CN114576797B - Control method of air conditioner and air conditioner - Google Patents

Control method of air conditioner and air conditioner Download PDF

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Publication number
CN114576797B
CN114576797B CN202210316583.3A CN202210316583A CN114576797B CN 114576797 B CN114576797 B CN 114576797B CN 202210316583 A CN202210316583 A CN 202210316583A CN 114576797 B CN114576797 B CN 114576797B
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air
air conditioner
temperature
load
heat
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CN114576797A (en
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李木湖
夏光辉
何振健
陈姣
林金煌
梁博
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F24F11/47—Responding to energy costs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/79—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling the direction of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/50—Load
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The invention discloses an air conditioner and a control method thereof. The control method comprises the following steps: acquiring a steady-state heat leakage quantity corresponding to a set working condition of the air conditioner, and determining a target control parameter of the air conditioner according to the steady-state heat leakage quantity; establishing a change relation among the air conditioner heat supply load, the indoor air load and the enclosure structure load; determining the optimal heat supply quantity of the air conditioner by combining the change relationship of the heat supply quantity of the air conditioner, the indoor air load and the load of the building enclosure, and selecting a preset heat supply parameter combination corresponding to the optimal heat supply quantity; determining preset control parameters of each load of the air conditioner according to the preset heating parameter combination; and controlling each load of the air conditioner to act according to preset control parameters so as to perform heating operation. The control method can indirectly monitor the heat load of the enclosure structure, solves the key problems of poor robustness and unmatched load grades in different heat leakage states of the existing method, realizes efficient heat supply of the air conditioner and high-efficiency heat of the air, reduces the energy consumption of the air conditioner in operation, and realizes efficient, energy-saving and comfortable operation.

Description

Control method of air conditioner and air conditioner
Technical Field
The invention relates to the field of air conditioners, in particular to a control method of an air conditioner and the air conditioner.
Background
At present, an air source heat pump air conditioner is a technology most suitable for a heat source provided by a distributed distribution mode, and plays a main role in the emission reduction and reformation tasks of a central heating mode in winter in northern China.
At present, a zero-carbon energy structure has the characteristic of discontinuous energy supply (such as nuclear power, wind power, photoelectricity and the like), has the key problem of contradiction between the supply and the demand of a power supply side and an energy utilization terminal, and needs to be developed to a demand side response mode, so that accurate judgment and efficient control of actual demands of the demand side are the key for realizing the demand side response mode.
High efficiency, energy conservation and comfort are all the key factors for restricting the future application development of small and medium-sized air source heat pumps. The energy efficiency of the multi-side heavy supply side unit of the conventional air source heat pump product is improved, the heating COP reaches more than 3, but the research on energy saving control of operation energy consumption of a demand side is rarely broken through, the problems of high-efficiency heat supply and low-efficiency heat utilization exist, the problems of heat supply demand guarantee and heat supply efficiency of a heat pump are more prominent, and the operation energy saving improvement of building equipment is urgent.
However, the existing heat pump air conditioning technology has at least the following problems in the aspect of user demand side response: the existing air conditioner can not detect the load of an enclosure structure in real time, the existing method for directly carrying out feedback closed-loop control on the air conditioner by monitoring the air temperature is difficult to rapidly feed back the load state of the enclosure structure, the problem of target overshoot or undershoot is very easy to occur when the thermal physical property and the state of the enclosure structure change, meanwhile, in the stage that the indoor air temperature tends to be stable, the air load is close to 0, the system is lack of active intervention control, the actual state of the load of the enclosure structure is difficult to reflect by the size of the air load, so that a unit can not meet the user requirements with the least heat and the highest energy efficiency, the robustness of the control system is poor, the system load grade is not matched with the actual room load grade, and the energy consumption of the system is high, and the bottleneck problem that the existing heat pump air conditioner is difficult to break through in efficient energy-saving operation research is solved.
Disclosure of Invention
In view of the above, the invention discloses a control method of an air conditioner and the air conditioner, which are used for at least solving the problems that the existing air conditioner control system is poor in robustness, the system load grade is not matched with the actual room load grade, and the system energy consumption is high.
In order to achieve the above object, the invention adopts the following technical scheme:
the invention discloses a control method of an air conditioner in a first aspect, which comprises the following steps:
determining target control parameters of the air conditioner according to the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner;
obtaining the variation relation of the air conditioner heat supply load, the indoor air load and the enclosure structure load;
determining the optimal heating load of the air conditioner by combining the target control parameter and the variation relation of the air conditioner heating load, the indoor air load and the enclosure structure load, and selecting a preset heating parameter combination corresponding to the optimal heating load;
determining a preset control parameter for operating the air conditioner according to the preset heat supply parameter combination;
and controlling each load of the air conditioner to act according to the preset control parameter so as to perform heating operation.
Further optionally, the determining the target control parameter of the air conditioner according to the steady-state heat leakage amount corresponding to the set working condition of the air conditioner includes: obtaining the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner,
the step of acquiring the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner comprises the following steps:
determining a working condition section of a preset working condition section in which the set working condition of the air conditioner is located;
and determining the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner according to the preset corresponding relation between the working condition interval and the steady-state heat leakage quantity.
Further optionally, the determining a target control parameter of the air conditioner according to the steady-state heat leakage amount includes:
calculating the minimum heat supply amount corresponding to the steady-state heat leakage amount according to the steady-state heat leakage amount;
and taking the minimum heat supply amount as a target control parameter.
Further optionally, the establishing a variation relationship among the air conditioning heat supply amount, the indoor air load and the enclosure load comprises:
establishing a relation between the indoor air load and the building envelope load based on a response relation between the room temperature second-order change rate and the total heat leakage quantity of the building envelope;
and establishing a change relation among the air conditioner heat supply amount, the indoor air load and the building envelope load by combining the air conditioner heat supply amount.
Further optionally, the determining the optimal heating load of the air conditioner by combining the target control parameter and the variation relationship among the air conditioner heating load, the indoor air load and the enclosure load comprises:
determining the minimum air outlet temperature of the air conditioner according to the steady-state heat leakage quantity;
and determining the optimal heat supply of the air conditioner based on the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature.
Further optionally, the determining the minimum outlet air temperature of the air conditioner according to the steady-state heat leakage amount includes:
taking the air conditioner heat supply amount corresponding to the steady-state heat leakage amount as the minimum heat supply amount;
and calculating the minimum air outlet temperature of the air conditioner according to the minimum heat supply amount.
Further optionally, the determining the optimal heat supply amount of the air conditioner based on the indoor temperature change rate, the outlet air temperature of the air conditioner, the inlet air temperature of the air conditioner, and the minimum outlet air temperature includes:
detecting indoor temperature, air outlet temperature of the air conditioner and air inlet temperature of the air conditioner in real time;
calculating the indoor temperature change rate according to the indoor temperature;
calculating real-time heat leakage quantity by combining the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature;
comparing the indoor temperature with the minimum outlet air temperature to obtain a temperature comparison result, and comparing the real-time heat leakage quantity with the minimum heat supply quantity to obtain a heat supply quantity comparison result;
and determining the optimal heat supply according to the temperature comparison result and the heat supply comparison result.
