.

[0056] The outdoor unit is also equipped with an outdoor throttling element 8. The outdoor throttling element 8 is correspondingly installed with the outdoor heat exchanger 16, and the two are fluidly connected.

[0057] In this application, "fluid connection" refers to the existence of a path that allows fluid to flow from one end to the other, including indirect fluid connections between the two via intermediate structures such as pipes or valves. In this application, "fluid connection" adopts a uniform definition and will not be described separately.

[0058] The outdoor throttling element 8 is used to guide the flow of refrigerant and reduce its pressure and expand it when needed. In some embodiments of this application, the outdoor throttling element 8 is an electronic expansion valve with an adjustable opening to control the flow and pressure of the refrigerant. The outdoor throttling element 8 adjusts its opening by the number of steps of its internal motor. The number of steps refers to the fixed angle the motor rotates each time it runs, and the opening refers to the size of the passage opened by the outdoor throttling element 8.

[0059] The outdoor unit is also equipped with an overcooler 9.

[0060] Through the subcooling throttling element 10, the subcooling pipe section of the subcooler 9 further throttles part of the high-pressure subcooled liquid refrigerant, making its temperature even lower. Then, through heat exchange, the subcooling degree of the refrigerant is increased, thereby improving the energy efficiency ratio of the air conditioning system.

[0061] The outdoor unit is also equipped with a gas-liquid separator 13.

[0062] The gas-liquid separator 13 is installed on the suction side of the compressor 1. The gas-liquid separator 13 separates the liquid droplets carried by the gaseous refrigerant from the gaseous refrigerant by utilizing the difference in physical properties between the gas and liquid phases, thereby preventing liquid slugging and improving lubricating oil backflow.

[0063] The outdoor unit is fluidly connected to various indoor units via high-pressure pipe 20, gas pipe 19, and liquid pipe 18. A high-pressure pipe shut-off valve is installed on high-pressure pipe 20, a gas pipe shut-off valve on gas pipe 19, and a liquid pipe shut-off valve on liquid pipe 18. One port of switching valve 7 is fluidly connected to the outlet of oil separator 3 via check valve 4, and the other three ports are connected to the high-pressure pipe shut-off valve, the gas pipe shut-off valve, and the inlet of gas-liquid separator 13, respectively. Subcooler 9 is a plate heat exchanger, and its main circuit is connected in series on the main liquid pipe 18 between the liquid pipe shut-off valve and the outdoor heat exchanger 16. The refrigerant flow rate in the main circuit of subcooler 9, and the throttling process of subcooler 9, are regulated by outdoor throttling element 8 and subcooling throttling element 10.

[0064] The outdoor unit provided in this application can be used with different types and quantities of indoor units, and the structure, type and quantity of the indoor units will not be described further here.

[0065] like Figure 3 As shown, the multi-split air conditioner also includes a control module 30.

[0066] The control module 30 is used to control, process data, and communicate with the multi-split air conditioner. The control module 30 adopts a modular design and can be flexibly configured according to different application scenarios and functional requirements.

[0067] The control module 30 includes a processor, which is a computing unit for performing the functions provided in this application. The processor includes one or more combinations of a central processing unit (CPU), a digital signal processor (DSP), a microcontroller unit (MCU), and an application-specific integrated circuit (ASIC).

[0068] The control module 30 includes a storage component for storing instructions, application programs, configuration parameters, and operating data required for the operation of the multi-split air conditioner. The storage component may be volatile memory and / or non-volatile memory.

[0069] The control module 30 is equipped with a variety of communication interfaces, including but not limited to those supporting serial communication, Wi-Fi, Bluetooth, Zigbee, LoRa, NB-IoT and other communication protocols.

[0070] The drive component of the control module 30 is used to manage peripheral devices and interact with the storage component, including but not limited to data reading, writing, signal conversion and event processing.

[0071] The processor, storage components, communication interface, and driver components are interconnected via a bus to form a data transmission channel.

[0072] The control module 30 can be implemented collaboratively by the outdoor unit board system and the indoor unit board system.

