Multi-connected air conditioner

Abstract

The application designs and provides a multi-connected air conditioner, comprising a refrigerant circulation system; the refrigerant circulation system comprises a heat dissipation module, a first refrigerant heat dissipation path and a second refrigerant heat dissipation path, an inlet of the first refrigerant heat dissipation path is arranged at a compressor exhaust side and is fluidly connected to the heat dissipation module, the first refrigerant heat dissipation path comprises a first valve element and a first adjusting element, the first valve element is switched between an open state and a closed state, and the first valve element guides refrigerant to flow into the first refrigerant heat dissipation path or cuts off the first refrigerant heat dissipation path; an inlet of the second refrigerant heat dissipation path is arranged between a supercooler and an outdoor throttling element, the second refrigerant heat dissipation path comprises a second valve element, and refrigerant enters the heat dissipation module through the second valve element; and a control module can be configured to: establish a dynamic coupling model of an environment temperature and a change trend; determine a corresponding proportional adjusting factor based on the dynamic coupling model according to a current environment temperature and the change trend; and adjust an opening degree of the second valve element by using the proportional adjusting factor. The application can realize the stability of a driving module temperature and avoid the risk of high temperature or condensation.

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 heating scenarios, the heat dissipation efficiency of both refrigerants can easily decrease due to the small volume of refrigerant circulating in the internal refrigerant system, triggering high-temperature alarms. This is especially true during refrigeration operation under long piping, low loads, and extremely high ambient temperatures. During startup, the refrigerant in the outdoor heat exchanger is in a two-phase state with a small volume of refrigerant circulating, causing a sharp 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 circulation system. The refrigerant circulation system includes a heat dissipation module, a first refrigerant heat dissipation path, and a second refrigerant heat dissipation path. The heat dissipation module dissipates heat to the drive module through refrigerant flowing inside. The inlet of the first refrigerant heat dissipation path is located on the compressor exhaust side, fluidly connected to the heat dissipation module, and includes a first valve element and a first regulating element fluidly connected. The first valve element can switch between an open state and a closed state to guide refrigerant into or cut off the first refrigerant heat dissipation path. The first regulating element is used to regulate the refrigerant pressure in the first refrigerant heat dissipation path. The inlet of the second refrigerant heat dissipation path is located between the subcooler and the outdoor throttling element, and includes a second valve element. The refrigerant enters the heat dissipation module through the second valve element. The control module can be configured to: establish a dynamic coupling model of ambient temperature and its changing trend; determine a corresponding proportional adjustment factor based on the dynamic coupling model according to the current ambient temperature and its changing trend; and adjust the opening degree of the second valve element using the proportional adjustment factor.

[0008] The above technical solution has the following advantages or beneficial effects: This application establishes a dynamic coupling model of ambient temperature and its changing trend, and uses the proportional factor adjustment of controllable valve elements to convert the heat dissipation load into a controlled refrigerant flow distribution without increasing hardware costs, thereby stabilizing the temperature of the drive module and avoiding the risk of excessive temperature or condensation.

[0009] In some embodiments of this application, the dynamic coupling model is a nonlinear control partition table.

[0010] In some embodiments of this application, the control module is configured to perform the following steps when determining the corresponding proportional adjustment factor based on a nonlinear control partition table according to the current ambient temperature and its changing trend: calculating the safe target temperature of the drive module based on the current ambient temperature and the drive module's limit tolerance temperature threshold; calculating the current calculated temperature difference between the current drive module temperature and the drive module's safe target temperature as a first load feature; calculating the changing trend of the current calculated temperature difference as a second load feature; and performing a two-dimensional search in the nonlinear control partition table based on the first load feature and the second load feature to obtain the corresponding proportional adjustment factor.

[0011] The above technical solution has the following advantages or beneficial effects: by using a nonlinear control partition table, the corresponding proportional adjustment factor can be accurately obtained based on the load characteristics of two dimensions.

[0012] In some embodiments of this application, the proportional adjustment factor is an amplification or reduction coefficient of the opening degree of the second valve element.

[0013] In some embodiments of this application, the nonlinear control partition table includes: an accelerated heat dissipation zone, a fast callback zone, a dynamic balance transition zone, and an asymmetric bias zone.

[0014] In some embodiments of this application, in the accelerated heat dissipation zone, the corresponding calculated temperature difference is positive, the calculated temperature difference change trend is positive, the proportional adjustment factor is greater than 1, and reaches or approaches a preset upper limit value.

[0015] In some embodiments of this application, in the fast callback zone, the corresponding calculated temperature difference is negative, the calculated temperature difference change trend is negative, the proportional adjustment factor is less than 1, and reaches or approaches a preset lower limit value.

[0016] In some embodiments of this application, in the dynamic equilibrium transition zone, the calculated temperature difference and the trend of the calculated temperature difference change cross the corresponding zero point: corresponding to the calculated temperature difference, the proportional adjustment factor increases with the increase of the trend of the calculated temperature difference change; corresponding to the trend of the calculated temperature difference change, the proportional adjustment factor increases with the increase of the calculated temperature difference.

[0017] In some embodiments of this application, in the asymmetric bias region, the calculated temperature difference and the calculated change trend have opposite signs, and the proportional adjustment factor fluctuates around 1.

[0018] The above technical solution has the following advantages or beneficial effects: through four different regions, the second valve element can achieve rapid expansion, rapid contraction, fine and smooth adjustment and dynamic control.

[0019] In some embodiments of this application, the second valve element is an electronic expansion valve.

[0020] In some embodiments of this application, the control module is configured to: compare the acquired first load feature with a preset temperature difference deviation range to determine the horizontal axis main column in which the first load feature falls; compare the acquired second load feature with a preset trend change range to determine the vertical axis main row in which the second load feature falls; calculate the intersection address of the horizontal axis main column and the vertical axis main row to read the corresponding current proportional adjustment factor; call the number of second valve element opening pulses output in the previous sampling period, and calculate the target value of the second valve element opening pulse in the current sampling period based on the step gain formula.

[0021] The above technical solution has the following advantages or beneficial effects: smooth flow regulation is achieved through step-by-step control.

