CN115782510A - Control method for heat pump system of automobile air conditioner - Google Patents
Control method for heat pump system of automobile air conditioner Download PDFInfo
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Abstract
The disclosure discloses a control method of an automobile air conditioner heat pump system, which comprises the following steps: selecting a working mode of an air-conditioning heat pump system and setting a target temperature; acquiring the refrigerating capacity or the heating capacity required in the carriage; solving the circulation efficiency of the system, and obtaining the valve opening degree of the system, the rotating speed of the compressor and the superheat degree of an evaporator outlet; reading the air outlet temperature of the heat exchanger and the superheat degree of an outlet of the evaporator, and adjusting the opening of a valve and the rotating speed of the compressor through a model prediction controller; judging the automobile running state after the opening of the valve and the rotating speed of the compressor are adjusted and judging whether the external state of the automobile changes; judging whether the system switches the working mode, if so, stopping the work of the compressor, opening the expansion valve to the maximum and switching the reversing valve; otherwise, continuing to execute the next step; judging whether the system needs to be closed, if so, closing the compressor and opening the expansion valve to the maximum; otherwise, the working mode of the air-conditioning heat pump system is reselected and the target temperature is set.
Description
Technical Field
The disclosure belongs to the field of system control, and particularly relates to a control method for an automobile air-conditioning heat pump system.
Background
At present, environmental problems are more and more emphasized by various countries, in order to reduce emission, china also recommends new energy vehicles to be used vigorously in recent years, however, energy supplement of the new energy vehicles is slower than that of traditional fuel vehicles, mileage is also shorter, an air conditioning system occupies a certain proportion in energy consumption of the new energy vehicles, waste heat generated by fuel is reduced compared with that of the traditional fuel vehicles, and the air conditioning system has higher requirements on air conditioning and heating of the new energy vehicles, so that optimized control of the automobile air conditioning system has important value for more efficient and energy-saving operation of the air conditioning system. However, the dynamic performance of the system is not concerned by the mainstream PID system control method at present, and the coupling characteristic of the system cannot be solved well, and although the conventional model predictive control can solve the above problems well, the regulation interval is small.
Disclosure of Invention
In view of the defects in the prior art, an object of the present disclosure is to provide a method for controlling an automotive air conditioning heat pump system, which can infer control parameters of the air conditioning heat pump system according to the current vehicle running state, and can ensure that the system runs with high efficiency and energy conservation in the dynamic process from the beginning of adjustment to stable operation after the parameters are set.
In order to achieve the above purpose, the present disclosure provides the following technical solutions:
a control method of an automobile air conditioning heat pump system comprises the following steps:
s100: selecting a working mode of an air-conditioning heat pump system and setting a target temperature;
s200: acquiring the refrigerating capacity or the heating capacity required in the automobile compartment;
s300: solving the circulation efficiency of the air-conditioning heat pump system according to the required refrigerating capacity or heating capacity, the target temperature and the measured air side temperature of the condenser so as to obtain the opening degree of a valve of the air-conditioning heat pump system, the rotating speed of a compressor and the superheat degree of an outlet of an evaporator;
s400: reading the air outlet temperature of the heat exchanger and the superheat degree of an outlet of the evaporator, and adjusting the opening of a valve and the rotating speed of the compressor through a model prediction controller;
s500: judging the running state of the automobile after the opening degree of the valve and the rotating speed of the compressor are adjusted and judging whether the external state of the automobile changes, if so, returning to the step S200 to obtain the refrigerating or heating quantity again; otherwise, continuing to execute the next step;
s600: judging whether the system switches the working mode, if so, stopping the work of the compressor, opening the expansion valve to the maximum and switching the reversing valve; otherwise, continuing to execute the next step;
s700: judging whether the system needs to be closed, if so, closing the compressor and opening the expansion valve to the maximum; otherwise, returning to the step S100 to reselect the working mode of the air-conditioning heat pump system and set the target temperature.
Preferably, in step S200, the amount of cooling or heating is obtained by the following formula:
wherein Q cool To the desired refrigeration capacity, Q heat To the required heating capacity, Q human Heat generated for passengers, Q convection For convective heat transfer from the cabin to the environment, Q radiate Is the radiant heat of sunlight.
Preferably, in step S300, the optimal system cycle efficiency is represented as:
wherein COP is the system cycle efficiency; h is a total of COMin Is the compressor inlet enthalpy; h is GCO Is the gas cooler outlet enthalpy; t is GCO Is the gas cooler exit temperature; p H The system high pressure; h is COMout Is the compressor outlet enthalpy; t is COMout Is the compressor outlet temperature.
