Real-time energy efficiency control method for a stationary air conditioner of a commercial vehicle

Abstract

The application relates to a real-time energy efficiency control method for a commercial vehicle stationary air conditioner, which comprises the following steps: S1, initializing the commercial vehicle stationary air conditioner system, and setting a cycle period, wherein the commercial vehicle stationary air conditioner system comprises a compressor and an evaporator connected with the compressor; S2, collecting operation data in each cycle period, and calculating the mass flow rate of the suction port of the compressor as the mass flow rate of the outlet of the evaporator; S3, respectively calculating the specific enthalpy of the outlet and the specific enthalpy of the inlet of the evaporator, and combining the mass flow rate to calculate the heat absorbed by the refrigerant in the evaporator as the system refrigerating capacity; S4, calculating the total power of the system according to a constructed total electric power model of the system, combining the refrigerating capacity to calculate the system energy efficiency in the cycle period, and performing energy efficiency control; and S5, returning to step S2 to update the system energy efficiency of the next cycle period, and realizing energy efficiency control. Compared with the prior art, the application has the advantages of low cost, efficient calculation and the like.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of energy efficiency control, in particular to a real-time energy efficiency control method for a commercial vehicle parked air conditioner. BACKGROUND

[0002] The application background of the commercial vehicle parked air conditioner is to provide air conditioning service for the driver continuously when the vehicle is turned off. The installed capacity of the parked air conditioner is nearly one million units per year. The main energy source of the air conditioner is the vehicle-mounted battery, which is generally 180Ah to 220Ah. The air conditioner refrigerating capacity is about 2000W to 2500W in summer. Therefore, the energy efficiency directly determines the time that the battery can support the continuous operation of the air conditioner.

[0003] In the prior art, patent application CN118935628A discloses a dynamic energy efficiency calculation method and device for an air conditioner, an air conditioner and a storage medium. The method comprises obtaining control parameters and environmental parameters of the air conditioner under test conditions; calculating the building heat load of the air conditioner under the test conditions based on the control parameters and the environmental parameters; calculating the dry bulb temperature and the wet bulb temperature of the indoor environment at different times under the test conditions according to the building heat load, the control parameters and the environmental parameters; adjusting the indoor side dry bulb temperature and the wet bulb temperature when the air conditioner is actually running based on the dry bulb temperature and the wet bulb temperature to calculate the dynamic energy efficiency of the air conditioner actually running, and obtaining the target dynamic energy efficiency. However, this method is for building air conditioners, not for vehicle air conditioners. The building wall heat load parameters and the vehicle metal heat load are different, and the glass proportion, orientation, etc. of the commercial vehicle are also different from the building. Therefore, this method cannot be directly applied to commercial vehicles. In addition, this method needs to collect more environmental parameters to calculate the heat load, which is not economical for commercial vehicles. It is also difficult to obtain stable parameters, and it cannot be applied to multiple scenarios, so the adaptability is poor. Patent application CN120056691A discloses an energy efficiency optimization method for a heat pump type thermal management system. The method collects environmental temperature, target temperature, actual temperature, high and low pressure side pressure and compressor power and other state parameters, and makes control decisions based on a deep Q network (DQN) model to adjust the compressor speed. The core is to use an adaptive discount factor, which is dynamically adjusted according to a system state index. The system state index is calculated by combining the current heat state deviation absolute value and the cycle pressure ratio. This invention makes DQN dynamically adjust the strategy focus according to the system deviation from the target and the running intensity, effectively balances the multiple and dynamic changes of the electric vehicle in terms of passenger comfort, battery health and range (energy efficiency), and improves the overall performance. This method is for the heat pump system of an electric vehicle. It calculates the cycle pressure ratio parameter, system state index and reward function, etc. It cannot calculate the actual parameters such as system refrigerating capacity and energy efficiency ratio in real time, and the method does not systematically construct the operation model and characteristics of the air conditioning system.

[0004] The energy efficiency of the current related products is calibrated by the laboratory under the rated operating condition, which cannot effectively evaluate the energy efficiency of the air conditioner in the actual vehicle running process, and further cannot directly support the improvement of the energy efficiency of the air conditioning system. SUMMARY

[0005] The purpose of the present application is to provide a real-time energy efficiency control method of a commercial vehicle parked air conditioner, which realizes real-time monitoring and control of dynamic energy consumption.

