CN110578998A - control method for evaporation pressure of air conditioner evaporator - Google Patents
control method for evaporation pressure of air conditioner evaporator Download PDFInfo
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- CN110578998A CN110578998A CN201910720681.1A CN201910720681A CN110578998A CN 110578998 A CN110578998 A CN 110578998A CN 201910720681 A CN201910720681 A CN 201910720681A CN 110578998 A CN110578998 A CN 110578998A
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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
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/61—Control or safety arrangements characterised by user interfaces or communication using timers
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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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
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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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
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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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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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
- F24F11/89—Arrangement or mounting of control or safety devices
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
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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
- F24F2140/00—Control inputs relating to system states
- F24F2140/10—Pressure
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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
- F24F2140/00—Control inputs relating to system states
- F24F2140/50—Load
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Abstract
The invention discloses a control method of evaporation pressure of an air conditioner evaporator, which comprises the steps of measuring indoor dry bulb temperature and relative humidity, calculating corresponding residual errors with target dry bulb temperature and target relative humidity, obtaining corresponding sensible heat load and wet load through the corresponding residual errors, further obtaining the whole indoor heat load, obtaining initial compressor frequency, then adjusting the compressor frequency to adjust the evaporation pressure of the evaporator, realizing control of the indoor relative humidity, improving the control effect, and achieving the technical effects of improving the energy conservation and comfort of a system.
Description
Technical Field
The invention relates to the technical field of control, in particular to a method for controlling the evaporation pressure of an air conditioner evaporator.
background
Nowadays, new requirements of air conditioners for thermal comfort, energy saving and the like of systems necessary for all places where people gather are gradually emerging. Therefore, it is important to improve the comfort provided by the air conditioner while developing a technology that ensures greater energy saving.
The existing evaporation pressure control technology only adopts dry bulb temperature to control evaporation pressure, has defects in improving comfort and is also large in energy consumption.
That is, the method in the prior art has the technical problem of poor control effect.
disclosure of Invention
In view of the above, the present invention provides a method for controlling an evaporation pressure of an air conditioner evaporator, so as to solve or at least partially solve the technical problem of poor control effect of the prior art method.
In order to solve the technical problem, the invention provides a method for controlling the evaporation pressure of an air conditioner evaporator, which comprises the following steps:
Step S1: measuring indoor temperature and indoor relative humidity;
Step S2: obtaining sensible heat load according to the indoor temperature and the target temperature;
Step S3: obtaining a wet load according to the indoor relative humidity and the target relative humidity;
Step S4: calculating the indoor heat load based on the sensible heat load and the wet load;
Step S5: obtaining the initial compressor frequency of the evaporator according to the indoor heat load and the compression frequency of the evaporator at the previous moment;
Step S6: the pressure of the evaporator is controlled based on the pressure reading at the outlet of the evaporator and the initial compressor frequency.
In one embodiment, step S1 specifically includes:
Measuring the indoor dry bulb temperature through an indoor dry bulb temperature sensor, and taking the indoor dry bulb temperature as the indoor temperature; the indoor relative humidity is measured by a relative humidity sensor.
in one embodiment, step S2 specifically includes:
step S2.1: calculating residual error e (t) of the dry bulb temperature according to the indoor temperature and the target temperature, and calculating a proportion value K of the residual error of the dry bulb temperature based on the residual error of the dry bulb temperaturepe(t)；
step S2.2: calculating a dry bulb temperature correction factor F (T) according to the indoor dry bulb temperature and the outdoor dry bulb temperaturei，To)；
Step S2.3: calculating sensible heat load L according to the proportional value of the dry-bulb temperature residual error and the dry-bulb temperature correction factorT：
LT＝(Kpe(t)+KDde(t)/d(t))×F(Ti，To) (1)
Wherein, KDde (t)/d (t) represents the rate of change of the dry bulb temperature residual over time, Kpand KDIs a constant.
