CN118066665A - Air conditioner, dehumidification control method and device thereof, storage medium and program product - Google Patents

Air conditioner, dehumidification control method and device thereof, storage medium and program product Download PDF

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Publication number
CN118066665A
CN118066665A CN202410460000.3A CN202410460000A CN118066665A CN 118066665 A CN118066665 A CN 118066665A CN 202410460000 A CN202410460000 A CN 202410460000A CN 118066665 A CN118066665 A CN 118066665A
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temperature
air conditioner
dehumidification
air
evaporation
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王晓倩
林金煌
何振健
李木湖
刘钊行
冯青龙
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Abstract

The invention provides an air conditioner, a dehumidification control method, a device, a storage medium and a program product thereof, wherein the dehumidification control method comprises the following steps: detecting current indoor environment parameters and system parameters of the air conditioner when the air conditioner is in dehumidification operation; determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the detected current indoor environment parameters and the detected system parameters of the air conditioner, and taking the evaporation temperature as the initial evaporation temperature of the air conditioner; and controlling the air conditioner to operate according to the determined initial evaporation temperature, and correcting the evaporation temperature according to the difference value between the air outlet temperature and the dehumidification set temperature and the change rate of the air inlet temperature. The scheme provided by the invention can ensure the dehumidification effect and simultaneously meet the comfort level of the user.

Description

Air conditioner, dehumidification control method and device thereof, storage medium and program product
Technical Field
The present invention relates to the field of control, and in particular, to an air conditioner, and a dehumidification control method, apparatus, storage medium, and program product thereof.
Background
Although most air conditioners have a dehumidification function, the dehumidification function is basically and temporarily not different from refrigeration, and the operation speed of an indoor fan is reduced or the air conditioner is operated in an intermittent operation mode only according to the indoor environment temperature, and the control mode reduces the air supply temperature during actual dehumidification, so that the indoor temperature is obviously reduced and is not matched with the comfort requirement of a user.
In order to solve the comfort problem, the related technical scheme mainly determines the target moisture content according to the set indoor temperature and indoor humidity, and determines to enter different dehumidification modes according to the relative sizes of the current moisture content and the target moisture content, and theoretical analysis is not performed by combining the dehumidification characteristics of the air conditioner and the air treatment process, and judgment is performed only according to the environmental parameters and preset target parameters, so that the control method is relatively simple and lacks theoretical support.
Disclosure of Invention
The present invention is directed to an air conditioner, a dehumidifying control method, an apparatus, a storage medium and a program product thereof, which overcome the above-mentioned drawbacks of the related art, and solve the problems that the dehumidifying scheme of the related art does not combine the dehumidifying characteristics of the air conditioner and the air treatment process.
In one aspect, the present invention provides a dehumidification control method of an air conditioner, including: detecting current indoor environment parameters and system parameters of the air conditioner when the air conditioner is in dehumidification operation; determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the detected current indoor environment parameters and the detected system parameters of the air conditioner, and taking the evaporation temperature as the initial evaporation temperature of the air conditioner; controlling the air conditioner to operate according to the determined initial evaporation temperature; and carrying out correction control on the evaporating temperature according to the difference value between the air outlet temperature and the dehumidification set temperature of the air conditioner.
Optionally, the indoor environment parameters include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner comprise: condensing temperature; according to the detected current indoor environment parameter and the detected system parameter of the air conditioner, determining the evaporation temperature corresponding to the current maximum dehumidification amount comprises the following steps: acquiring a compressor performance curve corresponding to the current condensing temperature according to the current condensing temperature of the air conditioner; and determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature and the compressor performance curve corresponding to the current condensation temperature.
Optionally, the method further comprises: and performing correction control of the evaporating temperature according to the difference value between the air outlet temperature and the dehumidification set temperature of the air conditioner, wherein the correction control comprises the following steps: judging whether the temperature difference DeltaT between the air outlet temperature T Air outlet and the dehumidification set temperature T Setting up is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2; if the temperature difference DeltaT is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2, the current running state is kept to run; if the temperature difference DeltaT is smaller than the first preset temperature difference DeltaT 1 or larger than the second preset temperature difference DeltaT 2, the evaporation temperature is corrected and controlled according to the temperature difference DeltaT, or the evaporation temperature is corrected and controlled according to the temperature difference DeltaT and the change rate of the air inlet temperature.
Optionally, the correction control of the evaporating temperature is performed according to the temperature difference Δt, including: if the temperature difference DeltaT is smaller than a first preset temperature difference DeltaT 1, correcting the evaporating temperature of the air conditioner by reducing the frequency of the compressor; if the temperature difference DeltaT is larger than a second preset temperature difference DeltaT 2, correcting the evaporating temperature of the air conditioner by increasing the frequency of the compressor; and/or, carrying out correction control on the evaporating temperature according to the temperature difference DeltaT and the change rate of the inlet air temperature, wherein the correction control comprises the following steps: determining an evaporation temperature change value delta tevp according to a preset rule according to the temperature difference delta T and the change rate of the inlet air temperature; and correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature change value delta tevp.
Optionally, determining the evaporation temperature change value Δ tevp according to a preset rule according to the temperature difference Δt and the change rate of the intake air temperature includes: according to the temperature difference DeltaT and the change rate of the inlet air temperature, determining an evaporation temperature change value Delta tevp according to the following formula: Δt (delta t) evp=a1(T Air outlet -T Setting up )+b1△T Air inlet /△S+c1
Wherein Δt evp represents an evaporation temperature change value, T Air outlet represents an air outlet temperature, T Setting up represents a dehumidification set temperature, Δt Air inlet /. DELTA.S represents a change rate of an air inlet temperature in the DeltaS time, and a1, b1, c1 are fitting coefficients.
