Compressor control method and device, medium and air conditioner

Abstract

According to the compressor control method and device, the medium and the air conditioner, vibration risk parameters of a compressor are obtained, an energy efficiency mode or a vibration suppression mode is triggered according to the vibration risk parameters, and target torque compensation coefficients and target operation frequencies in the two modes are correspondingly determined to control operation of the compressor. According to the scheme, the limitation of a traditional single frequency-torque compensation coefficient mapping relation is broken through, the regulation and control strategy can be dynamically switched according to the vibration risk, and energy efficiency improvement is guaranteed through the adaptive compensation coefficient and frequency when the energy efficiency mode is triggered; and when the vibration suppression mode is triggered, the mechanical resonance under the low-frequency working condition is effectively suppressed by the corresponding parameter combination, and the operation stability is improved, so that the precise balance between the energy efficiency improvement and the operation stability optimization is realized.

Description

Technical Field

[0001] This invention relates to the field of air conditioner technology, and in particular to a compressor control method, device, medium, and air conditioner. Background Technology

[0002] Mechanical resonance is particularly prominent when air conditioning compressors operate at low frequencies (e.g., 10–50Hz). Traditional control methods rely solely on a single frequency-torque compensation coefficient mapping relationship for regulation, which is insufficient to adapt to dynamic load changes across the entire frequency range. Ultimately, this makes it difficult to resolve the contradiction between improving compressor energy efficiency and optimizing operational stability. Summary of the Invention

[0003] Therefore, it is necessary to provide compressor control methods, devices, media, and air conditioners to solve the problem of the contradiction between the two requirements of energy efficiency improvement and operational stability optimization in existing technologies.

[0004] In a first aspect, embodiments of this application provide a compressor control method, the method comprising:

[0005] Obtain vibration risk parameters of the compressor; wherein, the vibration risk parameters are parameters used to characterize the degree of risk of mechanical resonance occurring during the operation of the air conditioning compressor; When the vibration risk parameter triggers the operating conditions of the energy efficiency mode, a first target torque compensation coefficient and a first target operating frequency under the energy efficiency mode are determined, and the operation of the compressor is controlled based on the first target torque compensation coefficient and the first target operating frequency. When the vibration risk parameter triggers the vibration suppression mode, the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode are determined, and the operation of the compressor is controlled based on the second target torque compensation coefficient and the second target operating frequency.

[0006] In some embodiments of this application, the vibration risk parameters include at least one of the compressor's current harmonic amplitude, torque fluctuation rate, and winding temperature fluctuation rate. After obtaining the compressor's vibration risk parameters, the process further includes: If, within a first preset time period, the current harmonic amplitude meets a first condition, the torque fluctuation rate meets a second condition, and the winding temperature meets a third condition, then the vibration risk parameter is determined to trigger the operating conditions of the energy efficiency mode; wherein, the first condition is that the current harmonic amplitude is less than or equal to a first harmonic amplitude threshold, the second condition is that the torque fluctuation rate is less than or equal to a first fluctuation rate threshold, and the third condition is that the winding temperature is less than or equal to a second fluctuation rate threshold; If the current harmonic amplitude does not meet the first condition, and / or the torque fluctuation rate does not meet the second condition, and / or the winding temperature does not meet the third condition, then the vibration risk parameter is determined to be the operating condition for triggering the vibration suppression mode.

[0007] In some embodiments of this application, determining the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode includes: In the energy efficiency mode, the operating frequency at which the compressor's energy efficiency ratio is at its maximum is determined as the first target operating frequency; Obtain the first mapping relationship, and determine the torque compensation coefficient corresponding to the first target operating frequency in the first mapping relationship as the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

[0008] In some embodiments of this application, the method for determining the first mapping relationship includes: Obtain the first test matrix; wherein, the first test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The first test matrix is ​​filtered based on the first screening condition to obtain the filtered first test matrix; wherein, the first screening condition includes the vibration amplitude being less than the first vibration amplitude threshold, the current harmonic amplitude being less than the second harmonic amplitude threshold, the torque fluctuation rate being less than the second fluctuation rate threshold, and the winding temperature being less than the first temperature threshold. In the first test matrix after screening, a torque compensation coefficient that maximizes the upper limit of the operating frequency is matched for each operating frequency to obtain the first mapping relationship.

[0009] In some embodiments of this application, controlling the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency includes: Obtain the compressor's current operating frequency and current torque compensation coefficient; The current operating frequency is increased at a preset first rate, and the current torque compensation coefficient is updated based on the first mapping relationship and the current operating frequency until the current operating frequency is equal to the first target operating frequency and the current torque compensation coefficient is equal to the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

[0010] In some embodiments of this application, determining the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode includes: In the vibration suppression mode, the operating frequency at which the vibration amplitude of the compressor is minimized is determined as the second target operating frequency; Obtain the second mapping relationship, and determine the torque compensation coefficient corresponding to the second target operating frequency in the second mapping relationship as the second target torque compensation coefficient; wherein, the second mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the vibration suppression effect of the compressor.

[0011] In some embodiments of this application, the method for determining the second mapping relationship includes: Obtain the second test matrix; wherein, the second test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The second test matrix is ​​filtered based on the second screening conditions to obtain the filtered second test matrix; wherein, the second screening conditions include the vibration amplitude being less than the second vibration amplitude threshold, the current harmonic amplitude being less than the third harmonic amplitude threshold, the torque fluctuation rate being less than the third fluctuation rate threshold, and the winding temperature being less than the second temperature threshold. In the second test matrix after screening, a torque compensation coefficient that minimizes torque ripple is matched for each operating frequency to obtain a second mapping relationship.

[0012] In some embodiments of this application, controlling the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency includes: Obtain the compressor's current operating frequency and current torque compensation coefficient; Calculate the difference between the second target torque compensation coefficient and the current torque compensation coefficient to obtain the coefficient difference; The current operating frequency is reduced at a preset second rate, and the current torque compensation coefficient is proportionally adjusted based on the time ratio between the reduction time and the total target adjustment time and the coefficient difference, until the current operating frequency is equal to the second target operating frequency and the current torque compensation coefficient is equal to the second target torque compensation coefficient.