[0073] The control module 30 can also be implemented collaboratively by the outdoor unit board system, the indoor unit board system, the edge control module, and the cloud server.

[0074] The control module 30 can also be implemented by a mobile smart terminal that communicates with the outdoor unit board system, the indoor unit board system, the edge control module and / or the cloud server.

[0075] like Figure 3 As shown, in order to effectively dissipate heat from the drive modules that drive the compressor 1 and the outdoor fan 17 motor, the multi-split air conditioner in this application also includes a heat dissipation module 14.

[0076] The heat dissipation module 14 dissipates heat from the drive module through the refrigerant flowing inside it, and the heat dissipation module 14 is fluidly connected in the refrigerant heat dissipation path.

[0077] The drive module is fixedly mounted on the heat dissipation module 14 and is in contact with the heat dissipation module 14. The heat generated by the drive module is carried away by the refrigerant flowing inside the heat dissipation module 14.

[0078] In some embodiments of this application, the heat dissipation module 14 may be a refrigerant heat sink.

[0079] The inlet of the refrigerant heat dissipation path is located between the subcooler 9 and the outdoor throttling element 8, and is led out from the liquid pipe 18. The refrigerant heat dissipation path includes a refrigerant regulating element 11. The refrigerant in the refrigerant heat dissipation path enters the heat dissipation module 14 through the refrigerant regulating element 11, and the refrigerant flowing out of the heat dissipation module 14 merges into the low-pressure return gas pipeline connecting the switching valve 7 and the gas-liquid separator 13.

[0080] In some embodiments of this application, the refrigerant regulating element 11 is an electronic expansion valve.

[0081] In some embodiments of this application, the multi-split air conditioner includes a sensing module.

[0082] In some embodiments of this application, the sensing module includes an ambient temperature sensor and a drive module temperature sensor.

[0083] An ambient temperature sensor is used to detect the outdoor ambient temperature. .

[0084] In some embodiments of this application, the ambient temperature sensor collects the outdoor ambient temperature. The data is fed back to the control module. The control module can use algorithms such as first-order filtering to smooth the original sampled values, eliminating high-frequency noise and obtaining a stable temperature scalar. The smoothed outdoor ambient temperature can be denoted as... ,use This avoids random fluctuations caused by external factors such as outdoor wind and sunlight, ensuring the stability of the algorithm's data foundation. In the following text, outdoor ambient temperature... It can be the original outdoor ambient temperature. However, the outdoor ambient temperature after smoothing is preferred. .

[0085] The drive module temperature sensor is used to detect the current temperature of the drive module. .

[0086] In some embodiments of this application, the drive module temperature sensor converts the internal junction temperature or surface temperature of the drive module into an electrical signal and feeds it back to the control module in real time. The control module processes, cleans, and obtains the current drive module temperature according to a predetermined algorithm. The current drive module temperature is denoted as... .

[0087] In some embodiments of this application, the sensing module is further configured to acquire the current compressor operating frequency. The compressor operating frequency reflects the current output level of the refrigerant circulation system and can be used to further assess the current heat load level.

[0088] In some embodiments of this application, the sensing module further includes a humidity sensor.

[0089] The humidity sensor is used to detect the current relative humidity (RH) at the location of the drive module (e.g., inside the electrical control box).

[0090] In some embodiments of this application, the sensing module further includes an evaporation temperature sensor 6, which is used to detect the refrigerant temperature at the outlet side of the heat dissipation module and to obtain the actual evaporation reference temperature of the refrigerant inside the heat dissipation module. .

[0091] Under extremely high heat load conditions, the surface temperature of the drive module is very prone to unevenness, resulting in excessive heat concentration in some areas. To avoid this problem, this application further designs the internal structure of the heat dissipation module.

[0092] In some embodiments of this application, the heat dissipation module includes a microchannel unit 141. The microchannel unit 141 includes multiple microchannels arranged in parallel and nested arrangement.