Another aspect of the present invention provides a dehumidification control device of an air conditioner, comprising: the detection unit is used for detecting the current indoor environment parameters and the system parameters of the air conditioner when the air conditioner is in dehumidification operation; the determining unit is used for determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor environment parameter and the system parameter of the air conditioner detected by the detecting unit and taking the evaporation temperature as the initial evaporation temperature of the air conditioner; the control unit is used for controlling the air conditioner to operate according to the determined initial evaporation temperature; and the correction control unit is used for carrying out correction control on the evaporation temperature according to the difference value between the air outlet temperature and the dehumidification set temperature of the air conditioner.
Optionally, the indoor environment parameters include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner comprise: condensing temperature; the determining unit determines an evaporation temperature corresponding to a current maximum dehumidification amount according to the detected current indoor environment parameter and the detected system parameter of the air conditioner, and includes: acquiring a compressor performance curve corresponding to the current condensing temperature according to the current condensing temperature of the air conditioner; and determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature and the compressor performance curve corresponding to the current condensation temperature.
Optionally, the correction control unit performs correction control of the evaporation temperature according to a difference between the air outlet temperature and the dehumidification setting temperature of the air conditioner, and includes: judging whether the temperature difference DeltaT between the air outlet temperature T Air outlet and the dehumidification set temperature T Setting up is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2; if the temperature difference DeltaT is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2, the current running state is kept to run; if the temperature difference DeltaT is smaller than the first preset temperature difference DeltaT 1 or larger than the second preset temperature difference DeltaT 2, the evaporation temperature is corrected and controlled according to the temperature difference DeltaT, or the evaporation temperature is corrected and controlled according to the temperature difference DeltaT and the change rate of the air inlet temperature.
Optionally, the correction control unit performs correction control of the evaporation temperature according to the temperature difference Δt, and includes: if the temperature difference DeltaT is smaller than a first preset temperature difference DeltaT 1, correcting the evaporating temperature of the air conditioner by reducing the frequency of the compressor; if the temperature difference DeltaT is larger than a second preset temperature difference DeltaT 2, correcting the evaporating temperature of the air conditioner by increasing the frequency of the compressor; and/or, the correction control unit performs correction control of the evaporating temperature according to the temperature difference DeltaT and the change rate of the air inlet temperature, and includes: determining an evaporation temperature change value delta tevp according to a preset rule according to the temperature difference delta T and the change rate of the inlet air temperature; and correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature change value delta tevp.
Optionally, determining the evaporation temperature change value Δ tevp according to a preset rule according to the temperature difference Δt and the change rate of the intake air temperature includes: according to the temperature difference DeltaT and the change rate of the inlet air temperature, determining an evaporation temperature change value Delta tevp according to the following formula: Δt (delta t) evp=a1(T Air outlet -T Setting up )+b1△T Air inlet /△S+c1
Wherein Δt evp represents an evaporation temperature change value, T Air outlet represents an air outlet temperature, T Setting up represents a dehumidification set temperature, Δt Air inlet /. DELTA.S represents a change rate of an air inlet temperature in the DeltaS time, and a1, b1, c1 are fitting coefficients.
In a further aspect the invention provides a storage medium having stored thereon a computer program which when executed by a processor performs the steps of any of the methods described above.
In a further aspect the invention provides an air conditioner comprising a processor, a memory and a computer program stored on the memory and executable on the processor, the processor implementing the steps of any of the methods described hereinbefore when the program is executed.
In still another aspect, the present invention provides an air conditioner, including any one of the foregoing dehumidification control devices.
In a further aspect the invention provides a computer program product comprising a computer program which, when executed by a processor, implements the steps of any of the methods described above.
According to the technical scheme of the invention, the relation between the evaporation temperature and the dehumidification amount of the air conditioner is determined by combining the performance curve of the compressor, the dehumidification evaporation temperature with the maximum dehumidification amount is determined as the dehumidification evaporation temperature, and the operation of the air conditioner is controlled according to the determined initial evaporation temperature, so that the dehumidification efficiency can be improved.
According to the scheme provided by the invention, the evaporation temperature is corrected according to the temperature difference between the air outlet temperature and the dehumidification set temperature, so that the difference between the air outlet temperature and the dehumidification set temperature is ensured to be within a certain temperature difference range, and the comfort level of a user can be met while the dehumidification effect is ensured.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and do not constitute a limitation on the invention. In the drawings:
Fig. 1 is a schematic diagram of a method of an embodiment of a dehumidification control method of an air conditioner according to the present invention;
FIG. 2 is a flow chart of one embodiment of the step of determining the evaporating temperature corresponding to the current maximum dehumidification based on the detected current indoor environment parameter and the system parameter of the air conditioner;
FIG. 3 shows an example of compressor performance curves for different condensing temperatures;
FIG. 4 is an air treatment process of the surface of a cold coil of an indoor heat exchanger during cooling and dehumidification of an air conditioner;
FIG. 5 is a schematic flow chart of a specific embodiment of the step of performing the correction control of the evaporating temperature according to the difference between the air-out temperature and the dehumidification setting temperature of the air conditioner;
FIG. 6 is a schematic diagram of a method of controlling dehumidification of an air conditioner according to an embodiment of the present disclosure;
FIG. 7 is a schematic diagram of a method of controlling dehumidification of an air conditioner according to an embodiment of the present disclosure;
Fig. 8 is a block diagram illustrating a structure of an embodiment of a dehumidifying control device for air conditioner according to the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to specific embodiments of the present invention and corresponding drawings. It will be apparent that the described embodiments are only some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present invention and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that the embodiments of the invention described herein may be implemented in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
Fig. 1 is a schematic diagram of a method of an embodiment of a dehumidification control method of an air conditioner according to the present invention.