[0013] In some embodiments of this application, the first target torque compensation coefficient is determined by the first target operating frequency based on a first mapping relationship, wherein the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's energy efficiency; the second target torque compensation coefficient is determined by the second target operating frequency based on a second mapping relationship, wherein the second mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's vibration suppression effect; the method further includes: Every second preset time interval, the torque compensation coefficient corresponding to each operating frequency in the first mapping relationship is updated based on the first attenuation coefficient; wherein, the first attenuation coefficient and the second preset time interval are positively correlated. Every third preset time interval, the torque compensation coefficient corresponding to each operating frequency in the second mapping relationship is updated based on the second attenuation coefficient; wherein, the second attenuation coefficient is positively correlated with the third preset time interval.

[0014] Secondly, embodiments of this application also provide a compressor control device, the compressor control device comprising: The parameter acquisition module is used to acquire the vibration risk parameters of the compressor; wherein, the vibration risk parameters are parameters used to characterize the degree of risk of mechanical resonance occurring during the operation of the air conditioning compressor; The first operating module is used to determine the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode when the vibration risk parameter triggers the operating conditions of the energy efficiency mode, and to control the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency. The second operating module is used to determine the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode when the vibration risk parameter triggers the vibration suppression mode operating condition, and to control the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency.

[0015] Thirdly, this application also provides an air conditioner, which includes a memory, a processor, and a computer program stored in the memory and executable on the processor. When the computer program is executed by the processor, it implements the steps in the compressor control method described above.

[0016] Fourthly, embodiments of this application also provide a computer-readable storage medium storing a computer program, which, when executed by a processor, implements the steps in the compressor control method described above.

[0017] Fifthly, embodiments of this application also provide a computer program product or computer program, which includes computer instructions stored in a computer-readable storage medium. A processor of a computer device reads the computer instructions from the computer-readable storage medium and executes the computer instructions, causing the computer device to perform the methods provided in the various optional implementations described in embodiments of this application.

[0018] This invention provides a compressor control method, device, medium, and air conditioner. By acquiring the vibration risk parameters of the compressor, it triggers either an energy efficiency mode or a vibration suppression mode based on the vibration risk parameters, and determines the target torque compensation coefficient and target operating frequency for each mode to control the compressor operation. This solution breaks the limitations of the traditional single frequency-torque compensation coefficient mapping relationship and can dynamically switch the control strategy according to the vibration risk. When the energy efficiency mode is triggered, it ensures energy efficiency improvement with an appropriate compensation coefficient and frequency. When the vibration suppression mode is triggered, it effectively suppresses mechanical resonance under low-frequency conditions and improves operational stability with the corresponding parameter combination, thereby achieving a precise balance between energy efficiency improvement and operational stability optimization. Attached Figure Description

[0019] 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 only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] in: Figure 1 This is a flowchart illustrating the compressor control method. Figure 2 A flowchart illustrating the process for determining the first target torque compensation coefficient and the first target operating frequency under energy efficiency mode; Figure 3 This is a schematic diagram of the process for controlling the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency; Figure 4 A flowchart illustrating the process for determining the second target torque compensation coefficient and the second target operating frequency under vibration suppression mode; Figure 5 This is a schematic diagram illustrating the process of controlling the compressor's operation based on the second target torque compensation coefficient and the second target operating frequency. Figure 6 This is a schematic diagram of the compressor control device. Figure 7 This is a structural block diagram of an air conditioner. Detailed Implementation

[0021] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0022] The terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish different objects, not to describe a specific order. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion. For example, a process, method, system, product, or apparatus that includes a series of steps or units is not limited to the listed steps or units, but may optionally include steps or units not listed, or may optionally include other steps or units inherent to these processes, methods, products, or apparatuses.

[0023] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0024] This invention provides a compressor control method, apparatus, medium, and air conditioner. In some embodiments of this application, the provided compressor control method can be applied to an air conditioner. Specifically, the air conditioner can be applied to different scenarios, including but not limited to industrial air conditioners or household air conditioners. In some embodiments of this application, the air conditioner can be a single unit, such as a cabinet air conditioner or a wall-mounted air conditioner; in some embodiments of this application, the air conditioner can also be a central air conditioning system composed of multiple air conditioner units, such as a multi-split air conditioner, an air-cooled heat pump system, or an air conditioning system with heat recovery function.

[0025] Please see Figure 1 , Figure 1 This is a flowchart illustrating a compressor control method provided in an embodiment of this application. Although the logical sequence is shown in the flowchart, in some cases, the steps shown or described may be performed in a different order than that shown in the figures. Specifically, the specific flow of the compressor control method is as follows: S101, obtain the vibration risk parameters of the compressor.

[0026] Among them, the vibration risk parameter refers to the parameter used to characterize the risk level of mechanical resonance during the operation of the air conditioning compressor.

[0027] Optionally, the vibration risk parameters include at least one of the compressor's current harmonic amplitude, torque fluctuation rate, and winding temperature fluctuation rate.

[0028] Optionally, the process of obtaining the current harmonic amplitude includes: firstly, acquiring the three-phase stator current signal during compressor operation using a current sensor; converting the current signal in the three-phase stationary coordinate system to the αβ two-phase stationary coordinate system using Clarke transform; then converting it to the current signal in the dq two-phase rotating coordinate system using Park transform; subsequently, performing spectrum analysis on the converted current signal using Fast Fourier Transform (FFT) to separate the fundamental current and each harmonic current; finally, calculating the effective value of each harmonic current and taking the harmonic component with the largest amplitude as the current harmonic amplitude.

[0029] Optionally, the process of obtaining the torque fluctuation rate includes: firstly, calculating the instantaneous torque based on the dq-axis current decoupling, the calculation formula of which is: ,in, This refers to the instantaneous torque; This represents the number of pole pairs of the motor. For d-axis flux linkage; For q-axis flux linkage; The current component is the d-axis component; This represents the q-axis current component. Multiple sets of instantaneous torque data are continuously collected within a preset statistical time period, and the mean and standard deviation of these data sets are calculated. The ratio of the standard deviation to the mean is ultimately determined as the torque ripple rate.

