Load energy efficiency control method based on multi-split air conditioner and related equipment

Abstract

The invention relates to the technical field of air conditioners, in particular to a load energy efficiency control method based on a multi-split air conditioner and related equipment. The multi-split air conditioner comprises a heat exchanger, a plurality of control valves, an indoor unit starting-up state detector, a plurality of heat exchange pipes, an indoor temperature sensor and an outdoor temperature sensor, the heat exchanger conveys refrigerants for heat exchange through the heat exchange pipes, and after heat exchange is completed, part of the heat exchange pipes continuously convey the refrigerants; the rest heat exchange tubes control circulation of a refrigerant through a plurality of control valves; the control method comprises the following steps: calculating data acquired by an indoor unit startup state detector, an indoor temperature sensor and an outdoor temperature sensor to obtain a capability demand proportion and an indoor unit startup proportion; and the opening degrees of the multiple control valves are controlled according to the capacity demand proportion and the indoor unit starting proportion. The outdoor unit heat exchanger can be fully utilized, the energy efficiency of the multi-split air conditioner is improved, and energy consumption and carbon emission are reduced.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to a load energy efficiency control method and related equipment based on multi-split air conditioning. Background Technology

[0002] When a multi-split air conditioning system operates under partial load conditions, such as when a single indoor unit is turned on or only some indoor units are running, existing technologies mainly reduce energy consumption by lowering the compressor frequency or reducing the outdoor fan speed to adapt to lower cooling demands. However, this type of adjustment method has obvious limitations. On the one hand, when the capacity demand is low, the actual area participating in heat exchange on the indoor side is small, and the corresponding refrigerant demand is also reduced. However, in the existing system, the full amount of refrigerant still needs to flow in the entire circulation loop. Excess refrigerant cannot be flexibly allocated according to actual demand, which not only causes energy loss in the refrigerant transportation process, but also makes it difficult to improve the system's energy efficiency. On the other hand, there is often a large amount of surplus heat exchange area on the outdoor side at this time. Due to the lack of a targeted adjustment mechanism, these surplus areas cannot be effectively utilized to optimize heat exchange efficiency, further exacerbating the energy efficiency shortcomings under partial load. At the same time, the high-pressure liquid receiver used to balance the refrigerant quantity in the existing system has a single function, which can only realize basic refrigerant storage and buffering. It cannot accurately control the refrigerant quantity according to the dynamic demand under partial load, making it difficult to solve the core problem of the mismatch between refrigerant quantity and actual heat exchange demand. Ultimately, the system faces the dilemma of low energy efficiency and poor adaptability between refrigerant circulation and heat exchange demand in partial load scenarios such as single operation and partial operation. Moreover, there is a lack of better alternatives to the high-pressure liquid receiver to overcome the existing technical bottlenecks.

[0003] In summary, the technical problems existing in the relevant technologies need to be improved. Summary of the Invention

[0004] The main objective of this application is to propose a load energy efficiency control method and related equipment based on multi-split air conditioners, which can make full use of the outdoor unit heat exchanger, improve the energy efficiency of multi-split air conditioners, and reduce energy consumption and carbon emissions.

[0005] To achieve the above objectives, one aspect of this application proposes a load energy efficiency control method based on a multi-split air conditioner. The multi-split air conditioner includes a heat exchanger, multiple control valves, an indoor unit start-up status detector, multiple heat exchange tubes, an indoor temperature sensor, and an outdoor temperature sensor. The heat exchanger delivers refrigerant through the multiple heat exchange tubes for heat exchange. After heat exchange is completed, some of the heat exchange tubes continuously deliver the refrigerant, while the remaining heat exchange tubes control the refrigerant flow through the multiple control valves. The control method includes the following steps: The capacity demand ratio and indoor unit operating ratio are calculated by analyzing the data obtained from the indoor unit operating status detector, the indoor temperature sensor, and the outdoor temperature sensor. The opening degree of multiple control valves is controlled according to the capacity demand ratio and the indoor unit start-up ratio; the flow rate of the refrigerant is adjusted by controlling the opening degree of the multiple control valves; The number of control valves is no less than two.

[0006] In some embodiments, calculating the capacity demand ratio and indoor unit operating ratio from the data acquired by the indoor unit operating status detector, the indoor temperature sensor, and the outdoor temperature sensor includes the following steps: The actual capacity requirement is calculated by using data obtained from the indoor unit power-on status detector, the indoor temperature sensor, and the outdoor temperature sensor. The capacity requirement ratio is obtained by calculating the ratio of the actual capacity requirement to the rated capacity of the outdoor unit. The capacity of the indoor unit when it is powered on is obtained through the indoor unit power-on status detector; The indoor unit operating ratio is obtained by comparing the ratio of the indoor unit's operating capacity to the outdoor unit's rated capacity.

[0007] In some embodiments, the calculation of actual capacity requirements based on data obtained from the indoor unit power-on status detector, the indoor temperature sensor, and the outdoor temperature sensor includes the following steps: The change in ambient temperature required for the capacity is calculated by analyzing the temperature data acquired by the indoor temperature sensor and the outdoor temperature sensor. The rated capacity of the indoor unit when it is turned on is obtained through the indoor unit power-on status detector; The actual capacity requirement is obtained by calculating the change in ambient temperature and the rated capacity of the indoor unit.

[0008] In some embodiments, the change in ambient temperature required for the capacity is calculated using the following formula: ; in, This indicates the change in ambient temperature that necessitates the measurement of the required capacity. Indicates indoor ambient temperature. denoted as outdoor ambient temperature, c as indoor temperature influence coefficient, d as outdoor temperature influence coefficient, b as the first critical temperature parameter, and h as the second critical temperature parameter.

[0009] In some embodiments, the system further includes a first capacity demand constant, a second capacity demand constant, a first indoor unit start-up constant, and a second indoor unit start-up constant; controlling the opening degree of the plurality of control valves according to the capacity demand ratio and the indoor unit start-up ratio includes the following steps: The capacity requirement ratio is compared with the first capacity requirement constant and the second capacity requirement constant, respectively; The indoor unit start-up ratio is compared with the first indoor unit start-up constant and the second indoor unit start-up constant, respectively; Based on the comparison between the capacity demand ratio and the indoor unit start-up ratio, the valve opening ratio coefficient is obtained; The opening degree of multiple control valves is controlled according to the valve opening ratio coefficient; Wherein, the first capacity requirement constant is less than the second capacity requirement constant, and the first indoor unit start-up constant is less than the second indoor unit start-up constant.