As shown in fig. 1, the method for controlling dehumidification of an air conditioner according to an embodiment of the present invention includes at least step S110, step S120, and step S130.
Step S110, detecting current indoor environment parameters and system parameters of the air conditioner when the air conditioner is in dehumidification operation.
In a specific embodiment, the indoor environment parameters may specifically include: indoor dry bulb temperature and indoor wet bulb temperature. The system parameters may specifically include: dehumidification set temperature, inlet air temperature, outlet air temperature, condensation temperature and evaporation temperature.
Step S120, determining an evaporation temperature corresponding to the current maximum dehumidification amount according to the detected current indoor environment parameter and the detected system parameter of the air conditioner, and using the evaporation temperature as an initial evaporation temperature of the air conditioner.
Specifically, according to the detected current indoor environment parameter, determining the evaporation temperature corresponding to the current maximum dehumidification amount by combining with the compressor performance curve of the air conditioner, and taking the evaporation temperature as the current initial evaporation temperature of the air conditioner. The indoor environment parameters may specifically include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner specifically may include: condensation temperature.
Fig. 2 is a flowchart of a specific embodiment of the step of determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the detected current indoor environment parameter and the detected system parameter of the air conditioner. As shown in fig. 2, in a specific embodiment, the step of determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the detected current indoor environment parameter and the detected system parameter of the air conditioner includes step S121 and step S122.
Step S121, obtaining a compressor performance curve corresponding to the current condensation temperature according to the current condensation temperature of the air conditioner.
The compressors of different models correspond to different compressor performance curves, and the output of the refrigerating capacity of the compressor and the evaporating temperature are in linear relation at different condensing temperatures. The compressor performance curve includes: and the relation curve of the refrigerating capacity and the evaporating temperature of the compressor at different condensing temperatures, namely different condensing temperatures correspond to different compressor performance curves. Fig. 3 shows an example of the linear relationship between the output of the compressor refrigeration and the evaporation temperature at different condensation temperatures. As shown in FIG. 3, the abscissa represents the evaporation temperature (in. Degree. C.) and the ordinate represents the compressor cooling capacity (in. Degree. W.), and the curves in FIG. 3 are compressor performance curves at different condensing temperatures, respectively.
The compressor performance curve may be expressed as a linear relationship of compressor capacity versus evaporating temperature at different condensing temperatures, q= A tevp +b, where tevp is evaporating temperature; q is compressor capacity (e.g., in kw); a is the increment of refrigerating capacity when the evaporating temperature rises by a unit temperature value, for example, the increment of refrigerating capacity when the evaporating temperature rises by 1 ℃, for example, the unit can be kw/DEG C; b is the cooling capacity (for example, the unit may be kw) at an evaporation temperature of 0 ℃. For example, q= Atevp +b= 0.2024 tevp+5.7221 is known from the compressor refrigerating capacity performance curve at a condensation temperature of 55 ℃.
Step S122, determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature and the compressor performance curve corresponding to the current condensation temperature.
Specifically, according to the current indoor dry bulb temperature and indoor wet bulb temperature, the association relation between the evaporating temperature and the dehumidifying amount is determined by combining the corresponding compressor refrigerating capacity performance curve at the current condensing temperature, so that the evaporating temperature with the maximum dehumidifying amount is determined, namely the current initial evaporating temperature of the air conditioner is determined.
(1) Fig. 4 shows an air treatment process of the surface of the cold coil of the indoor heat exchanger during cooling and dehumidifying of the air conditioner, as shown in fig. 4, the abscissa represents the moisture content d, the ordinate represents the indoor dry bulb temperature, after the user selects the dehumidifying mode, the air at the indoor state point 1 exchanges heat with the indoor heat exchanger coil, the air state point after being treated (after dehumidifying) becomes 2, the connection state points 1 and 2 are prolonged and intersect with a 100% relative humidity line at a point b, the point is the saturated air point state corresponding to the wall surface temperature of the cold coil of the indoor heat exchanger, tb represents the wall surface temperature of the cold coil, and the wet bulb temperatures t1 'and t2' of two points can be obtained by taking the isenthalpic line of the state points 1 and 2. t1 and t2 represent the dry bulb temperatures at the state points 1 and 2, respectively.
Point a represents the intersection of the isenthalpic line of state point 1 and the saturated air state line (100% relative humidity line), the ordinate t1 'of point a being the wet bulb temperature t1' of state point 1, the ordinate t2 'of point c being the wet bulb temperature t2' of state point 2.