[0006] The purpose of the present application can be achieved by the following technical solutions:

[0007] A real-time energy efficiency control method of a commercial vehicle parked air conditioner, comprising the following steps:

[0008] S1, initializing a commercial vehicle parked air conditioning system, setting a cycle period, wherein the commercial vehicle parked air conditioning system comprises a compressor and an evaporator connected thereto;

[0009] S2, in each cycle period, collecting the running data of the commercial vehicle parked air conditioning system, calculating the mass flow rate of the suction port of the compressor as the mass flow rate of the evaporator outlet;

[0010] S3, respectively calculating the evaporator outlet specific enthalpy and the evaporator inlet specific enthalpy, and calculating the heat absorbed by the refrigerant in the evaporator as the refrigerating capacity of the commercial vehicle parked air conditioning system in combination with the mass flow rate of the evaporator outlet;

[0011] S4, calculating the system total power of the commercial vehicle parked air conditioning system according to the constructed system total power model, and calculating the system energy efficiency in this cycle period in combination with the refrigerating capacity to perform energy efficiency control;

[0012] S5, returning to step S2 to update the system energy efficiency of the next cycle period to realize energy efficiency control.

[0013] Further, the commercial vehicle parked air conditioning system further comprises a condenser fan, a condenser, a liquid accumulator, an electronic expansion valve, an evaporative fan and a plurality of temperature and pressure sensors, the condenser is connected with the liquid accumulator, the electronic expansion valve, the evaporator and the compressor in sequence, the condenser fan is installed above the condenser to form a condenser assembly with the condenser, and the evaporative fan is installed above the evaporator to form an evaporator assembly with the evaporator.

[0014] Further, the calculation expression of the mass flow rate of the suction port of the compressor is:

[0015] ,

[0016] In the formula, is the mass flow rate of the suction port of the compressor, also known as the refrigerant mass flow rate, is the volumetric flow rate, is the density, is the compressor speed, is the compressor displacement, is the specific volume.

[0017] Further, the specific volume is solved by the following PR equation:

[0018] ,

[0019] wherein, , are PR equation factors, respectively calculated by:

[0020] ,

[0021] ,

[0022] ,

[0023] wherein, is the pressure, is the gas constant, is the temperature, is the critical temperature, is the critical pressure, is the eccentric factor correlation parameter, is the eccentric factor.

[0024] Further, the evaporator outlet specific enthalpy and the evaporator inlet specific enthalpy are both composed of an ideal gas specific enthalpy and a residual specific enthalpy, wherein the calculation expression of the outlet specific enthalpy is:

[0025] ,

[0026] the calculation expression of the inlet specific enthalpy is:

[0027] ,

[0028] wherein, is the evaporator outlet specific enthalpy, is the ideal gas specific enthalpy of the evaporator outlet, is the residual specific enthalpy of the evaporator outlet, is the evaporator inlet specific enthalpy, is the ideal gas specific enthalpy of the evaporator inlet, is the residual specific enthalpy of the evaporator inlet.

[0029] Further, the ideal gas specific enthalpy is expressed by a cubic equation polynomial with respect to the temperature T, and the expression of the ideal gas specific enthalpy is:

[0030] ,

[0031] wherein, is the specific enthalpy of the ideal gas, , , , is a constant, T is the temperature.

[0032] Further, the expression of the specific residual enthalpy is:

[0033] ,

[0034] wherein:

[0035] ,

[0036] ,

[0037] wherein, is the specific residual enthalpy, is the gas constant, is the temperature, is the compressibility factor, , are the PR equation factors, is a characteristic parameter of the substance, is the specific enthalpy offset, is the pressure, is the specific volume, is the inverse of the density ρ , , , is a constant, different constants are selected when the refrigerant is in liquid or gaseous state.