[0010] In some embodiments, obtaining the valve opening ratio coefficient based on a comparison between the capacity demand ratio and the indoor unit operating ratio includes the following steps: When the capacity demand ratio is less than the first capacity demand constant and the indoor unit start-up ratio is greater than the second indoor unit start-up constant, the valve opening ratio coefficient is 50%. When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than or equal to the second capacity demand constant, and the indoor unit start-up ratio is greater than the second indoor unit start-up constant, the valve opening ratio coefficient is 80%. When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit start-up ratio is greater than the second indoor unit start-up constant, the valve opening ratio coefficient is 100%. When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit start-up ratio is greater than or equal to the first indoor unit start-up constant and less than or equal to the second indoor unit start-up constant, the valve opening ratio coefficient is 65%. When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit start-up ratio is less than the first indoor unit start-up constant, the valve opening ratio coefficient is 40%. When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit start-up ratio is less than or equal to the first indoor unit start-up constant, the valve opening ratio coefficient is 10%. When the capacity demand ratio is less than the first capacity demand constant, and the indoor unit start-up ratio is less than the first indoor unit start-up constant, the valve opening ratio coefficient is 0. When the capacity demand ratio is less than the first capacity demand constant, and the indoor unit start-up ratio is greater than or equal to the first indoor unit start-up constant and less than or equal to the second indoor unit start-up constant, the valve opening ratio coefficient is 20%. When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit start-up ratio is greater than or equal to the first indoor unit start-up constant and less than or equal to the second indoor unit start-up constant, the valve opening ratio coefficient is 30%.

[0011] In some embodiments, the following steps are also included: If two control valves are configured, when the valve opening ratio coefficient is 10%-50%, only one control valve will be opened. When the valve opening ratio coefficient is greater than 50%, both control valves are opened; When the valve opening proportional coefficient is 0, both control valves are closed.

[0012] In some embodiments, the multi-split air conditioner further includes a refrigerant pressure sensor and an external pipe temperature sensor, wherein the refrigerant pressure sensor and the external pipe temperature sensor are respectively disposed in the high-pressure pipeline of the external unit between the heat exchanger and the compressor; the control method further includes the following steps: The system high pressure is acquired in real time using the refrigerant pressure sensor. When the system high pressure is less than the high pressure threshold and the duration is greater than the pressure-time threshold, the outer tube temperature is acquired in real time through the outer tube temperature sensor. When the temperature of the outer pipe is less than the difference between the refrigerant saturation temperature corresponding to the high pressure of the system and the temperature difference safety threshold, and there is a control valve in the closed state, one of the control valves is opened.

[0013] To achieve the above objectives, another aspect of this application proposes a load energy efficiency control system based on a multi-split air conditioner. The multi-split air conditioner includes a heat exchanger, multiple control valves, an indoor unit start-up status detector, multiple heat exchange tubes, an indoor temperature sensor, and an outdoor temperature sensor. The heat exchanger delivers refrigerant through the multiple heat exchange tubes for heat exchange. After heat exchange is completed, some of the heat exchange tubes continuously deliver the refrigerant, while the remaining heat exchange tubes control the refrigerant flow through the multiple control valves. The control system includes: The ratio calculation module is used to calculate the capacity requirement ratio and the indoor unit start-up ratio based on the data obtained by the indoor unit start-up status detector, the indoor temperature sensor and the outdoor temperature sensor. An opening control module is used to control the opening degree of multiple control valves according to the capacity demand ratio and the indoor unit start-up ratio; and to adjust the refrigerant flow rate by controlling the opening degree of multiple control valves. The number of control valves is no less than two.

[0014] To achieve the above objectives, another aspect of this application provides an electronic device, which includes a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the method described above.

[0015] The embodiments of this application include at least the following beneficial effects: This application provides a load energy efficiency control method and related equipment based on multi-split air conditioning. This scheme calculates the capacity demand ratio and indoor unit operating ratio by analyzing data obtained from an indoor unit operating status detector, an indoor temperature sensor, and an outdoor temperature sensor; then controls the opening degree of multiple control valves based on the capacity demand ratio and indoor unit operating ratio; and adjusts the refrigerant flow rate by controlling the opening degree of the multiple control valves. This solves the problem of low energy efficiency under partial load, avoids full refrigerant circulation loss, resolves the problem of refrigerant quantity and heat exchange mismatch, adapts to indoor demand and excess outdoor unit heat exchange area, optimizes the system structure, enhances the flexibility of refrigerant regulation, and ensures safe and efficient system operation, real-time monitoring of anomalies and automatic adjustment, extends equipment life, and balances energy saving and stability. Attached Figure Description

[0016] Figure 1 This is a flowchart of a load energy efficiency control method based on a multi-split air conditioner provided in an embodiment of this application; Figure 2 This is a schematic diagram illustrating the area affected by the constants of capacity demand ratio and indoor unit operating ratio; Figure 3 This is a flowchart illustrating the valve opening control process for the capacity demand ratio and the indoor unit start-up ratio. Figure 4 This is a schematic diagram of a multi-split air conditioner with two control valves. Figure 5 This is a schematic diagram of the load energy efficiency control system based on a multi-split air conditioner provided in an embodiment of this application; Figure 6 This is a schematic diagram of the hardware structure of the electronic device provided in the embodiments of this application. Detailed Implementation

[0017] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of this application and are not intended to limit it. In the following description, when referring to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with those of this application; they are merely examples of apparatuses and methods consistent with some aspects of the embodiments of this application as detailed in the appended claims.

[0018] It is understood that the terms “first,” “second,” etc., used in this application may be used herein to describe various concepts, but unless otherwise stated, these concepts are not limited by these terms. These terms are only used to distinguish one concept from another. For example, without departing from the scope of the embodiments of this application, first information may also be referred to as second information, and similarly, second information may also be referred to as first information. Depending on the context, the words “if,” “when,” or “in response to a determination” as used herein may be interpreted as “when…” or “when…” or “in response to a determination.”