(2) Depending on the characteristics of the cooling coil, the cooling efficiency η and the cooling full efficiency E can be expressed as:
The cooling efficiency was calculated as dry bulb temperature:
η=（t1-t2）/（t1-tb） （1-1）
the total cooling efficiency calculated by wet bulb temperature is:
E=（t1’-t2’）/（t1’-tb） （1-2）
In the processing process of the air conditioner, the three points a, b and c can be approximately regarded as a straight line, and can be obtained by using a similar triangle method for approximate simplification,
E=（t1’-t2’）/（t1’-tb）≈ac/ab=12/1b =（t1-t2）/（t1-tb）=η
η=[（t1-t2）-（t1’-t2’）]/（t1-t1’） （1-3）
The arrangement of formulas (1-3) shows that
（t1-t2）=η（t1-t1’）+（t1’-t2’） （1-4）
(3) The ratio of the total heat exchange amount to the sensible heat exchange amount, that is,
ζ=（h1-h2）/cp（t1-t2） （1-5）
H1 represents the enthalpy value of the state point 1, and h2 represents the enthalpy value of the state point 2; h1-h2 represent the enthalpy difference Δh between state point 1 and state point 2; since the wet bulb temperature of air flowing through a room air conditioner is generally in the range of 10-22 ℃, the enthalpy of the wet air in this interval is approximately linear with the wet bulb temperature, namely:
（h1-h2）=2.92（t1’-t2’） （1-6）
2.92 is the slope between the enthalpy curve and the wet bulb temperature curve, which is the constant value, and the wet coefficient ζ can be obtained by integrating the formulas 1-2, 1-4, 1-5 and 1-6
ζ=2.92E（t1’- tb）/cp[η（t1- t1’）+E（t1’- tb）] （1-7）
(4) According to the analysis of the air treatment process with a heat-humidity ratio epsilon in an air conditioner, the ratio of the enthalpy difference deltah to the moisture content difference deltad of the state point 1 and the state point 2 is represented, and m represents the air flow, namely:
ε=m（h1-h2）/m（d1-d2） =Q/W （1-8）
Wherein Q is the refrigerating capacity, W is the dehumidifying capacity, d1 and d2 are the moisture contents of the state point 1 and the state point 2 respectively, and d1-d2 represent the moisture content difference delta d between the state point 1 and the state point 2;
calculation formula combined with air enthalpy value
h=cp*t+d（2500+1.84t）=cp*t+2500*d+1.84t*d （1-9）
The integration of 1-7, 1-8, 1-9 can give the correlation of the heat-moisture ratio ε and the moisture-separating coefficient ζ:
ε=2500/(1-1/ζ)
=2500/[1-(cp/k)*(η/E)*( （t1- t1’）/（t1’- tb）)-1/k]；
k is the slope between the enthalpy curve and the wet bulb temperature curve, which may be approximately 2.92, for example, then,
ε=2500/(1-1/ζ)
=2500/[1-(cp/2.92)*( η/ E)*( （t1- t1’）/（t1’- tb）)-1/2.92] （1-10）
2500 Is the latent heat of vaporization (kJ/kg) of water at 0 ℃,1.84 is the average specific heat of water vapor (kJ/(kg. K)); t is the air temperature (DEG C), d is the moisture content of air, cp is the specific heat of air (the average specific heat of dry air at constant pressure, kJ/(kg.K));
the foregoing analysis shows that η≡E, and the air specific heat cp can be regarded as a constant of 1.01 kJ/(kg ℃ C.), the heat-humidity ratio ε can be reduced to:
ε=2500/（0.658-0.346*（t1- t1’）/（t1’- tb）） （1-11）
Considering the thin metal wall, the cold coil wall temperature tb can be considered equal to the evaporation temperature, i.e. the coil temperature tevp of the indoor heat exchanger during dehumidification, and therefore:
ε=2500/（0.658-0.346*（t1- t1’）/（t1’- tevp）） （1-12）
(5) From the performance curve of the compressor, it can be seen that the compressor refrigerating capacity and the evaporating temperature approximately have a linear relationship when the current condensing temperature of the air conditioner is determined:
Q=A tevp+B （1-13）
wherein Q is the refrigerating capacity kw of the compressor; a is the increment of refrigerating capacity when the evaporating temperature rises by 1 ℃, and kw/DEG C; b is the refrigerating capacity at the evaporation temperature of 0 ℃ and kw.
(6) For the air conditioner, when the condensing temperature, the evaporating temperature and the inlet air state are determined, the heat-humidity ratio epsilon and the refrigerating capacity Q can be calculated, and the condensing water flow, namely the dehumidifying capacity of the current air conditioner can be obtained by combining the formulas 1-8, 1-12 and 1-13:
W=（A tevp+B）/2500*（0.658-0.346*（t1- t1’）/（t1’- tevp） ） （1-14）
the values in formulas (1-14) above may be different under different conditions or numerical choices, and thus (1-14) can be written as:
W=（A tevp+B）/a*（b-c*（t1- t1’）/（t1’- tevp））
The above formulas (1-14) show that when the air intake parameter is fixed, the dehumidifying amount of the air conditioner depends on the evaporating temperature, and by carrying out primary derivation on the formulas (1-14), dW/d tevp =0 exists, and the secondary derivation exists that d 2W/d2 tevp is smaller than 0, namely the maximum dehumidifying amount W exists at the evaporating temperature tevp. Therefore, according to the current indoor dry bulb temperature t1 and the indoor wet bulb temperature t1', the compressor performance curve (q= A tevp +b) at the current condensing temperature, the evaporating temperature with the maximum dehumidification amount can be obtained by using the above formulas (1-14), and the evaporating temperature is used as the current initial evaporating temperature of the air conditioner.