Preferably, the compressor outlet temperature is calculated by the following equation:
T COMout ＝(T EVA +T SHmin )(P H /P L ) (n-1)/n
wherein, T COMout Is the compressor outlet temperature; t is EVA Is the evaporation temperature; t is SHmin Minimum superheat; p is H Circulating high pressure; p L Is a cyclic low pressure; n is a process index.
Preferably, in step S300, the expansion valve opening and the compressor rotation speed are obtained according to the following formula:
q mc ＝w k V k ρ cin (1+C k -D k (P H /P L ) 1/n )
wherein q is mc Is the compressor mass flow; q. q of me Is the expansion valve mass flow; omega k Is the compressor speed; v k Is the theoretical volume of the compressor; rho cin Is the compressor suction density; p H 、P L Respectively a system high-pressure side pressure and a system low-pressure side pressure; c k 、D k 、C v Is a constant coefficient; n is a compression process index; a is v The opening degree of the expansion valve; rho ein Is the expansion valve inlet density; subscript k is a compressor, and subscript v is an expansion valve parameter; subscript H high pressure side parameter; subscript L is the low side parameter.
Preferably, in step S400, the model predictive controller is represented as:
y＝Cx+Du
wherein x represents a state space variable of the system,
the derivative of the state variable with respect to time is represented, u represents the control variable, y represents the output quantity, and a, B, C, D represent the coefficient matrix.
Preferably, in step S400, the adjusting the control parameter by the model predictive controller includes the following steps:
s401: acquiring the current operating state of the air-conditioning heat pump system according to the read air outlet temperature of the heat exchanger and the superheat degree of the outlet of the evaporator, and updating a reference working point and a state space expression;
s402: according to the current operation state of the air-conditioning heat pump system, correcting the prediction result of the model prediction controller, and solving an optimal performance function according to the existing state space expression to obtain a control sequence;
s403: judging whether the air-conditioning heat pump system is stable or not, and if so, not executing the controller; otherwise, returning to the step S401 to acquire the current operating state of the air-conditioning heat pump system again.
Preferably, in step S4023, the optimal performance function is represented as:
wherein J represents the optimal performance function, Δ y i Indicating the deviation, Δ u, between the ith step output and a reference value i Indicating the rate of change, COP, of the control quantity of the ith step i And (3) expressing the circulation efficiency of the system in the ith step, respectively expressing Q, R and T as weight coefficient matrixes, P as a prediction time domain, and M as a control time domain.
Compared with the prior art, the beneficial effect that this disclosure brought does:
the system can quickly and efficiently adjust in a large range according to the optimal high-pressure and corresponding system control parameters of the circulation efficiency by obtaining the required refrigeration or heating quantity in the carriage according to the running state and the external working condition of the automobile. Meanwhile, when the system enters a stable state, the model prediction controller is started, the linear model of the system is preferably selected as the prediction model according to the state of the system, the optimal performance function is solved, the accurate control on the rotating speed of a compressor and the opening degree of an expansion valve of the system is realized, the dynamic response of the system in the control process is fast, the energy consumption of the controller is low, the circulating efficiency of the system is high, the system can run in a more energy-saving mode no matter the system is started, the working mode is switched or the system runs in a stable state, and therefore the new energy vehicle has a higher mileage.
Drawings
Fig. 1 is a schematic structural diagram of a heat pump system of an automotive air conditioner according to an embodiment of the present disclosure;
fig. 2 is a flowchart illustrating a method for controlling a heat pump system of an air conditioner of a vehicle according to an embodiment of the present disclosure;
FIG. 3 is a schematic flow chart diagram of model predictive control provided by another embodiment of the present disclosure;
FIG. 4 is a graph showing a comparison between a model predictive controller and a PID controller for system superheat control, according to another embodiment of the disclosure.
Detailed Description
Specific embodiments of the present disclosure will be described in detail below with reference to fig. 1 to 4. While specific embodiments of the disclosure are shown in the drawings, it should be understood that the disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.
It should be noted that certain terms are used throughout the description and following claims to refer to particular components. As one skilled in the art will appreciate, various names may be used to refer to a component. This specification and claims do not intend to distinguish between components that differ in name but not function. In the following description and in the claims, the terms "include" and "comprise" are used in an open-ended fashion, and thus should be interpreted to mean "include, but not limited to. The description which follows is a preferred embodiment of the disclosure, but is made for the purpose of illustrating the general principles of the disclosure and not for the purpose of limiting the scope of the disclosure. The scope of the disclosure is to be determined by the claims appended hereto.