[0019] As used in this application, the terms "at least one", "multiple", "each", "any", etc., "at least one" includes one, two or more, "multiple" includes two or more, "each" refers to each of the corresponding multiples, and "any" refers to any one of the multiples.

[0020] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing embodiments of this application only and is not intended to limit this application.

[0021] Before providing a detailed description of the embodiments of this application, some of the nouns and terms involved in the embodiments of this application will be explained first. The nouns and terms involved in the embodiments of this application are subject to the following interpretations.

[0022] Rated capacity of indoor unit: The maximum cooling / heating capacity of the indoor unit as specified by the manufacturer (e.g., 2.2kW). It is the upper limit of the capacity of a single indoor unit when running at full load, reflects the core performance of the indoor unit, and provides a benchmark for calculating actual needs.

[0023] Heat exchange tubes: Multiple thin tubes (condenser tubes) arranged in parallel in the outdoor unit condenser, which transport refrigerant and exchange heat through fins. They are the core components for heat exchange between the refrigerant and the outdoor air, and their number varies with the capacity of the outdoor unit.

[0024] System high pressure: The high pressure of the refrigerant from the condenser inlet to the expansion valve (e.g., 2.4 MPa), reflecting the high-pressure side circulation status and related to the efficiency of the compressor and condenser.

[0025] Outdoor fan: The heat dissipation component of the outdoor unit. Its operation accelerates the airflow through the condenser, enhancing the refrigerant heat dissipation efficiency. The speed is adjusted according to the load.

[0026] Figure 1 This is an optional flowchart of a load energy efficiency control method based on a multi-split air conditioner provided in this application embodiment. The multi-split air conditioner supporting this method includes a heat exchanger, multiple control valves, an indoor unit start-up status detector, multiple heat exchange tubes, an indoor temperature sensor, and an outdoor temperature sensor. The heat exchanger delivers refrigerant for heat exchange through multiple heat exchange tubes. After heat exchange is completed, some of the heat exchange tubes continue to deliver refrigerant, while the remaining heat exchange tubes control the flow of refrigerant through multiple control valves. Figure 1 The control method may include, but is not limited to, steps S110 to S120.

[0027] Step S110: Calculate the data obtained from the indoor unit's on-state detector, indoor temperature sensor, and outdoor temperature sensor to obtain the capacity demand ratio and the indoor unit's on-state ratio; Step S102: Control the opening degree of multiple control valves according to the capacity demand ratio and the indoor unit start-up ratio; adjust the refrigerant flow rate by controlling the opening degree of multiple control valves; wherein the number of control valves is not less than two.

[0028] In related technologies, a multi-split system can be flexibly composed of multiple outdoor units and / or multiple indoor units. However, the smallest outdoor unit is often much larger than the smallest indoor unit, resulting in a mismatch between the two, leading to low energy efficiency. This is even more pronounced in residential multi-split air conditioners, which often use one outdoor unit and four to five indoor units. The unit that is used for extended periods is often the smallest indoor unit, thus remaining in a low-energy-efficiency range for a long time.

[0029] In view of this, the embodiments of this application provide steps S110 to S120 as shown, which calculate the capacity demand ratio and indoor unit operating ratio by analyzing data obtained from the indoor unit operating status detector, indoor temperature sensor, and outdoor temperature sensor. By accurately calculating the capacity demand ratio and indoor unit operating ratio, and combining data such as indoor unit operating status and indoor and outdoor temperatures, the opening of the control valve is adjusted to avoid full refrigerant circulation, significantly improving energy efficiency when operating only or partially, and reducing energy consumption. The control valve controls the refrigerant flow in multiple heat exchange tubes, replacing the traditional high-pressure liquid receiver, simplifying the hardware while achieving dynamic refrigerant distribution, and making full use of the outdoor unit's surplus heat exchange area; in addition, the linkage between various sensors and controllers allows the system to automatically diagnose and adjust abnormalities, reducing the risk of failure, extending equipment life, and balancing energy saving and reliability. After heat exchange is completed in a multi-split air conditioner, some of the heat exchange tubes continuously supply refrigerant, while the remaining heat exchange tubes control the refrigerant flow through multiple control valves. This means that in the refrigerant control device of a multi-split air conditioner, some heat exchange tubes are kept uninterrupted by the control valves, and refrigerant is always transferred through these heat exchange tubes. This ensures that the refrigerant transfer of the multi-split air conditioner is carried out even when the refrigerant demand is at its lowest, that is, even when all control valves are closed, refrigerant is still continuously transferred through these heat exchange tubes.

[0030] In some embodiments, in step S110, the temperature data obtained by the indoor temperature sensor and the outdoor temperature sensor are calculated to obtain the change in ambient temperature of the capacity requirement; the rated capacity of the indoor unit is obtained by the indoor unit power-on status detector; the change in ambient temperature of the capacity requirement is calculated with the rated capacity of the indoor unit to obtain the actual capacity requirement; the ratio of the actual capacity requirement to the rated capacity of the outdoor unit is calculated to obtain the capacity requirement ratio; the capacity of the indoor unit is obtained by the indoor unit power-on status detector; and the indoor unit power-on ratio is obtained based on the ratio of the indoor unit capacity to the rated capacity of the outdoor unit.