[0022] In some embodiments of this application, the control module is configured to compare the calculated target value of the opening pulse with a preset upper limit and lower limit of the physical safety range: if the calculated target value of the opening pulse is higher than the upper limit of the physical safety range, an opening adjustment command is issued to the second valve element at the upper limit of the physical safety range; if the calculated target value of the opening pulse is lower than the lower limit of the physical safety range, an opening adjustment command is issued to the second valve element at the lower limit of the physical safety range; if the calculated target value of the opening pulse is neither higher than the upper limit of the physical safety range nor lower than the lower limit of the physical safety range, an opening adjustment command is issued to the second valve element at the target value of the opening pulse.

[0023] The above technical solution has the following advantages or beneficial effects: by clamping operation, the opening command issued to the second valve element is between the upper limit and the lower limit of the physical safety range, preventing the stepper motor from overshooting.

[0024] In some embodiments of this application, the control module is configured to: retrieve the current ambient temperature; search an ambient temperature gradient interval table, map and compare the current ambient temperature with multiple ambient temperature intervals to confirm the ambient temperature interval into which the current ambient temperature falls; determine the corresponding correction coefficient from the ambient temperature gradient interval table based on the temperature interval into which the current ambient temperature falls; the correction coefficient represents the initial heat load formed by the current external ambient temperature on the drive module; and input the correction coefficient into a preset feedforward opening calculation model to calculate the initial opening of the second valve element.

[0025] The above technical solution has the following advantages or beneficial effects: it embeds the spatial dynamic changes of the external environment into the control reference of the refrigerant flow in the subsequent composite refrigerant heat dissipation path.

[0026] In some embodiments of this application, the first valve element is a solenoid valve.

[0027] In some embodiments of this application, the control module is configured to: acquire the current ambient temperature and the current drive module temperature; calculate the flow path reconstruction determination temperature difference, wherein the flow path reconstruction determination temperature difference is the temperature difference between the current drive module temperature and the current ambient temperature; determine whether the flow path reconstruction determination temperature difference meets the preset refrigerant circulation system reconstruction conditions; if not, maintain the closed state of the first valve element; if it meets the conditions, start a timer and determine whether the duration for which the refrigerant circulation system reconstruction conditions are met reaches a first preset duration; if the first preset duration is reached, drive the first valve element to switch from the current closed state to the open state.

[0028] The above technical solution has the following advantages or beneficial effects: the refrigerant on the exhaust side is guided into the heat dissipation module through the first valve element, reconstructing the heat dissipation circuit to achieve heat balance and ensure heat dissipation effect.

[0029] In some embodiments of this application, the control module is configured to: determine whether the flow path reconstruction determination temperature difference meets the preset exit reconstruction condition; if not, maintain the open state of the first valve element; if it meets the condition, start a timer and determine whether the duration of meeting the exit reconstruction condition reaches a second preset duration; if the second preset duration is reached, drive the first valve element to switch from the current open state to the closed state.

[0030] The above technical solution has the following advantages or beneficial effects: after detecting a sufficient safety gradient, the first refrigerant heat dissipation path is cut off to avoid the risk of overheating.

[0031] In some embodiments of this application, in the cooling mode, the control module is configured to perform the following steps to perform graded control of the subcooling throttling element: acquiring the current ambient temperature and the current drive module temperature, and determining whether they meet a preset first load judgment condition or a second load judgment condition; when the preset first load judgment condition is met, controlling the target opening of the subcooling throttling element to be in the fully open operating range, so as to form a low-resistance refrigerant flow path in the subcooled pipe section; when the preset second load judgment condition is met, controlling the target opening of the subcooling throttling element to be in the throttling operating range, so as to adjust the flow rate and pressure of the refrigerant in the subcooled pipe section.

[0032] The above technical solution has the following advantages or beneficial effects: Based on the current operating mode and the preset temperature difference boundary conditions, the subcooling throttling element used to adjust the subcooling of the refrigerant in the heat dissipation module is subject to forced state switching or proportional adjustment to change the refrigerant flow loop and reduce the risk of condensation under extreme operating conditions, thus providing safety protection.

[0033] In some embodiments of this application, the control module is configured to: calculate the condensation protection judgment temperature difference, which is the difference between the current ambient temperature and the current drive module temperature; determine whether the condensation protection judgment temperature difference meets the preset anti-condensation active protection conditions; when the anti-condensation active protection conditions are met, stop dynamically calculating the target opening degree of the subcooled throttling element according to the adjustment weight factor, and control the target opening degree of the subcooled throttling element to be in the fully open working range so as to form a low-resistance refrigerant flow path in the subcooled pipe section.

[0034] The above technical solution has the following advantages or beneficial effects: the refrigerant flow rate in the subcooled pipe section can be finely adjusted by adjusting the opening of the subcooled throttling element.

[0035] 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

[0036] 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.

[0037] 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;

[0038] Figure 2 This is a schematic diagram of the composite refrigerant heat dissipation path in a multi-split air conditioner provided in some embodiments of the present invention;

[0039] Figure 3 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0040] Figure 4 Here is an example of an ambient temperature range table;

[0041] Figure 5 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0042] Figure 6 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0043] Figure 7 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0044] Figure 8 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0045] Figure 9 An example of a nonlinear control partition table;

[0046] Figure 10 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0047] Figure 11 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0048] Figure 12 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0049] Figure 13 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0050] Figure 14 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0051] Figure 15 Example of a fitted curve for calculating the adjustment weighting factor;

[0052] Figure 16 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0053] Figure 17 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0054] Figure 18 A flowchart illustrating a multi-split air conditioner provided in some embodiments of the present invention;

[0055] Figure 19 A flowchart illustrating a multi-split air conditioner provided in some embodiments of the present invention;

[0056] Figure 20 A flowchart of a multi-split air conditioner provided in some embodiments of the present invention;

[0057] In the picture:

[0058] 1. Compressor; 2. First protection element; 3. Oil separator; 4. Check valve; 5. First pressure sensor; 6. First valve element; 7. Switching valve; 8. Outdoor throttling element; 9. Subcooler; 10. Subcooling throttling element; 11. Second valve element; 12. Second pressure sensor; 13. Gas-liquid separator; 14. Heat dissipation module; 15. First regulating element; 16. Outdoor heat exchanger; 17. Outdoor fan; 18. Liquid pipe; 19. Gas pipe; 20. High-pressure pipe. Detailed Implementation

[0059] 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.

[0060] 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.

[0061] 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.

[0062] 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.

[0063] 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.

[0064] 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.

[0065] 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.

[0066] An oil separator 3 is also installed in the outdoor unit.

[0067] 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.