For example, taking a compressor (model: QXFS-M213Zh 070) used by an air conditioner as an example, deriving according to the above theory, the compressor performance curve is shown in fig. 2, the refrigerating capacity performance curve with a condensation temperature of 55 ℃ can be known as q= A tevp +b= 0.2024 tevp+5.7221, namely a= 0.2024B = 5.7221, and the correlation between the dehumidification amount W and the evaporation temperature tevp can be obtained by the formula (1-14) by combining the intake air state, the indoor air dry bulb temperature t1=27 ℃, the wet bulb temperature t1' =21.5 ℃).
W=（0.2024 tevp+5.7221）/2500*（0.658-0.346*（27-21.5）/（21.5- tevp）
The primary derivation and the secondary derivation are available, when tevp =9.5 ℃, dW/d tevp =0 and d 2W/d2 tevp is less than 0; the current maximum dehumidification W can be obtained by carrying the formula (1-14), which shows that the maximum dehumidification W exists in the air conditioner when the condensation temperature is 55 ℃, the temperature of the dry bulb of the inlet air is 27 ℃, the temperature of the wet bulb is 21.5 ℃, the evaporation temperature is 9.5 ℃.
And step S130, controlling the air conditioner to operate according to the determined initial evaporation temperature.
After the initial evaporation temperature is obtained, the air conditioner can be controlled to operate according to the initial evaporation temperature, for example, the air conditioner is controlled to operate according to the determined initial evaporation temperature by adjusting the frequency of the compressor. For example, the current evaporating temperature of the air conditioner is detected, and the compressor frequency is increased or decreased according to the difference between the current evaporating temperature and the initial evaporating temperature.
According to the embodiment of the invention, the relation between the evaporation temperature and the dehumidification amount of the air conditioner is determined by combining the performance curve of the compressor, the dehumidification evaporation temperature with the maximum dehumidification amount is determined, and the operation of the air conditioner is controlled according to the determined evaporation temperature, so that the dehumidification efficiency can be improved, and the comfort level of a user can be met while the dehumidification effect is ensured.
Preferably, as shown in fig. 1, the method may further include step S140.
Step S140, performing correction control of the evaporating temperature according to the difference between the air outlet temperature and the dehumidification setting temperature of the air conditioner.
Fig. 5 is a schematic flow chart of a specific embodiment of the step of performing the correction control of the evaporating temperature according to the difference between the air outlet temperature and the dehumidification setting temperature of the air conditioner. As shown in fig. 5, in a specific embodiment, step S140 may specifically include step S141 and step S142.
In step S141, it is determined whether the temperature difference Δt between the air outlet temperature T Air outlet and the dehumidification setting temperature T Setting up is greater than or equal to the first preset temperature difference Δt1 and less than or equal to the second preset temperature difference Δt2.
In step S142, if the temperature difference Δt is greater than or equal to the first preset temperature difference Δt1 and less than or equal to the second preset temperature difference Δt2, the current operation state is maintained.
In step S143, if the temperature difference Δt is smaller than the first preset temperature difference Δt1 or larger than the second preset temperature difference Δt2, the evaporation temperature is corrected according to the temperature difference Δt, or the evaporation temperature is corrected according to the temperature difference Δt and the change rate of the intake air temperature.
Specifically, the temperature difference delta T between the air outlet temperature T Air outlet and the dehumidification setting temperature T Setting up is judged, and if the temperature difference delta T between the air outlet temperature and the dehumidification setting temperature is within the range of [ [ delta ] T1, [ delta ] T2], the current running state is kept unchanged; otherwise, the air conditioner evaporating temperature correction control is entered. The dehumidification setting temperature T Setting up is an indoor environment comfort temperature in a dehumidification mode, and can be 24-26 ℃ for example. The first preset temperature difference DeltaT 1 can be, for example, -2-0 ℃; the second preset temperature difference DeltaT 2 may be, for example, 0 ℃ to 2 ℃.
In one embodiment, the evaporation temperature is controlled by correcting the evaporation temperature according to the temperature difference Δt. Specifically, if the temperature difference Δt is smaller than a first preset temperature difference Δt1, correcting an evaporation temperature of the air conditioner by reducing a compressor frequency; and if the temperature difference delta T is larger than a second preset temperature difference delta T2, correcting the evaporation temperature of the air conditioner by increasing the frequency of the compressor.
If T Air outlet -T Setting up < [ delta ] T1, indicating that the temperature of the air outlet is lower than the comfortable interval of the set temperature, the tube temperature of the indoor heat exchanger is relatively low, and the evaporation temperature can be corrected by reducing the frequency of the compressor; if T Air outlet -T Setting up >. DELTA.T2, it indicates a comfortable interval where the outlet air temperature is higher than the set temperature, the indoor heat exchanger tube temperature is relatively high, and the evaporating temperature can be corrected by raising the compressor frequency.
In another embodiment, the correction control of the evaporation temperature is performed according to the temperature difference Δt and the change rate of the intake air temperature. Specifically, according to the temperature difference DeltaT and the change rate of the inlet air temperature, determining an evaporation temperature change value Delta tevp according to a preset rule; and correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature change value delta tevp.
In one specific embodiment, the evaporation temperature change value Delta tevp is determined according to the following formula according to the temperature difference DeltaT and the change rate of the inlet air temperature,
△tevp=a1(T Air outlet -T Setting up )+b1△T Air inlet /△S+c1
Wherein Δt evp represents an evaporation temperature variation value, T Air outlet represents an air outlet temperature, T Setting up represents a dehumidification set temperature, Δt Air inlet /Δsrepresents an air inlet temperature variation rate in Δs time, that is, a ratio of a temperature difference Δt Air inlet between an air inlet temperature at time i and an air inlet temperature at time j and a time interval Δs (Δs=i-j), and a1, b1, and c1 are fitting coefficients, respectively, which can be determined in advance through experimental tests according to actual measurement values.