[0031] Specifically, first, determine the corrected capacity requirement for a single operating indoor unit. For each operating indoor unit, its rated capacity (Qinternal) is used as the basis, for example, if a certain indoor unit has a rated cooling capacity of 2.2kW, and then multiplied by the ambient temperature change determined by the indoor and outdoor ambient temperatures, to obtain the actual capacity requirement Qinternal of that indoor unit. That is, Qinternal = Qinternal * (Qinternal * Qinternal) Q represents the required capability to activate the internal unit. This represents the change in ambient temperature that determines computing power requirements, with Qinternal representing the rated capacity. The key is that if there is a large temperature difference between indoors and outdoors, such as 30℃ indoors and 35℃ outdoors, the demand for cooling is high. A reading close to or slightly greater than 1 indicates that the indoor unit needs to operate at full or overload capacity; if the temperature difference between indoors and outdoors is small, such as 26°C indoors and 28°C outdoors, the cooling demand is weak. If the value is less than 1, such as 0.6, the indoor unit only needs 60% of its rated capacity to meet the demand. The value is entirely determined by the comparison between indoor and outdoor temperatures, reflecting the impact of temperature on actual demand. Next, the capacity requirements of all activated indoor units are summarized to obtain the actual system capacity requirement. The Q-values ​​of all currently activated indoor units are then calculated and summed, resulting in the actual capacity requirement = Let 'i' represent the i-th indoor unit that is turned on. For example, if 3 indoor units are turned on, the Q values ​​of these 3 units are added together. Finally, substitute these values ​​into the capacity demand ratio (Qp) formula to calculate the capacity demand ratio. That is, divide the summed "actual capacity demand" by the "rated capacity of the outdoor unit". For example, if the rated cooling capacity of the outdoor unit is 14kW, then Qp = actual capacity demand ÷ rated capacity of the outdoor unit, and the result is expressed as a percentage. For example, if 2 indoor units with a rated capacity of 2.2kW are turned on, the indoor and outdoor temperature difference is small. =0.5, outdoor unit rated capacity 14kW; then single unit Q_indoor = 2.2 × 0.5 = 1.1kW, actual capacity requirement = 1.1 + 1.1 = 2.2kW, Qp = 2.2 ÷ 14 ≈ 15.7%.

[0032] The rated capacity of the indoor unit (Q_internal capacity) is the "basic reference," specifying the maximum capacity limit of a single indoor unit and determining "the maximum cooling capacity that the indoor unit can provide," serving as the starting point for calculations; indoor and outdoor temperatures are "dynamic correction factors," adjusted based on changes in ambient temperature. This determines how much cooling capacity the indoor unit "actually needs to output," such as when it doesn't need to be at full load. <1, when full load is required The value ≈1 is crucial for ensuring the calculation accurately reflects actual operating conditions. The combined Q_internal value obtained from both is the true capacity requirement of a single indoor unit. By summing up the Q_internal values ​​of all operating indoor units, the final system "actual capacity requirement" is formed. Therefore, the actual cooling demand of a multi-split system cannot be determined solely by "how many indoor units are running and what the rated capacity of each unit is," as ignoring temperature leads to misjudgments. Nor can it be determined solely by "how much heat is generated indoors and outdoors," as this lacks a quantitative basis without indoor unit capacity benchmarks. Instead, it should be based on the rated capacity of each operating indoor unit, corrected by indoor and outdoor temperatures to determine the actual demand of each unit, then summed up the demands of all operating indoor units to obtain the true actual capacity requirement of the system. Finally, this demand is divided by the rated capacity of the outdoor units to calculate Q_p. The ultimate goal is for Q_p to accurately reflect "the proportion of the current system's actual required capacity to the maximum capacity of the outdoor units," providing a basis for subsequent adjustments to the heat exchanger area and refrigerant volume.

[0033] The formula for calculating the change in ambient temperature for the above-mentioned capacity requirements is: ; in, This indicates the change in ambient temperature that necessitates the measurement of the required capacity. Indicates indoor ambient temperature. denoted as outdoor ambient temperature, c as indoor temperature influence coefficient, d as outdoor temperature influence coefficient, b as the first critical temperature parameter, and h as the second critical temperature parameter.

[0034] In the formula for calculating the change in ambient temperature of capacity demand, the deviation between indoor and outdoor temperatures and the preset critical temperature is used, combined with weighting coefficients, to quantify the correction of temperature on the ratio of actual demand to rated capacity of the indoor unit. b measures the degree to which the indoor temperature deviates from the target, and h measures the degree to which the outdoor temperature deviates from the heat exchange criticality. c and d are then used to adjust the weighting of their impact on demand, ultimately yielding the correction coefficient. This allows actual capacity requirements to better align with real-world operating conditions, rather than solely focusing on the rated capacity of the indoor unit.

[0035] In the formula, 'c' represents the weight of the impact of a 1°C change in indoor temperature on the actual demand of a single indoor unit. In a cooling scenario: if c > 0, then... The higher, The smaller the value of the term, if b is 26℃, when At 30℃, =-4. If c is positive, this term will lower the numerator, requiring balance with other terms. Overall, it reflects the principle that "the hotter the indoor environment, the more the demand is adjusted." In heating scenarios: the logic is reversed. The lower the value (the colder the room), the stronger the heating demand; the symbol or value of 'c' needs to be adjusted.

[0036] d represents the weight of the impact of a 1°C change in outdoor temperature on the actual demand of a single indoor unit. In a cooling scenario: if d > 0, then The higher the value, the more d*(h- The smaller the value of the term, if h is the "outdoor critical temperature", for example, 30℃, when At 35℃, h- =-5, if d is positive, this term lowers the numerator, reflecting that "the hotter the outdoor temperature, the worse the heat exchange of the outdoor unit, requiring adjustments to the indoor unit's requirements." In heating scenarios, The lower the value, the stronger the demand; the symbol or value of d may need to be adjusted.

[0037] b and h are "critical temperature parameters" preset by the manufacturer based on product performance and experimental data, which need to be determined through "laboratory calibration + operating condition verification". b usually corresponds to the "indoor design temperature", such as 26℃ for cooling and 20℃ for heating, and is a benchmark value for judging the "degree of deviation of indoor temperature". The first critical temperature parameter is obtained by conducting a large number of "cooling / heating experiments under different indoor temperatures", statistically analyzing the ratio of the actual demand of the indoor unit to the rated capacity, and finally fitting a benchmark temperature that best reflects the "correction law of indoor temperature to demand". It does not require on-site data collection and is a preset constant. h corresponds to the "critical temperature of outdoor heat exchange efficiency". For example, 30℃ for cooling. When the outdoor temperature exceeds 30℃, the heat exchange efficiency of the outdoor unit condenser drops sharply; -5℃ for heating. When the outdoor temperature is below -5℃, the heat absorption efficiency of the outdoor unit evaporator drops sharply. The second critical temperature parameter is obtained by conducting "unit operation experiments under different outdoor temperatures", testing the correlation between the heat exchange efficiency of the outdoor unit and the actual demand of the indoor unit, and fitting a critical temperature that can distinguish "whether the outdoor heat exchange is friendly". It is also a constant calibrated during the research and development stage and does not require on-site data collection.