[0038] Further, the expression for calculating the refrigeration capacity is:

[0039] ,

[0040] wherein, is the refrigeration capacity, i.e. the heat absorbed by the refrigerant in the evaporator, is the mass flow rate at the suction port of the compressor, , are the specific enthalpy at the outlet and at the inlet of the evaporator, respectively.

[0041] Further, the expression for calculating the total power of the system is:

[0042] ,

[0043] wherein, Ptotal is the total power of the system, Vin is the input voltage of the system, Iin is the input current of the system, Icomp is the compressor current, Ievap is the evaporator fan current, Icond is the condenser fan current, Icontroller is the system controller and temperature and pressure sensor current.

[0044] Further, the calculation expression of the system energy efficiency is:

[0045] ,

[0046] wherein, E is the system energy efficiency, Q is the refrigeration capacity, Ptotal is the total power of the system.

[0047] Compared with the prior art, the present application has the following beneficial effects:

[0048] (1) The present application realizes real-time monitoring and control of dynamic energy consumption through calculation of the refrigeration capacity of the refrigerant side of the air conditioning system and calculation of the total power of the system under the optimization of the control algorithm.

[0049] (2) In the traditional control algorithm, the refrigeration capacity and energy efficiency data of the air conditioning system need to be measured in a professional laboratory, which is time-consuming and costly, and the data cannot be obtained in real time in actual application. The present application can obtain the refrigeration capacity and energy efficiency data in real time without increasing much additional cost, solves the high cost problem in actual application, and only needs to collect several necessary parameters of the air conditioning system to realize dynamic energy efficiency calculation; at the same time, it solves the evaluation system deviation caused by the difference between actual application working conditions and laboratory working conditions.

[0050] (3) In the traditional control algorithm, bench tests can only measure static tests of single working condition point or multiple working condition points, and cannot evaluate the energy efficiency performance index under the complex working conditions of actual application with uncertainty. The present application can calculate the refrigeration capacity and energy efficiency of the air conditioning system in real time through the optimization of the control algorithm by building a thermodynamic model of the air conditioning system, and can more objectively express the running state of the system.

[0051] (4) The present application only needs to build a mathematical model about the refrigerant for the air conditioning system itself, which not only can realize millisecond-level control requirements, but also can improve the multi-scene applicability of the mathematical model.

[0052] (5) Compared with the traditional energy efficiency control method for the air conditioning system, the present application simplifies the operation amount of the mathematical model, can realize efficient and rapid calculation on the integrated terminal device, and has higher real-time performance. BRIEF DESCRIPTION OF DRAWINGS

[0053] Figure 1 This is a schematic diagram of the method flow of the present invention;

[0054] Figure 2 This is a schematic diagram of the structure of a commercial vehicle parking air conditioning system according to an embodiment of the present invention. Detailed Implementation

[0055] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments. These embodiments are based on the technical solution of the present invention and provide detailed implementation methods and specific operating procedures. However, the scope of protection of the present invention is not limited to the following embodiments.

[0056] This embodiment provides a real-time energy efficiency control method for a commercial vehicle parking air conditioner, the method comprising the following steps:

[0057] S1. Initialize the commercial vehicle parking air conditioning system and set the cycle, wherein the commercial vehicle parking air conditioning system includes a compressor and an evaporator connected thereto;

[0058] S2. In each cycle, collect the operating data of the commercial vehicle parking air conditioning system, calculate the mass flow rate of the compressor suction port, and use it as the mass flow rate of the evaporator outlet.

[0059] S3. Calculate the specific enthalpy at the evaporator outlet and the specific enthalpy at the inlet, and calculate the heat absorbed by the refrigerant in the evaporator in combination with the mass flow rate at the evaporator outlet, which is used as the cooling capacity of the commercial vehicle parking air conditioning system.

[0060] S4. Calculate the total power of the commercial vehicle parking air conditioning system based on the constructed total power model, and calculate the system energy efficiency in this cycle based on the cooling capacity, and perform energy efficiency control.

[0061] S5. Return to step S2 to update the system energy efficiency for the next cycle and achieve energy efficiency control.