[0093] In some embodiments of this application, the heat dissipation module includes a fluid inlet 142 and a fluid outlet 143. Refrigerant flowing through the refrigerant regulating element enters the heat dissipation module from the fluid inlet 142 and is distributed into multiple microchannels. The fluid outlet 143 is located on the same side as the fluid inlet 142. The refrigerant in the multiple microchannels converges and flows out from the fluid outlet 143. The multiple parallel microchannels are arranged in multiple layers from the inside out, centered on the geometric axis of the heat dissipation module.

[0094] In some embodiments of this application, the heat dissipation module has an overall rectangular design. For example... Figure 4 As shown, the fluid inlet 142 is located at the edge of the heat dissipation module's channel, i.e., the first side of the heat dissipation module. Refrigerant flowing through the refrigerant regulating element enters the heat dissipation module through the fluid inlet 142. The fluid outlet 143 is also located on the first side of the heat dissipation module, and refrigerant in the heat dissipation module flows out through the fluid outlet 143. The geometric axis extends longitudinally, i.e., perpendicular to the edge of the first side. Multiple parallel microchannels are arranged in multiple layers from the inside out along the geometric axis of the heat dissipation module, centered on it. The refrigerant at the fluid inlet 142 is diverted into the multiple parallel microchannels, and the refrigerant in the multiple parallel microchannels converges at the fluid outlet 143.

[0095] As shown in the figure, the microchannel piping includes a forward section 144, a diversion section 145, and a return section 146. The forward section 144 is fluidly connected to the fluid inlet 142 and extends away from the fluid inlet 142 in a direction parallel to the geometric axis. The diversion section 145 is fluidly connected to the forward section 144 to change the refrigerant flow direction of the forward section 144. The return section 146 is fluidly connected to the diversion section 145 and extends towards the fluid outlet 143 in a direction parallel to the geometric axis. The forward sections 144 and return sections 146 of multiple microchannel piping are arranged alternately; in any two adjacent microchannel piping, one is the forward section 144 and the other is the return section 146.

[0096] As shown in the figure, the outgoing pipe section 144 is fluidly connected to the fluid inlet 142 and extends towards the second side of the heat dissipation module in a direction parallel to the geometric axis; the turning pipe section 145 can be a 180-degree bend; the return pipe section 146 is fluidly connected to the turning pipe section 145 and extends towards the first side of the heat dissipation module in a direction parallel to the geometric axis; the outgoing pipe sections 144 and return pipe sections 146 of multiple microchannel pipelines are arranged alternately, that is, in any two adjacent microchannel pipelines, one is the outgoing pipe section 144 and the other is the return pipe section 146. Through multiple parallel microchannel pipelines, the refrigerant of the heat dissipation module enters and exits on the same side, and the outgoing pipe section 144 and return pipe section 146 are staggered. Through heat transfer between the outgoing pipe section 144 and return pipe section 146, a heat load gradient is avoided, thereby making the surface temperature of the heat dissipation module highly uniform.

[0097] In some embodiments of this application, the design inner diameter of the microchannel tubing is denoted as... The inner diameter of the microchannel pipeline is designed to meet the following requirements: .

[0098] In some embodiments of this application, the design spacing between the centers of adjacent outgoing pipe sections and the centers of adjacent return pipe sections satisfies: ;in, The design spacing between the centers of adjacent outgoing and return pipe sections. The design wall thickness for microchannel pipelines.

[0099] In some embodiments of this application, the design length of the microchannel pipeline is calculated based on the effective heat exchange area of ​​the microchannel pipeline, the design inner diameter of the microchannel pipeline, and the design wall thickness of the microchannel pipeline.

[0100] In some embodiments of this application, the design length of the microchannel tubing satisfies:

[0101]

[0102] in, The design length of the microchannel pipeline, To optimize the heat exchange area of ​​the microchannel pipeline design, The design inner diameter of the microchannel pipeline, The design wall thickness of microchannel pipelines.

[0103] In some embodiments of this application, the design length of the microchannel pipeline is the sum of the lengths of the outgoing pipeline, the turning pipeline, and the return pipeline.