[0038] Indoor unit operating ratio (Kp), Kp = indoor unit capacity in operation / outdoor unit rated capacity * 100%. For example, if the outdoor unit rated capacity is 16kW, and the indoor units include one 22-inch indoor unit, one 28-inch indoor unit, one 40-inch indoor unit, and one 71-inch indoor unit, when only one 22-inch indoor unit is in operation, Kp = 2.2 / 16 * 100% = 13.75%.

[0039] In some embodiments, the system further includes a first capacity demand constant, a second capacity demand constant, a first indoor unit start-up constant, and a second indoor unit start-up constant; controlling the opening degree of multiple control valves according to the capacity demand ratio and the indoor unit start-up ratio includes the following steps: comparing the capacity demand ratio with the first capacity demand constant and the second capacity demand constant respectively; comparing the indoor unit start-up ratio with the first indoor unit start-up constant and the second indoor unit start-up constant respectively; obtaining a valve opening ratio coefficient based on the comparison result of the capacity demand ratio and the indoor unit start-up ratio; controlling the opening degree of multiple control valves according to the valve opening ratio coefficient; wherein, the first capacity demand constant is less than the second capacity demand constant, and the first indoor unit start-up constant is less than the second indoor unit start-up constant.

[0040] The first capacity demand constant (a1) and the second capacity demand constant (a2) are two constants that measure the capacity demand ratio (Qp); the first indoor unit start-up constant (b1) and the second indoor unit start-up constant (b2) are two constants that measure the indoor unit start-up ratio (Kp). The first capacity demand constant, the second capacity demand constant, the first indoor unit start-up constant and the second indoor unit start-up constant will all affect the heat exchange demand required by the outdoor unit. The higher the heat exchange demand of the outdoor unit, the more solenoid valves will be opened.

[0041] Based on the comparison between the capacity demand ratio and the indoor unit operating ratio, the valve opening ratio coefficient is obtained, including the following steps: When the capacity demand ratio is less than the first capacity demand constant and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 50%; when the capacity demand ratio is greater than or equal to the first capacity demand constant and less than or equal to the second capacity demand constant, and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 80%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 100%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than or equal to the first indoor unit operating constant and less than or equal to the second indoor unit operating constant, the valve opening ratio coefficient is 65 ... the second indoor unit operating constant, the valve opening ratio coefficient is 100%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than or equal to the first indoor unit operating constant and less than or equal to the second indoor unit operating constant, the valve opening ratio coefficient is 65%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 65%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 65%; when the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit operating ratio is greater than the second indoor unit operating constant, the valve opening ratio coefficient is 65%; when the capacity demand ratio is greater than the second capacity demand When the indoor unit start-up ratio is less than the first indoor unit start-up constant, the valve opening ratio coefficient is 40%; when the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit start-up ratio is less than or equal to the first indoor unit start-up constant, the valve opening ratio coefficient is 10%; when the capacity demand ratio is less than the first capacity demand constant, and the indoor unit start-up ratio is less than the first indoor unit start-up constant, the valve opening ratio coefficient is 0; when the capacity demand ratio is less than the first capacity demand constant, and the indoor unit start-up ratio is greater than or equal to the first indoor unit start-up constant and less than or equal to the second indoor unit start-up constant, the valve opening ratio coefficient is 20%; when the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit start-up ratio is greater than or equal to the first indoor unit start-up constant and less than or equal to the second indoor unit start-up constant, the valve opening ratio coefficient is 30%.

[0042] like Figure 2 As shown, Figure 2 This is a schematic diagram illustrating the constant influence of capacity demand ratio and indoor unit start-up ratio on the region. A1, A2, B1, and B2 are divided into 9 regions using a coordinate system. Each region is assigned a value to the right of A1 or A2, indicating greater than / greater than or equal to; a value to the left of A1 or A2, indicating less than / less than or equal to; a value above B1 or B2, indicating less than / less than or equal to; and a value below B1 or B2, indicating less than / less than or equal to. Different valve opening ratio coefficients (Fp) are matched for each of the 9 regions.

[0043] like Figure 3 As shown, Figure 3 This is a flowchart illustrating the valve opening control process for the capacity demand ratio and the indoor unit start-up ratio. The control valves include the condenser liquid distribution solenoid valve, the condenser height adjustment valve, or the electronic expansion valve. When there are 8 control valves, i.e., control valve 1: SV1; control valve 2: SV2... control valve 8: SV8. Figure 3First, Qp and Kp are calculated. Then, Qp and Kp are compared with a1, a2, b1, and b2 respectively to obtain Fp for 9 different regions, as follows: Region 1: When Qp < a1 and b2 < Kp, Fp = 50%, that is, SV1~SV4 are on and SV5~SV8 are off; Region 2: When a1≤Qp≤a2 and b2<Kp, Fp=80%, that is, SV1~SV7 are on and SV8 is off; Region 3: When a2 < Qp and b2 < Kp, Fp = 100%, that is, SV1~SV8 are enabled; Region 4: When a2 < Qp and b1 ≤ Kp ≤ b2, Fp = 65%, that is, SV1~SV6 are on and SV7~SV8 are off; Region 5: When a2 < Qp and Kp < b1, Fp = 40%, that is, SV1~SV4 are on, and SV5~SV8 are off; Region 6: When a1≤Qp<a2 and Kp≤b1, Fp=10%, that is, SV1 is on and SV2~SV8 are off; Region 7: When Qp < a1 and Kp < b1, Fp = 0, that is, SV1~SV8 are closed; Region 8: When Qp < a1 and b1 ≤ Kp ≤ b2, Fp = 20%, that is, SV1~SV2 are on, and SV3~SV8 are off; Region 9: When a1≤Qp<a2 and b1≤Kp≤b2, Fp=30%, that is, SV1~SV3 are on and SV4~SV8 are off.