Further optionally, the following relation is adopted in calculating the real-time heat leakage quantity
Q s (t)＝∫ t q m c p [T c '(t)-T j '(t)]dt-ρV m c p ΔT r ＝k x (t)A(T r -T w )
Wherein Q s (t) real-time heat leakage, q m Mass flow of air supplied to the air conditioner, c p Is the specific heat at constant pressure of air, T c (T) is the real-time outlet air temperature, T j (t) real-time inlet air temperature, rho indoor air density, V m Is the room volume, Δ T r Is the change value of room temperature in unit time, k x (T) is the real-time heat leakage coefficient, A is the total heat exchange area inside the room enclosure structure, T r Is the average indoor temperature per unit time, T w Is the outdoor ambient temperature.
Further optionally, the selecting a preset heat supply parameter combination corresponding to the optimal heat supply amount includes:
selecting the air supply quantity corresponding to the optimal heat supply quantity;
and selecting the air outlet temperature corresponding to the optimal heat supply amount.
Further optionally, the determining the preset control parameter for operating the air conditioner according to the preset heating parameter combination includes:
determining the frequency of a compressor in the air conditioner and/or the opening degree of a throttling element and/or the rotating speed of an inner fan and/or the rotating speed of an outer fan;
and determining the air supply angle of the air conditioner corresponding to the preset heat supply parameter combination.
Further optionally, the determining an air supply angle of the air conditioner corresponding to the preset heating parameter combination includes:
determining the optimal air supply angle corresponding to the heat supply parameter combination in different operation stages based on the height of an air supply outlet and the size of an air inlet of the air conditioner;
and the optimal air supply angle is the air outlet angle when the heat supply parameter is combined with the air outlet of the corresponding air conditioner to achieve the optimal air flow organization form.
Further optionally, obtaining the optimal airflow pattern comprises:
according to a non-isothermal jet theory, obtaining axis speed trajectory lines corresponding to different air supply heights, different air supply parameter combinations and different indoor environment temperature states;
obtaining an air supply coverage rule of a space airflow organization based on the axis speed trajectory line;
introducing a dimensionless coefficient A, defined as:
Figure BDA0003569159780000041
wherein Δ T ho A vertical air temperature difference representing a set reference profile; t is a unit of ro Representing the indoor ambient temperature of the set control reference scheme; delta T h Represents the vertical air temperature difference; t is r Is the average indoor temperature per unit time;
wherein: when A is a negative value and the vertical air temperature difference attenuation value is a positive value, the corresponding air flow structure form is the optimal air flow structure form when the A value is the most approximate to zero;
when A is a positive value and the vertical air temperature difference attenuation value is a positive value, the corresponding air flow organization form is the optimal air flow organization form when the A value is maximum;
for air supply at the same air port height, when the value A is a negative value and the difference of the values A does not exceed a preset value, the larger the inclination angle is, the smaller the vertical air temperature difference is, and at the moment, the airflow organization form corresponding to the value A is the optimal airflow organization form.
The invention discloses an air conditioner in a second aspect, and the air conditioner adopts any one of the control methods.
Has the advantages that: the heat supply and heat supply double-efficient operation control method can indirectly monitor the heat load of the enclosure structure, solves the key problems of poor robustness and unmatched load grades in different heat leakage states of the existing air load monitoring method, realizes efficient heat supply and high-efficiency air heating of the air conditioner, reduces the operation energy consumption of the air conditioner, and realizes efficient, energy-saving and comfortable operation.
Drawings
The above and other objects, features and advantages of the present disclosure will become more apparent by describing in detail exemplary embodiments thereof with reference to the attached drawings. The drawings described below are merely exemplary embodiments of the present disclosure, and other drawings may be derived by those skilled in the art without inventive effort.
FIG. 1 illustrates a flow diagram of a control method of an embodiment;
FIG. 2 illustrates an equivalent distribution plot of indoor airflow velocity for different supply air patterns at a particular f (m, T0) for an embodiment;
FIG. 3 (a) is a graph showing a comparison of dimensionless A-value differences for different blowing patterns for a specific f (m, T0) of an embodiment;
FIG. 3 (b) is a graph illustrating a comparison of dimensionless A-value differences for different blow patterns at a particular f (m, T0) for one embodiment;
FIG. 4 (a) is a graph showing an amplitude-frequency characteristic of the A value of an embodiment;
FIG. 4 (b) is a graph showing another amplitude-frequency characteristic of the A value of an embodiment;
FIG. 5 (a) shows a response law of a real-time total heat leakage coefficient k and a temperature rise rate change rate of an embodiment;
FIG. 5 (b) shows an enlarged view of a portion of the curve in FIG. 5;
FIG. 6 is a graph comparing the control curves of the outlet air temperature for different control methods according to an embodiment;
FIG. 7 is a graph comparing control curves for k value of total heat leakage coefficient for different control methods according to an embodiment;
FIG. 8 (a) is a comparison graph of control effect without overshoot at room temperature;
FIG. 8 (b) is a comparison graph of control effect when overshoot phenomenon exists at room temperature;
FIG. 9 (a) is a diagram showing the energy saving effect of the air conditioning control system at 30 deg.C during heating operation;
fig. 9 (b) is a diagram showing the energy saving effect of the air conditioning control system setting the temperature of 27 ℃ and the heating operation;
FIG. 10 shows an overall logic diagram of the heat supply dual efficient operation control of an embodiment.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the examples of the present invention and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, and "a" and "an" generally include at least two, but do not exclude at least one, unless the context clearly dictates otherwise.
It should be understood that the term "and/or" as used herein is merely one type of association that describes an associated object, meaning that three relationships may exist, e.g., a and/or B may mean: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a good or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such good or system. Without further limitation, an element defined by the phrase "comprising a … …" does not exclude the presence of additional like elements in a commodity or system comprising the element.
The existing air conditioning system with double high-efficiency heat supply cannot realize high-efficiency energy-saving operation. The invention provides an operation control method of an air conditioning system with double high-efficiency heat supply, which is characterized in that the corresponding relation among the heat supply quantity of an air conditioner, the indoor air load and the total heat leakage load is obtained by calculating through acquiring the second-order change rate of the indoor air temperature, the air outlet temperature of the air conditioner and the air outlet quantity in real time during heating operation, the optimal heat supply quantity of the air conditioner and the corresponding heat supply parameter f (m, T0) are determined in real time, the real-time matching between the heat supply quantity and the heat leakage quantity is realized, the indoor temperature reaches the target set temperature and the comfortable air outlet temperature with smaller heat supply quantity and higher energy efficiency, the energy consumption is saved, and the high-efficiency heat supply is realized; in addition, the air supply inclination angle alpha corresponding to the optimal air supply airflow organization form can be calculated and determined according to the current heat supply parameters and regulated in real time based on the A value amplitude-frequency characteristic rule curve, so that the air heat utilization rate of an indoor human body activity area and the indoor heat leakage quantity are comprehensively optimal, and indoor efficient, energy-saving, comfortable and applicable heat operation is realized.