[0104] The design of microchannel pipelines effectively increases the heat exchange area. The heat generated by the drive module when it operates under extreme or near-extreme frequency conditions, and the temperature difference between the corresponding drive module and the environment (which determines the heat exchange capacity) are jointly determined.

[0105] In some embodiments of this application, the effective heat transfer area of ​​the microchannel pipeline is calculated based on the transient heat generation threshold of the drive module, the heat transfer coefficient, the design drive module temperature, and the design evaporation temperature. .

[0106] For example, the effective heat exchange area of ​​microchannel pipeline design satisfy:

[0107]

[0108] in, The transient heat generation threshold for the preset drive module can be obtained under experimental conditions based on the compressor model. Let be the heat transfer coefficient. Wherein, the heat transfer coefficient... It can be obtained through experimental testing or through numerical simulation. To design the temperature of the drive module. To design the evaporation temperature. and It can be a preset value or an observed value under simulation or experimental conditions.

[0109] In some embodiments of this application, an effective heat exchange area is designed. Correspondingly, the heat transfer coefficient The calibration composite constant for a specific experimental environment is a customized parameter obtained by performing multiple linear regression analysis on the geometric surface area, refrigerant fluid resistance characteristics, and measured temperature difference of a large number of sample heat dissipation modules within a preset working window. The dimensions have been converted to reduce the computing power requirements for microcontrollers or embedded systems to execute instructions.

[0110] In some embodiments of this application, the transient heat generation threshold of the drive module is calculated based on the upper limit operating frequency of the compressor, a first correction coefficient, and a second correction coefficient. The first correction coefficient is obtained based on the real-time operating current of the compressor and the ambient temperature, and the second correction coefficient is obtained based on the reference heat generation.

[0111] In some embodiments of this application, the drive module is designed with a transient heat generation threshold. It can be obtained through the following formula:

[0112]

[0113] in, This is the upper limit of the compressor's operating frequency. The first correction factor is... This is the second correction factor.

[0114] In some embodiments of this application, the upper limit operating frequency of the compressor may be the highest frequency allowed to operate under the current operating conditions, or it may be the target operating frequency under the current operating conditions.

[0115] In some embodiments of this application, the first correction coefficient This can be obtained based on the compressor's operating current and the ambient temperature. More specifically, the first correction factor A two-dimensional search can be performed within a two-dimensional matrix based on the compressor's operating current and ambient temperature. The two-dimensional matrix can be obtained through testing in an experimental environment and stored in advance for later retrieval. First correction coefficient. It can also be used to convert the dimensions between frequency and heat generation.

[0116] In some embodiments of this application, the second correction coefficient The heat output can be obtained by testing and mapping when the drive module is in a low-frequency standby state, and used as a reference heat output.

[0117] In some embodiments of this application, the number of microchannels in the heat dissipation module satisfies the following:

[0118]

[0119] in, The width of the heat dissipation module in the direction centered on the geometric axis. A safety margin is reserved between the heat dissipation module and the edge;

[0120] In some embodiments of this application, the total heat exchange area of ​​the outgoing, turning, and returning pipe sections of multiple microchannel pipelines is not less than the designed effective heat exchange area of ​​the microchannel pipeline. The sum of .

[0121] Assume that the microchannel tubing is numbered from the inside out, based on the geometric axis:

[0122] ( ).

[0123] Microchannel tubing The length can be expressed as: ;in, This refers to the length of the outgoing or returning pipe segment. When the drive module adopts a rectangular design, it is preferable to design that the outgoing and returning pipe segments in all microchannel pipelines have the same length, i.e., satisfying:

[0124]

[0125] Let be the radius of the turning section in the microchannel pipeline. Due to the close arrangement of microchannel pipelines, the radius of the turning section satisfies:

[0126]

[0127] in, The radius of the innermost turning pipe section.

[0128] In some embodiments of this application, to meet the requirements of engineering practice, the lengths of the outgoing and returning pipe sections can be summed as the length of a single microchannel pipeline, thereby further matching it with the design length of the microchannel pipeline (e.g., the deviation is within a certain range). within).

[0129] In some embodiments of this application, the control module is configured to perform, as Figure 5 The steps shown are to calculate the target opening degree of the refrigerant regulating element for the current controller cycle.