[0044] The conditions corresponding to regions 1 to 9 and the data corresponding to Fb can also be applied to multi-split air conditioning systems with different numbers of control valves installed in the heat exchange tubes. The valve opening and closing methods are divided according to the region based on the number n of valves adjusting the condenser height. Fb = number of control valves open / total number of control valves. The principle for opening the control valves is that the controller calculates the valve opening ratio coefficient based on relevant parameters, and the selection of the opening and closing control valves follows the principle of first-to-stop, first-to-open.

[0045] like Figure 4 As shown, Figure 4This is a schematic diagram of a multi-split air conditioner with two control valves. In cooling mode, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor first passes through an oil separator to remove the accompanying refrigerant oil, which flows back into the compressor for lubrication. It then enters the heat exchanger (condenser) through a four-way valve. Inside the condenser, the refrigerant flows through multiple heat exchange tubes, exchanging heat with the outdoor air and condensing into a high-temperature, high-pressure liquid refrigerant. Two control valves and one section of the heat exchange tubes without a control valve are located at the outlet of the heat exchanger. The section without the control valve maintains constant refrigerant flow, and the refrigerant flow is controlled by opening or closing the control valves. After flowing out of the heat exchange tubes, the refrigerant is depressurized by a throttling valve into a low-temperature, low-pressure gas-liquid mixture, which is then sent to the indoor unit through the heat exchanger's gas pipe. In heating mode, the four-way valve reverses, allowing the high-temperature, high-pressure gaseous refrigerant discharged from the compressor to flow directly to the indoor unit via the gas pipe. After releasing heat, it becomes low-temperature, low-pressure gaseous refrigerant and returns to the outdoor unit. It first undergoes gas separation to separate any potential liquid refrigerant (preventing liquid slugging in the compressor) before being drawn back into the compressor to complete the cycle. During this process, the flow rate of the refrigerant is controlled by both control valves and multiple heat exchangers without control valves. For control, the indoor unit's on-state detector is linked to the controller to adjust the switching of the heat exchanger branch control valves, controlling the number of heat exchange tubes involved in heat exchange to match the Qp requirement. The oil separator ensures compressor lubrication, while the gas separator protects the compressor's safety; both work together to improve system stability. The throttling valve dynamically adjusts the refrigerant pressure reduction based on the load, achieving a precise match between the refrigerant quantity and heat exchange requirements. The diagram shows two control valves. When the valve opening ratio is between 10% and 50%, only one control valve is open. When the valve opening ratio is greater than 50%, both control valves are open. When the valve opening ratio is 0, both control valves are closed, and the refrigerant flows only through the multiple heat exchange tubes without control valves.

[0046] In some embodiments, the multi-split air conditioner further includes a refrigerant pressure sensor and an external pipe temperature sensor, which are respectively installed in the high-pressure pipeline of the outdoor unit between the heat exchanger and the compressor; the control method further includes: acquiring the system high pressure in real time through the refrigerant pressure sensor; when the system high pressure is less than the high pressure threshold and the duration is greater than the pressure-time threshold, acquiring the external pipe temperature in real time through the external pipe temperature sensor; when the external pipe temperature is less than the difference between the refrigerant saturation temperature corresponding to the system high pressure and the temperature difference safety threshold, and there is a control valve in a closed state, opening a control valve.

[0047] Specifically, if the system high pressure (Pd) is less than m and lasts for x minutes during operation, the T-pipe is checked. If the external pipe temperature is less than Pd-s1, the control valve (SVn) status is checked. If any control valve is closed, an additional control valve is opened. Here, m, x, and s1 are preset constants.

[0048] In the operation of multi-split air conditioner outdoor units, determining whether the outdoor pipe temperature needs adjustment requires first clarifying the actual meaning of the system high pressure (Pd). Pd is not a direct pressure value (unit: MPa), but rather a value preset by the system controller to correspond to the refrigerant's "pressure - refrigerant saturation temperature." For example, fixed physical property data for refrigerants such as R32 and R410A are converted into the refrigerant's saturation temperature (unit: °C, i.e., the reference temperature of the refrigerant in a gas-liquid coexistence state) at that pressure, thus achieving unit consistency with the outdoor pipe temperature (unit: °C). Here, s1 is a safety temperature difference constant (unit: °C) calibrated by the manufacturer based on refrigerant characteristics and outdoor unit heat exchange design. It is used to define the normal range of difference between the outdoor pipe temperature and the high-pressure saturation temperature. For example, for R32 refrigerant condensers, s1 is usually preset to 8 °C, meaning that the outdoor pipe temperature is normally within 8 °C lower than the high-pressure saturation temperature. When the detected external pipe temperature is less than (the refrigerant saturation temperature corresponding to Pd) - s1, it indicates that the refrigerant is excessively subcooled in the heat exchanger (condenser). This may be due to excessively low outdoor temperature, excessive condenser circuit input, or excessive refrigerant charge. This will cause reduced refrigerant flow, abnormally low system high pressure, and even compressor pressure ratio imbalance. At this time, the system will automatically initiate regulation: control valves are installed at the heat exchanger outlet of the multiple heat exchange tubes flowing through the heat exchanger. If any of these control valves are not open, the refrigerant flow will be regulated by opening one of them; if all control valves are open, the external pipe temperature can be raised to above (the refrigerant saturation temperature corresponding to Pd) - s1 by fine-tuning the flow valve opening. This ensures reasonable refrigerant subcooling, guaranteeing the cooling efficiency of the subsequent indoor unit and preventing compressor damage due to abnormal operating conditions, thus maintaining stable system operation. Pressure and temperature sensors monitor the system high pressure and external pipe temperature in real time, and adjust the outdoor fan speed and control valve status in conjunction with the Pd-s1 logic to maintain normal refrigerant subcooling. Based on the conversion of refrigerant saturation temperature corresponding to refrigerant pressure, and through the judgment logic of external pipe temperature and Pd-s1, the refrigerant subcooling is accurately controlled, which solves the problem of mismatch between refrigerant quantity and heat exchange demand under partial load and ensures stable system operation.