To further illustrate the technical solution of the present invention, the following specific examples are provided as shown in fig. 1 to 10.
As shown in fig. 1, the present embodiment provides a control method of an air conditioner, the control method including: determining target control parameters of the air conditioner according to the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner; obtaining the change relationship among the air conditioner heating load, the indoor air load and the enclosure structure load; determining the optimal heat supply quantity of the air conditioner by combining the target control parameters and the variation relation of the heat supply quantity of the air conditioner, the indoor air load and the load of the building enclosure, and selecting a preset heat supply parameter combination corresponding to the optimal heat supply quantity; determining preset control parameters of each load of the air conditioner according to the preset heating parameter combination; and controlling each load of the air conditioner to act according to preset control parameters so as to perform heating operation.
The air conditioner in the embodiment matches the heating load and the heating load grade in real time based on the indoor air load grade and the size and the heat leakage quantity of the enclosure structure, so that the indoor temperature can reach the target set temperature and the comfortable air outlet temperature by using smaller heat and higher energy efficiency, the energy consumption is saved, and the high-efficiency heat supply is realized.
In some optional manners, the determining the target control parameter of the air conditioner according to the steady-state heat leakage amount corresponding to the set working condition of the air conditioner comprises: and acquiring the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner in real time. Specifically, the step of acquiring the steady-state heat leakage amount corresponding to the set working condition of the air conditioner in real time comprises the following steps: determining a working condition section of a preset working condition section in which the set working condition of the air conditioner is located; and determining the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner according to the preset corresponding relation between the working condition interval and the steady-state heat leakage quantity.
It should be noted that the operating condition period may be divided into n groups, where n is a positive integer. The larger the value of n is, the more the divided intervals are, so that the set working condition can be more accurately matched with the corresponding steady-state heat leakage amount. Therefore, when the working condition interval is divided sufficiently, the set working condition and the steady-state heat leakage quantity can be directly correspondingly matched. When the air conditioner operates under a certain working condition, the indoor state is achieved, the heat supply quantity = the steady-state heat leakage quantity, and therefore the steady-state heat leakage quantity under the working condition can be preset or corrected.
In some alternatives, determining the target control parameter of the air conditioner based on the steady-state heat leakage amount includes: calculating the minimum heat supply amount corresponding to the steady-state heat leakage amount according to the steady-state heat leakage amount; the minimum heat supply amount is used as a target control parameter.
It should be noted that, the heat supply = the air outlet volume, the constant pressure, the specific heat cp, the air inlet and outlet temperature difference, and the control of the minimum heat supply is to control the air outlet volume and the air inlet and outlet temperature difference at the same time. Similarly, the minimum air outlet volume corresponding to the steady-state heat leakage quantity can be calculated based on the steady-state heat leakage quantity, and the control of the minimum air outlet volume is the control of the rotating speed of the inner fan.
In some alternatives, establishing a varying relationship of air conditioning heat supply, indoor air load, and enclosure load comprises: establishing a relation between the indoor air load and the building envelope load based on a response relation between the room temperature second-order change rate and the total heat leakage quantity of the building envelope; and establishing a change relation among the air conditioner heat supply, the indoor air load and the building envelope load by combining the air conditioner heat supply.
Preferably, the determining the optimal heat supply of the air conditioner by combining the target control parameter and the variation relationship among the heat supply of the air conditioner, the indoor air load and the load of the building envelope comprises the following steps: determining the minimum air outlet temperature of the air conditioner according to the steady-state heat leakage quantity; and determining the optimal heat supply amount of the air conditioner based on the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature.
In this embodiment, determining the minimum outlet air temperature of the air conditioner according to the steady-state heat leakage amount includes: taking the air conditioner heat supply amount corresponding to the steady-state heat leakage amount as the minimum heat supply amount; and calculating the minimum air outlet temperature of the air conditioner according to the minimum heat supply amount.
Wherein, the best heat supply load of confirming the air conditioner based on indoor temperature change rate, the air-out temperature of air conditioner, the air inlet temperature and the minimum air-out temperature of air conditioner includes: detecting indoor temperature, air outlet temperature of the air conditioner and air inlet temperature of the air conditioner in real time; calculating the indoor temperature change rate according to the indoor temperature; calculating real-time heat leakage quantity by combining the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature; comparing the indoor temperature with the minimum air outlet temperature to obtain a temperature comparison result, and comparing the real-time heat leakage quantity with the minimum heat supply quantity to obtain a heat supply quantity comparison result; and determining the optimal heat supply according to the temperature comparison result and the heat supply comparison result.
Preferably, the following relation is adopted in calculating the real-time heat leakage quantity:
Q s (t)＝∫ t q m c p [T c '(t)-T j '(t)]dt-ρV m c p ΔT r ＝k x (t)A(T r -T w )
wherein Q s (t) real-time heat leakage, q m Mass flow of air supplied to the air conditioner, c p Is the specific heat of air at constant pressure, T c (T) is the real-time outlet air temperature, T j (t) real-time inlet air temperature, rho indoor air density, V m Is the room volume,. DELTA.T r Is the change value of room temperature in unit time, k x (T) is the real-time heat leakage coefficient, A is the total heat exchange area inside the room enclosure structure, T r Is the mean of the interior space per unit timeMean temperature, T w Is the outdoor ambient temperature.
In some optional manners, selecting the preset heat supply parameter combination corresponding to the optimal heat supply amount includes: selecting the air supply quantity corresponding to the optimal heat supply quantity; and selecting the air outlet temperature corresponding to the optimal heat supply amount. In this embodiment, after determining the optimal heat supply amount, the heat supply parameter combination f (m, T0) can be determined according to the actual situation: (1) when the air damper (air volume m) of the air conditioner is fixed, determining the optimal air outlet temperature T0 according to the optimal heat supply quantity; (2) and when the air outlet temperature T0 of the air conditioner is not changed, determining the optimal air supply volume m according to the optimal heat supply volume.
The control method in the embodiment matches the heating load and the heating load grade in real time based on the indoor air load grade and the size and the heat leakage quantity of the building enclosure, so that the indoor temperature can reach the target set temperature and the comfortable air outlet temperature by using smaller heat and higher energy efficiency, the energy consumption is saved, and the high-efficiency heat supply is realized; based on the preset heat supply parameters f (m, T0) of the air conditioner and the indoor/outdoor working condition environment, the optimal air supply inclination angle alpha of the air conditioner is determined, so that the vertical temperature difference of a room and the heat leakage quantity of an enclosure structure are small, the comprehensive effect of energy conservation and comfort is realized, and the indoor high-efficiency heat utilization is realized.