In one embodiment, step S3 specifically includes:
Step S3.1: calculating residual error r (t) of the relative humidity according to the indoor relative humidity and the target relative humidity, and calculating a residual error proportion value K of the relative humidity based on the residual error of the relative humiditypr(t)；
Step S3.2: calculating according to the indoor relative humidity and the outdoor relative humidityRelative humidity correction factor F (R)i)；
Step S3.3: calculating the humidity load L according to the proportion value of the relative humidity residual error and the relative humidity correction factorR：
LR＝(Kpr(t)+KDdr(t)/d(t))×F(Ri) (2)
Wherein, KDdr (t)/d (t) represents the rate of change of the relative humidity residual over time, KpAnd KDis a constant.
In one embodiment, step S4 specifically includes: calculating the indoor heat load L according to the formula (3)E，
LE＝LT+a×LR (3)
wherein L isTRepresents the sensible heat load, LRRepresenting the wet load, the value of the variable a is related to the residual error of the dry bulb temperature and the relative humidity within the preset time.
In one embodiment, the variable a is determined by:
And judging whether the residual error of the dry-bulb temperature in the preset time is smaller than a first threshold, if so, judging whether the variable a is 0, otherwise, judging whether the current relative humidity is larger than the target relative humidity, if so, judging the variable a is 1, and if not, judging the variable a is-1.
In one embodiment, step S5 specifically includes: the initial compressor frequency of the evaporator is calculated according to equation (4),
fcomp，n＝fcomp，n-1×g(LE)
wherein f iscomp，nindicating the initial compressor frequency of the evaporator, fcomp，n-1denotes the compressor frequency of the evaporator at the previous moment, g (L)E) Represents the indoor heat load LEIs estimated from the indoor heat load, LEthe corrected value of (d) is proportional to the difference between the indoor dry bulb temperature and the target dry bulb temperature and the difference between the indoor relative humidity and the target relative humidity.
One or more technical solutions in the embodiments of the present application have at least one or more of the following technical effects:
The invention provides a control method of evaporating pressure of an air conditioner evaporator, which comprises the following steps of firstly, measuring indoor temperature and indoor relative humidity; secondly, acquiring sensible heat load according to the indoor temperature and the target temperature; next, obtaining a wet load according to the indoor relative humidity and the target relative humidity; then calculating the indoor heat load based on the sensible heat load and the wet load; then obtaining the initial compressor frequency of the evaporator according to the indoor heat load and the compression frequency of the evaporator at the previous moment; finally, the evaporator pressure is controlled based on the evaporator outlet pressure reading and the initial compressor frequency.
The method of the invention firstly calculates sensible heat load and wet load, then calculates indoor heat load, can control the pressure of the evaporator according to the pressure reading at the outlet of the evaporator and the initial compressor frequency, and can control the evaporation pressure of the air-conditioning evaporator by integrating the compression frequency at the previous moment, the relation between the indoor temperature and the target temperature and the relation between the indoor relative humidity and the target relative humidity as the initial compressor frequency is controlled according to the indoor heat load and the compression frequency at the previous moment, thereby improving the control effect.
Further, the method provided by the invention increases the frequency of the compressor when the set dry bulb temperature is greatly different from the indoor dry bulb temperature during the initial cooling operation so as to reduce the sensible heat load. If the room is at a relative humidity above the comfort zone of the dry bulb temperature (room temperature), the compressor frequency is slowly increased further to reduce the wet load. Therefore, the frequency of the compressor corresponding to the indoor heat load can be kept, the pressure of the evaporator is adjusted while the frequency of the compressor is adjusted, the constant evaporation pressure is maintained by adjusting the opening degree of the electronic expansion valve, the surface temperature of the evaporator is kept constant, the flow of the refrigerant is matched with the load of the evaporator, and the energy saving performance of the system is further ensured. When the indoor environment is kept in a comfortable area, the frequency of a compressor of the system is gradually reduced, the energy saving performance of the system is ensured, and meanwhile, when the indoor environment is kept in the comfortable area, the indoor dry bulb temperature and the indoor dry bulb relative humidity are also kept stable, and the condition of comfort is also ensured.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a schematic flow chart of a method for controlling the evaporating pressure of an air conditioner evaporator according to the present invention;
Fig. 2 is a route chart of an implementation of the control method provided by the present invention in the embodiment;
Fig. 3 is a flow chart of a method for determining the variable a.