After determining the evaporation temperature variation delta tevp, correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature variation delta tevp, wherein the corrected evaporation temperature t evp Correction is equal to the sum of the initial evaporation temperature tevp Initial initiation and the evaporation temperature variation delta tevp, namely
tevp Correction = tevp Initial initiation +△tevp。
After the corrected evaporating temperature is obtained, the air conditioner operates according to the corrected evaporating temperature, and particularly, the air conditioner can be controlled to operate according to the corrected evaporating temperature t evp Correction by adjusting the frequency of the compressor. For example, the compressor frequency is increased or decreased according to the difference between the current actual evaporation temperature and the corrected evaporation temperature T evp Correction , so that the difference Δt between the outlet air temperature of the air conditioner and the dehumidification setting temperature is between [ Δt1, Δt2 ].
By correcting the evaporation temperature in the specific embodiment, the difference delta T between the air outlet temperature and the dehumidification setting temperature is ensured to be between [ deltaT 1 and delta T2), and the comfort of a user can be met while the dehumidification effect is ensured.
In order to clearly illustrate the technical scheme of the present invention, a specific embodiment is used to describe the execution flow of the dehumidification control method of the air conditioner provided by the present invention.
Fig. 6 is a schematic diagram of a method of a dehumidifying control method of an air conditioner according to an embodiment of the present invention. As shown in figure 6 of the drawings,
In the air conditioner dehumidification operation process, real-time monitoring and recording indoor environment parameters (indoor dry bulb temperature and wet bulb temperature) and system parameters (air conditioner dehumidification set temperature, air inlet temperature, air outlet temperature, condensation temperature and evaporation temperature), and determining the current dehumidification initial evaporation temperature tevp Initial initiation through an air conditioner theoretical maximum dehumidification amount judgment program; and the evaporation temperature correction value tevp Correction is determined according to the difference value delta T of the air outlet temperature and the dehumidification setting temperature and the change rate T' of the air inlet temperature, and according to whether the difference value delta T of the air outlet temperature and the dehumidification setting temperature is [ delta T1, delta T2], the dehumidification effect is ensured, and the comfort level of a user is met.
Fig. 7 is a schematic diagram of a method of another embodiment of a dehumidification control method of an air conditioner according to the present disclosure. As shown in figure 7 of the drawings,
When the air conditioner is operated in a dehumidification mode, detecting and recording an indoor dry bulb temperature T1, a wet bulb temperature T1', an air conditioner dehumidification set temperature T Setting up (an indoor environment comfort temperature in the dehumidification mode can be selected from a value range of 24-26 ℃), an air inlet temperature T Air inlet , an air outlet temperature T Air outlet , a condensation temperature tcon and an evaporation temperature tevp in real time, determining that the air conditioner is operated at a preset initial evaporation temperature tevp Initial initiation according to a maximum program of an air conditioner theoretical dehumidification amount, judging whether a difference value DeltaT between the air outlet temperature T Air outlet and the dehumidification set temperature T Setting up is between [ DeltaT1 and DeltaT 2], and keeping a current operation state unchanged if the difference value DeltaT between the air outlet temperature and the dehumidification set temperature is between [ DeltaT1 and DeltaT 2 ]. Otherwise, the air conditioner evaporating temperature correction control is entered.
Fig. 8 is a block diagram illustrating a structure of an embodiment of a dehumidifying control device for air conditioner according to the present invention. As shown in fig. 8, the dehumidification control device 100 includes: a detection unit 110, a determination unit 120 and a control unit 130.
And a detection unit 110 for detecting a current indoor environment parameter and a system parameter of the air conditioner when the air conditioner is operated in dehumidification.
In a specific embodiment, the indoor environment parameters may specifically include: indoor dry bulb temperature and indoor wet bulb temperature. The system parameters may specifically include: dehumidification set temperature, inlet air temperature, outlet air temperature, condensation temperature and evaporation temperature.
And a determining unit 120, configured to determine an evaporation temperature corresponding to a current maximum dehumidification amount according to the current indoor environment parameter and the system parameter of the air conditioner detected by the detecting unit 110, and use the evaporation temperature as an initial evaporation temperature of the air conditioner.
Specifically, the determining unit 120 determines, according to the detected current indoor environment parameter, an evaporation temperature corresponding to a current maximum dehumidification amount in combination with a compressor performance curve of the air conditioner, and uses the evaporation temperature as a current initial evaporation temperature of the air conditioner. The indoor environment parameters may specifically include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner specifically may include: condensation temperature.
In one specific embodiment, the determining unit 120 determines, according to the detected current indoor environment parameter and the detected system parameter of the air conditioner, an evaporation temperature corresponding to a current maximum dehumidification amount, including: acquiring a compressor performance curve corresponding to the current condensing temperature according to the current condensing temperature of the air conditioner; and determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature and the compressor performance curve corresponding to the current condensation temperature.
The compressors of different models correspond to different compressor performance curves, and the output of the refrigerating capacity of the compressor and the evaporating temperature are in linear relation at different condensing temperatures. The compressor performance curve includes: and the relation curve of the refrigerating capacity and the evaporating temperature of the compressor at different condensing temperatures, namely different condensing temperatures correspond to different compressor performance curves. Fig. 3 shows an example of the linear relationship between the output of the compressor refrigeration and the evaporation temperature at different condensation temperatures. As shown in FIG. 3, the abscissa represents the evaporation temperature (in. Degree. C.) and the ordinate represents the compressor cooling capacity (in. Degree. W.), and the curves in FIG. 3 are compressor performance curves at different condensing temperatures, respectively.