In this embodiment, a specific control concept of the heat supply dual-efficient operation is shown in fig. 10:
one) steady-state heat leakage under the current working condition is obtained, and the minimum heat supply amount or the minimum air outlet amount corresponding to the steady-state heat leakage amount is calculated and used as a steady-state target control parameter (such as: presetting a target outlet air temperature or a target outlet air volume under a steady state);
secondly), acquiring the relation between the indoor air load and the heat leakage quantity of the enclosure structure in real time, namely acquiring the change relation between the indoor air load and the heat leakage quantity of the enclosure structure in real time based on the response relation between the room temperature second-order change rate and the heat leakage quantity of the enclosure structure;
thirdly), judging the indoor heat leakage state according to the relation between each load and the air conditioner heat supply amount, determining the optimal heat supply amount of the air conditioner according to the indoor temperature change rate delta Tr, the air outlet temperature T0 and the minimum air outlet temperature Tcmin, and presetting a heat supply parameter combination f (m, T0). Wherein: the air conditioner heat supply = air load (heat for temperature rise) + envelope heat leakage. (1) When the indoor temperature change rate delta Tr is large (temperature rise is fast) and the air outlet temperature is high, the air load is large, the heat leakage quantity is also large, and the requirement can be met only by large heat supply quantity; (2) when the air temperature change rate Δ Tr is small (close to 0), but the outlet air temperature is still high, because it is not known whether the heat leakage quantity is already minimum at this time, the former room temperature second-order change rate response is utilized (i.e. the heat supply quantity is reduced, whether the room temperature fluctuates violently or not is seen, if the room temperature is not reduced obviously, the heat leakage quantity is not minimum at this time, the outlet air temperature or the air quantity is continuously reduced to reduce the heat supply quantity, otherwise, the heat supply quantity is increased), that is: and controlling the optimal heat supply quantity of the air conditioner in real time according to the change relation of the load and the relation between the real-time air outlet temperature and the minimum air outlet temperature (or the relation between the real-time heat supply quantity and the minimum heat supply quantity).
In this embodiment, a steady-state heat leakage coefficient k (total heat leakage coefficient) is obtained based on the steady-state heat leakage amount, and the control method is described below with reference to the steady-state heat leakage coefficient k.
When the air conditioner is in heating operation, more than 75% of heat supply is used for temperature rise and heat dissipation of the building enclosure so as to maintain the target indoor environment temperature. The prior heat pump technology can realize quick heating starting, greatly improve the indoor air temperature rise rate in the early stage of operation, quickly reach the target set temperature indoors, but increase the steady-state time difference between an enclosure structure and indoor air, when air load is used as a monitoring target to control the air conditioner heat supply amount, the air load adjusting time is short, the actual indoor load state is difficult to reflect, when the parameters or the state of the enclosure structure is changed, the indoor temperature is easily overshot or undershot, the air conditioner is frequently started and stopped, and meanwhile, the problems of low operation energy efficiency and high air conditioner energy consumption exist in the high-load operation of the air conditioner. Therefore, the present invention provides an active intervention type efficient energy-saving comfortable operation control strategy for solving the above problems, and a specific control method thereof includes: and establishing a corresponding relation among the air conditioner heat supply quantity Q, the heat for air temperature rise and the heat leakage quantity Qs of the building envelope based on the second-order change rate (temperature rise rate change rate) of the room temperature and the heat leakage load response rule of the building envelope.
As shown in fig. 5 (a), when the heat for air temperature rise approaches 0 (i.e. the temperature rise rate is 0), the heat supply amount of the air conditioner is mainly used for the temperature rise and heat dissipation of the building envelope until the wall temperature reaches a steady state, and the real-time total heat leakage coefficient kx of the room gradually decreases until reaching a steady state ks. It can be seen from the figure that when the air temperature load is close to 0, the building enclosure load is still changed, when the air load is constant to 0 and the total heat leakage coefficient k curve is linearly changed, the air conditioner heat supply is only used for the temperature rise and the heat dissipation of the wall body, the larger the air conditioner heat supply is, the larger the slope k 'of the k value curve is, the shorter the time for reaching the steady state is, the maximum temperature rise rate of the building enclosure is reached, the k' value is only related to the thermophysical property of the building enclosure and the size of a room, and the heat supply is the maximum heat supply for maintaining the current room temperature.
As shown in fig. 5 (b), the indoor temperature is maintained as it is when the k' curve is changed. When the k1 'curve is changed, the k value is rapidly reduced to a steady state value, namely, the heat supply amount and the heat leakage amount are both reduced, compared with the k' curve, the room temperature is firstly reduced, then slowly increased to a target temperature value, meanwhile, the wall temperature rise rate is slowed, the time for reaching the steady state is slightly longer, but at the moment, the heat supply load of the air conditioner is reduced, the energy efficiency is improved, and the energy-saving system has a positive effect on system energy conservation. When the curve is changed into a k2', the heat supply load of the system is large, the room temperature exceeds a target value, overshoot occurs, the temperature rise rate of the enclosure structure is accelerated, and although the time for reaching a steady state is shortened, the main problems of large heat supply load, low energy efficiency and high energy consumption of the air conditioner are solved. In the prior art, a reasonable k ' curve is difficult to find in a self-adaptive manner under various working conditions and various building envelopes, so that the phenomena of k1' underregulation and k2' overshoot can occur in the conventional control, and the energy conservation and the comfort of an air conditioner are not facilitated.
In the actual control process, the k2' curve is avoided as much as possible, namely, the energy efficiency is improved as much as possible, the energy-saving and comfortable comprehensive effect is better when the curve is closer to the k ' curve, and the time for the curve to reach the steady state when the curve is closer to the k1' is longer, but the energy is more saved. Therefore, when the air load approaches to 0, how to indirectly monitor the actual load state of the enclosure structure to carry out energy-saving comfortable control on the air conditioner is the key of the control method. Through research, when the air temperature rise rate approaches to 0, the heating load of the air conditioner is subjected to multiple times of self-adaptive control to reduce the k value, the air temperature rise rate can respond in time, the response rule can be used as the basis of k value regulation, the real-time kx value change of actual operation approaches to a k curve', the influence of specific parameters of the decoupling enclosure structure on the indoor air temperature rise and the system control accuracy is decoupled, the heating load and the heat leakage quantity are subjected to self-adaptive matching, and the maximum energy-saving comfortable operation of the air conditioner is realized.
By taking a heating operation example, the method for realizing the high-efficiency energy-saving comfortable control of the airflow organization comprises the following steps:
1) When the room temperature is maintained at the specific temperature for more than T minutes and the room temperature is judged to be balanced, detecting and recording the current indoor environment temperature T r Outdoor ambient temperature T w And the current steady-state heat supply quantity Q of the air conditioner is equal to the steady-state heat leakage quantity Q of the enclosure structure s Qs = f (Tr, tw), i.e.
Q s ＝k s A(T r -T w )＝ρq v (T c -T j )＝Q g
In the formula, k s For a steady state heat leakage coefficient, T r Is the indoor ambient temperature, T w Is the outdoor ambient temperature, T c Is the temperature T of the outlet air j Is the temperature of the intake air, ρ q v The air supply mass flow of the air conditioner is shown as A, and the total heat exchange area of the room is shown as A.