Detailed Description
the invention aims to provide a control method of the evaporation pressure of an air conditioner evaporator aiming at the technical problem of poor control effect of the method in the prior art, so as to achieve the aim of improving the control effect.
In order to achieve the technical effects, the invention mainly comprises the following concepts:
The invention provides a control method of evaporation pressure of an air conditioner evaporator, which comprises the steps of measuring indoor temperature and indoor relative humidity, obtaining sensible heat load according to the indoor temperature and target temperature, obtaining wet load according to the indoor relative humidity and target relative humidity, further obtaining the whole indoor heat load, obtaining initial compressor frequency, and then adjusting the compressor frequency to adjust the evaporation pressure of the evaporator and realize the control of the indoor relative humidity, thereby improving the energy conservation and comfort of a system and improving the control effect.
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 present embodiment provides a method for controlling an evaporation pressure of an air conditioner evaporator, please refer to fig. 1, the method includes:
Step S1: the indoor temperature and the indoor relative humidity were measured.
In specific implementation, the measurement can be performed through a temperature sensor and a humidity sensor.
In one embodiment, step S1 specifically includes:
Measuring the indoor dry bulb temperature through an indoor dry bulb temperature sensor, and taking the indoor dry bulb temperature as the indoor temperature; the indoor relative humidity is measured by a relative humidity sensor.
Specifically, the indoor temperature and the indoor relative humidity obtained after measurement can be transmitted by the control chip for subsequent calculation.
Step S2: sensible heat load is obtained according to the indoor temperature and the target temperature.
Wherein, step S2 specifically includes:
Step S2.1: calculating residual error e (t) of the dry bulb temperature according to the indoor temperature and the target temperature, and calculating a proportion value K of the residual error of the dry bulb temperature based on the residual error of the dry bulb temperaturepe(t)；
Step S2.2: calculating a dry bulb temperature correction factor F (T) according to the indoor dry bulb temperature and the outdoor dry bulb temperaturei，To)；
Step S2.3: calculating sensible heat load L according to the proportional value of the dry-bulb temperature residual error and the dry-bulb temperature correction factorT：
LT＝(Kpe(t)+KDde(t)/d(t))×F(Ti，To) (1)
Wherein, KDde (t)/d (t) represents the rate of change of the dry bulb temperature residual over time, KpAnd KDIs a constant.
Specifically, after the dry bulb temperature in the room is obtained through measurement, the corresponding dry bulb temperature residual error is obtained through the transmission of the control chip and the calculation of the set target dry bulb temperature. And further calculating the proportional value K of the temperature residual error of the dry bulbpe (t), the proportional value is in direct proportion to the size of the dry-bulb temperature residual error. Then obtaining the change rate K of the dry bulb temperature residual error along with the timeDde (T)/d (T), estimating a dry bulb temperature correction factor F (T) according to the indoor and outdoor dry bulb temperaturesi，To)。
And when the outdoor dry bulb temperature is less than 0 ℃, the dry bulb temperature is not corrected.
step S3: the wet load is obtained based on the indoor relative humidity and the target relative humidity.
Wherein, step S3 specifically includes:
Step S3.1: calculating residual error r (t) of the relative humidity according to the indoor relative humidity and the target relative humidity, and calculating a residual error proportion value K of the relative humidity based on the residual error of the relative humiditypr(t)；
Step S3.2: calculating a relative humidity correction factor F (R) based on the indoor relative humidity and the outdoor relative humidityi)；
Step S3.3: calculating the humidity load L according to the proportion value of the relative humidity residual error and the relative humidity correction factorR：
LR＝(Kpr(t)+KDdr(t)/d(t))×F(Ri) (2)
Wherein, KDdr (t)/d (t) represents the rate of change of the relative humidity residual over time, KpAnd KDIs a constant.
specifically, after the indoor relative humidity is obtained through measurement, the corresponding relative humidity residual error is obtained through the transmission of the control chip and the set target relative humidity calculation, and the proportion value K of the relative humidity residual error is calculatedpr (t), which is proportional to the magnitude of the rh residual. The rate of change K of the relative humidity residual over time was also calculatedDdr (t)/d (t), according to the relative humidity RiEstimating a relative humidity correction factor F (R)i). Finally, the wet load L is obtained according to the formula (2)R。
Step S4: based on the sensible heat load and the wet load, the indoor heat load is calculated.