[0130] Step S101: Calculate the target evaporation temperature and target drive module temperature for the current control cycle based on real-time environmental status parameters.

[0131] Step S102: Calculate the transient deviation of the current evaporation temperature of the heat dissipation module based on the target evaporation temperature, and obtain the gain opening coefficient based on the transient deviation and the rate of change of the transient deviation.

[0132] Step S103: Calculate the thermal load control deviation of the current drive module temperature based on the target drive module temperature.

[0133] Step S104: Calculate the reference opening degree of the refrigerant regulating element for the current control cycle based on the heat load control deviation.

[0134] Step S105: Calculate the dynamic gain opening based on the target opening degree and gain opening degree coefficient of the refrigerant regulating element in the previous control cycle.

[0135] Step S106: Calculate the target opening of the refrigerant regulating element for the current control cycle based on the baseline opening and the dynamic gain opening.

[0136] This application maps the target evaporation temperature and target drive module temperature of the current control cycle to real-time environmental state parameters, thereby separating heat absorption and heat generation as two dimensions. Then, it further calculates the reference opening degree of the refrigerant regulating element based on the target drive module temperature and the dynamic gain opening degree of the refrigerant regulating element based on the target evaporation temperature. In the transient stage when the heat generation of the drive module suddenly increases, it can achieve rapid response, while in the steady-state condition, it can suppress the risk of condensation and system pressure oscillation.

[0137] In some embodiments of this application, real-time environmental state parameters include the current internal dew point temperature. .

[0138] Specifically, the control module pre-stores the air state equation or dew point calculation formula. .

[0139] The control module is configured to perform, such as Figure 6 The following steps are shown:

[0140] Step S201: Obtain the current relative humidity and current ambient temperature .

[0141] Step S202: Set the current relative humidity and current ambient temperature Substitute into the air state equation or dew point calculation formula Calculate the current internal dew point temperature corresponding to the point where the air inside the electrical control box where the current drive module is located reaches saturation. .

[0142] Current internal dew point temperature This indicates the critical temperature threshold at which condensation begins to form on the surface of the heat dissipation module under the current environment.

[0143] In some embodiments of this application, the control module is configured to perform, as Figure 7 The following steps are shown:

[0144] Step S301: Obtain the current internal dew point temperature .

[0145] Step S302: Obtain the preset physical safety temperature difference margin .

[0146] In some embodiments of this application, physical safety temperature difference margin satisfy .

[0147] Step S303: Generate the first constraint target temperature based on the current internal dew point temperature and the preset safety temperature margin.

[0148] In some embodiments of this application, the current internal dew point temperature is superimposed. and physical safety temperature difference margin To generate the first constraint target temperature.

[0149] In some embodiments of this application, the first constraint target temperature can be expressed as .

[0150] Step S304: Obtain the current temperature of the drive module .

[0151] Step S305: Obtain the preset design convection heat transfer temperature difference .

[0152] In some embodiments of this application, a convective heat transfer temperature difference is designed. It can be set to .

[0153] Step S306: Based on the current drive module temperature and the design of convection heat transfer temperature difference The temperature difference between them generates the second constraint target temperature.

[0154] In some embodiments of this application, the second constraint target temperature can be expressed as .

[0155] Step S307: Select the larger of the first constraint target temperature and the second constraint target temperature as the target evaporation temperature of the refrigerant in the heat dissipation module in the current control cycle.

[0156] Specifically, the first constraint target temperature and the second constraint target temperature are compared, and the larger one between the two is selected as the target evaporation temperature of the heat dissipation module in the current control cycle.

[0157] That is:

[0158]

[0159] in, This is the target evaporation temperature of the heat dissipation module within the current control cycle.

[0160] In this application, if the first constraint target temperature is higher than the second constraint target temperature within a certain control cycle, the control module uses the first constraint target temperature as the target evaporation temperature and automatically raises the target evaporation temperature from an execution perspective to ensure electrical safety. Conversely, if the second constraint target temperature is higher than the first constraint target temperature within a certain control cycle, it indicates that the environment is relatively dry. Using the second constraint target temperature as the target evaporation temperature fully releases the heat exchange potential of the refrigerant under low refrigerant pressure and fully utilizes the heat dissipation capacity of the heat dissipation module.