2) And controlling the heat supply of the air conditioner not to be lower than the steady-state heat supply to ensure that the indoor temperature can reach the preset indoor temperature, and defining the heat supply as the lowest heat supply under the working condition. When the air conditioner is operated with the lowest heating load for heating, the energy consumption for operating the air conditioner is the lowest, but the time for reaching the temperature rise of the target temperature is the longest.
Deducing the minimum air outlet temperature T of the air conditioner heating operation according to the minimum heat supply quantity cmin (or minimum air volume):
Figure BDA0003569159780000111
in the formula, q m For air-conditioning supply mass flow, T 2 The temperature is set for the air conditioner. I.e. each blast volume q m Corresponding to a minimum outlet air temperature T cmin . It should be particularly noted that, when the comfort of the air supply temperature is to be ensured, the minimum air outlet volume is used as a reference parameter for control; when the heat exchange efficiency and the wind gear of the system are ensured to be constant, the minimum wind outlet temperature is used as a reference parameter for control.
3) At the minimum outlet air temperature T cmin The control method is exemplified by detecting and recording the indoor temperature change value delta T every 1min r And real-time air outlet temperature T of air conditioner c Real-time air inlet temperature T j Calculating the real-time heat leakage quantity Q s (t)
Q s (t)＝∫ t q m c p [T c '(t)-T j '(t)]dt-ρV m c p ΔT r ＝k x (t)A(T r -T w )
In practical application, the current air outlet temperature T is adopted c (T) and the minimum outlet air temperature T under indoor/outdoor working conditions corresponding to the wind gear cmin Difference value Δ T of c In combination with DeltaT r And judging the real-time heat leakage condition of the room.
4) According to the current indoor temperature value and the current monitoring real-time heat leakage quantity, comparing with a steady-state target value, regulating and controlling the air supply temperature and the air supply quantity of the air conditioner in real time, and reducing the grade and the total heat supply quantity of the heat supply load of the air conditioner to the maximum extent on the premise of maintaining the room temperature at the set temperature, wherein the target heat supply quantity expression is as follows:
Q goal ＝f(k x -k s ,T r ,T c ,q m )
k when the minimum outlet air temperature is used as the control reference x -k s Corresponding to Δ T c 。
When the indoor ambient temperature T r And a set temperature T 2 When the difference is larger than a, namely the room temperature does not reach a steady state, the normal and rapid heating operation is maintained to control the operation;
when the indoor ambient temperature T r And a set temperature T 2 When the difference is less than a, namely the room temperature approaches to the steady state, the indoor air load approaches to 0, and the current outlet air is detected and recordedTemperature T c 、ΔT c Judgment of Δ T c With a predetermined value Δ T c1 In the context of (a) or (b),
i when Δ T c Greater than Δ T c1 (ΔT c1 Greater than zero), i.e. the outlet air temperature is higher, according to delta T c The air outlet temperature Tc is reduced, and the temperature change value delta T is judged after the operation is continued for a min r With a preset value Δ T r1 、ΔT r2 The relationship of (1):
a when Δ T r Less than Δ T r1 When the temperature is too low, the air-out temperature T of the air conditioner is slightly increased c ；
c when Δ T r Greater than or equal to Δ T r1 And is less than or equal to Δ T r2 When the current state is maintained, the operation is continued;
b when Δ T r Greater than Δ T r2 Time, namely the indoor temperature rise rate is faster, according to the current indoor environment temperature T r And a set temperature T 2 The difference value of (2) reduces the air-out temperature T of the air conditioner c ；
II when Δ T c Is less than or equal to Delta T c1 And when the air outlet temperature is more than 0, the air outlet temperature is close to the minimum air outlet temperature, and the air outlet temperature T does not need to be adjusted frequently at the moment c According to the current indoor ambient temperature T r Rate of change with temperature Δ T r The control is carried out so as to control,
a is when T r When the set temperature is not reached, and Δ T r Less than Δ T r1 At the moment, the temperature rise rate is slow, and the air outlet temperature T is improved c ；
b is when T r When the set temperature is not reached, and Δ T r Greater than Δ T r1 Maintaining the current state to run;
c. when T is r When the set temperature is reached, and Δ T r Less than Δ T r1 Maintaining the current state to run;
when T is r When the set temperature is reached, and Δ T r Greater than Δ T r1 At the moment, the air outlet temperature is higher, and the air outlet temperature T is reduced c ；
III when Δ T c When the temperature is less than 0, the indoor environment temperature T is judged r And a set temperature T 2 In the context of (a) or (b),
a if T r Less than T 2 That is, the air conditioner can not reach the set temperature, the temperature rise change rate delta T is used r The air conditioner air outlet temperature T is improved by increasing the air conditioner air outlet temperature c ；
b if T r Greater than or equal to T 2 If the room reaches the set temperature, the current state is maintained to continue running or the air outlet temperature T is reduced c And (5) operating.
The control method is used for controlling when the indoor environment temperature is close to the set temperature, and controlling the operation energy consumption and the comfort in the rapid temperature rise-steady state operation transition stage on the premise of ensuring that the indoor overall comfort is not influenced. As shown in fig. 6, the curve (1) is a conventional outlet air temperature control, that is, a feedback adjustment is performed by using a room temperature rise condition during the operation, a step-by-step frequency reduction operation method is adopted when the room temperature approaches a set temperature, the air conditioner load is gradually reduced, and the k value curve is as shown in fig. 7.
As shown in fig. 6, the minimum outlet air temperature T is increased by adopting the above improved outlet air temperature control curve (2) cmin The control of the air conditioner and the control method design an air outlet temperature adaptive change route in a transition stage and an approximately zigzag adaptive adjustment method, so that on the premise of ensuring the comfort of indoor temperature and air outlet temperature, the heat supply amount of the air conditioner is reduced to the maximum extent, the load of the air conditioner is reduced, the energy efficiency of the system is improved, and a k value curve is shown as an energy-saving comfortable control curve in fig. 7. The maximum energy-saving curve is quickly reduced to the minimum heat supply amount when the indoor temperature is close to the set temperature, so that the air conditioner has the highest operating energy efficiency and the lowest energy efficiency, but the indoor environment temperature can be quickly rebounded and reduced, the time for the room temperature and the temperature of the enclosure structure to reach the steady state is longest, and the maximum energy-saving curve can be generally used in the indoor air preheating stage in the unmanned environment.
The room temperature control method is actively controlled in an intervening mode, and the heat load of the enclosure structure is monitored in a feedback mode, so that the adaptivity of the air conditioner in different states is improved, and the operation energy efficiency of the air conditioner is reduced to the maximum extent on the premise that the air supply comfort is guaranteed.
In some optional implementations, the determining the preset control parameter of each load of the air conditioner according to the preset heating parameter combination includes: determining the frequency of a compressor in the air conditioner and/or the opening degree of a throttling element and/or the rotating speed of an inner fan and/or the rotating speed of an outer fan; and determining the air supply angle of the air conditioner corresponding to the preset heat supply parameter combination.