Specifically, step S4 specifically includes: calculating the indoor heat load L according to the formula (3)E，
LE＝LT+a×LR (3)
Wherein L isTRepresents the sensible heat load, LRRepresenting the wet load, the value of the variable a is related to the residual error of the dry bulb temperature and the relative humidity within the preset time.
Specifically, the method provided by the invention calculates sensible heat load and wet load, and further calculates heat load of the whole room. And meanwhile, the corrected value of the heat load of the whole room is obtained by estimating the air load of the whole room. The value is a control value which is increased progressively according to the operation mode and is in direct proportion to the difference between the indoor dry bulb temperature and the target dry bulb temperature and the difference between the indoor relative humidity and the target relative humidity.
Wherein, the variable a is determined in the following way:
And judging whether the residual error of the dry-bulb temperature in the preset time is smaller than a first threshold, if so, judging whether the variable a is 0, otherwise, judging whether the current relative humidity is larger than the target relative humidity, if so, judging the variable a is 1, and if not, judging the variable a is-1.
Specifically, the preset time and the first threshold may be set according to actual conditions and test conditions, for example, 60, 70, 80, 90, 100 seconds, etc., and the first threshold is 0.1, 0.2, 0.3 degrees, please refer to fig. 3, which is a determination manner of the variable a. Centralized data for indoor conditions include dry bulb temperature and relative humidity.
If the dry bulb temperature residual error at a certain moment e (t)n-1Residual error from dry bulb temperature after 90 seconds e (t)nIn contrast, below 0.2 ℃, the variable a is 0, which indicates that the indoor air is cooled by less than 0.2 ℃ for 90 seconds, i.e., there is still a significant sensible heat load L in the roomT. Thus, by setting the variable a to 0, the entire chamber in the above formula can be consideredInternal thermal load LEIs the sensible heat load LT. In this case, according to the sensible heat load LTTo measure the entire indoor heat load LE。
If sensible heat load LTvery much, only dry bulb temperature is controlled first, since humans are seven to nine times more sensitive to changes in dry bulb temperature than to changes in humidity. Secondly, if the temperature residual error e (t) of the dry bulb within a certain timen-1dry bulb temperature residual e (t) after more than 90 secondsn0.2 ℃ higher, sensible heat load LTit will decrease. At this time, the relative humidity is further judged, if the relative humidity R isiExceeding the target relative humidity Ri，targetThen the whole indoor heat load LEby loading sensible heat LTPlus the wet load LRWhen the measurement is performed, a is 1. Finally, if sensible load LTReduced relative humidity RiLess than target relative humidity Ri，targetThen the load L can be loaded by the sensible heatTMinus the moisture load LRTo estimate the indoor thermal load, a is-1.
Step S5: and obtaining the initial compressor frequency of the evaporator according to the indoor heat load and the compression frequency of the evaporator at the previous moment.
Wherein, step S5 specifically includes: the initial compressor frequency of the evaporator is calculated according to equation (4),
fcomp，n＝fcomp，n-1×g(LE)
Wherein f iscomp，nIndicating the initial compressor frequency of the evaporator, fcomp，n-1Denotes the compressor frequency of the evaporator at the previous moment, g (L)E) Represents the indoor heat load LEIs estimated from the indoor heat load, LEThe corrected value of (d) is proportional to the difference between the indoor dry bulb temperature and the target dry bulb temperature and the difference between the indoor relative humidity and the target relative humidity.
Specifically, g (L)E) The proportion can be calculated according to the difference between the indoor dry bulb temperature and the set dry bulb temperature and the difference between the indoor relative humidity and the target relative humidity to obtain the proportion value,A specific expression form can be obtained.