To facilitate an understanding of the embodiments of the present disclosure, the following detailed description is to be considered in conjunction with the accompanying drawings, and the drawings are not to be construed as limiting the embodiments of the present disclosure.
In one embodiment, as shown in fig. 2, the present disclosure provides a method for controlling a heat pump system of an air conditioner of a vehicle, including the steps of:
s100: selecting a working mode of an air-conditioning heat pump system and setting a target temperature;
as shown in fig. 1, the air conditioning system of the vehicle includes a compressor, an indoor heat exchanger, an expansion valve, an intermediate heat exchanger, an outdoor heat exchanger, a liquid collector, a four-way reversing valve, and an indoor electric heater. The system comprises a refrigerating mode and a heating mode, and the refrigerating mode and the heating mode can be switched through a four-way reversing valve.
In the step, the target temperature is set by adopting a memory function, the corresponding target temperature is intelligently set according to the habit of a user and the original setting, the mode of the air-conditioning heat pump system is set according to the numerical value of the outdoor temperature sensor, when the external temperature is more than 30 ℃, the system is automatically switched into a refrigerating mode, and when the external temperature is less than 20 ℃, the air-conditioning heat pump is automatically switched into a heating mode.
S200: acquiring the refrigerating or heating quantity required in the automobile compartment;
in this step, besides the target temperature, the amount of heat or refrigeration required in the vehicle compartment needs to be calculated by considering the radiation outside the compartment, the temperature, the vehicle speed and the number of people in the compartment, wherein the radiation outside the compartment, the temperature and the vehicle speed are obtained according to corresponding sensors, the number of people in the vehicle is obtained through a pressure sensor mounted on a seat, the radiation intensity and the convection heat transfer coefficient are obtained through corresponding formulas, so that the solar radiation heat transfer amount and the compartment convection heat transfer amount are further obtained, the calorific value of the human body is obtained according to a natural convection heat transfer formula and the number of people, and then according to the law of energy conservation, the calculation formula of the amount of heat or refrigeration required for maintaining the constant temperature of the compartment is as follows:
wherein the content of the first and second substances,Q cool to the required refrigeration capacity, Q heat To the required heating capacity, Q human Heat generated for passengers, Q convection For convective heat transfer from the cabin to the environment, Q radiate Is the radiant heat of sunlight.
Wherein, the radiation intensity calculation formula is as follows:
wherein, I is the solar radiation intensity, T is the time point number, P is the air pollution index, and a is the constant coefficient.
The natural convection heat exchange formula is as follows:
Nu＝0.59(Gr Pr) 1/4
wherein Nu is Nussel number of convective heat transfer, G r Is the Gravax number, P r Are prandtl numbers.
S300: solving the circulation efficiency of the air-conditioning heat pump system according to the required refrigerating capacity or heating capacity, the target temperature and the measured temperature of the air side of the condenser so as to obtain the valve opening degree and the compressor rotating speed of the air-conditioning heat pump system and the superheat degree of an outlet of the evaporator;
in this step, when the air-conditioning heat pump system is in the refrigeration mode, the condenser outlet temperature T can be obtained according to the heat exchange temperature difference and the outdoor temperature, assuming that the outdoor heat exchange is sufficient GCO ＝T amb + Δ T (where T is GCo Gas cooler exit temperature; t is amb Is ambient temperature; Δ T is a heat exchange temperature difference), and the pressure and temperature of the low pressure side can be obtained from the target temperature set by the user and the experienced heat exchange temperature difference, wherein the low pressure side temperature is: t is EVA ＝T ref Δ T (in the formula, T) EVA Is the evaporation dimension; t is ref Is a reference temperature; delta T is the heat exchange temperature difference), the low-pressure side is a two-phase region, and the pressure and the temperature are single-value functions, so that the low-pressure P can be obtained through physical property software L 。
When air conditioning heat pump system is the mode of heating, supposing that indoor heat exchanger fully exchanges heat, then indoor heat exchanger exit temperature is: t is GCO ＝T ref + Δ T, the outdoor side refrigerant temperature can be obtained from the difference between the outdoor ambient temperature and the heat exchange temperature: t is EVA ＝T amb Δ T, while the pressure P on the low-pressure side can be obtained as a single-valued function of the low-pressure and the temperature due to the two-phase region of the outdoor refrigerant heat exchange L . According to the inverse Carnot cycle formula, if the temperature of the high-pressure side of the cycle needs to be reduced to improve the cycle efficiency, the outlet temperature of the compressor is in positive correlation with the superheat degree of the system, so that the cycle superheat degree is reduced to be beneficial to improving the cycle efficiency, and in order to ensure the dryness of the inlet air of the compressor, the system is safely operated to provide the minimum superheat degree T for the system sHmin Then the compressor inlet enthalpy h can be obtained CoMin ＝h CoMin (P L ，T EVA +T SHmin ) Setting the high pressure of the system as P H Then, the compressor outlet temperature can be obtained according to the equation of the process with the multiple squares as:
T COMout ＝(T EVA +T SHmin )(P H /P L ) (n-1)/n
wherein, T COMout Is the compressor outlet temperature; t is EVA Is the evaporation temperature; t is SHmin Minimum superheat; p is H Is a cyclic high pressure; p L Circulating low pressure; n is a process index.