[0030] Optionally, the process of obtaining the winding temperature fluctuation rate includes: firstly, continuously collecting the winding temperature data within a set period using a temperature sensor embedded inside the compressor motor winding; then calculating the mean and standard deviation of the set of temperature data within that period; and finally defining the ratio of the standard deviation to the mean as the winding temperature fluctuation rate.

[0031] In some embodiments of this application, after obtaining the vibration risk parameters of the compressor in step S101, the following steps are further performed: if the current harmonic amplitude meets the first condition, the torque fluctuation rate meets the second condition, and the winding temperature meets the third condition within a first preset time period, then the vibration risk parameters are determined to trigger the operating conditions of the energy efficiency mode. If the current harmonic amplitude does not meet the first condition, and / or the torque fluctuation rate does not meet the second condition, and / or the winding temperature does not meet the third condition, then the vibration risk parameters are determined to trigger the operating conditions of the vibration suppression mode.

[0032] The first condition is that the current harmonic amplitude is less than or equal to the first harmonic amplitude threshold; the second condition is that the torque fluctuation rate is less than or equal to the first fluctuation rate threshold; and the third condition is that the winding temperature is less than or equal to the second fluctuation rate threshold.

[0033] For example, the first preset duration is set to 10 minutes, the first harmonic amplitude threshold is set to 5%, the first volatility threshold is set to 4%, and the second volatility threshold is set to 2°C. Of course, other values ​​can also be set, which are not limited here.

[0034] Understandably, a larger current harmonic amplitude indicates more severe current distortion, meaning lower electromagnetic conversion efficiency within the compressor motor, greater energy loss, and increased motor vibration, resulting in a higher risk of resonance. Conversely, a smaller current harmonic amplitude indicates a current waveform closer to an ideal sine wave, more efficient electromagnetic conversion, less energy loss, smoother motor operation, and a lower risk of resonance. A larger torque ripple rate indicates more drastic fluctuations in the compressor's current output torque, which can easily cause component vibration and wear, resulting in a higher risk of resonance. Conversely, a smaller torque ripple rate indicates a more balanced torque output, smoother mechanical load operation, more even component stress, and a lower risk of resonance. A larger winding temperature ripple rate indicates more drastic fluctuations in the current winding temperature, which can affect motor performance parameters and result in a higher risk of resonance. Conversely, a smaller winding temperature ripple rate indicates gentler winding temperature changes, more stable motor performance, and a lower risk of resonance. Therefore, in the first case, it indicates that the compressor is operating stably and the risk of resonance is low. In this case, the energy efficiency mode is triggered to prioritize improving energy utilization efficiency. In the second case, if any one or more parameters do not meet the corresponding threshold requirements, it indicates that the compressor has a high risk of mechanical resonance. In this case, the vibration suppression mode needs to be triggered to suppress vibration and ensure operational stability.

[0035] S102, when the vibration risk parameter triggers the operating conditions of the energy efficiency mode, determine the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode, and control the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency.

[0036] Among them, the energy efficiency mode refers to the operation control mode aimed at improving the energy utilization efficiency of the compressor. The first target torque compensation coefficient is the target proportional coefficient used to correct the output torque of the compressor motor in the energy efficiency mode. The first target operating frequency is the target operating frequency that the compressor needs to maintain stably in the energy efficiency mode.

[0037] In some embodiments of this application, such as Figure 2 As shown, S102 determines the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode, including steps S201-S202, as follows: S201, in energy efficiency mode, the operating frequency at which the compressor's energy efficiency ratio is at its maximum is determined as the first target operating frequency.

[0038] Optionally, before the compressor leaves the factory, a set test platform is used to simulate typical operating conditions such as different ambient temperatures, loads, and power supply voltages. The operating frequency is traversed in a fixed step of 1Hz within a specific frequency range. The input power and cooling / heating capacity at each frequency are recorded and the energy efficiency ratio is calculated. The frequency corresponding to the peak energy efficiency ratio under each operating condition is selected and a "operating condition-optimal frequency" lookup table is generated and stored in the controller. In energy efficiency mode, after identifying the current operating condition, the corresponding frequency is directly retrieved from the lookup table as the first target operating frequency.

[0039] S202, obtain the first mapping relationship, and determine the torque compensation coefficient corresponding to the first target operating frequency in the first mapping relationship as the first target torque compensation coefficient.

[0040] The first mapping relationship is the mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

[0041] Optionally, the first mapping relationship is retrieved from the static parameter table stored in the controller, and the torque compensation coefficient that matches the first target operating frequency in the first mapping relationship is found and extracted. This coefficient is the first target torque compensation coefficient in the energy efficiency mode. Its function is to cooperate with the first target operating frequency to further optimize the torque output of the compressor and ensure that the energy efficiency is always maintained at the highest level at this operating frequency without resonance.

[0042] In some embodiments of this application, the determination of the first mapping relationship in S202 is specifically as follows: A first test matrix is ​​obtained. The first test matrix is ​​filtered based on a first filtering condition to obtain a filtered first test matrix. In the filtered first test matrix, a torque compensation coefficient that maximizes the upper limit of the operating frequency is matched for each operating frequency to obtain the first mapping relationship.

[0043] The first test matrix characterizes the compressor's vibration amplitude, current harmonic amplitude, torque fluctuation rate, and winding temperature under different operating frequencies and torque compensation coefficients during the test environment. The first screening criteria include a vibration amplitude less than a first vibration amplitude threshold, a current harmonic amplitude less than a second harmonic amplitude threshold, a torque fluctuation rate less than a second fluctuation rate threshold, and a winding temperature less than a first temperature threshold. The upper limit of the operating frequency refers to the highest operating frequency at which the compressor can operate continuously without mechanical resonance under a specific torque compensation coefficient.