Step S6: the pressure of the evaporator is controlled based on the pressure reading at the outlet of the evaporator and the initial compressor frequency.
specifically, by calculating the correction value of the heat load of the entire room and the compressor frequency at the previous time, the initial compressor frequency can be calculated. Therefore, the frequency of the compressor can be adjusted by utilizing the temperature and the relative humidity of the dry bulb, and the evaporation pressure of the air conditioner evaporator can be adjusted. The invention provides an evaporation pressure control method, which can change the evaporation pressure according to the dry bulb temperature and the relative air humidity. When switching between the conventional control method and the newly proposed control method, a performance test was performed on one and the same air conditioner. The results show that the method not only improves the thermal comfort of indoor air, but also improves the energy utilization efficiency.
In order to more clearly illustrate the specific implementation process of the method provided by the present invention, the following is described in detail by using fig. 2.
The rightmost side of fig. 2 shows a room in which a dry bulb temperature sensor and a relative humidity sensor are installed, the relative humidity sensor being composed of a front end sensor part, a rear Printed Circuit Board (PCB), and a housing protecting the relative humidity sensor. The relative humidity sensor part is composed of a dehumidifying film containing dehumidifying liquid on a plate. The resistance of the dehumidifying liquid changes with the change of water vapor in the air. Σ denotes the joint action of two factors, and X denotes multiplication.
The two sensors measure the temperature and the relative humidity of the dry bulb in the room, the temperature and the relative humidity are respectively transmitted to the left side to be calculated with the target temperature and the target relative humidity, the residual error e (t) of the dry bulb temperature is estimated, and the proportion value K of the residual error of the dry bulb temperature is calculatedpe (t), the proportional value is in direct proportion to the size of the dry-bulb temperature residual error, and the change rate K of the dry-bulb temperature residual error along with the time is further calculatedDde (T)/d (T), estimating a dry bulb temperature correction factor F (T) according to the indoor and outdoor dry bulb temperaturesi，To). Similarly, the residual error r (t) of the relative humidity is estimated according to the measured relative humidity and the target relative humidity, and the proportion value K of the residual error of the relative humidity is calculatedpr (t), which is proportional to the magnitude of the rh residual. Then further calculating the change rate K of the residual error of the relative humidity along with the timeDdr (t)/d (t), and furthermore, in terms of relative humidity RiEstimating a relative humidity correction factor F (R)i) Finally, the wet load L is obtainedR。
after calculating the sensible heat load and the wet load, the indoor heat load may be calculated according to equation (3), and then the initial compressor frequency may be obtained according to equation (4). Compressor frequency adjustments may then be made to adjust indoor relative humidity and evaporator pressure, with the actual evaporator pressure being measured as the operating conditions of the relevant components of the main components of the heat pump system. And changing the frequency of the compressor according to the change of the set dry bulb temperature and the change of the relative humidity and the relative humidity so as to enable the target evaporation pressure to be equal to the actual evaporation pressure. The evaporator evaporating pressure is adjusted by reducing the frequency of the compressor along with the reduction of the load, and the opening degree of the electronic expansion valve is adjusted to maintain constant evaporating pressure, so that the surface temperature of the evaporator is kept constant, and the flow rate of the refrigerant is matched with the load of the evaporator.
Generally, compared with the prior art, the technical scheme of the invention has the following advantages and beneficial effects:
The invention provides an energy-saving and comfortable control method for the evaporation pressure of an air conditioner evaporator, wherein during the initial cooling operation, if the difference between the set dry bulb temperature and the indoor dry bulb temperature is larger, the frequency of a compressor is increased to reduce the dry bulb temperature load. If the relative humidity in such a dry bulb room exceeds the comfort zone, the compressor frequency is further increased to reduce the relative humidity load. As a result, the frequency of the compressor corresponding to the indoor load can be maintained. In this way, when the comfort zone is exceeded, the relative humidity load can also be adjusted by increasing the compressor frequency, so that the operating conditions always meet the comfort requirements. The pressure of the evaporator is adjusted while the frequency of the compressor is adjusted, and the opening degree of the electronic expansion valve is adjusted to maintain constant evaporation pressure, so that the surface temperature of the evaporator is kept constant, the flow of the refrigerant is matched with the load of the evaporator, and the energy saving performance of the system is further ensured.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, it is intended that the appended claims be interpreted as including preferred embodiments and all such alterations and modifications as fall within the scope of the invention.
it will be apparent to those skilled in the art that various modifications and variations can be made in the embodiments of the present invention without departing from the spirit or scope of the embodiments of the invention. Thus, if such modifications and variations of the embodiments of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to encompass such modifications and variations.