The system cycle efficiency is calculated by:
wherein COP is the system cycle efficiency; h is COMin Is the compressor inlet enthalpy; h is GCo Is the gas cooler outlet enthalpy; t is GCO Is the gas cooler exit temperature; p is H Is a cyclic high pressure; h is COMout Is the compressor outlet enthalpy; t is a unit of COMout Is the compressor outlet temperature.
The optimal COP equation is solved through an optimization algorithm, so that the high-pressure P can be obtained H And according to the required refrigerating capacity, the system flow can be obtained as follows: q. q.s m ＝Q cool /(h COMin -h GCO ) And simultaneously can be based on the flow formula q of the compressor mc ＝w k V k ρ cin (1+C k -D k (P H /P L ) 1/n ) And expansion valve flow type
And obtaining the opening of the expansion valve and the rotating speed information of the compressor. Wherein q is mc Is the compressor mass flow; q. q.s me Is the expansion valve mass flow; w is a k Is the compressor speed; v k Is the theoretical volume of the compressor; rho cin Is the compressor suction density; p H 、P L Respectively a system high-pressure side pressure and a system low-pressure side pressure; c k 、D k 、C v Is a constant coefficient; n is a compression process index; a is v Is the valve opening; rho ein Is the expansion valve inlet density; subscript k is a compressor, and subscript v is an expansion valve parameter; subscript H high pressure side parameter; subscript L is the low side parameter.
S400: reading the air outlet temperature of the heat exchanger and the superheat degree of an evaporator outlet, and adjusting the opening of a valve and the rotating speed of a compressor through a model prediction controller;
in this step, as shown in fig. 3, the adjusting of the control parameters by the model predictive controller includes the steps of:
s401: acquiring output parameters of the air-conditioning heat pump system from the sensor, acquiring the current running state of the air-conditioning heat pump system according to the output parameters, and updating a reference working point and a state space expression;
specifically, the system cycle efficiency is obtained by obtaining the inlet and outlet pressure temperatures of the compressor and the front and rear pressure temperatures of the expansion valve through the sensor, and simultaneously, the outlet air temperature and the superheat degree of the indoor heat exchanger are read, and the system cycle efficiency, the outlet air temperature and the superheat degree are input into the controller as the output quantity of the system.
Specifically, since the predictive model of the model predictive controller is a model linearized at a preferred operating point based on the nonlinear model of the system, efficient control of the model predictive controllerTo solve this problem, the present embodiment employs a method of storing a plurality of preferred operating points and their corresponding shapes in the controller in advance
The linear system model of (1) (where x is the state space variable of the system under study;
is the derivative of the state variable with respect to time; u is a control variable; A. b is a coefficient matrix), and the controller makes a judgment according to the read data, and compares the current state vector X with a preselected system state vector set X = { X = { X = 01 ，x 02 ，…，x 0n Matching each state vector in the state vector, and selecting a system preset state vector x closest to the current state vector x 0i And according to the system preset state vector x 0i And obtaining the state space expression corresponding to the state point, thereby updating the state space expression.
S402: according to the current operation state of the air-conditioning heat pump system, correcting the prediction result of the model prediction controller, and solving an optimal performance function according to the existing state space expression to obtain a control sequence;
specifically, the model predictive controller obtains a set of optimal control sequences of the compressor rotation speed and the expansion valve opening degree by solving the following objective optimization function with the current input value as an initial condition, wherein the set of control sequences are the optimal result of the cycle efficiency when the response speed of the system, the energy consumption of the controller and the dynamic response of the system are comprehensively considered.