Preferably, when determining the air supply angle of the air conditioner corresponding to the preset heating parameter combination, the following steps are adopted: determining the optimal air supply angle corresponding to the heat supply parameter combination in different operation stages based on the height of an air supply outlet and the size of an air inlet of the air conditioner; the optimal air supply angle is the air outlet angle when the heat supply parameter combination corresponds to the optimal air flow organization form.
When the existing heat pump air conditioner is used for heating during operation, the heat and humidity load of indoor air is far lower than that of an enclosure structure, for example, the heat for air temperature rise only accounts for 5% -15% of the total heat supply of the air conditioner in the heating temperature rise process of a common brick wall structure, and the heat exchange between indoor circulating airflow and the enclosure structure is the main reason for high energy consumption of the air conditioner in operation. The existing heat pump air conditioner mainly reduces the heat transfer temperature difference of a system (reduces the load of the system) through frequency conversion control so as to enable the unit to save energy and improve the efficiency, but when heat supply parameters are changed, the indoor airflow organization form is not changed along with the change of the heat supply parameters, because the frequency control and the airflow organization form lack of cooperative control, the indoor airflow organization cannot reach the optimal state, hot air is easy to float upwards and gather with a human body inactive area, forced convection heat exchange and dissipation with an enclosure structure are large, and therefore the heat utilization rate of indoor air is low, and the energy consumption of the air conditioner is large. The air conditioner in the embodiment can maintain the optimal airflow organization form indoors all the time by monitoring the cooperative regulation and control of the heat supply parameters of the air conditioner and the airflow organization form in real time, and improves the air heat utilization rate and the thermal comfort of a human body activity area in the operation process.
Specifically, as shown in fig. 10, the control method is based on the following specific modes when the indoor maintains the optimal airflow organization form all the time by monitoring the cooperative regulation and control of the air conditioner heating parameters and the airflow organization form in real time:
fourthly) controlling each load action of the air conditioner according to the preset heating parameter combination f (m, T0) to reach the preset value with the highest energy efficiency;
and fifthly), acquiring the optimal air supply inclination angle alpha of the air conditioner corresponding to different heat supply parameters f (m, T0), acquiring the current heat supply parameters f (m, T0) and the indoor/outdoor environment temperature state in real time, determining and regulating the optimal air supply inclination angle alpha of the air conditioner, and realizing dual-efficient operation for supplying heat (the optimal airflow organization determining method corresponds to the second part). Each load includes: compressor, inner fan, outer fan, throttle valve opening degree, etc.
The following description is directed to an optimum blowing angle α for achieving efficient and comfortable blowing corresponding to the optimum airflow pattern
The air source heat pump utilizes indoor forced airflow circulation to regulate the indoor air temperature and humidity. Researches show that the convective heat transfer strength at the edge of a temperature control area can be effectively weakened through adaptive matching control of indoor airflow circulation and a thermal environment, and the operation load of a heat pump is indirectly reduced so as to improve the operation energy efficiency.
The specific adaptive matching method is as follows:
1) According to the non-isothermal jet theory, axis speed trajectory lines corresponding to different air supply heights, different air supply parameter combinations (air speed/air quantity, air temperature and air supply angle) and different indoor environment temperature states are obtained.
The formula of the speed locus of the non-isothermal inclined incidence axis is as follows:
Figure BDA0003569159780000151
in the formula, the air outlet position is taken as an original point, x is a horizontal coordinate (air supply distance), and y is a vertical coordinate (air supply landing height); a. The 0 Is the effective air outlet area (m) 2 ) I.e. the area A of the outlet multiplied by the spray coefficient C d Where C is d =0.8; alpha is the downdip angle of air supply (the horizontal direction of the air port is taken as a reference); t is 0 Is the blast temperature (K); t is a unit of r Is the indoor ambient temperature (K); ar is an Archimedes number, and the calculation formula is as follows:
Figure BDA0003569159780000152
in the formula (I), the compound is shown in the specification,U 0 is the blowing speed (m/s); g is a gravity coefficient; Δ T = T 0 -T r 。
2) The air supply coverage rule of the large-space air flow organization can be obtained through the axis speed trajectory line, and the distribution characteristics of the air flow organization in the limited space are further researched. The characteristics of velocity flow distribution and temperature flow distribution under different working conditions and different air supply parameter combinations in a limited space are obtained through simulation or experiments.
FIG. 2 shows a comparison of contour maps of blowing speeds corresponding to different blowing opening heights and different jet angles under a specific f (m, T0). In the example, the height H =2.8m of the room and the blowing air quantity m is 1080m 3 H, supply air temperature T 0 The temperature was 48 ℃. When the height of the air port is higher, the heat floats on the roof, and the heat coverage of the human activity area is small; when the air supply angle is too large, hot air is blown to the ground seriously, the comfort in the front and the back of a room is poor due to uneven hot air diffusion, and the heat leakage of the enclosure structure is large. Therefore, it is necessary to find the optimum blowing inclination angle α.
3) Based on the heat comfort of the human body activity area and the energy saving of the air conditioner operation, the indoor environment temperature T is under the combination of certain specific heat supply and air supply parameters r Higher means less heat dissipation of the enclosure; vertical air temperature difference delta T h The smaller the size, the more heat is applied to the active region of the human body, and the better the comfort is. In order to quantitatively evaluate different air flow organization forms, a dimensionless coefficient A is introduced and defined as
Figure BDA0003569159780000161
In the formula, wherein Δ T ho A vertical air temperature difference representing a set reference profile; t is a unit of ro Representing the indoor ambient temperature of the set control reference scheme; delta T h Represents the vertical air temperature difference; t is r Is the average indoor temperature per unit time. According to the formula, the larger the value A is, the better the comprehensive effect of energy saving and comfort of the verification scheme is, but it needs to be particularly noted that the numerator and denominator of the formula must be positive values, otherwise, the discussion needs to be distinguished. The following examples are presented:
due to the upward floating characteristic of hot air flow during heating, the height L of the air opening from the ground is close to the roof, and alpha =0 degrees is taken as a reference point (at the moment, the surface of the enclosure structure has large thermal disturbance and the vertical air temperature difference is large). By adopting other air supply schemes, the vertical temperature difference is reduced, the indoor environment temperature is simultaneously improved, namely the value A is a negative value, the absolute value of the value A is reduced when the indoor environment temperature is greatly improved, the absolute value of the value A is increased when the vertical air temperature difference is reduced, and the two values have contradictions and can be judged only by adding weight analysis. In the actual design process, energy saving is generally taken as a primary index, so that the higher the heat utilization rate of the indoor air is, the better the heat utilization rate of the indoor air is, and when the indoor air temperature is higher, the vertical air temperature difference can be generally in a relatively comfortable range, so that for the situation, the judgment criterion of the value A is as follows:
(1) when the vertical delta temperature attenuation value is positive, the scheme that the value A is negative is better than the scheme that the value A is positive.