[0068] 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.

[0069] 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.

[0070] 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.

[0071] 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.

[0072] 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.

[0073] The outdoor unit is also equipped with an overcooler 9.

[0074] 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.

[0075] The outdoor unit is also equipped with a gas-liquid separator 13.

[0076] 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.

[0077] The outdoor unit is fluidly connected to various indoor units via a high-pressure pipe 20, a gas pipe 19, and a liquid pipe 18. A high-pressure pipe shut-off valve is installed on the high-pressure pipe 20, a gas pipe shut-off valve on the gas pipe 19, and a liquid pipe shut-off valve on the liquid pipe 18. One port of the switching valve 7 is fluidly connected to the outlet of the oil separator 3 via a one-way 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 the gas-liquid separator 13, respectively. The 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 the subcooler 9, as well as the throttling process of the subcooler 9, are regulated by the outdoor throttling element 8 and the subcooling throttling element 10.

[0078] 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.

[0079] Multi-split air conditioners also include a control module.

[0080] The control module is used for the control, data processing, and communication of the multi-split air conditioner. The control module adopts a modular design, allowing for flexible configuration according to different application scenarios and functional requirements.

[0081] The control module includes a processor, which is a computing unit for performing the functions provided in this application, including but not limited to one or a combination of the following: a central control module, a dedicated processor, a microcontroller unit, and a graphics control module.

[0082] The control module 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 can be volatile memory and / or non-volatile memory.

[0083] The control module 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.

[0084] The driver component of the control module 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.

[0085] The processor, storage components, communication interface, and driver components are interconnected via a bus to form a data transmission channel.

[0086] The control module can be implemented collaboratively by the outdoor unit board system and the indoor unit board system.

[0087] The control module can also be implemented collaboratively by the outdoor unit board system, the indoor unit board system, the edge control module, and the cloud server.

[0088] The control module 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.

[0089] like Figure 2 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 further includes a heat dissipation module 14. The heat dissipation module 14 dissipates heat from the drive modules through refrigerant flowing inside it, and the heat dissipation module 14 is fluidly connected in the first refrigerant heat dissipation path and the second refrigerant heat dissipation path.

[0090] From a principle perspective, the first refrigerant heat dissipation path is a refrigerant heat dissipation regulation loop, and the second refrigerant heat dissipation path is an evaporative refrigerant heat dissipation loop. Both the first and second refrigerant heat dissipation paths are fluidly connected to the heat dissipation module 14. The drive module is fixedly mounted on and in contact with the heat dissipation module 14, and the heat generated by the drive module is carried away by the refrigerant flowing inside the heat dissipation module 14.

[0091] In some embodiments of this application, the heat dissipation module 14 may be a refrigerant heat sink.

[0092] The inlet of the first refrigerant heat dissipation path is located on the discharge side of compressor 1, specifically downstream of check valve 4. The first refrigerant heat dissipation path includes a first valve element 6 and a first regulating element 15 connected in fluid connection, and the first valve element 6 and the first regulating element 15 are arranged in series. The first valve element 6 can switch between an open state and a closed state to guide refrigerant into the first refrigerant heat dissipation path or to cut off the first refrigerant heat dissipation path. The first regulating element 15 is used to regulate the refrigerant pressure in the first refrigerant heat dissipation path.

[0093] In some embodiments of this application, the first valve element 6 is a solenoid valve.

[0094] In some embodiments of this application, the first adjusting element 15 is a capillary.

[0095] The first refrigerant heat dissipation path extends to the inlet end of the heat dissipation module 14, and the refrigerant in the first refrigerant heat dissipation path can adjust the temperature of the heat dissipation module 14.

[0096] The inlet of the second 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 second refrigerant heat dissipation path includes a second valve element 11. The refrigerant in the second refrigerant heat dissipation path enters the heat dissipation module 14 through the second valve element 11. 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.

[0097] In some embodiments of this application, the second valve element 11 is an electronic expansion valve.

[0098] In some embodiments of this application, the multi-split air conditioner includes a sensing module.

[0099] In some embodiments of this application, the sensing module includes an ambient temperature sensor and a drive module temperature sensor.

[0100] An ambient temperature sensor is used to detect the outdoor ambient temperature. .

[0101] 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. .

[0102] The drive module temperature sensor is used to detect the real-time temperature of the drive module. .

[0103] 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 acquires the real-time temperature of the drive module according to a predetermined algorithm. The real-time temperature of the drive module is denoted as... .

[0104] Because of the design of a composite refrigerant heat dissipation path, in some embodiments of this application, the multi-split air conditioner can dynamically adjust according to different operating conditions, selecting one or more refrigerant heat dissipation paths to achieve precise control.

[0105] For example, if the outdoor ambient temperature meets the preset ultra-high temperature condition, and the multi-split air conditioner is started or operating under the preset low load condition, the control module is configured to open the first valve element on the first refrigerant heat dissipation path, guiding a portion of the refrigerant from the compressor exhaust side into the first refrigerant heat dissipation path. After being throttled, depressurized, and cooled by the first regulating element (capillary tube), it forms a medium-temperature, medium-pressure (or two-phase) refrigerant, which then enters the heat dissipation module to forcibly cool the drive module. Under such severe conditions, the refrigerant flow rate in the refrigerant circulation system is small, and the liquid pipe cannot provide sufficient subcooled refrigerant. At the same time, the compressor drive heat generation is high. After receiving a high-temperature signal from the ambient temperature sensor or the drive module temperature sensor, the control module opens the first valve element on the first refrigerant heat dissipation path. The first refrigerant heat dissipation path directly obtains refrigerant from the exhaust side, independent of the refrigerant flow distribution in the main circulation loop. This ensures that the multi-split air conditioner still has a stable heat exchange temperature difference for the drive module during startup or low-load operation, preventing the compressor from being frequency-limited or unable to operate normally due to high temperature.