[0062] This embodiment uses Figure 2 The R134a commercial parking air conditioning system shown is for real-time energy efficiency control in this application context. The specific steps in this embodiment are as follows: Figure 1 The steps 1-8 shown are as follows: S1 corresponds to steps 1-2, S2 corresponds to steps 3-4, S3 corresponds to steps 5-6, and S4-S5 correspond to steps 7-8. Specifically, as... Figure 1 As shown, the method in this embodiment specifically includes the following steps:

[0063] Step 1: System initialization.

[0064] like Figure 2The shown R134a commercial stationary air conditioning system, the system includes condensing fan 2, compressor 1, evaporator 7, condenser 3, reservoir 4, electronic expansion valve EXV 5, evaporating fan 6 and a plurality of temperature and pressure sensors 8, condenser 3 is connected with reservoir 4, electronic expansion valve 5, evaporator 7 and compressor 1 in turn, condensing fan 2 is installed above condenser 3, and condenser 3 together constitutes a condenser assembly, evaporating fan 6 is installed above evaporator 7, and evaporator 7 together constitutes an evaporator assembly. Five temperature and pressure sensors 8 are added in the system to collect key information of the system for subsequent model construction and calculation. The displacement of the compressor 1 is represented by D, which can be obtained during system selection, and the speed of the compressor 1 is represented by n, which can be monitored in real time during actual operation of the system.

[0065] Step 2, set a cycle period of time with a timer.

[0066] In this embodiment, a cycle period of 10 seconds is set.

[0067] Step 3, system data acquisition.

[0068] In this embodiment, the running data of the commercial stationary air conditioning system is collected, including the displacement D of the compressor 1, the speed n of the compressor 1, pressure data, temperature data, etc.

[0069] Step 4, calculation of compressor suction port mass flow.

[0070] This step uses the running data collected in step 3 to calculate the mass flow of the compressor 1 suction port, which is the mass flow of the evaporator 7 outlet, and the calculation expression is:

[0071] ,

[0072] In the formula, is the mass flow of the compressor 1 suction port, also known as the refrigerant mass flow ; V is the volume flow ); ρ is the density ; n is the speed of the compressor 1 (r / min); D is the displacement of the compressor 1 (cc); v: specific volume , the reciprocal of the density ρ .

[0073] Among them, the specific volume v is solved by the PR equation:

[0074] ,

[0075] Among them, P is the pressure (Pa); T : temperature (K); The PR equation factors are calculated using the following formula:

[0076] ,

[0077] Where R is the gas constant (J / kg·K); The critical temperature (K); The critical pressure (Pa); The PR equation factors are calculated using the following formula:

[0078] ,

[0079] ,

[0080] Eccentricity factor .

[0081] Step 5: Calculate the enthalpy at the evaporator outlet and the enthalpy at the inlet.

[0082] In this embodiment, the outlet specific enthalpy and inlet specific enthalpy of evaporator 7 are both composed of the ideal gas specific enthalpy and the residual specific enthalpy. The expression for calculating the outlet specific enthalpy is as follows:

[0083] ,

[0084] The expression for calculating the inlet enthalpy is:

[0085] ,

[0086] In the formula, The specific enthalpy at the outlet of evaporator 7. The ideal gas specific enthalpy at the outlet of evaporator 7. The residual specific enthalpy at the outlet of evaporator 7. The specific enthalpy at the inlet of evaporator 7. The ideal gas specific enthalpy at the inlet of evaporator 7. This is the residual specific enthalpy at the inlet of evaporator 7.

[0087] Furthermore, in this embodiment, the enthalpy of an ideal gas can be expressed as temperature. T The cubic polynomial, expressed through experimental simulation, is as follows:

[0088] ,

[0089] in, = 271.92, =0.1971, =0.0012, =-4e-7;

[0090] In the formula, For ideal gas specific enthalpy, , , , is constant.

[0091] The expression of the residual specific enthalpy is:

[0092] ,

[0093] Wherein:

[0094] ,

[0095] ,

[0096] In the formula, is the residual specific enthalpy, is the gas constant (J / kg·K), is the temperature (K), is the compression factor, , are PR equation factors, is the material characteristic parameter, is the specific enthalpy offset, is the pressure (Pa), is the specific volume is the reciprocal of the density ρ , , , is constant, when the refrigerant is in liquid or gaseous state, different constants are selected, for example, when the refrigerant is in liquid state:

[0097] ,

[0098] ,

[0099] ,

[0100] When the refrigerant is in gaseous state:

[0101] ,

[0102] ,

[0103] .