Claims (7)
1. A control method for the evaporation pressure of an air conditioner evaporator is characterized by comprising the following steps:
Step S1: measuring indoor temperature and indoor relative humidity;
Step S2: obtaining sensible heat load according to the indoor temperature and the target temperature;
Step S3: obtaining a wet load according to the indoor relative humidity and the target relative humidity;
Step S4: calculating the indoor heat load based on the sensible heat load and the wet load;
Step S5: obtaining the initial compressor frequency of the evaporator according to the indoor heat load and the compression frequency of the evaporator at the previous moment;
Step S6: the pressure of the evaporator is controlled based on the pressure reading at the outlet of the evaporator and the initial compressor frequency.
2. The method according to claim 1, wherein step S1 specifically comprises:
Measuring the indoor dry bulb temperature through an indoor dry bulb temperature sensor, and taking the indoor dry bulb temperature as the indoor temperature; the indoor relative humidity is measured by a relative humidity sensor.
3. The method according to claim 1, wherein step S2 specifically comprises:
Step S2.1: calculating residual error e (t) of the dry bulb temperature according to the indoor temperature and the target temperature, and calculating a proportion value K of the residual error of the dry bulb temperature based on the residual error of the dry bulb temperaturepe(t)；
Step S2.2: calculating a dry bulb temperature correction factor F (T) according to the indoor dry bulb temperature and the outdoor dry bulb temperaturei，To)；
Step S2.3: calculating sensible heat load L according to the proportional value of the dry-bulb temperature residual error and the dry-bulb temperature correction factorT：
LT＝(Kpe(t)+KDde(t)/d(t))×F(Ti，To) (1)
wherein, KDde (t)/d (t) represents the rate of change of the dry bulb temperature residual over time, KpAnd KDIs a constant.
4. the method according to claim 1, wherein step S3 specifically comprises:
Step S3.1: calculating residual error r (t) of the relative humidity according to the indoor relative humidity and the target relative humidity, and calculating a residual error proportion value K of the relative humidity based on the residual error of the relative humiditypr(t)；
step S3.2: calculating a relative humidity correction factor F (R) based on the indoor relative humidity and the outdoor relative humidityi)；
step S3.3: calculating the humidity load L according to the proportion value of the relative humidity residual error and the relative humidity correction factorR：
LR＝(Kpr(t)+KDdr(t)/d(t))×F(Ri) (2)
Wherein, KDdr (t)/d (t) represents the rate of change of the relative humidity residual over time, KpAnd KDis a constant.
5. The method of claim 1, wherein the method further comprises the step of applying a voltage to the substrateStep S4 specifically includes: calculating the indoor heat load L according to the formula (3)E，
LE＝LT+a×LR (3)
Wherein L isTRepresents the sensible heat load, LRrepresenting the wet load, the value of the variable a is related to the residual error of the dry bulb temperature and the relative humidity within the preset time.
6. The method of claim 5, wherein the variable a is determined by:
And judging whether the residual error of the dry-bulb temperature in the preset time is smaller than a first threshold, if so, judging whether the variable a is 0, otherwise, judging whether the current relative humidity is larger than the target relative humidity, if so, judging the variable a is 1, and if not, judging the variable a is-1.