The compressor performance curve may be expressed as a linear relationship of compressor capacity versus evaporating temperature at different condensing temperatures, q= A tevp +b, where tevp is evaporating temperature; q is compressor capacity (e.g., in kw); a is the increment of refrigerating capacity when the evaporating temperature rises by a unit temperature value, for example, the increment of refrigerating capacity when the evaporating temperature rises by 1 ℃, for example, the unit can be kw/DEG C; b is the cooling capacity (for example, the unit may be kw) at an evaporation temperature of 0 ℃. For example, q= Atevp +b= 0.2024 tevp+5.7221 is known from the compressor refrigerating capacity performance curve at a condensation temperature of 55 ℃.
And determining the association relation between the evaporating temperature and the dehumidifying amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature and the corresponding compressor refrigerating capacity performance curve under the current condensing temperature, thereby determining the evaporating temperature with the maximum dehumidifying amount, namely determining the current initial evaporating temperature of the air conditioner.
(1) Fig. 4 shows an air treatment process of the surface of the cold coil of the indoor heat exchanger during cooling and dehumidifying of the air conditioner, as shown in fig. 4, the abscissa represents the moisture content d, the ordinate represents the indoor dry bulb temperature, after the user selects the dehumidifying mode, the air at the indoor state point 1 exchanges heat with the indoor heat exchanger coil, the air state point after being treated (after dehumidifying) becomes 2, the connection state points 1 and 2 are prolonged and intersect with a 100% relative humidity line at a point b, the point is the saturated air point state corresponding to the wall surface temperature of the cold coil of the indoor heat exchanger, tb represents the wall surface temperature of the cold coil, and the wet bulb temperatures t1 'and t2' of two points can be obtained by taking the isenthalpic line of the state points 1 and 2. t1 and t2 represent the dry bulb temperatures at the state points 1 and 2, respectively.
Point a represents the intersection of the isenthalpic line of state point 1 and the saturated air state line (100% relative humidity line), the ordinate t1 'of point a being the wet bulb temperature t1' of state point 1, the ordinate t2 'of point c being the wet bulb temperature t2' of state point 2.
(2) Depending on the characteristics of the cooling coil, the cooling efficiency η and the cooling full efficiency E can be expressed as:
The cooling efficiency was calculated as dry bulb temperature:
η=（t1-t2）/（t1-tb） （1-1）
the total cooling efficiency calculated by wet bulb temperature is:
E=（t1’-t2’）/（t1’-tb） （1-2）
In the processing process of the air conditioner, the three points a, b and c can be approximately regarded as a straight line, and can be obtained by using a similar triangle method for approximate simplification,
E=（t1’-t2’）/（t1’-tb）≈ac/ab=12/1b =（t1-t2）/（t1-tb）=η
η=[（t1-t2）-（t1’-t2’）]/（t1-t1’） （1-3）
The arrangement of formulas (1-3) shows that
（t1-t2）=η（t1-t1’）+（t1’-t2’） （1-4）
(3) The ratio of the total heat exchange amount to the sensible heat exchange amount, that is,
ζ=（h1-h2）/cp（t1-t2） （1-5）
H1 represents the enthalpy value of the state point 1, and h2 represents the enthalpy value of the state point 2; h1-h2 represent the enthalpy difference Δh between state point 1 and state point 2; since the wet bulb temperature of air flowing through a room air conditioner is generally in the range of 10-22 ℃, the enthalpy of the wet air in this interval is approximately linear with the wet bulb temperature, namely:
（h1-h2）=2.92（t1’-t2’） （1-6）
2.92 is the slope between the enthalpy curve and the wet bulb temperature curve, which is the constant value, and the wet coefficient ζ can be obtained by integrating the formulas 1-2, 1-4, 1-5 and 1-6
ζ=2.92E（t1’- tb）/cp[η（t1- t1’）+E（t1’- tb）] （1-7）
(4) According to the analysis of the air treatment process with a heat-humidity ratio epsilon in an air conditioner, the ratio of the enthalpy difference deltah to the moisture content difference deltad of the state point 1 and the state point 2 is represented, and m represents the air flow, namely:
ε=m（h1-h2）/m（d1-d2） =Q/W （1-8）
Wherein Q is the refrigerating capacity, W is the dehumidifying capacity, d1 and d2 are the moisture contents of the state point 1 and the state point 2 respectively, and d1-d2 represent the moisture content difference delta d between the state point 1 and the state point 2;
calculation formula combined with air enthalpy value
h=cp*t+d（2500+1.84t）=cp*t+2500*d+1.84t*d （1-9）
The integration of 1-7, 1-8, 1-9 can give the correlation of the heat-moisture ratio ε and the moisture-separating coefficient ζ:
ε=2500/(1-1/ζ)
=2500/[1-(cp/k)*(η/E)*( （t1- t1’）/（t1’- tb）)-1/k]；
k is the slope between the enthalpy curve and the wet bulb temperature curve, which may be approximately 2.92, for example, then,
ε=2500/(1-1/ζ)
=2500/[1-(cp/2.92)*(η/ E)*( （t1- t1’）/（t1’- tb）)-1/2.92] （1-10）
2500 Is the latent heat of vaporization (kJ/kg) of water at 0 ℃,1.84 is the average specific heat of water vapor (kJ/(kg. K)); t is the air temperature (. Degree.C.), d is the moisture content of air, and cp is the specific heat of air (the average specific heat of dry air at constant pressure, kJ/(kg. K)).