[0106] For example, if the outdoor environmental parameters meet the preset high temperature and high humidity conditions, and the multi-split air conditioner is operating in cooling mode, the control module is configured to monitor the real-time temperature of the drive module and dynamically adjust the opening of the second valve element on the second refrigerant heat dissipation path, coordinating with the on / off state of the first valve element for heat dissipation. If the outdoor environment is under high temperature and high humidity conditions, and the temperature of the refrigerant used for cooling is too low, the surface of the heat dissipation module is extremely prone to reaching the air dew point temperature, resulting in condensation and damaging electrical components. Through the second refrigerant heat dissipation path, liquid refrigerant from the liquid pipe flows through the heat dissipation module, undergoes throttling and evaporation through the second valve element, absorbs heat from the drive module, and finally returns to the low-pressure return gas line. When the real-time temperature of the drive module is detected to be too low, posing a risk of condensation, the control module reduces the opening of the second valve element to increase the evaporation pressure and corresponding saturation temperature inside the heat dissipation module; or, it briefly opens the first valve element to introduce high-temperature exhaust refrigerant to mix with the refrigerant in the main liquid pipe, thereby accurately controlling the temperature of the heat dissipation module above the air dew point temperature and maintaining it within the safe operating temperature range.

[0107] The composite refrigerant heat dissipation path enables precise and safe heat dissipation of the drive module through the coordinated action of the first and second valve elements under operating conditions such as long piping, low load, high ambient temperature heating, and ultra-high ambient temperature cooling start-up. This completely avoids alarms, compressor frequency limiting operation, or damage to electrical components caused by poor heat dissipation.

[0108] In some embodiments of this application, the control module may be configured to perform, such as Figure 3 The steps shown are as follows:

[0109] S101: Establish a dynamic coupling model of ambient temperature and its changing trend.

[0110] S102: Based on the current ambient temperature and its changing trend, determine the corresponding scaling factor using a dynamic coupling model.

[0111] S103: Adjust the opening degree of the second valve element using a proportional adjustment factor.

[0112] In this application, the dynamic coupling model can respond to both ambient temperature and its changing trend simultaneously, treating one as a static indicator and the other as a dynamic indicator. By capturing the interaction between the two dimensions, it outputs a proportional adjustment factor that can correct the opening degree of the second valve element in real time.

[0113] The dynamic coupling model can be an empirical formula, such as a bivariate nonlinear function of temperature and rate of change.

[0114] The dynamic coupling model can also be a set of fuzzy control rules that take ambient temperature and its changing trend as fuzzy inputs.

[0115] This application establishes a dynamic coupling model of ambient temperature and its changing trend, and uses the proportional factor adjustment of controllable valve elements to convert the heat dissipation load into a controlled refrigerant flow distribution without increasing hardware costs, thereby stabilizing the temperature of the drive module and avoiding the risk of excessive temperature or condensation.

[0116] In some embodiments of this application, the dynamic coupling model is a preset nonlinear control partition table. The control process of the second valve element is described in detail below.

[0117] In some embodiments of this application, the control module is configured to: determine the severity level of the outdoor environment based on the outdoor ambient temperature, determine a correction coefficient based on the determined severity level, and generate the initial opening degree of the second valve element based on the correction coefficient.

[0118] Specifically, the control module pre-stores an ambient temperature gradient range table. This table includes multiple preset outdoor environmental severity levels and corresponding ambient temperature ranges, which are divided by temperature range thresholds.

[0119] For example:

[0120] The first temperature range threshold is 50℃. If the outdoor ambient temperature... If the temperature is above 50℃, it is considered to be in the most stringent preset level;

[0121] The second temperature range threshold is 45℃, if the outdoor ambient temperature... Temperatures above 50°C but below 45°C are considered the next most stringent preset level.

[0122] Similarly, the threshold for the third temperature range is 40℃, and the threshold for the fourth temperature range is 35℃.

[0123] outdoor ambient temperature When the temperature is below 35℃, it falls within the normal operating temperature range, which is the lowest preset severity level.

[0124] An example of an ambient temperature range table is as follows: Figure 4 As shown.

[0125] The control module is configured to perform, such as Figure 5 The following steps are shown:

[0126] Step S201: Retrieve the current ambient temperature .

[0127] Step S202: Look up the ambient temperature gradient interval table and set the current ambient temperature... The current ambient temperature is confirmed by mapping and comparing it with the above-mentioned multiple ambient temperature ranges. The ambient temperature range in which it falls.

[0128] Step S203: Based on the current ambient temperature For the temperature range that falls within, determine the corresponding correction coefficient from the ambient temperature gradient range table. .

[0129] Step S204: Adjust the correction coefficients The initial opening of the second valve element is calculated by substituting it into the preset feedforward opening calculation model.

[0130] For example, the feedforward opening calculation model can be expressed as: .

[0131] In some embodiments of this application, the correction coefficient It is a dimensionless constant, which can be considered as a weighting factor used to characterize the initial thermal load on the drive module caused by the current ambient temperature. Current ambient temperature The higher the value, the higher the corresponding correction coefficient. The larger the value, the more it is used to weight and amplify the subsequent control effect. The control module will then adjust the correction coefficient. The initial opening pulse count of the second valve element is calculated by inputting it into the preset feedforward opening calculation model, so that the initial pulse count matches the predicted initial heat load. The refrigerant discharged during the initial startup of the compressor passes through the second refrigerant heat dissipation path, forming a certain degree of cold accumulation at the heat dissipation module in advance to cope with the rapid heat rise of the drive module.

[0132] After passing the initial startup phase and entering steady-state operation, the control module generates the opening degree of the second valve element by monitoring the deviation between the real-time temperature of the drive module and the dynamic target temperature.

[0133] In some embodiments of this application, the control module is configured to perform the following when determining the corresponding proportional adjustment factor based on a nonlinear control partition table according to the current ambient temperature and its changing trend: Figure 6 The following steps are shown:

[0134] Step S301: Calculate the safe target temperature of the drive module based on the current ambient temperature and the extreme tolerance temperature threshold of the drive module.

[0135] Step S302: Calculate the current calculated temperature difference between the current drive module temperature and the drive module safety target temperature as the first load characteristic.

[0136] Step S303: Calculate the current calculated temperature difference change trend as the second load characteristic.

[0137] Step S304: Based on the first load characteristics and the second load characteristics, perform a two-dimensional search in the nonlinear control partition table to obtain the corresponding proportional adjustment factor.

[0138] In some embodiments of this application, the control module is configured to perform, as Figure 7 The steps shown are to calculate the current ideal thermal equilibrium point based on dynamic external environmental conditions.

[0139] Step S401: Within the preset sampling period, acquire the current ambient temperature. .

[0140] Step S402: Call the limit tolerance temperature threshold of the drive module and the preset correction deviation to calculate the safe target temperature of the drive module.