[0049] Please see Figure 5 This application also provides a load energy efficiency control system based on a multi-split air conditioner, which can implement the above-mentioned method. The multi-split air conditioner includes a heat exchanger, multiple control valves, an indoor unit start-up status detector, multiple heat exchange tubes, an indoor temperature sensor, and an outdoor temperature sensor. The heat exchanger delivers refrigerant for heat exchange through multiple heat exchange tubes. After heat exchange is completed, some of the heat exchange tubes continue to deliver refrigerant, while the remaining heat exchange tubes control the flow of refrigerant through multiple control valves. The control system includes: The proportional calculation module is used to calculate the capacity requirement ratio and the indoor unit start-up ratio based on the data obtained from the indoor unit start-up status detector, indoor temperature sensor and outdoor temperature sensor. The opening control module is used to control the opening degree of multiple control valves according to the capacity demand ratio and the indoor unit start-up ratio; the refrigerant flow rate is adjusted by controlling the opening degree of multiple control valves. The number of control valves shall not be less than two.

[0050] It is understood that the content of the above method embodiments is applicable to this system embodiment. The specific functions implemented in this system embodiment are the same as those in the above method embodiments, and the beneficial effects achieved are also the same as those achieved in the above method embodiments.

[0051] This application also provides an electronic device, which includes a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the above-described method. This electronic device can be any smart terminal, including tablet computers, in-vehicle computers, etc.

[0052] It is understood that the content of the above method embodiments is applicable to this device embodiment. The specific functions implemented by this device embodiment are the same as those of the above method embodiments, and the beneficial effects achieved are also the same as those achieved by the above method embodiments.

[0053] Please see Figure 6 , Figure 6 The hardware structure of an electronic device according to another embodiment is illustrated. The electronic device includes: The processor 610 can be implemented using a general-purpose CPU (Central Processing Unit), microprocessor, application-specific integrated circuit (ASIC), or one or more integrated circuits, and is used to execute relevant programs to implement the technical solutions provided in the embodiments of this application. The memory 620 can be implemented as a read-only memory (ROM), a static storage device, a dynamic storage device, or a random access memory (RAM). The memory 620 can store the operating system and other applications. When the technical solutions provided in the embodiments of this specification are implemented through software or firmware, the relevant program code is stored in the memory 620 and is called and executed by the processor 610 using the methods described in the embodiments of this application. The input / output interface 630 is used to realize information input and output; The communication interface 640 is used to enable communication and interaction between this device and other devices. Communication can be achieved through wired means (such as USB, network cable, etc.) or wireless means (such as mobile network, WIFI, Bluetooth, etc.). Bus 650 transmits information between various components of the device (e.g., processor 610, memory 620, input / output interface 630, and communication interface 640); The processor 610, memory 620, input / output interface 630 and communication interface 640 are connected to each other within the device via bus 650.

[0054] Memory, as a non-transitory computer-readable storage medium, can be used to store non-transitory software programs and non-transitory computer-executable programs. Furthermore, memory may include high-speed random access memory, and may also include non-transitory memory, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. In some embodiments, memory may optionally include memory remotely located relative to the processor, and these remote memories can be connected to the processor via a network. Examples of such networks include, but are not limited to, the Internet, intranets, local area networks, mobile communication networks, and combinations thereof.

[0055] The embodiments described in this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided by the embodiments of this application. As those skilled in the art will know, with the evolution of technology and the emergence of new application scenarios, the technical solutions provided by the embodiments of this application are also applicable to similar technical problems.

[0056] Those skilled in the art will understand that the technical solutions shown in the figures do not constitute a limitation on the embodiments of this application, and may include more or fewer steps than shown, or combine certain steps, or different steps.

[0057] Those skilled in the art will understand that all or some of the steps in the methods disclosed above, as well as the functional modules / units in the systems and devices, can be implemented as software, firmware, hardware, or suitable combinations thereof.

[0058] It should be understood that the data used in this way can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in a sequence other than those illustrated or described herein. Furthermore, the terms “comprising” and “having”, and any variations thereof, are intended to cover a non-exclusive inclusion, for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such process, method, product, or apparatus.

[0059] It should be understood that in this application, "at least one (item)" means one or more, and "more than" means two or more. "And / or" is used to describe the relationship between related objects, indicating that three relationships can exist. For example, "A and / or B" can represent three cases: only A exists, only B exists, and both A and B exist simultaneously, where A and B can be singular or plural. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "At least one (item) of the following" or similar expressions refer to any combination of these items, including any combination of single or plural items. For example, at least one (item) of a, b, or c can represent: a, b, c, "a and b", "a and c", "b and c", or "a and b and c", where a, b, and c can be single or multiple.

[0060] In the several embodiments provided in this application, it should be understood that the disclosed apparatus and methods can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative; for instance, the division of the units described above is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be through some interfaces; the indirect coupling or communication connection between apparatuses or units may be electrical, mechanical, or other forms.

[0061] The units described above as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of this embodiment according to actual needs.

[0062] The preferred embodiments of the present application have been described above with reference to the accompanying drawings, but this does not limit the scope of the claims of the present application. Any modifications, equivalent substitutions, and improvements made by those skilled in the art without departing from the scope and substance of the embodiments of the present application shall be within the scope of the claims of the present application.

Claims

1. A control method based on the load energy efficiency of a multi-split air conditioner, characterized in that, The multi-connected air conditioner comprises a heat exchanger, a plurality of control valves, an indoor unit start state detector, a plurality of heat exchange pipes, an indoor temperature sensor and an outdoor temperature sensor. The heat exchanger exchanges heat through the plurality of heat exchange pipes. After heat exchange, part of the plurality of heat exchange pipes continuously transport refrigerant, and the remaining heat exchange pipes control the flow of refrigerant through the plurality of control valves. The control method comprises the following steps: Calculating the data obtained by the indoor unit start state detector, the indoor temperature sensor and the outdoor temperature sensor to obtain a capacity demand ratio and an indoor unit start ratio; Controlling the opening degree of the plurality of control valves according to the capacity demand ratio and the indoor unit start ratio; adjusting the flow of refrigerant by controlling the opening degree of the plurality of control valves; Wherein, the number of control valves is not less than two.