[0044] Optionally, the first test matrix is ​​obtained as follows: First, a professional test environment is built to simulate the typical operating conditions of the compressor. A test plan is designed for the 10-50Hz low-frequency range (the range where mechanical resonance occurs frequently). 41 operating frequency test points are set with a step size of 1Hz. At each frequency point, 20 sets of torque compensation coefficient parameters are set from 5% to 100% with a step size of 5%. For each set of "operating frequency-torque compensation coefficient" combination, the vibration amplitude (XYZ three-axis RMS value), current harmonic amplitude, torque fluctuation rate and winding temperature are continuously collected within 30 seconds. Finally, the first test matrix containing 41×20=820 sets of data is formed, which comprehensively covers the key operating data of the compressor under different combinations of operating parameters.

[0045] Optionally, the first vibration amplitude threshold is set to 0.8g, the second harmonic amplitude threshold is set to 4%, the second volatility threshold is set to 3%, and the first temperature threshold is set to 70℃. Other values ​​can also be used, and are not limited here. Each of the 820 data sets in the first test matrix is ​​verified, and invalid data combinations that do not meet the requirement of "all four conditions being met simultaneously" are removed. Only valid data where all parameters are within safe ranges are retained, resulting in the filtered first test matrix, which provides a reliable data foundation for subsequent optimal parameter matching.

[0046] Optionally, taking the 15Hz frequency group as an example, among the filtered valid data, the torque compensation coefficient (e.g., 25%) that can support the compressor to run stably up to the highest frequency (e.g., 50Hz) is finally selected as the optimal value at that frequency; according to this logic, the corresponding optimal torque compensation coefficient is matched for each of the 41 operating frequencies, and finally the first mapping relationship of "operating frequency - torque compensation coefficient" is formed.

[0047] In some embodiments of this application, such as Figure 3 As shown, S102 controls the compressor's operation based on the first target torque compensation coefficient and the first target operating frequency, including steps S301-S302, as follows: S301, obtain the compressor's current operating frequency and current torque compensation coefficient.

[0048] S302, the current operating frequency is increased at a preset first rate, and the current torque compensation coefficient is updated based on the first mapping relationship and the current operating frequency until the current operating frequency is equal to the first target operating frequency and the current torque compensation coefficient is equal to the first target torque compensation coefficient.

[0049] Optionally, the first rate is set to 0.5 Hz / s, but other values ​​are also possible and are not limited here.

[0050] Optionally, during the entire frequency adjustment process, since the first mapping relationship clearly defines the optimal torque compensation coefficient for different operating frequencies, as the current operating frequency is gradually increased, a torque compensation coefficient matching the current frequency can be retrieved in real time from the first mapping relationship to replace the original current torque compensation coefficient. This ensures that a suitable torque compensation coefficient is matched at each frequency adjustment stage, maintaining balanced torque output and stable operation. The entire adjustment process continues until the current operating frequency accurately reaches the first target operating frequency, and the current torque compensation coefficient perfectly matches the first target torque compensation coefficient. At this point, the compressor enters a stable operating state with optimal energy efficiency.

[0051] Optionally, the calculated first target torque compensation coefficient will dynamically correct the duty cycle, carrier frequency, or modulation wave phase of the compressor PWM signal through the compensation intensity corresponding to the coefficient, thereby precisely adjusting the stator voltage and current output of the motor, so that the motor outputs torque more efficiently at the target frequency.

[0052] S103, when the vibration risk parameter triggers the vibration suppression mode, determine the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode, and control the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency.

[0053] Among them, vibration suppression mode refers to the operating control mode aimed at suppressing compressor mechanical resonance. The second target torque compensation coefficient is the target proportional coefficient used to correct the compressor motor output torque in vibration suppression mode. The second target operating frequency is the target operating frequency that the compressor needs to stably maintain in vibration suppression mode.

[0054] In some embodiments of this application, such as Figure 4 As shown, determining the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode in S103 includes steps S401-S402, as follows: S401, in vibration suppression mode, the operating frequency at which the compressor's vibration amplitude is minimized is determined as the second target operating frequency.

[0055] Optionally, before the compressor leaves the factory, a professional testing platform is used to simulate typical operating conditions such as different ambient temperatures, loads, and power supply voltages. The operating frequency is traversed in the 10-50Hz low-frequency range with fixed steps of 1Hz. Vibration amplitude (XYZ three-axis RMS value) is collected by a three-axis accelerometer. The frequency with the smallest vibration amplitude under each operating condition is selected and a "operating condition-optimal vibration suppression frequency" reference table is generated and stored in the controller. In vibration suppression mode, the current operating condition and vibration status are identified in real time, and the corresponding frequency is directly retrieved from the reference table as the second target operating frequency.

[0056] S402, obtain the second mapping relationship, and determine the torque compensation coefficient corresponding to the second target operating frequency in the second mapping relationship as the second target torque compensation coefficient.

[0057] The second mapping relationship is the mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the vibration suppression effect of the compressor.

[0058] Optionally, the second mapping relationship can be retrieved from the static parameter table stored in the controller, and the torque compensation coefficient that matches the second target operating frequency in the second mapping relationship can be found and extracted. This coefficient is the second target torque compensation coefficient in the vibration suppression mode. Its function is to cooperate with the second target operating frequency, optimize the smoothness of the compressor motor torque output, and suppress mechanical resonance to the maximum extent.

[0059] In some embodiments of this application, the determination of the second mapping relationship in S402 is specifically as follows: A second test matrix is ​​obtained. The second test matrix is ​​filtered based on the second filtering conditions to obtain a filtered second test matrix. In the filtered second test matrix, a torque compensation coefficient that minimizes torque fluctuation is matched for each operating frequency to obtain the second mapping relationship.

[0060] The second test matrix characterizes the compressor's vibration amplitude, current harmonic amplitude, torque fluctuation rate, and winding temperature under different operating frequencies and torque compensation coefficients during the test environment. The second screening criteria include a vibration amplitude less than a second vibration amplitude threshold, a current harmonic amplitude less than a third harmonic amplitude threshold, a torque fluctuation rate less than a third fluctuation rate threshold, and a winding temperature less than a second temperature threshold.