(2) When a is negative (and the vertical air temperature difference attenuation value is positive), the a value is as close to zero as possible. I.e., the value of a closest to 0, obtained in a limited number of experiments under these conditions, is optimal, where it forms the best flow pattern.
(3) When a is a positive value (and the vertical air temperature difference attenuation value is a positive value), the larger the value of a, the better; i.e. the maximum a value obtained in a limited number of experiments under the conditions resulting in the optimal gas flow pattern.
(4) For air supply at the same air port height, when the value A is a negative value and the difference of the value A does not exceed the preset difference value, the larger the inclination angle is, the smaller the vertical air temperature difference is, and the smaller the value A is, the better the air temperature difference is. I.e. the minimum a value obtained in a limited number of experiments under the conditions that result in the best gas flow pattern.
As shown in fig. 3 (a), m =1080m for different heights 3 /h，T 0 In the 48 ℃ air supply scheme, when the air supply inclination angle is larger than 40 degrees, the value A is rapidly attenuated or has a positive value, which shows that compared with a control group scheme, the indoor temperature rise effect is improved little, even the temperature rise is negatively influenced, and at the moment, the air conditioner has poor air flow organization distribution, high energy consumption and poor comfort, so that the air supply inclination angle is required to be controlled to be not larger than 40 degrees for different heights.
And further analyzing the difference of the A values of the schemes with the air supply inclination angle smaller than 40 degrees, as shown in fig. 3 (b), the A values at different heights are almost negative values, and the practical significance indicates that the schemes can simultaneously reduce the temperature difference of vertical air, improve the temperature rise heat utilization rate of indoor air and improve the ventilation and heat exchange efficiency compared with a control group. In addition, because the heat exchange occurs in the airflow circulation in the limited space, the enclosure structure interferes with the movement law of the airflow, so that the phase difference and amplitude difference of the curves of the values a of the air supply at different heights are obvious, and the values a have amplitude-frequency characteristics, but it is noted that although the values a are the same, the values a have obvious difference in practical guiding significance, and it can be known from the data analysis in fig. 3 (a) -3 (b):
when the air supply inclination angle is smaller, the value A (negative value) is close to 0 and is reduced along with the increase of the air supply inclination angle, and the influence of the enclosure structure on the air supply is small at the moment; when the air supply inclination angle is increased to a certain value, the air supply jet tends to be attached to the limited jet, the A value is suddenly changed, the inclination angle is continuously increased, the A value gradually tends to 0, the indoor temperature is high, the vertical temperature difference is small, the comprehensive effect is good, the air supply temperature distribution in the far and near areas of the air supply is uneven, meanwhile, the convection heat exchange dissipation of the wall body is increased due to the blowing of hot air, the temperature rise rate is slowed, and although the local air temperature is high and the temperature difference is small, the unevenness also needs to be considered synchronously; when the air supply inclination is too big, the air supply air current blows to the ground seriously, the air current organizes the diffusion inhomogeneous, leads to vertical air temperature difference to begin the grow, and air temperature rise rate, vertical temperature difference all worsen, are unfavorable for indoor travelling comfort and air conditioner energy-conservation.
In summary, the influence of the air supply angle on the indoor temperature and the vertical temperature difference is not the same as the simple guess of "the inclination angle is larger, the blowing area is more serious, the vertical temperature difference is smaller, and the indoor environment temperature is smaller" in most cases, but in the scheme of researching the free space jet flow and the attached jet flow in the inclination angle range, the obtained a value curve at least comprises two abrupt points, as shown in fig. 4:
for fig. 4 (a), the Oa section increases the inclination angle, the vertical air temperature difference decreases, but the temperature rise improvement effect decreases, and the larger the amplitude, the less obvious the temperature rise improvement effect; the ab section increases the inclination angle, the vertical temperature difference is small, the indoor average temperature is high, but the phenomenon of uneven local temperature rise caused by the hot air blowing to the ground is aggravated; after the point b, the vertical temperature difference is increased, the temperature rise effect is worsened and the air flow structure is not good due to the limited jet aggravation. The left diagram generally occurs when the height L of the air outlet from the ground is low. For fig. 4 (b), the section Oa increases the inclination angle, the vertical air temperature difference decreases, the improvement effect of the indoor temperature rise increases, and the increase of the inclination angle is beneficial to comfort; the ab section increases the inclination angle, the improvement effect of the indoor temperature rise is changed slightly, but the vertical air temperature difference is reduced greatly, the influence of the surrounding structure on the jet flow of the air conditioner is small, and the air flow organization form is comprehensive and better; the limited jet flow is aggravated after the point b, and the air flow structure distribution is poor. The right drawing generally occurs when the height L of the blower opening from the ground is high.
For FIG. 4 (a), the optimum gas flow structure design point is before point a, the closer the value of A is to 0 and the smaller the vertical temperature difference, the best gas flow structure combination effect. For example, when L =0.1H, the horizontal air blowing effect is optimal; when L =0.3H, the air supply effect is best when the angle is declined by about 10 degrees. For fig. 4 (b), the optimum airflow structure design point is at the ab segment, and in the case that the indoor temperature rise effect is not very different, the smaller the vertical air temperature difference is, the smaller the a value is, and the airflow structure comprehensive effect is optimum. For example, when L =0.5H, the effect of blowing and temperature rising by tilting 10 degrees is optimal, the vertical temperature difference is small and the effect of temperature rising is good when blowing by tilting 30-40 degrees, at the moment, the two schemes can achieve the better blowing effect, and the comprehensive effect of blowing by tilting 40 degrees is optimal; when the air inlet is close to the roof, the comprehensive effect is best when the air inlet is declined by 40-50 degrees for air supply.
4) Determining the proper height L of the air outlet from the ground according to the air supply inclination angle range which can be reached by the air supply tail end of the air conditioner, and training different f (m, T) by adopting the method in the step (3) 0 ) And (4) corresponding optimal air supply inclination angle.
As can be seen from fig. 3, when the heat pump air conditioner is operated for heating, the lower the height of the air port from the ground, the smaller the vertical air temperature difference, and the smaller the downward inclination angle of the air supply required for reaching the optimal value a, which has a positive effect on ensuring high air supply efficiency, high air volume and high heat exchange performance at the end of the air conditioner, the lower L is the better when the air conditioner is operated for heating. On the premise of determining the height of the air port, the optimal air supply airflow organization forms corresponding to different f (m, T0) are obtained, and a foundation is laid for realizing the real-time control of the optimal air supply airflow organization forms.
5) According to the air conditioner air-out temperature T0 (or inner pipe temperature), the air quantity m (air-out speed or inner fan rotating speed) and the indoor environment temperature Tr in the air conditioner operation process, the air supply inclination angle alpha is regulated and controlled in real time to maintain the optimal airflow organization state, the air heat utilization rate and the heat comfort of a human body activity area are improved, and the air conditioner operation energy consumption is reduced.