[0141] Drive module safety target temperature It can be represented as: ;

[0142] in, This refers to the maximum tolerable temperature threshold of the drive module. This is a preset correction deviation, used to reserve a safety margin beyond physical limits. It can be based on the current ambient temperature The constant that is set.

[0143] Step S403: Determine whether the calculated target temperature of the drive module meets the preset boundary conditions.

[0144] Step S404: If the calculated safe target temperature of the drive module meets the preset boundary conditions, then the calculated safe target temperature of the drive module shall be used as the upper limit of the current target temperature.

[0145] Specifically, if the drive module's target temperature is safe If the temperature is higher than the sum of the current ambient temperature and the preset benchmark deviation, it is determined that the calculated safe target temperature of the drive module meets the preset boundary conditions, and the calculated safe target temperature of the drive module is further taken as the upper limit of the current target temperature.

[0146] That is, taking a preset reference deviation of 10℃ as an example, if the following conditions are met: If the preset boundary conditions are met, the calculated safe target temperature of the drive module is taken as the upper limit of the current target temperature.

[0147] Even when the preset boundary conditions are not met, the current target temperature upper limit is still clamped at the benchmark represented by the preset boundary conditions, and the spatial dynamic changes of the external environment are embedded into the control benchmark of the refrigerant flow in the subsequent composite refrigerant heat dissipation path.

[0148] After obtaining the current target temperature upper limit, the control module is configured to extract the first load characteristic and the second load characteristic, specifically as follows: Figure 8 The steps shown are as follows:

[0149] S501: Obtain the current temperature of the drive module within the preset sampling period. .

[0150] S502: Based on the current drive module temperature and the safe target temperature of the drive module The current calculated temperature difference between Based on the current calculated temperature difference This is the first load characteristic.

[0151] Current calculated temperature difference It can be represented as: .

[0152] S503: Obtain the historical temperature difference deviation corresponding to the previous sampling period. .

[0153] S504: Based on the current calculated temperature difference and historical temperature deviation Calculate the current trend of temperature difference change. Based on the current calculated trend of temperature difference change This is the second load characteristic.

[0154] Current calculated temperature difference trend It can be represented as: .

[0155] S505: After obtaining the first load characteristic and the second load characteristic, using one of the first load characteristics as the first addressing pointer and the other as the second addressing pointer, perform two-dimensional cross-addressing according to the preset nonlinear control partition table to obtain the proportional adjustment factor matching the current load state. .

[0156] Proportional adjustment factor It is a dimensionless rate of change coefficient.

[0157] In some embodiments of this application, the preset nonlinear control partition table is configured as a two-dimensional input nonlinear gain mapping matrix, where the horizontal axis input is the first load characteristic, i.e., the current calculated temperature difference. The vertical axis input represents the second load characteristic, which is the current calculated trend of temperature difference change. .

[0158] An example of a preset nonlinear control partition table is as follows: Figure 9 As shown.

[0159] Organized by column, it includes 9 preset temperature difference deviation ranges, from arrive Used to accurately locate the current temperature of the drive module. Distance from the dynamic target; measured in rows, including 9 preset trend change intervals, from... Extending all the way to This is used to represent the trend of change. The value of the cross cell is the dimensionless scaling factor. Proportional adjustment factor As a factor for amplifying or reducing the opening degree of the second valve element, in some embodiments of this application, the value is limited to [value missing]. Within the nonlinear distribution range.

[0160] Specifically, this includes four non-linear control zones: an accelerated heat dissipation zone, a fast callback zone, a dynamic balance transition zone, and an asymmetric bias zone.

[0161] In the accelerated heat dissipation zone, the corresponding calculated temperature difference is positive, the calculated temperature difference trend is positive, the scaling factor is greater than 1, and it reaches or approaches the preset upper limit. If the current calculated temperature difference... And calculate the trend of temperature difference change Being in the accelerated heat dissipation zone indicates that the actual temperature of the drive module has exceeded the safe target temperature of the drive module, and the heating trend is still accelerating dramatically. The proportional adjustment factor corresponding to the heating and heat dissipation zone... The value is assigned a value greater than 1 (e.g., the area shown in red in the figure), and reaches or approaches the upper limit (e.g., 1.2). The control module adjusts the corresponding proportional factor. The opening degree of the second valve element is calculated, and the opening degree of the second valve element will expand rapidly, quickly introducing refrigerant for heat dissipation, thereby offsetting the impact of heat load by adjusting the refrigerant flow.

[0162] In the fast pullback zone, the corresponding calculated temperature difference is negative, the calculated temperature difference trend is negative, the scaling factor is less than 1, and it reaches or approaches the preset lower limit. If the current calculated temperature difference... And calculate the trend of temperature difference change Being in the fast pullback zone indicates that the actual temperature of the driver module has fallen below the safe target temperature and is still decreasing. The proportional adjustment factor corresponding to the fast pullback zone... The value assigned is less than 1 (e.g., the area shown in green in the figure), and reaches or approaches the lower limit (e.g., 0.8). The control module adjusts the corresponding proportional factor accordingly. The opening of the second valve element is calculated, and the opening of the second valve element will be rapidly reduced, thereby forcibly limiting the refrigerant flow and preventing overcooling, energy efficiency degradation, or increased condensation risk.

[0163] In the dynamic equilibrium transition region, the corresponding calculated temperature difference and its changing trend cross the corresponding zero point, for example, satisfying... and In the dynamic equilibrium transition zone, corresponding to the calculated temperature difference, the proportional adjustment factor increases with the increase of the calculated temperature difference trend; corresponding to the calculated temperature difference trend, the proportional adjustment factor increases with the increase of the calculated temperature difference. In the dynamic equilibrium transition zone, the proportional adjustment factor exhibits a monotonic change with the fluctuation of the calculated temperature difference or the calculated temperature difference trend, as shown in the area indicated by black text in the figure. This makes the action of the second valve element precise and smooth, achieving dynamic equilibrium near the safe target temperature of the drive module.

[0164] In the asymmetric bias region, the calculated temperature difference and the trend of its change have opposite signs. For example, the calculated temperature difference... It is a positive value, but the trend of temperature difference change is calculated. A negative value indicates that although the temperature deviation is large, the trend shows that the deviation is decreasing on its own, or the calculated temperature difference... It is a negative value, but it calculates the trend of temperature difference changes. A positive value indicates that although the temperature deviation is relatively small, there is a deterioration trend. The proportional adjustment factor corresponds to the asymmetric bias region. Fluctuating around 1, such as the area shown in blue in the figure, small adjustments are made tentatively to further optimize based on feedback results. On the one hand, control measures are taken in advance through the feedforward prediction mechanism, and on the other hand, overshooting of refrigerant flow is avoided.