[0061] Optionally, the second test matrix is ​​obtained as follows: First, a professional test environment is built to simulate the typical operating conditions of the compressor. A test plan is designed for the 10-50Hz low-frequency range (the range where mechanical resonance occurs frequently). 41 operating frequency test points are set with a step size of 1Hz. At each frequency point, 20 sets of torque compensation coefficient parameters are set from 5% to 100% in 5% steps. For each set of "operating frequency-torque compensation coefficient" combination, the vibration amplitude (XYZ three-axis RMS value), current harmonic amplitude, torque fluctuation rate and winding temperature are continuously collected within 30 seconds. Finally, a second test matrix containing 41×20=820 sets of data is formed, which comprehensively covers the key operating data of the compressor under different combinations of operating parameters.

[0062] Optionally, the second vibration amplitude threshold is set to 0.5g, the third harmonic amplitude threshold is set to 3%, the third volatility threshold is set to 2%, and the second temperature threshold is set to 65℃. Other values ​​can also be used, and are not limited here. Each of the 820 data sets in the second test matrix is ​​verified, and invalid data combinations that do not meet the requirement of "all four conditions being met simultaneously" are removed. Only valid data where all parameters are within safe ranges are retained, resulting in the final filtered second test matrix, providing a reliable data foundation for subsequent optimal parameter matching.

[0063] Optionally, taking the 20Hz frequency group as an example, in the filtered valid data, the torque fluctuation rate corresponding to different torque compensation coefficients is compared, and the torque compensation coefficient with the smallest torque fluctuation rate (e.g., 1.5%) (e.g., 30%) is finally selected as the optimal value at this frequency; according to this logic, the corresponding optimal torque compensation coefficient is matched for each of the 41 operating frequencies, and finally a second mapping relationship of "operating frequency - torque compensation coefficient" is formed.

[0064] In some embodiments of this application, such as Figure 5 As shown, S103 controls the compressor's operation based on the second target torque compensation coefficient and the second target operating frequency, including steps S501-S503, as follows: S501, obtain the compressor's current operating frequency and current torque compensation coefficient.

[0065] S502, calculate the difference between the second target torque compensation coefficient and the current torque compensation coefficient to obtain the coefficient difference.

[0066] S503, the current operating frequency is reduced at a preset second rate, and the current torque compensation coefficient is proportionally adjusted based on the time ratio and coefficient difference between the reduction time and the total target adjustment time, until the current operating frequency is equal to the second target operating frequency and the current torque compensation coefficient is equal to the second target torque compensation coefficient.

[0067] Optionally, the second rate is set to 1 Hz / s, but it can also be other values, which are not limited here.

[0068] Optionally, the formula for proportionally adjusting the current torque compensation coefficient based on the time ratio and coefficient difference between the reduction time and the total target adjustment time is as follows: ,in, To adjust the compensation coefficient at time t after the start; The difference in coefficients; This is the current current compensation coefficient; This is the second target torque compensation coefficient; For time proportions; The total target adjustment time can be set to 30 seconds by default, or it can be linked to the load rate and extended to 60 seconds under heavy load. To adjust the downtime after the start.

[0069] It is understandable that the above embodiment reduces the current operating frequency at a uniform rate of the second speed, which can avoid the frequency change from aggravating the vibration. At the same time, based on the proportion of the reduction time to the total adjustment time, the torque compensation coefficient is gradually updated according to the coefficient difference, which can ensure that the torque output is synchronously adapted to the reduction of the frequency, thus suppressing mechanical resonance and avoiding the operation fluctuation caused by parameter change, and finally achieving the effect of rapid reduction of vibration amplitude and stable and reliable operation.

[0070] Optionally, the calculated second target torque compensation coefficient will dynamically correct the duty cycle, carrier frequency, or modulation wave phase of the compressor PWM signal through the compensation intensity corresponding to the coefficient, thereby precisely adjusting the stator voltage and current output of the motor, thus offsetting the torque pulsation caused by resonance and suppressing current harmonics and mechanical vibration.

[0071] The above embodiments obtain the vibration risk parameters of the compressor, trigger either the energy efficiency mode or the vibration suppression mode based on the vibration risk parameters, and determine the target torque compensation coefficient and target operating frequency for each mode to control the compressor operation. This solution breaks the limitations of the traditional single frequency-torque compensation coefficient mapping relationship and can dynamically switch the control strategy according to the vibration risk. When the energy efficiency mode is triggered, the appropriate compensation coefficient and frequency are used to ensure energy efficiency improvement. When the vibration suppression mode is triggered, the corresponding parameter combination is used to effectively suppress mechanical resonance under low-frequency conditions and improve operating stability, thereby achieving a precise balance between energy efficiency improvement and operating stability optimization.

[0072] In some embodiments of this application, the first target torque compensation coefficient is determined by the first target operating frequency based on a first mapping relationship. The first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's energy efficiency. The second target torque compensation coefficient is determined by the second target operating frequency based on a second mapping relationship. The second mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's vibration suppression effect. The compressor control method may also periodically execute the following steps: every second preset time interval, update the torque compensation coefficient corresponding to each operating frequency in the first mapping relationship based on the first attenuation coefficient. Every third preset time interval, update the torque compensation coefficient corresponding to each operating frequency in the second mapping relationship based on the second attenuation coefficient.

[0073] The first attenuation coefficient is positively correlated with the second preset duration. The second attenuation coefficient is positively correlated with the third preset duration.

[0074] For example, the second preset duration is 3 months, corresponding to a first attenuation coefficient of 1.02; the third preset duration is 6 months, corresponding to a second attenuation coefficient of 1.05 (the longer the duration, the larger the attenuation coefficient, which conforms to a positive correlation). During the compressor's operation, the first mapping relationship is automatically updated every 3 months. For example, the original torque compensation coefficient of 25% corresponding to 15Hz is updated to 25%×1.02=25.5%, and the 30% corresponding to 20Hz is updated to 30.6%. The second mapping relationship is updated every 6 months. For example, the original coefficient of 35% corresponding to 25Hz is updated to 35%×1.05=36.75%, and the 40% corresponding to 30Hz is updated to 42%. The compensation coefficient is gradually increased to adapt to the increased resonance risk caused by equipment aging.