Wherein J is the objective function; Δ y i The deviation value between the output quantity of the ith step and a reference value is calculated; Δ u i Is the change rate of the control quantity of the ith step; COP i The circulation efficiency of the system in the ith step is calculated; q, R and T are weight coefficient matrixes respectively; p is a prediction time domain; m is a control time domain。
S403: judging whether the air-conditioning heat pump system is stable, if so, not executing the controller; otherwise, returning to the step S401 to acquire the current operating state of the air-conditioning heat pump system again.
S500: judging whether the convective heat transfer radiation heat exchange quantity of the vehicle is changed or not through an illumination sensor, a temperature sensor and a vehicle speed sensor on the outdoor side, so as to judge and judge the running state and the external state of the vehicle, and if the convective heat transfer radiation heat exchange quantity is changed, returning to the step S200 to obtain the refrigeration or heating quantity again; otherwise, continuing to execute the next step;
in the step, if the speed of the automobile is changed to 10.8Km/h, or the ambient temperature outside the automobile is changed to 3 ℃, or the solar radiation intensity is changed to 150W/m 2 In time, the required amount of refrigeration or heating needs to be recalculated; if the above variation amounts are within the respective ranges, the next step is performed.
S600: judging whether the system switches the working mode, if the working mode is switched, stopping the work of the compressor, opening the expansion valve to the maximum, and switching the reversing valve; otherwise, continuing to execute the next step;
in the step, if the working mode is switched, for example, the cooling mode is switched to the heating mode or the heating mode is switched to the cooling mode, the compressor needs to be stopped, the expansion valve is opened to the maximum, the four-way reversing valve is adjusted to be switched to the corresponding mode when the circulating high-low pressure differential pressure is less than 0.5bar, finally, the compressor is restarted, and the step S100 is skipped to, and the set temperature is read again. And if the working mode is not switched, executing the next step.
S700: judging whether the system needs to be closed, if so, closing the compressor and opening the expansion valve to the maximum; otherwise, returning to the step S100 to reselect the working mode of the air-conditioning heat pump system and set the target temperature.
In this step, if the air conditioner is to be shut down, the compressor needs to be shut down, the expansion valve needs to be opened to the maximum, and the whole air conditioner heat pump system stops working. If not, a new cycle is performed.
The present disclosure will now be described with reference to the cooling mode as an example to illustrate the effects of the method of the present disclosure. The outdoor temperature of a working point is 35 ℃, the indoor temperature is set to be 25 ℃, the rotating speed of a compressor is 3000rpm, the opening degree of an expansion valve is 36%, and a coefficient matrix of a state space expression of the system obtained by performing linearization processing according to the working point is as follows:
the system state variables are: [ P ] c h c T cw L 1 P e h eout T ew1 T ew2 ] T The temperature of the evaporator is the gas cooler pressure, the gas cooler average enthalpy, the gas cooler wall temperature, the length of the two-phase region of the evaporator, the evaporator pressure, the evaporator outlet enthalpy, the wall temperature of the two-phase region of the evaporator and the wall temperature of the superheat region of the evaporator.
The control variables are: [ a ] A v n] T The opening of the expansion valve and the rotation speed of the compressor are respectively.
The output variables are: [ T ] e T SH ] T The evaporation temperature and the degree of superheat at the outlet of the evaporator are indicated.
The transfer function of the PID controller is as follows:
and P = -1E-2, I = -2.5E-3 can be calculated according to the performance curve of the working condition point. By setting the superheat reference value to be increased by 4 ℃, the control of the MPC controller and the PID controller is as shown in fig. 4, respectively, and it can be seen that the response speed of the MPC controller is much faster than that of the PID controller.
By the adjusting method, the problem that the conventional PID control method cannot well guarantee the energy consumption performance of the system in the dynamic response process is solved, and the defect that the conventional model predictive control cannot be adjusted in a large range is overcome, so that the system can operate in a mode of the optimal cycle efficiency or the approximate optimal cycle efficiency of the system in the aspects of steady state and dynamic performance.
The above general description of the invention and the description of its specific embodiments in this application should not be construed as limiting the technical solutions of the invention. Those skilled in the art can add, reduce or combine the technical features disclosed in the general description and/or the specific embodiments (including the examples) to form other technical solutions within the protection scope of the present application according to the disclosure of the present application without departing from the structural elements of the present invention.