[0165] More specifically, the control module is configured to periodically execute, such as Figure 10 The following steps are shown:

[0166] S601: The first load characteristic obtained (based on the current calculated temperature difference) (For example) Compare with the preset temperature difference deviation range to determine the horizontal axis column where the first load characteristic falls.

[0167] S602: The acquired second load characteristic (based on the current calculated temperature difference change trend) (For example) Compare with the preset trend change range to determine the main vertical axis line into which the second load feature falls.

[0168] S603: Calculate the intersection address of the horizontal axis main column and the vertical axis main row in the storage unit, and read the value corresponding to that address as the current scaling factor. .

[0169] S604: Recalls the number of opening pulses output in the previous sampling period. The target value of the opening pulse in the current sampling period is calculated based on the step gain formula.

[0170] The step gain formula can be expressed as: .

[0171] In other embodiments of this application, the control module is configured to compare the calculated target value of the opening pulse with preset upper and lower limits of the physical safety range, specifically as follows: Figure 11 The following steps are shown:

[0172] S701: Compare the calculated target value of the opening pulse with the preset upper limit and lower limit of the physical safety range.

[0173] S702: If the calculated target value of the opening pulse is higher than the upper limit of the physical safety range, a drive pulse is sent to the stepper motor of the second valve element at the upper limit of the physical safety range.

[0174] S703: If the calculated target value of the opening pulse is lower than the lower limit of the physical safety range, a drive pulse is sent to the stepper motor of the second valve element at the lower limit of the physical safety range.

[0175] S704: If the calculated target value of the opening pulse is not higher than the upper limit of the physical safety range and not lower than the lower limit of the physical safety range, then a drive pulse is sent to the stepper motor of the second valve element at the target value of the opening pulse.

[0176] By clamping, the opening command sent to the second valve element is kept between the upper and lower limits of the physical safety range, preventing the stepper motor from overshooting.

[0177] In some embodiments of this application, in addition to performing the closed-loop regulation of the second valve element as described above, the control module also performs refrigerant circuit regulation and extreme condition protection. Based on the current operating mode and preset temperature difference boundary conditions, the subcooling throttling element used to regulate the subcooling of the refrigerant in the heat dissipation module is forced to switch states or proportionally adjust, so as to change the refrigerant flow circuit and reduce the risk of condensation under extreme conditions, providing safety protection.

[0178] In some embodiments of this application, the multi-split air conditioner is in cooling mode, and the control module is configured to perform actions such as... Figure 12 The following steps are shown to perform graded control of the subcooled throttling element:

[0179] Step S801: Obtain the current ambient temperature and the current temperature of the drive module It is then determined whether the load meets the preset first load judgment condition.

[0180] Step S802: When the preset first load judgment condition is met, control the target opening of the subcooling throttling element to be in the fully open working range, forming a low-resistance refrigerant flow path.

[0181] In some embodiments of this application, if the following conditions are met And satisfy If the load condition is met, it is determined that the current drive module load is low and no significant throttling and cooling is required. The control module controls the target opening of the subcooling throttling element to be in the fully open operating range (e.g., a maximum step of 470 pls), ensuring unobstructed refrigerant flow and forming a low-resistance refrigerant flow path. This is a preset cooling reference temperature threshold. To avoid low temperatures caused by throttling and pressure reduction of the overcooling throttling element, the refrigerant maintains high flow when the preset first load judgment condition is met, preventing it from accumulating near the heat dissipation module and reducing compressor power consumption.

[0182] Or, such as Figure 13 As shown:

[0183] Step S803: Obtain the current ambient temperature and the current temperature of the drive module It is then determined whether the load meets the preset second load judgment condition.

[0184] Step S804: When the preset second load judgment condition is met, control the target opening of the subcooling throttling element to be in the throttling working range, so as to adjust the flow rate of refrigerant in the subcooling pipe section.

[0185] In some embodiments of this application, if the following conditions are met And satisfy If the load is high, it is determined that the second load judgment condition is met, indicating that the current drive module load is high. The control module controls the target opening of the subcooling throttling element to be in the throttling working range, increasing the subcooling to accelerate heat dissipation.

[0186] The control module is configured to perform, such as Figure 14 The following steps are shown:

[0187] Step S901: Calculate the current temperature of the drive module With cooling reference temperature threshold The temperature difference.

[0188] Step S902: Obtain the preset adjustment weight factor based on the temperature difference, and dynamically calculate the target opening degree of the subcooled throttling element. .

[0189] In some embodiments of this application, the target opening degree of the subcooled throttling element is dynamically calculated using the following formula.

[0190]

[0191] in, The initial opening is preset, for example, it can be 32pls. This represents the maximum opening within the fully open working range, for example, it could be 470pls. To adjust the weighting factor.

[0192] Adjustment weight factor It can be obtained based on the temperature difference. For example, the current temperature difference can be dynamically calculated using the curve shown in the figure, and the corresponding adjustment weight factor can be calculated based on the current temperature difference.

[0193] like Figure 15 The curve shown can be obtained through nonlinear fitting under experimental conditions, for example, satisfying:

[0194]

[0195] in, To adjust the weighting factor, For temperature difference .

[0196] The control module finely adjusts the refrigerant flow rate in the subcooled pipe section by precisely adjusting the opening of the subcooled throttling element.

[0197] In some embodiments of this application, the multi-split air conditioner is in heating mode, and the control module is configured to perform actions such as... Figure 16 The following steps are shown to control the subcooled throttling element:

[0198] Step S1001: Obtain the current ambient temperature and the current temperature of the drive module .

[0199] Step S1002: Calculate the current ambient temperature and the current temperature of the drive module The temperature difference used to determine condensation protection is, for example: .

[0200] Step S1003: Start timing and monitor whether the temperature difference of the condensation protection determination meets the preset forced intervention conditions.

[0201] Step S1004: When the preset forced intervention conditions are met, the target opening degree of the subcooled throttling element is controlled to be in the fully open operating range.