[0075] Understandably, this embodiment aims to dynamically adapt to the performance degradation of the compressor after long-term operation and maintain the effectiveness of the mapping relationship. As usage time increases, compressor components wear down, performance declines, and the risk of mechanical resonance gradually increases. The magnitude of the torque compensation coefficient directly affects the ability to counteract resonance; specifically, a larger coefficient results in higher compensation strength and a more significant vibration suppression effect. By periodically adjusting and updating the torque compensation coefficient in the two mapping relationships based on the attenuation coefficient (positively correlated with duration), the performance loss caused by equipment aging can be slowly offset. This avoids energy efficiency reduction or increased vibration due to decreased adaptability of the original coefficients, ensuring the stability of energy efficiency and vibration suppression during long-term compressor operation.

[0076] To facilitate better implementation of the compressor control method of this application, this application also provides a compressor control device based on the above-described compressor control method. The meanings of the terms used are the same as in the compressor control method described above, and specific implementation details can be found in the descriptions of the method embodiments.

[0077] Please see Figure 6 , Figure 6 This is a schematic diagram of the compressor control device provided in the embodiments of this application, which may specifically include: The parameter acquisition module is used to acquire the vibration risk parameters of the compressor; among which, the vibration risk parameters are used to characterize the degree of risk of mechanical resonance occurring during the operation of the air conditioning compressor. The first operating module is used to determine the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode when the vibration risk parameter triggers the operating condition of the energy efficiency mode, and to control the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency. The second operation module is used to determine the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode when the vibration risk parameter triggers the vibration suppression mode, and to control the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency.

[0078] In the above embodiment, the parameter acquisition module is used to acquire the vibration risk parameters of the compressor. The first operation module and the second operation module are used to trigger the energy efficiency mode or the vibration suppression mode respectively based on the vibration risk parameters. The target torque compensation coefficient and the target operating frequency are determined for the two modes to control the operation of the compressor. This solution breaks the limitation of the traditional single frequency-torque compensation coefficient mapping relationship. It can dynamically switch the control strategy according to the vibration risk. When the energy efficiency mode is triggered, the appropriate compensation coefficient and frequency are used to ensure energy efficiency improvement. When the vibration suppression mode is triggered, the corresponding parameter combination is used to effectively suppress mechanical resonance under low-frequency conditions and improve the operating stability, thereby achieving a precise balance between energy efficiency improvement and operating stability optimization.

[0079] In some embodiments of this application, the vibration risk parameters include at least one of the compressor's current harmonic amplitude, torque fluctuation rate, and winding temperature fluctuation rate. After acquiring the compressor's vibration risk parameters, the parameter acquisition module is further used for: If, within a first preset time period, the current harmonic amplitude meets the first condition, the torque fluctuation rate meets the second condition, and the winding temperature meets the third condition, then the vibration risk parameter is determined to trigger the operating condition of the energy efficiency mode; wherein, the first condition is that the current harmonic amplitude is less than or equal to the first harmonic amplitude threshold, the second condition is that the torque fluctuation rate is less than or equal to the first fluctuation rate threshold, and the third condition is that the winding temperature is less than or equal to the second fluctuation rate threshold. If the current harmonic amplitude does not meet the first condition, and / or the torque fluctuation rate does not meet the second condition, and / or the winding temperature does not meet the third condition, then the vibration risk parameter is determined to trigger the vibration suppression mode operating condition.

[0080] In some embodiments of this application, the first operating module determines a first target torque compensation coefficient and a first target operating frequency under energy efficiency mode, including: In energy efficiency mode, the operating frequency at which the compressor's energy efficiency ratio is at its maximum is determined as the first target operating frequency; Obtain the first mapping relationship, and determine the torque compensation coefficient corresponding to the first target operating frequency in the first mapping relationship as the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

[0081] In some embodiments of this application, the method for determining the first mapping relationship includes: Obtain the first test matrix; wherein, the first test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The first test matrix is ​​filtered based on the first screening conditions to obtain the filtered first test matrix; wherein, the first screening conditions include the vibration amplitude being less than the first vibration amplitude threshold, the current harmonic amplitude being less than the second harmonic amplitude threshold, the torque fluctuation rate being less than the second fluctuation rate threshold, and the winding temperature being less than the first temperature threshold. In the first test matrix after screening, a torque compensation coefficient that maximizes the upper limit of the operating frequency is matched for each operating frequency to obtain the first mapping relationship.

[0082] In some embodiments of this application, the first operating module controls the operation of the compressor based on a first target torque compensation coefficient and a first target operating frequency, including: Obtain the compressor's current operating frequency and current torque compensation coefficient; The current operating frequency is increased at a preset first rate, and the current torque compensation coefficient is updated based on the first mapping relationship and the current operating frequency until the current operating frequency equals the first target operating frequency and the current torque compensation coefficient equals the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

[0083] In some embodiments of this application, the second operating module determines the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode, including: In vibration suppression mode, the operating frequency at which the compressor's vibration amplitude is minimized is determined as the second target operating frequency; Obtain the second mapping relationship, and determine the torque compensation coefficient corresponding to the second target operating frequency in the second mapping relationship as the second target torque compensation coefficient; wherein, the second mapping relationship is the mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the vibration suppression effect of the compressor.

[0084] In some embodiments of this application, the method for determining the second mapping relationship includes: Obtain the second test matrix; wherein, the second test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The second test matrix is ​​filtered based on the second screening conditions to obtain the filtered second test matrix; wherein, the second screening conditions include the vibration amplitude being less than the second vibration amplitude threshold, the current harmonic amplitude being less than the third harmonic amplitude threshold, the torque fluctuation rate being less than the third fluctuation rate threshold, and the winding temperature being less than the second temperature threshold. In the second test matrix after screening, a torque compensation coefficient that minimizes torque ripple is matched for each operating frequency to obtain a second mapping relationship.