Claims (8)
1. A control method of an automobile air conditioning heat pump system comprises the following steps:
s100: selecting a working mode of an air-conditioning heat pump system and setting a target temperature;
s200: acquiring the refrigerating capacity or the heating capacity required in the automobile compartment;
s300: solving the circulation efficiency of the air-conditioning heat pump system according to the required refrigerating capacity or heating capacity, the target temperature and the measured temperature of the air side of the condenser so as to obtain the valve opening degree and the compressor rotating speed of the air-conditioning heat pump system and the superheat degree of an outlet of the evaporator;
s400: reading the air outlet temperature of the heat exchanger and the superheat degree of an evaporator outlet, and adjusting the opening of a valve and the rotating speed of a compressor through a model prediction controller;
s500: judging the running state of the automobile after the opening degree of the valve and the rotating speed of the compressor are adjusted and judging whether the external state of the automobile changes, if so, returning to the step S200 to obtain the refrigerating or heating quantity again; otherwise, continuing to execute the next step;
s600: judging whether the system switches the working mode, if so, stopping the work of the compressor, opening the expansion valve to the maximum and switching the reversing valve; otherwise, continuing to execute the next step;
s700: judging whether the system needs to be closed, if so, closing the compressor and opening the expansion valve to the maximum; otherwise, returning to the step S100 to reselect the working mode of the air-conditioning heat pump system and set the target temperature.
2. The method of claim 1, wherein, preferably, in step S200, the amount of refrigeration or heating is obtained by the following formula:
wherein Q cool To the desired refrigeration capacity, Q heat To the required heating capacity, Q human Heat generated for passengers, Q convection For convective heat transfer from the cabin to the environment, Q radiate Is the radiant heat of sunlight.
3. The method according to claim 1, wherein in step S300, the expansion valve opening and the compressor rotation speed are obtained according to the following formula:
q mc ＝ω k V k ρ cin (1+C k -D k (P H /P L ) 1/n )
wherein q is mc Is the compressor mass flow; q. q.s me Is the expansion valve mass flow; omega k Is the compressor speed; v k Is the theoretical volume of the compressor; rho cin Is the compressor suction density; p is H 、P L The high-pressure side pressure and the low-pressure side pressure of the system are respectively; c k 、D k 、C υ Is a constant coefficient; n is a compression process index; a upsilon is the opening degree of the expansion valve; ρ e in Is an expansion valveMouth density; subscript k is a compressor, and subscript v is an expansion valve parameter; subscript H high pressure side parameter; subscript L is the low side parameter.
4. The method of claim 1, wherein in step S300, the cycle efficiency is represented by the following formula:
wherein COP is the system cycle efficiency; h is COMin Is the compressor inlet enthalpy; h is GCO Is the gas cooler outlet enthalpy; t is a unit of GCO Is the gas cooler exit temperature; p H The system high pressure; h is COMout Is the compressor outlet enthalpy; t is COMout Is the compressor outlet temperature.
5. The method of claim 4, wherein the compressor outlet temperature is calculated by:
T COMout ＝(T EVA +T SHmin )(P H /P L ) (n-1)/n
wherein, T COMout Is the compressor outlet temperature; t is EVA Is the evaporation temperature; t is SHmim Is the minimum superheat degree; p H Is a cyclic high pressure; p L Circulating low pressure; n is a process index.
6. The method of claim 1, wherein in step S400, the model predictive controller is represented as:
y＝Cx+Du
wherein x represents a state space variable of the system,
the derivative of the state variable with time is shown, u is the control variable, y is the output quantity, and A, B, C, D are the coefficient matrix.
7. The method of claim 1, wherein the adjusting of the control parameters by the model predictive controller in step S400 comprises:
s401: acquiring the current running state of the air-conditioning heat pump system according to the read air outlet temperature of the heat exchanger and the superheat degree of the outlet of the evaporator, and updating a reference working point and a state space expression;
s402: according to the current operation state of the air-conditioning heat pump system, correcting the prediction result of the model prediction controller, and solving an optimal performance function according to the existing state space expression to obtain a control sequence;
s403: judging whether the air-conditioning heat pump system is stable, if so, not executing the controller; otherwise, returning to step S401 to re-acquire the current operating state of the air-conditioning heat pump system.
8. The method of claim 7, wherein in step S402, the optimal performance function is represented as:
wherein J represents the optimal performance function, Δ y i Representing the deviation, Δ u, between the output of the i-th step and a reference value i Shows the change rate, COP, of the control quantity of the i-th step i And (3) expressing the circulation efficiency of the system in the ith step, respectively expressing Q, R and T as weight coefficient matrixes, P as a prediction time domain, and M as a control time domain.
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