[0202] For example, if the following conditions are met If the duration reaches the preset time threshold, it indicates that the drive module and ambient temperature remain close for an extended period due to abnormal heat dissipation, resulting in insufficient heat dissipation. To prevent the drive module from failing under heating conditions, the control module triggers a forced intervention mechanism, causing the overcooled throttling element to enter its fully open operating range and introducing maximum refrigerant flow for heat dissipation balance.

[0203] In some embodiments of this application, the multi-split air conditioner is in cooling mode, and the control module is configured to perform actions such as... Figure 17 The following steps are shown to perform active protection control against condensation on the subcooled throttling element:

[0204] Step S1101: Obtain the current ambient temperature and the current temperature of the drive module It is then determined whether the load meets the preset second load judgment condition.

[0205] Step S1102: When the preset second load judgment condition is met, calculate the current drive module temperature. With cooling reference temperature threshold The temperature difference.

[0206] Step S1103: Obtain the preset adjustment weight factor based on the temperature difference, and dynamically calculate the target opening degree of the subcooled throttling element. .

[0207] Step S1104: Start timing and calculate the current ambient temperature. and the current temperature of the drive module The temperature difference between the two points is used to determine whether the condensation protection temperature difference meets the preset active protection conditions for condensation prevention.

[0208] Step S1105: When the preset anti-condensation active protection conditions are met, stop the dynamic calculation of the target opening of the subcooled throttling element based on the adjustment weight factor, and forcibly control the target opening of the subcooled throttling element to be in the fully open working range, forming a low-resistance refrigerant flow path.

[0209] In some embodiments of this application, if the following conditions are met If the condition is met, it is determined that the preset anti-condensation active protection conditions are met. There is an extremely high risk of secondary condensation on the surface of the current drive module. The control module immediately terminates the current proportional adjustment, forces the subcooled throttling element to fully open, changes the pressure and flow direction of the refrigerant, and avoids the risk of short circuit or corrosion of the drive module due to condensation.

[0210] In some embodiments of this application, the multi-split air conditioner is in heating mode, and the control module is configured to perform actions such as... Figure 18 The following steps are shown to provide active protection control for the subcooled throttling element under extreme operating conditions:

[0211] Step S1201: Start timing and calculate the current ambient temperature. and the current temperature of the drive module The extreme operating condition protection judgment temperature difference is monitored to determine whether the extreme operating condition protection judgment temperature difference meets the preset extreme operating condition active protection conditions.

[0212] Step S1202: When the preset extreme working condition active protection conditions are met, the locking is triggered, and the target opening of the overcooled throttling element is controlled to be in the fully closed working range.

[0213] In some embodiments of this application, if the following conditions are met If the condition is met, it is determined that the preset extreme operating condition active protection conditions are met. The control module controls the target opening of the subcooled throttling element to be in the fully closed working range, and prevents system-level failures caused by heat dissipation failure by completely cutting off the subcooled pipe section.

[0214] The following describes the control process of the first valve element. The control module is configured to execute the following... Figure 19 The following steps are shown:

[0215] Step S1301: Obtain the current ambient temperature and the current temperature of the drive module .

[0216] Step S1302: Calculate the current ambient temperature and the current temperature of the drive module The temperature difference between the reconstruction determination points, for example: .

[0217] Step S1303: Determine whether the preset refrigerant circulation system reconfiguration conditions are met.

[0218] Step S1304: If the preset refrigerant circulation system reconfiguration conditions are not met, it is determined to be in a non-start-up intervention condition, and the current closed state of the first valve element is maintained.

[0219] Step S1305: If the preset refrigerant circulation system reconfiguration conditions are met, start the timer and determine whether the time for meeting the refrigerant circulation system reconfiguration conditions has reached the preset time.

[0220] Step S1306: If the preset time is reached, drive the first valve element to switch from the current closed state to the open state.

[0221] For example, if the following conditions are met If the refrigerant circulation system reconstruction conditions are met and the condition is maintained for more than 10 minutes, the control module determines that the temperature of the drive module is very close to that of the outdoor environment, the refrigerant flow rate in the main liquid pipe is very small, the heat distribution of the refrigerant circulation system is unbalanced, and the refrigerant flow is stagnant. At this time, the refrigerant on the exhaust side is guided into the heat dissipation module through the first valve element, and the heat dissipation circuit is reconstructed to achieve heat balance and ensure heat dissipation effect.

[0222] After the first valve element opens, the control module is configured to perform actions such as... Figure 20 The following steps are shown:

[0223] Step S1401: Obtain the current ambient temperature and the current temperature of the drive module .

[0224] Step S1402: Calculate the current ambient temperature and the current temperature of the drive module The temperature difference between the reconstruction determination points, for example: .

[0225] Step S1403: Determine whether the preset exit reconstruction conditions are met.

[0226] Step S1404: If the preset exit reconfiguration conditions are not met, the first valve element remains open to maintain the bypass flow of refrigerant on the exhaust side.

[0227] Step S1405: If the preset exit reconstruction conditions are met, start the timer and determine whether the duration of the exit reconstruction conditions has reached the preset duration.

[0228] Step S1406: If the preset time is reached, drive the first valve element to switch from the current open state to the closed state.

[0229] For example, if the following conditions are met If the preset exit reconfiguration conditions are met and this condition persists for more than 5 minutes, it indicates that a sufficient safety gradient has been established between the drive module and the external environment. Continuing to introduce exhaust-side refrigerant will risk overheating. After the exit reconfiguration conditions are met, the control module outputs a command to the first valve element, switching it to the closed state. The first refrigerant heat dissipation path is cut off, and the control module re-performs the current ambient temperature... and the current temperature of the drive module Polling.

[0230] When the compressor stops, the opening degree of the second valve element is 0.

[0231] 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.

[0232] 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: A refrigerant circulation system, characterized in that it comprises: The heat dissipation module cools the drive module through a refrigerant flowing inside it. The first refrigerant heat dissipation path has its inlet located on the compressor exhaust side, and is fluidly connected to the heat dissipation module. It also includes a first valve element and a first regulating element that are fluidly connected. The first valve element can switch between an open state and a closed state to guide refrigerant into the first refrigerant heat dissipation path or to cut off the first refrigerant heat dissipation path. The first regulating element is used to regulate the refrigerant pressure in the first refrigerant heat dissipation path. The second refrigerant heat dissipation path has its inlet located between the subcooler and the outdoor throttling element, and includes a second valve element through which the refrigerant enters the heat dissipation module. The control module can be configured as follows: Establish a dynamic coupling model between ambient temperature and its changing trend; Based on the current ambient temperature and its changing trend, the corresponding proportional adjustment factor is determined using a dynamic coupling model. The opening degree of the second valve element is adjusted using a proportional adjustment factor.