In addition, in the present embodiment, technical application verification is also performed on the control method. The method comprises the following specific steps:
as shown in fig. 8 (a) -8 (b), fig. 8 (a) is a comparison of control effects when there is no overshoot of room temperature, and under the same working condition, the indoor temperature rise effects of the two schemes are equivalent, and the energy-saving verification scheme has an energy-saving power consumption of 4.7kWh after 2.5h of heating and starting operation, and saves energy by 15.7% (5.58 kWh) compared with the default scheme. Fig. 8 (b) is a comparison of control effects when the overshoot phenomenon occurs at room temperature, under the same working condition, through intervention and adjustment, the energy-saving verification scheme does not have the room temperature overshoot phenomenon, the heating power-on operation is performed for 2.5h, the power consumption is 5.16kWh, and the energy is saved by 17.2% compared with the default scheme (6.028 kWh).
As shown in fig. 9 (a) -9 (b), fig. 9 (a) and 9 (b) respectively set the heating operation at 30 ℃ and 27 ℃, and the hatched area in the figure indicates the magnitude of the actual energy saving effect of the improved scheme. In addition, the output of ineffective heat consumption is controlled under the high-load working condition, the system operation energy efficiency is effectively and obviously improved, and the power consumption is reduced.
Exemplary embodiments of the present disclosure are specifically illustrated and described above. It is to be understood that the present disclosure is not limited to the precise arrangements, instrumentalities, or instrumentalities described herein; on the contrary, the disclosure is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

Claims (7)

1. A control method of an air conditioner, characterized in that the control method comprises:
determining target control parameters of the air conditioner according to the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner;
obtaining the change relationship among the air conditioner heating load, the indoor air load and the enclosure structure load;
determining the optimal heating load of the air conditioner by combining the target control parameter and the variation relation of the air conditioner heating load, the indoor air load and the enclosure structure load, and selecting a preset heating parameter combination corresponding to the optimal heating load;
determining a preset control parameter for operating the air conditioner according to the preset heating parameter combination;
controlling each load of the air conditioner to act according to the preset control parameters so as to carry out heating operation;
the step of determining the target control parameters of the air conditioner according to the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner comprises the following steps:
determining a working condition section of a preset working condition section in which the set working condition of the air conditioner is located;
determining the steady-state heat leakage quantity corresponding to the set working condition of the air conditioner according to the preset corresponding relation between the working condition interval and the steady-state heat leakage quantity;
the determining the optimal heat supply quantity of the air conditioner by combining the target control parameter and the variation relation among the heat supply quantity of the air conditioner, the indoor air load and the building envelope load comprises the following steps:
determining the minimum outlet air temperature of the air conditioner according to the steady-state heat leakage amount;
determining the optimal heat supply quantity of the air conditioner based on the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature;
the determining the minimum outlet air temperature of the air conditioner according to the steady-state heat leakage quantity comprises the following steps:
taking the air conditioner heat supply amount corresponding to the steady-state heat leakage amount as the minimum heat supply amount;
calculating the minimum air outlet temperature of the air conditioner according to the minimum heat supply amount;
the optimal heat supply amount of the air conditioner is determined based on the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature, and the optimal heat supply amount comprises the following steps:
detecting the indoor temperature, the air outlet temperature of the air conditioner and the air inlet temperature of the air conditioner in real time;
calculating the indoor temperature change rate according to the indoor temperature;
calculating real-time heat leakage quantity by combining the indoor temperature change rate, the air outlet temperature of the air conditioner, the air inlet temperature of the air conditioner and the minimum air outlet temperature;
comparing the indoor temperature with the minimum outlet air temperature to obtain a temperature comparison result, and comparing the real-time heat leakage quantity with the minimum heat supply quantity to obtain a heat supply quantity comparison result;
and determining the optimal heat supply according to the temperature comparison result and the heat supply comparison result.
2. The control method of claim 1, wherein the obtaining the variation relationship among the air conditioner heating load, the indoor air load and the building envelope load comprises:
establishing a relation between the indoor air load and the building envelope load based on a response relation between the room temperature second-order change rate and the total heat leakage quantity of the building envelope;
and combining the air conditioner heat supply amount to establish a change relation among the air conditioner heat supply amount, the indoor air load and the enclosure structure load.
3. The control method according to claim 1, wherein the following relation is adopted in calculating the real-time heat leakage amount:
Q s (t)＝∫ t q m c p [T c '(t)-T j '(t)]dt-ρV m c p ΔT r ＝k x (t)A(T r -T w )
wherein Q s (t) real-time heat leakage, q m Mass flow of air supplied to the air conditioner, c p Is air constant pressure specific heat, T' c (T) is the real-time outlet air temperature, T' j (t) real-time inlet air temperature, rho indoor air density, V m Is the room volume,. DELTA.T r Is the change value of room temperature in unit time, k x (t) real-time heat leakage coefficient, A is total heat exchange in room enclosureHeat area, T r Is the average indoor temperature per unit time, T w Is the outdoor ambient temperature.
4. The control method according to claim 1, wherein the selecting a preset heat supply parameter combination corresponding to the optimal heat supply amount comprises:
selecting the air supply quantity corresponding to the optimal heat supply quantity;
and selecting the air outlet temperature corresponding to the optimal heat supply amount.
5. The control method according to claim 1, wherein the determining preset control parameters for operating the air conditioner according to the preset heating parameter combination comprises:
determining the frequency of a compressor in the air conditioner and/or the opening degree of a throttling element and/or the rotating speed of an inner fan and/or the rotating speed of an outer fan;
and determining an air supply angle of the air conditioner corresponding to the preset heat supply parameter combination, wherein the air supply angle of the air conditioner is an air outlet angle when the air outlet of the air conditioner corresponding to the heat supply parameter combination reaches an optimal airflow organization form.
6. The control method of claim 5, wherein said obtaining the optimal airflow pattern comprises:
according to a non-isothermal jet theory, obtaining axis speed trajectory lines corresponding to different air supply heights, different air supply parameter combinations and different indoor environment temperature states;
obtaining an air supply coverage rule of a space airflow organization based on the axis speed trajectory line;
introducing a dimensionless coefficient A, defined as:
Figure FDA0004112437550000021
wherein Δ T ho A vertical air temperature differential indicative of a set reference profile; t is ro Represents the indoor ambient temperature of the set control reference protocol; delta T h Represents the vertical air temperature difference; t is a unit of r Is the average indoor temperature per unit time;
wherein: when A is a negative value and the vertical air temperature difference attenuation value is a positive value, the corresponding air flow structure form is the optimal air flow structure form when the A value is the most approximate to zero;
when A is a positive value and the vertical air temperature difference attenuation value is a positive value, the corresponding air flow organization form is the optimal air flow organization form when the A value is maximum;
and for air supply at the same air port height, when the value A is a negative value and the difference of the values A does not exceed a preset value, the larger the inclination angle is, the smaller the temperature difference of vertical air is, and the air flow organization form corresponding to the value A is the optimal air flow organization form at the moment.
7. An air conditioner characterized in that the air conditioner employs the control method of any one of claims 1 to 6.
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