[0085] In some embodiments of this application, the second operating module controls the operation of the compressor based on a second target torque compensation coefficient and a second target operating frequency, including: Obtain the compressor's current operating frequency and current torque compensation coefficient; Calculate the difference between the second target torque compensation coefficient and the current torque compensation coefficient to obtain the coefficient difference; The current operating frequency is reduced at a preset second rate, and the current torque compensation coefficient is proportionally adjusted based on the time ratio and coefficient difference between the reduction time and the total target adjustment time, until the current operating frequency equals the second target operating frequency and the current torque compensation coefficient equals the second target torque compensation coefficient; wherein, the second mapping relationship is the mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the vibration suppression effect of the compressor.

[0086] In some embodiments of this application, the first target torque compensation coefficient is determined by the first target operating frequency based on a first mapping relationship, which is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's energy efficiency. The second target torque compensation coefficient is determined by the second target operating frequency based on a second mapping relationship, which is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the compressor's vibration suppression effect. The compressor control device is further used for: Every second preset time interval, the torque compensation coefficient corresponding to each operating frequency in the first mapping relationship is updated based on the first attenuation coefficient; wherein, the first attenuation coefficient and the second preset time interval are positively correlated. Every third preset time interval, the torque compensation coefficient corresponding to each operating frequency in the second mapping relationship is updated based on the second attenuation coefficient; wherein, the second attenuation coefficient and the third preset time interval are positively correlated.

[0087] In addition, this application also provides an air conditioner, such as Figure 7 As shown, it illustrates the structural diagram of the air conditioner involved in this application, specifically: The air conditioner may include components such as a processor 701 with one or more processing cores, a memory 702 with one or more computer-readable storage media, a power supply 703, and an input unit 704. Those skilled in the art will understand that... Figure 7 The air conditioner structure shown does not constitute a limitation on the air conditioner and may include more or fewer components than shown, or combine certain components, or have different component arrangements. Wherein: The processor 701 is the control center of the air conditioner. It connects to various parts of the air conditioner via various interfaces and lines. By running or executing software programs and / or modules stored in the memory 702, and by calling data stored in the memory 702, it performs various functions and processes data, thereby providing overall monitoring of the air conditioner. Optionally, the processor 701 may include one or more processing cores; preferably, the processor 701 may integrate an application processor and a modem processor, wherein the application processor mainly handles the operating system, user interface, and applications, and the modem processor mainly handles wireless communication. It is understood that the modem processor may not be integrated into the processor 701.

[0088] The memory 702 can be used to store software programs and modules. The processor 701 executes various functional applications and data processing by running the software programs and modules stored in the memory 702. The memory 702 may mainly include a program storage area and a data storage area. The program storage area may store the operating system, application programs required for at least one function, etc.; the data storage area may store data created based on the use of the air conditioner, etc. In addition, the memory 702 may include high-speed random access memory, and may also include non-volatile memory, such as at least one disk storage device, flash memory device, or other volatile solid-state storage device. Accordingly, the memory 702 may also include a memory controller to provide the processor 701 with access to the memory 702.

[0089] The air conditioner also includes a power supply 703 that supplies power to the various components. Preferably, the power supply 703 can be logically connected to the processor 701 through a power management system, thereby enabling functions such as charging, discharging, and power consumption management through the power management system. The power supply 703 may also include one or more DC or AC power supplies, recharging systems, power equipment debugging circuits, power converters or inverters, power status indicators, and other arbitrary components.

[0090] The air conditioner may also include an input unit 704, which can be used to receive input digital or character information, and generate keyboard, mouse, joystick, optical or trackball signal inputs related to user settings and function control.

[0091] Although not shown, the air conditioner may also include a display unit, etc., which will not be described in detail here. Specifically, in this embodiment, the processor 701 in the air conditioner will load the executable files corresponding to the processes of one or more application programs into the memory 702 according to the following instructions, and the processor 701 will run the application programs stored in the memory 702 to realize the steps in any of the compressor control methods provided in this application embodiment: obtaining the vibration risk parameters of the compressor; when the vibration risk parameters trigger the operating conditions of the energy efficiency mode, determining the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode, and controlling the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency; when the vibration risk parameters trigger the operating conditions of the vibration suppression mode, determining the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode, and controlling the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency.

[0092] The above embodiments obtain the vibration risk parameters of the compressor, trigger either the energy efficiency mode or the vibration suppression mode according to the vibration risk parameters, and determine the target torque compensation coefficient and target operating frequency for each mode to control the compressor operation. This solution breaks the limitations of the traditional single frequency-torque compensation coefficient mapping relationship and can dynamically switch the control strategy according to the vibration risk. When the energy efficiency mode is triggered, the appropriate compensation coefficient and frequency are used to ensure energy efficiency improvement. When the vibration suppression mode is triggered, the corresponding parameter combination is used to effectively suppress mechanical resonance under low-frequency conditions and improve operating stability, thereby achieving a precise balance between energy efficiency improvement and operating stability optimization.

[0093] For details on the implementation of each of the above operations, please refer to the previous examples, which will not be repeated here.

[0094] Those skilled in the art will understand that all or part of the steps in the various methods of the above embodiments can be performed by instructions, or by instructions controlling related hardware. These instructions can be stored in a computer-readable storage medium and loaded and executed by a processor.

[0095] Therefore, this application provides a computer-readable storage medium storing a computer program that can be loaded by a processor to execute the steps of any of the compressor control methods provided in this application.

[0096] For details on the implementation of each of the above operations, please refer to the previous examples, which will not be repeated here.

[0097] The computer-readable storage medium may include: read-only memory (ROM), random access memory (RAM), disk or optical disk, etc.

[0098] Since the instructions stored in the computer-readable storage medium can execute the steps of any of the compressor control methods provided in this application, the beneficial effects that any of the compressor control methods provided in this application can achieve can be realized, as detailed in the preceding embodiments, and will not be repeated here.