[0104] Step 6, refrigeration capacity calculation.

[0105] The refrigeration capacity is equal to the heat absorbed by the refrigerant in the evaporator 7, which can be calculated by mass flow and enthalpy difference. The refrigeration capacity is calculated by using the refrigeration capacity calculation model :

[0106] ,

[0107] wherein, , are the specific enthalpy at the outlet and at the inlet of the evaporator 7 respectively .

[0108] Step 7, system total power calculation.

[0109] The system total power calculation expression is:

[0110] ,

[0111] wherein, is the system total power, is the system input voltage, is the system input current, is the compressor 1 current, is the evaporator fan current, is the condenser fan current, is the system controller and temperature and pressure sensor current.

[0112] Step 8, real-time system energy efficiency COP calculation.

[0113] The system energy efficiency COP calculation expression is:

[0114] .

[0115] Thereafter, return to step 2 to enter the next cycle period, update the system energy efficiency, and realize energy efficiency control.

[0116] If the above functions are realized in the form of software function units and sold or used as independent products, they can be stored in a computer readable storage medium. Based on this understanding, the technical solutions of the present application or the parts that essentially contribute to the prior art or parts of the technical solutions can be embodied in the form of software products. The computer software product is stored in a storage medium and includes a number of instructions for causing a computer device (which can be a personal computer, a server, or a network device, etc.) to execute all or part of the steps of the method described in various embodiments of the present application. The aforementioned storage medium includes: a U disk, a mobile hard disk, a read-only memory (ROM, Read-Only Memory), a random access memory (RAM, Random Access Memory), a magnetic disk or an optical disk, and various program code storage media.

[0117] Those skilled in the art will appreciate that embodiments of the present application can be readily used as software, hardware, or a combination of software and hardware. In a software embodiment, the methods can be tangibly embodied in a machine-readable storage medium having stored thereon instructions that can be used to program a computer to perform any of the methods. The software implementation can be initialized by loading and executing a set of instructions arranged to perform one of the methods into the computer's memory. Alternatively, hard-wired circuitry can be used in place of, or in combination with, software instructions. Thus, the

[0118] The present application is described in reference to the flowchart and / or block diagrams of the methods, apparatus (systems) and computer program products according to embodiments of the application. It will be understood that each block of the flowchart and / or block diagrams, and combinations of blocks in the flowchart and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks.

[0119] These computer program instructions can also be stored in a computer- readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instructions which implement the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks.

[0120] These computer program instructions can also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer-implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks. Figure 1 one or more functions specified in one or more of the flowchart and / or block diagram block or blocks.

[0121] While preferred embodiments of the application have been described, modifications and alterations thereto will occur to those skilled in the art upon reading the preceding description. In particular, it will be apparent to those skilled in the art that parts can be added to, or substituted for, parts of the described embodiment. It is therefore contemplated that the claims be construed to include all such alterations and modifications as fall within the true spirit and scope of the application. Accordingly, while the preferred embodiment of the application has been described above, it will be recognized and understood that many additions, modifications, and substitutions can be made to the above description by one of ordinary skill in the art, in light of the foregoing, without departing from the spirit and scope of the application.

[0122] It will be apparent to those skilled in the art that various modifications and variations can be made to the present application without departing from the spirit or scope of the application. Thus, it is intended that the present application cover modifications and variations of this application provided they come within the scope of the appended claims and their equivalents.