[0161] In some embodiments of this application, the control module is configured to perform, as Figure 8 The following steps are shown:

[0162] Step S401: Obtain the current internal dew point temperature .

[0163] Step S402: Obtain the preset physical safety temperature difference margin .

[0164] In some embodiments of this application, the preset physical safety temperature difference margin satisfies .

[0165] Step S403: Obtain the preset comprehensive heat transfer margin .

[0166] In some embodiments of this application, a preset overall heat transfer margin is used. It can be set to .

[0167] Step S404: Generate an adaptive evaporation temperature based on the current internal dew point temperature, physical safety temperature difference margin, and comprehensive heat transfer margin.

[0168] In some embodiments of this application, the current internal dew point temperature is superimposed. Physical safety temperature difference margin and overall heat transfer margin To generate an adaptive evaporation temperature;

[0169] The adaptive evaporation temperature can be expressed as:

[0170]

[0171] Step S405: Obtain the preset lower efficiency limit temperature .

[0172] In some embodiments of this application, the efficiency lower limit temperature It can be set to .

[0173] Step S406: Obtain the preset safe upper limit temperature .

[0174] In some embodiments of this application, the safe upper limit temperature It can be set to .

[0175] Step S407: Select the larger of the adaptive evaporation temperature and the lower limit of efficiency temperature as the efficiency target temperature.

[0176] Specifically, the adaptive evaporation temperature and the efficiency lower limit temperature are compared, and the larger of the two is selected as the efficiency target temperature of the heat dissipation module in the current control cycle.

[0177] Step S408: Select the smaller of the efficiency target temperature and the safety upper limit temperature as the target drive module temperature for the current control cycle.

[0178] Specifically, the efficiency target temperature and the safety upper limit temperature are compared, and the smaller of the two is selected as the target drive module temperature for the current control cycle.

[0179] That is:

[0180]

[0181] in, The target drive module temperature for the current control cycle.

[0182] Through the above control process, under normal or relatively dry operating conditions, the temperature of the target drive module within the corresponding control cycle will be automatically anchored at the lower efficiency limit temperature (e.g., When humidity is high, the target evaporation temperature will rise, and correspondingly, the control module will automatically raise the target drive module temperature to maintain the target drive module temperature. to The temperature fluctuations within the range are smooth, allowing the heat dissipation module to operate normally with a normal temperature difference, maintaining a balance between heat dissipation efficiency and anti-condensation safety boundaries.

[0183] In some embodiments of this application, the control module is configured to perform, as Figure 9 The following steps are shown:

[0184] S501: Get the current drive module temperature .

[0185] S502: Calculate the temperature of the target drive module and current drive module temperature The temperature difference between them is used as the heat load control deviation.

[0186] Target drive module temperature and current drive module temperature The temperature difference between them, i.e., the heat load control deviation satisfy:

[0187]

[0188] Alternatively, it could also be:

[0189] Simply adjust the direction of the PID controller.

[0190] S503: Based on heat load control deviation The preset PID negative feedback model is invoked to calculate the reference opening degree of the refrigerant regulating element in the current control cycle.

[0191] Considering the unique design of the heat dissipation module, if it is controlled by only the ordinary PID algorithm, it is easy to cause oscillation, resulting in alternating hot and cold temperatures on the surface of the heat dissipation module, causing the transient temperature to drop below the dew point temperature, leading to the failure of the anti-condensation mechanism. To solve this problem, this application improves the traditional PID model.

[0192] Reference opening satisfy:

[0193]

[0194] In the above formula, , and These are the proportional gain, integral gain, and derivative gain.

[0195] In some embodiments of the present invention, the proportional gain operator Integral gain operator Differential gain operator .

[0196] That is, satisfying: .