[0099] The above provides a detailed description of a compressor control method, apparatus, air conditioner, and computer-readable storage medium provided in this application. Specific examples have been used to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and core ideas of the present invention. At the same time, those skilled in the art will recognize that there will be changes in the specific implementation methods and application scope based on the ideas of the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A compressor control method, characterized in that, The method includes: Obtain vibration risk parameters of the compressor; wherein, the vibration risk parameters are parameters used to characterize the degree of risk of mechanical resonance occurring during the operation of the air conditioning compressor; When the vibration risk parameter triggers the operating conditions of the energy efficiency mode, a first target torque compensation coefficient and a first target operating frequency under the energy efficiency mode are determined, and the operation of the compressor is controlled based on the first target torque compensation coefficient and the first target operating frequency. When the vibration risk parameter triggers the vibration suppression mode, the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode are determined, and the operation of the compressor is controlled based on the second target torque compensation coefficient and the second target operating frequency.

2. The compressor control method according to claim 1, characterized in that, The vibration risk parameters include at least one of the compressor's current harmonic amplitude, torque fluctuation rate, and winding temperature fluctuation rate. After obtaining the compressor's vibration risk parameters, the process further includes: If, within a first preset time period, the current harmonic amplitude meets a first condition, the torque fluctuation rate meets a second condition, and the winding temperature meets a third condition, then the vibration risk parameter is determined to trigger the operating conditions of the energy efficiency mode; wherein, the first condition is that the current harmonic amplitude is less than or equal to a first harmonic amplitude threshold, the second condition is that the torque fluctuation rate is less than or equal to a first fluctuation rate threshold, and the third condition is that the winding temperature is less than or equal to a second fluctuation rate threshold; If the current harmonic amplitude does not meet the first condition, and / or the torque fluctuation rate does not meet the second condition, and / or the winding temperature does not meet the third condition, then the vibration risk parameter is determined to be the operating condition for triggering the vibration suppression mode.

3. The compressor control method according to claim 1, characterized in that, Determining the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode includes: In the energy efficiency mode, the operating frequency at which the compressor's energy efficiency ratio is at its maximum is determined as the first target operating frequency; Obtain the first mapping relationship, and determine the torque compensation coefficient corresponding to the first target operating frequency in the first mapping relationship as the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

4. The compressor control method according to claim 3, characterized in that, The method for determining the first mapping relationship includes: Obtain the first test matrix; wherein, the first test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The first test matrix is ​​filtered based on the first screening condition to obtain the filtered first test matrix; wherein, the first screening condition includes the vibration amplitude being less than the first vibration amplitude threshold, the current harmonic amplitude being less than the second harmonic amplitude threshold, the torque fluctuation rate being less than the second fluctuation rate threshold, and the winding temperature being less than the first temperature threshold. In the first test matrix after screening, a torque compensation coefficient that maximizes the upper limit of the operating frequency is matched for each operating frequency to obtain the first mapping relationship.

5. The compressor control method according to claim 1, characterized in that, The method of controlling the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency includes: Obtain the compressor's current operating frequency and current torque compensation coefficient; The current operating frequency is increased at a preset first rate, and the current torque compensation coefficient is updated based on the first mapping relationship and the current operating frequency until the current operating frequency is equal to the first target operating frequency and the current torque compensation coefficient is equal to the first target torque compensation coefficient; wherein, the first mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the energy efficiency of the compressor.

6. The compressor control method according to claim 1, characterized in that, Determining the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode includes: In the vibration suppression mode, the operating frequency at which the vibration amplitude of the compressor is minimized is determined as the second target operating frequency; Obtain the second mapping relationship, and determine the torque compensation coefficient corresponding to the second target operating frequency in the second mapping relationship as the second target torque compensation coefficient; wherein, the second mapping relationship is a mapping relationship between the operating frequency and the torque compensation coefficient constructed to maximize the vibration suppression effect of the compressor.

7. The compressor control method according to claim 6, characterized in that, The method for determining the second mapping relationship includes: Obtain the second test matrix; wherein, the second test matrix characterizes the vibration amplitude, current harmonic amplitude, torque fluctuation rate and winding temperature of the compressor under different operating frequencies and different torque compensation coefficients under the test environment; The second test matrix is ​​filtered based on the second screening conditions to obtain the filtered second test matrix; wherein, the second screening conditions include the vibration amplitude being less than the second vibration amplitude threshold, the current harmonic amplitude being less than the third harmonic amplitude threshold, the torque fluctuation rate being less than the third fluctuation rate threshold, and the winding temperature being less than the second temperature threshold. In the second test matrix after screening, a torque compensation coefficient that minimizes torque ripple is matched for each operating frequency to obtain a second mapping relationship.

8. The compressor control method according to claim 1, characterized in that, The method of controlling the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency includes: Obtain the compressor's current operating frequency and current torque compensation coefficient; Calculate the difference between the second target torque compensation coefficient and the current torque compensation coefficient to obtain the coefficient difference; The current operating frequency is reduced at a preset second rate, and the current torque compensation coefficient is proportionally adjusted based on the time ratio between the reduction time and the total target adjustment time and the coefficient difference, until the current operating frequency is equal to the second target operating frequency and the current torque compensation coefficient is equal to the second target torque compensation coefficient.

9. A compressor control device, characterized in that, The compressor control device includes: The parameter acquisition module is used to acquire the vibration risk parameters of the compressor; wherein, the vibration risk parameters are parameters used to characterize the degree of risk of mechanical resonance occurring during the operation of the air conditioning compressor; The first operating module is used to determine the first target torque compensation coefficient and the first target operating frequency under the energy efficiency mode when the vibration risk parameter triggers the operating conditions of the energy efficiency mode, and to control the operation of the compressor based on the first target torque compensation coefficient and the first target operating frequency. The second operating module is used to determine the second target torque compensation coefficient and the second target operating frequency under the vibration suppression mode when the vibration risk parameter triggers the vibration suppression mode operating condition, and to control the operation of the compressor based on the second target torque compensation coefficient and the second target operating frequency.

10. A computer-readable storage medium, characterized in that, The device stores a computer program that, when executed by a processor, causes the processor to perform the steps of the method as described in any one of claims 1 to 8.

11. An air conditioner, characterized in that, It includes a memory and a processor, the memory storing a computer program that, when executed by the processor, causes the processor to perform the steps of the method as described in any one of claims 1 to 8.

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