Claims

1. A method of real-time energy efficiency control of a stationary air conditioner of a commercial vehicle, characterized in that, The method comprises the following steps: S1, initializing a commercial vehicle stationary air conditioning system, setting a cycle period, wherein the commercial vehicle stationary air conditioning system comprises a compressor and an evaporator connected thereto; S2, in each cycle period, collecting operation data of the commercial vehicle stationary air conditioning system, calculating the mass flow rate of the suction port of the compressor as the mass flow rate of the outlet of the evaporator; S3, calculating the specific enthalpy of the outlet and the inlet of the evaporator respectively, and calculating the heat absorbed by the refrigerant in the evaporator as the refrigerating capacity of the commercial vehicle stationary air conditioning system according to the mass flow rate of the outlet of the evaporator; S4, calculating the total power of the commercial vehicle stationary air conditioning system according to the constructed total electric power model of the system, and calculating the system energy efficiency in the cycle period according to the refrigerating capacity to perform energy efficiency control; S5, returning to step S2 to update the system energy efficiency of the next cycle period to realize energy efficiency control. The calculation expression of the mass flow rate of the suction port of the compressor is: ， wherein is the mass flow rate of the suction of the compressor, also referred to as refrigerant mass flow rate, is the volumetric flow rate, is the density, is the compressor speed, is the compressor displacement, is the specific volume; The specific volume Solved by the PR equation: ， wherein , are PR equation factors, calculated from the following equations, respectively: ， ， ， wherein P is pressure, R is the gas constant, T is temperature, Tc is the critical temperature, Pc is the critical pressure, Zc is the eccentric factor correlation parameter, Z is the eccentric factor.

2. A real-time energy efficiency control method for a stationary air conditioner of a commercial vehicle according to claim 1, characterized in that, The commercial vehicle stationary air conditioning system further comprises a condenser fan, a condenser, a liquid accumulator, an electronic expansion valve, an evaporator fan and a plurality of temperature and pressure sensors, the condenser is connected with the liquid accumulator, the electronic expansion valve, the evaporator and the compressor in sequence, the condenser fan is installed above the condenser to form a condenser assembly together with the condenser, and the evaporator fan is installed above the evaporator to form an evaporator assembly together with the evaporator.

3. The method of claim 1, wherein, The specific enthalpy of the outlet and the inlet of the evaporator are both composed of ideal gas specific enthalpy and residual specific enthalpy, wherein the calculation expression of the outlet specific enthalpy is: ， The calculation expression of the inlet specific enthalpy is: ， wherein is the specific enthalpy at the evaporator outlet, is the specific ideal gas enthalpy at the evaporator outlet, is the specific residual enthalpy at the evaporator outlet, is the specific enthalpy at the evaporator inlet, is the specific ideal gas enthalpy at the evaporator inlet, is the specific residual enthalpy at the evaporator inlet.

4. The method of claim 3, wherein, The ideal gas specific enthalpy is expressed by a cubic equation polynomial with respect to temperature T, and the expression of the ideal gas specific enthalpy is: ， wherein is the specific enthalpy of the ideal gas, , , , is a constant, T is the temperature.

5. The method of claim 3, wherein, The expression of the residual specific enthalpy is: ， Wherein: ， ， wherein is the specific enthalpy of the remaining, is the gas constant, is the temperature, is the compression factor, , are both PR equation factors, is a characteristic parameter of the substance, is the specific enthalpy offset, is the pressure, is the specific volume, and is the inverse of the density The calculation expression of the refrigerating capacity is: , , , is a constant, which is selected differently when the refrigerant is in a liquid or gaseous state.

6. The method of real-time energy efficiency control of a stationary air conditioner of a commercial vehicle according to claim 1, characterized in that, The calculation expression of the total power of the system is: ， wherein Q is the refrigeration capacity, i.e. the heat absorbed by the refrigerant in the evaporator, is the mass flow rate at the suction of the compressor, , are the specific enthalpy at the outlet and at the inlet of the evaporator, respectively.

7. The method of real-time energy efficiency control of a stationary air conditioner of a commercial vehicle according to claim 1, characterized in that, The calculation expression of the system energy efficiency is: ， wherein, Ptotais the total system power, Vinis the system input voltage, Iinis the system input current, Ic is the compressor current, Ie is the evaporator fan current, Ic is the condenser fan current, Ic is the system controller and temperature and pressure sensor current.

8. The method of real-time energy efficiency control of a stationary air conditioner of a commercial vehicle according to claim 1, characterized in that, ​ ， wherein Qsysis the system energy efficiency, Qrefis the refrigeration capacity, Ptotis the total system power.

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