7. The method according to claim 1, wherein step S5 specifically comprises: the initial compressor frequency of the evaporator is calculated according to equation (4),
fcomp，n＝fcomp，n-1×g(LE)
Wherein f iscomp，nIndicating the initial compressor frequency of the evaporator, fcomp，n-1Denotes the compressor frequency of the evaporator at the previous moment, g (L)E) Represents the indoor heat load LEis estimated from the indoor heat load, LEThe corrected value of (d) is proportional to the difference between the indoor dry bulb temperature and the target dry bulb temperature and the difference between the indoor relative humidity and the target relative humidity.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111829206A (en) * | 2020-06-04 | 2020-10-27 | 广东奥伯特节能设备有限公司 | Unloading expansion valve heat pump unit and control method and device thereof and storage medium |
| CN114688705A (en) * | 2022-04-14 | 2022-07-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Heat exchanger, air conditioning system and control method of air conditioning system |
| WO2023273685A1 (en) * | 2021-06-30 | 2023-01-05 | 美的集团股份有限公司 | Air conditioner refrigeration control method, air conditioner and computer-readable storage medium |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54146447A (en) * | 1978-05-04 | 1979-11-15 | Mitsubishi Electric Corp | Air conditioner |
| CN1946974A (en) * | 2004-03-31 | 2007-04-11 | 大金工业株式会社 | Air conditioner and its control method |
| CN101603751A (en) * | 2009-07-15 | 2009-12-16 | 北京科技大学 | A kind of frequency conversion energy-saving control method of refrigeration system |
| CN102317699A (en) * | 2009-02-20 | 2012-01-11 | 三菱电机株式会社 | Use-side unit and air conditioner |
| CN105864920A (en) * | 2016-03-31 | 2016-08-17 | 华为技术有限公司 | Light-load dehumidification method and air conditioner |
| CN108518821A (en) * | 2018-06-19 | 2018-09-11 | 广东美的制冷设备有限公司 | The control method and device of air-conditioning |
| CN108800466A (en) * | 2018-06-19 | 2018-11-13 | 广东美的制冷设备有限公司 | The control method and device of air-conditioning |
| CN109654660A (en) * | 2018-12-24 | 2019-04-19 | 美的集团武汉制冷设备有限公司 | Air conditioner and its control method and device |
-
2019
- 2019-08-06 CN CN201910720681.1A patent/CN110578998A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54146447A (en) * | 1978-05-04 | 1979-11-15 | Mitsubishi Electric Corp | Air conditioner |
| CN1946974A (en) * | 2004-03-31 | 2007-04-11 | 大金工业株式会社 | Air conditioner and its control method |
| CN102317699A (en) * | 2009-02-20 | 2012-01-11 | 三菱电机株式会社 | Use-side unit and air conditioner |
| CN101603751A (en) * | 2009-07-15 | 2009-12-16 | 北京科技大学 | A kind of frequency conversion energy-saving control method of refrigeration system |
| CN105864920A (en) * | 2016-03-31 | 2016-08-17 | 华为技术有限公司 | Light-load dehumidification method and air conditioner |
| CN108518821A (en) * | 2018-06-19 | 2018-09-11 | 广东美的制冷设备有限公司 | The control method and device of air-conditioning |
| CN108800466A (en) * | 2018-06-19 | 2018-11-13 | 广东美的制冷设备有限公司 | The control method and device of air-conditioning |
| CN109654660A (en) * | 2018-12-24 | 2019-04-19 | 美的集团武汉制冷设备有限公司 | Air conditioner and its control method and device |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111829206A (en) * | 2020-06-04 | 2020-10-27 | 广东奥伯特节能设备有限公司 | Unloading expansion valve heat pump unit and control method and device thereof and storage medium |
| CN111829206B (en) * | 2020-06-04 | 2021-12-07 | 广东奥伯特节能设备有限公司 | Unloading expansion valve heat pump unit and control method and device thereof and storage medium |
| WO2023273685A1 (en) * | 2021-06-30 | 2023-01-05 | 美的集团股份有限公司 | Air conditioner refrigeration control method, air conditioner and computer-readable storage medium |
| CN114688705A (en) * | 2022-04-14 | 2022-07-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Heat exchanger, air conditioning system and control method of air conditioning system |
| CN114688705B (en) * | 2022-04-14 | 2023-10-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Heat exchanger, air conditioning system and control method of air conditioning system |
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