2. The method of claim 1, wherein, The calculation of the data obtained by the indoor unit start state detector, the indoor temperature sensor and the outdoor temperature sensor to obtain a capacity demand ratio and an indoor unit start ratio comprises the following steps: Calculating the data obtained by the indoor unit start state detector, the indoor temperature sensor and the outdoor temperature sensor to obtain an actual capacity demand; Obtaining the capacity demand ratio by calculating the ratio of the actual capacity demand to the outdoor unit rated capacity; Obtaining the indoor unit start ratio according to the ratio of the indoor unit capacity to the outdoor unit rated capacity. The calculation of the data obtained by the indoor unit start state detector, the indoor temperature sensor and the outdoor temperature sensor to obtain an actual capacity demand comprises the following steps:

3. The method of claim 2, wherein, Calculating the temperature data obtained by the indoor temperature sensor and the outdoor temperature sensor to obtain a capacity demand environment temperature change amount; Obtaining the indoor unit rated capacity by the indoor unit start state detector; Calculating the actual capacity demand by the capacity demand environment temperature change amount and the indoor unit rated capacity. The capacity demand environment temperature change amount is calculated by the following formula:

4. The method of claim 3, wherein, Further comprising a first capacity demand constant, a second capacity demand constant, a first indoor unit start constant and a second indoor unit start constant. The control of the opening degree of the plurality of control valves according to the capacity demand ratio and the indoor unit start ratio comprises the following steps: ； wherein, represents a capacity demand ambient temperature change amount, represents an indoor ambient temperature, represents an outdoor ambient temperature, c represents an indoor temperature influence coefficient, d represents an outdoor temperature influence coefficient, b represents a first critical temperature parameter, and h represents a second critical temperature parameter.

5. The method of claim 1, wherein, Comparing the capacity demand ratio with the first capacity demand constant and the second capacity demand constant respectively; Comparing the indoor unit start ratio with the first indoor unit start constant and the second indoor unit start constant respectively; Obtaining a valve opening ratio coefficient according to the comparison results of the capacity demand ratio and the indoor unit start ratio; Controlling the opening degree of the plurality of control valves according to the valve opening ratio coefficient; Wherein, the first capacity demand constant is less than the second capacity demand constant, and the first indoor unit start constant is less than the second indoor unit start constant. The obtaining of the valve opening ratio coefficient according to the comparison results of the capacity demand ratio and the indoor unit start ratio comprises the following steps:

6. The method of claim 5, wherein, ​ When the capacity demand ratio is less than the first capacity demand constant, and the indoor unit startup ratio is greater than the second indoor unit startup constant, the opening valve ratio coefficient is 50%; When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than or equal to the second capacity demand constant, and the indoor unit startup ratio is greater than the second indoor unit startup constant, the opening valve ratio coefficient is 80%; When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit startup ratio is greater than the second indoor unit startup constant, the opening valve ratio coefficient is 100%; When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit startup ratio is greater than or equal to the first indoor unit startup constant and less than or equal to the second indoor unit startup constant, the opening valve ratio coefficient is 65%; When the capacity demand ratio is greater than the second capacity demand constant, and the indoor unit startup ratio is less than the first indoor unit startup constant, the opening valve ratio coefficient is 40%; When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit startup ratio is less than or equal to the first indoor unit startup constant, the opening valve ratio coefficient is 10%; When the capacity demand ratio is less than the first capacity demand constant, and the indoor unit startup ratio is less than the first indoor unit startup constant, the opening valve ratio coefficient is 0; When the capacity demand ratio is less than the first capacity demand constant, and the indoor unit startup ratio is greater than or equal to the first indoor unit startup constant and less than or equal to the second indoor unit startup constant, the opening valve ratio coefficient is 20%; When the capacity demand ratio is greater than or equal to the first capacity demand constant and less than the second capacity demand constant, and the indoor unit startup ratio is greater than or equal to the first indoor unit startup constant and less than or equal to the second indoor unit startup constant, the opening valve ratio coefficient is 30%.

7. The method of claim 6, wherein, Further comprising the following steps: If the control valve is set to two, when the opening valve ratio coefficient is 10%-50%, only one of the control valves is opened; When the opening valve ratio coefficient is greater than 50%, both of the control valves are opened; When the opening valve ratio coefficient is 0, both of the control valves are closed.

8. The method of claim 6, wherein, The multi-connected air conditioner further comprises a refrigerant pressure sensor and an external pipe temperature sensor, which are arranged in the outdoor unit high-pressure pipeline between the heat exchanger and the compressor; the control method further comprises the following steps: Real-time acquisition of system high pressure through the refrigerant pressure sensor; When the system high pressure is less than the high pressure threshold and the duration is greater than the pressure time threshold, real-time acquisition of external pipe temperature through the external pipe temperature sensor; When the external pipe temperature is less than the difference between the refrigerant saturation temperature corresponding to the system high pressure and the temperature difference safety threshold, and there is a control valve in the closed state, one of the control valves is opened.

9. A control system based on the load energy efficiency of a multi- connected air conditioner, characterized by, The multi-connected air conditioner comprises a heat exchanger, a plurality of control valves, an indoor unit start state detector, a plurality of heat exchange pipes, an indoor temperature sensor and an outdoor temperature sensor, the heat exchanger transports refrigerant through the plurality of heat exchange pipes to exchange heat, after the heat exchange, part of the plurality of heat exchange pipes continuously transport the refrigerant, and the remaining heat exchange pipes control the flow of the refrigerant through the plurality of control valves; the control system comprises: a proportion calculation module, configured to calculate data obtained by the indoor unit start state detector, the indoor temperature sensor and the outdoor temperature sensor to obtain a capacity demand proportion and an indoor unit start proportion; an opening control module, configured to control the opening of the plurality of control valves according to the capacity demand proportion and the indoor unit start proportion; and adjust the flow of the refrigerant by controlling the opening of the plurality of control valves; wherein the number of the control valves is not less than two.

10. An electronic device, comprising: The electronic device comprises a memory and a processor, the memory stores a computer program, and the processor implements the method of any one of claims 1 to 8 when executing the computer program.

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