[0197] S504: Calculate the dynamic gain opening based on the target opening degree and gain opening degree coefficient of the refrigerant regulating element in the previous control cycle.

[0198] Dynamic gain opening satisfies: ;in, This serves as the historical opening reference for the output of the previous adjacent control cycle. This is the gain opening factor.

[0199] S505: Calculate the target opening degree of the refrigerant regulating element in the current control cycle based on the reference opening degree and the dynamic gain opening degree.

[0200] Specifically, the target opening of the refrigerant regulating element in the current control cycle is calculated by superimposing the baseline opening and dynamic gain opening of the refrigerant regulating element in the current control cycle.

[0201] The target opening degree of the refrigerant regulating element in the current control cycle can be expressed as:

[0202]

[0203] Alternatively, the target opening degree of the refrigerant regulating element in the current control cycle can be expressed as:

[0204]

[0205] In some embodiments of this application, the control module is configured to perform, as Figure 10 The following steps are shown to calculate the dynamic gain opening factor. .

[0206] Step S601: Calculate the transient deviation.

[0207] Transient deviation Characterizing the reference temperature of actual evaporation Target evaporation temperature of the current control cycle The deviation.

[0208] In some embodiments of this application, transient deviation amount satisfy:

[0209]

[0210] Step S602: Calculate the rate of change of transient deviation.

[0211] Transient deviation rate of change It represents the change between the transient deviation in the current control cycle and the transient deviation in the previous control cycle.

[0212] Transient deviation rate of change satisfy:

[0213]

[0214] S603: Based on the transient deviation and its rate of change, a lookup table is performed in the two-dimensional nonlinear correction matrix to obtain the corresponding gain opening coefficient. .

[0215] An example of a two-dimensional nonlinear correction matrix is ​​as follows: Figure 11 As shown.

[0216] For example, when Greater than 0, which is the actual evaporation reference temperature. Above the target evaporation temperature ,and A value greater than 7 indicates the actual evaporation reference temperature. It is still accelerating its deviation from the target evaporation temperature. The control module queries the two-dimensional nonlinear correction matrix and retrieves the corresponding gain opening coefficient. The upper limit, based on the baseline opening, increases the refrigerant flow rate by a relatively large amount to quickly dissipate heat at high temperatures.

[0217] For example, when Less than 3, which is the actual evaporation reference temperature. Severely below the target evaporation temperature It is extremely close to the dew point temperature boundary, and When the value is less than or equal to -8, it indicates the actual evaporation reference temperature. The situation is worsening further; the control module queries the two-dimensional nonlinear correction matrix and retrieves the corresponding gain opening coefficient. Lower limit value, increase pressure, and ensure electrical safety against condensation.

[0218] In the description of the above embodiments, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples. The above functional forms and parameters are merely examples, and those skilled in the art can adjust them according to different models, refrigerant types, and control objectives without affecting the technical concept of achieving coordinated pressure and flow control of the present invention.

[0219] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. Multi-split air conditioners, including: The refrigerant heat dissipation path has its inlet located between the subcooler and the outdoor throttling element, and includes: a refrigerant regulating element, through which the refrigerant enters the heat dissipation module; The heat dissipation module is characterized by comprising: A microchannel unit, comprising multiple microchannels arranged in parallel and nested configurations; Also includes: The control module is configured as follows: Based on real-time environmental status parameters, calculate the target evaporation temperature and target drive module temperature for the current control cycle; Calculate the transient deviation of the current evaporation temperature of the heat dissipation module based on the target evaporation temperature, and obtain the gain opening coefficient based on the transient deviation and the rate of change of the transient deviation. The thermal load control deviation is calculated based on the target drive module temperature to determine the current drive module temperature. The reference opening degree of the refrigerant regulating element in the current control cycle is calculated based on the heat load control deviation. Calculate the dynamic gain opening based on the target opening degree and gain opening coefficient of the refrigerant regulating element in the previous control cycle; The target opening degree of the refrigerant regulating element in the current control cycle is calculated based on the baseline opening degree and the dynamic gain opening degree.