2. The multi-split air conditioner according to claim 1, characterized in that: The dynamic coupling model is a nonlinear control partition table; The control module is configured to perform the following steps when determining the corresponding proportional adjustment factor based on a nonlinear control partition table according to the current ambient temperature and its changing trend: Calculate the safe target temperature of the drive module based on the current ambient temperature and the extreme tolerance temperature threshold of the drive module; The calculated temperature difference between the current drive module temperature and the drive module's safe target temperature is used as the first load characteristic. The current calculated temperature difference trend is used as the second load characteristic; Based on the first load characteristics and the second load characteristics, a two-dimensional search is performed in the nonlinear control partition table to obtain the corresponding proportional adjustment factor.

3. The multi-split air conditioner according to claim 2, characterized in that: The proportional adjustment factor is the amplification or reduction coefficient of the opening degree of the second valve element; The nonlinear control partition table includes: an accelerated heat dissipation zone, a fast callback zone, a dynamic balance transition zone, and an asymmetric bias zone. In the accelerated heat dissipation zone, the corresponding calculated temperature difference is positive, the calculated temperature difference change trend is positive, the proportional adjustment factor is greater than 1, and reaches or approaches the preset upper limit value. In the fast callback zone, the corresponding calculated temperature difference is negative, the calculated temperature difference change trend is negative, the proportional adjustment factor is less than 1, and reaches or approaches the preset lower limit value. In the dynamic equilibrium transition zone, the calculated temperature difference and the trend of the calculated temperature difference change cross the corresponding zero point: corresponding to the calculated temperature difference, the proportional adjustment factor increases with the increase of the trend of the calculated temperature difference change; corresponding to the trend of the calculated temperature difference change, the proportional adjustment factor increases with the increase of the calculated temperature difference. In the asymmetric bias region, the calculated temperature difference and the calculated change trend have opposite signs, and the proportional adjustment factor fluctuates around 1.

4. The multi-split air conditioner according to claim 2, characterized in that: The second valve element is an electronic expansion valve; The control module is configured as follows: The first load characteristic is compared with the preset temperature difference deviation range to determine the main column of the horizontal axis where the first load characteristic falls. The acquired second load feature is compared with the preset trend change range to determine the main vertical axis row in which the second load feature falls. Calculate the intersection address of the main column on the horizontal axis and the main row on the vertical axis to read the corresponding current scaling factor; The number of second valve element opening pulses output from the previous sampling period is used to calculate the target value of the second valve element opening pulse in the current sampling period based on the step gain formula.

5. The multi-split air conditioner according to claim 4, characterized in that: The control module is configured to compare the calculated target value of the opening pulse with the preset upper limit and lower limit of the physical safety range: If the calculated target value of the opening pulse is higher than the upper limit of the physical safety range, then the opening adjustment command is sent to the second valve element at the upper limit of the physical safety range. If the calculated target value of the opening pulse is lower than the lower limit of the physical safety range, an opening adjustment command is sent to the second valve element at the lower limit of the physical safety range. If the calculated target value of the opening pulse is not higher than the upper limit of the physical safety range and not lower than the lower limit of the physical safety range, then the opening adjustment command is sent to the second valve element based on the target value of the opening pulse.

6. The multi-split air conditioner according to claim 2, characterized in that: The control module is configured as follows: Call the current ambient temperature; Look up the ambient temperature gradient interval table, map and compare the current ambient temperature with multiple ambient temperature intervals to confirm the ambient temperature interval into which the current ambient temperature falls. Based on the temperature range into which the current ambient temperature falls, the corresponding correction coefficient is determined from the ambient temperature gradient range table; the correction coefficient represents the initial thermal load formed by the current external ambient temperature on the drive module; The correction coefficients are substituted into the preset feedforward opening calculation model to calculate the initial opening of the second valve element.

7. The multi-split air conditioner according to claim 1, characterized in that: The first valve element is a solenoid valve; The control module is configured as follows: Get the current ambient temperature and the current driver module temperature; Calculate the flow path reconstruction determination temperature difference, which is the temperature difference between the current drive module temperature and the current ambient temperature; Determine whether the temperature difference meets the preset refrigerant circulation system reconfiguration conditions for flow path reconstruction; If the condition is not met, the first valve element remains closed. If the conditions are met, a timer is started to determine whether the duration for which the refrigerant circulation system reconfiguration conditions are met has reached the first preset duration. If the first preset time is reached, the first valve element is driven to switch from the current closed state to the open state.

8. The multi-split air conditioner according to claim 7, characterized in that: The control module is configured as follows: Determine whether the temperature difference during flow path reconstruction meets the preset exit reconstruction conditions; If the condition is not met, the first valve element remains open. If the conditions are met, start the timer and determine whether the duration for which the exit reconstruction condition has been met has reached the second preset duration. If the second preset time is reached, the first valve element will be driven to switch from the current open state to the closed state.

9. The multi-split air conditioner according to claim 1, characterized in that: In cooling mode, the control module is configured to perform the following steps to perform graded control of the subcooling throttling element: Get the current ambient temperature and the current drive module temperature, and determine whether they meet the preset first load judgment condition or the second load judgment condition; When the preset first load judgment condition is met, the target opening of the subcooled throttling element is controlled to be in the fully open working range so as to form a low-resistance refrigerant flow path in the subcooled pipe section. When the preset second load judgment condition is met, the target opening of the subcooling throttling element is controlled to be in the throttling working range, so as to regulate the flow rate and pressure of the refrigerant in the subcooling pipe section.

10. The multi-split air conditioner according to claim 9, characterized in that: The control module is configured as follows: Calculate the condensation protection judgment temperature difference, which is the difference between the current ambient temperature and the current drive module temperature; Determine whether the temperature difference meets the preset anti-condensation active protection conditions for condensation protection; When the conditions for active protection against condensation are met, the dynamic calculation of the target opening of the subcooled throttling element based on the adjustment weight factor is stopped, and the target opening of the subcooled throttling element is controlled to be in the fully open working range, so as to form a low-resistance refrigerant flow path in the subcooled pipe section.

Images