2. The multi-split air conditioner according to claim 1, characterized in that, The control module is configured to perform the following steps to calculate the target evaporation temperature for the current control cycle based on real-time environmental state parameters: Get the current internal dew point temperature; Obtain the preset physical safety temperature difference margin; The first constraint target temperature is generated based on the current internal dew point temperature and the preset safety temperature margin. Get the current temperature of the driver module; Obtain the preset design convective heat transfer temperature difference; A second constraint target temperature is generated based on the current driving module temperature and the design convection heat transfer temperature difference. The larger of the first constraint target temperature and the second constraint target temperature is selected as the target evaporation temperature of the refrigerant in the heat dissipation module during the current control cycle.

3. The multi-split air conditioner according to claim 1, characterized in that, The control module is configured to perform the following steps to calculate the target drive module temperature for the current control cycle based on real-time environmental state parameters: Get the current internal dew point temperature; Obtain the preset physical safety temperature difference margin; Obtain the preset overall heat transfer margin; An adaptive evaporation temperature is generated based on the current internal dew point temperature, physical safety temperature difference margin, and comprehensive heat transfer margin. Obtain the preset lower limit temperature for efficiency; Obtain the preset safe upper limit temperature; Choose the larger of the adaptive evaporation temperature and the lower limit of efficiency temperature as the efficiency target temperature. Choose the smaller of the efficiency target temperature and the safety upper limit temperature as the target drive module temperature for the current control cycle.

4. The multi-split air conditioner according to claim 1, characterized in that, The control module is configured as follows: Get the current temperature of the driver module; Calculate the temperature difference between the target drive module temperature and the current drive module temperature as the thermal load control deviation; Based on the heat load control deviation, a preset PID negative feedback model is invoked to calculate the reference opening degree of the refrigerant regulating element in the current control cycle.

5. The multi-split air conditioner according to claim 1, characterized in that, The control module is configured as follows: Based on the transient deviation and the rate of change of the transient deviation, a two-dimensional search is performed in the preset two-dimensional nonlinear correction matrix to obtain the corresponding gain opening coefficient; Furthermore, the product of the target opening degree and the gain opening degree coefficient of the refrigerant regulating element in the previous control cycle is used as the dynamic gain opening degree.

6. The multi-split air conditioner according to any one of claims 1 to 5, characterized in that, The heat dissipation module includes: The refrigerant flowing through the refrigerant regulating element enters the heat dissipation module through the fluid inlet and is distributed into multiple microchannel pipelines; A fluid outlet is located on the same side as the fluid inlet, from which the refrigerant in multiple microchannel pipelines converges and flows out. Multiple parallel microchannels are arranged in multiple layers from the inside out, with the geometric axis of the heat dissipation module as the center.

7. The multi-split air conditioner according to claim 6, characterized in that, The microchannel conduit includes: The outgoing pipe section is fluidly connected to the fluid inlet and extends away from the fluid inlet in a direction parallel to the geometric axis; A diverting pipe section, which is fluidly connected to the outgoing pipe section, to change the refrigerant flow direction of the outgoing pipe section; The return pipe section is fluidly connected to the diverting pipe section and extends in a direction parallel to the geometric axis toward the fluid outlet. The outbound and return segments of multiple microchannel pipelines are arranged alternately. In any two adjacent microchannel pipelines, one is the outbound segment and the other is the return segment.

8. The multi-split air conditioner according to claim 7, characterized in that, The design length of a microchannel pipeline is calculated based on its effective heat exchange area, design inner diameter, and design wall thickness.

9. The multi-split air conditioner according to claim 8, characterized in that, The effective heat exchange area of ​​the microchannel pipeline is calculated based on the transient heat generation threshold, heat transfer coefficient, design drive module temperature, and design evaporation temperature.

10. The multi-split air conditioner according to claim 9, characterized in that, The transient heat generation threshold of the drive module is calculated based on the compressor's upper limit operating frequency, a first correction coefficient, and a second correction coefficient. The first correction coefficient is obtained based on the compressor's real-time operating current and ambient temperature, while the second correction coefficient is obtained based on the reference heat generation.

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