The foregoing analysis shows that η≡E, and the air specific heat cp can be regarded as a constant of 1.01 kJ/(kg ℃ C.), the heat-humidity ratio ε can be reduced to:
ε=2500/（0.658-0.346*（t1- t1’）/（t1’- tb）） （1-11）
Considering the thin metal wall, the cold coil wall temperature tb can be considered equal to the evaporation temperature, i.e. the coil temperature tevp of the indoor heat exchanger during dehumidification, and therefore:
ε=2500/（0.658-0.346*（t1- t1’）/（t1’- tevp）） （1-12）
(5) From the performance curve of the compressor, it can be seen that the compressor refrigerating capacity and the evaporating temperature approximately have a linear relationship when the current condensing temperature of the air conditioner is determined:
Q=A tevp+B （1-13）
wherein Q is the refrigerating capacity kw of the compressor; a is the increment of refrigerating capacity when the evaporating temperature rises by 1 ℃, and kw/DEG C; b is the refrigerating capacity at the evaporation temperature of 0 ℃ and kw.
(6) For the air conditioner, when the condensing temperature, the evaporating temperature and the inlet air state are determined, the heat-humidity ratio epsilon and the refrigerating capacity Q can be calculated, and the condensing water flow, namely the dehumidifying capacity of the current air conditioner can be obtained by combining the formulas 1-8, 1-12 and 1-13:
W=（A tevp+B）/2500*（0.658-0.346*（t1-t1’）/（t1’- tevp） ） （1-14）
the values in formulas (1-14) above may be different under different conditions or numerical choices, and thus (1-14) can be written as:
W=（A tevp+B）/a*（b-c*（t1- t1’）/（t1’- tevp））
The above formulas (1-14) show that when the air intake parameter is fixed, the dehumidifying amount of the air conditioner depends on the evaporating temperature, and by carrying out primary derivation on the formulas (1-14), dW/d tevp =0 exists, and the secondary derivation exists that d 2W/d2 tevp is smaller than 0, namely the maximum dehumidifying amount W exists at the evaporating temperature tevp. Therefore, according to the current indoor dry bulb temperature t1 and the indoor wet bulb temperature t1', the compressor performance curve (q= A tevp +b) at the current condensing temperature, the evaporating temperature with the maximum dehumidification amount can be obtained by using the above formulas (1-14), and the evaporating temperature is used as the current initial evaporating temperature of the air conditioner.
For example, taking a compressor (model: QXFS-M213Zh 070) used by an air conditioner as an example, deriving according to the above theory, the compressor performance curve is shown in fig. 2, the refrigerating capacity performance curve with a condensation temperature of 55 ℃ can be known as q= A tevp +b= 0.2024 tevp+5.7221, namely a= 0.2024B = 5.7221, and the correlation between the dehumidification amount W and the evaporation temperature tevp can be obtained by the formula (1-14) by combining the intake air state, the indoor air dry bulb temperature t1=27 ℃, the wet bulb temperature t1' =21.5 ℃).
W=（0.2024 tevp+5.7221）/2500*（0.658-0.346*（27-21.5）/（21.5- tevp）
The primary derivation and the secondary derivation are available, when tevp =9.5 ℃, dW/d tevp =0 and d 2W/d2 tevp is less than 0; the current maximum dehumidification W can be obtained by carrying the formula (1-14), which shows that the maximum dehumidification W exists in the air conditioner when the condensation temperature is 55 ℃, the temperature of the dry bulb of the inlet air is 27 ℃, the temperature of the wet bulb is 21.5 ℃, the evaporation temperature is 9.5 ℃.
And a control unit 130 for controlling the air conditioner to operate according to the determined initial evaporation temperature.
The control unit 130 may control the air conditioner to operate at the initial evaporation temperature after obtaining the initial evaporation temperature, for example, by adjusting the compressor frequency to control the air conditioner to operate at the determined initial evaporation temperature. For example, the current evaporating temperature of the air conditioner is detected, and the compressor frequency is increased or decreased according to the difference between the current evaporating temperature and the initial evaporating temperature.
According to the above embodiment of the present invention, the relationship between the evaporation temperature and the dehumidification amount of the air conditioner is determined in combination with the compressor performance curve, and the dehumidification evaporation temperature at which the maximum dehumidification amount exists is determined, and the operation of the air conditioner is controlled according to the determined evaporation temperature, so that the dehumidification efficiency can be improved.
Preferably, as shown in fig. 8, the apparatus 100 further comprises a correction control unit 140.
And the correction control unit 140 is used for performing correction control on the evaporation temperature according to the difference value between the air outlet temperature and the dehumidification setting temperature of the air conditioner.
In a specific embodiment, the correction control unit 140 may specifically perform the correction control of the evaporation temperature according to the difference between the air outlet temperature and the dehumidification setting temperature of the air conditioner, and the correction control may include: judging whether the temperature difference DeltaT between the air outlet temperature T Air outlet and the dehumidification set temperature T Setting up is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2; if the temperature difference DeltaT is larger than or equal to a first preset temperature difference DeltaT 1 and smaller than or equal to a second preset temperature difference DeltaT 2, the current running state is kept to run; if the temperature difference DeltaT is smaller than the first preset temperature difference DeltaT 1 or larger than the second preset temperature difference DeltaT 2, the evaporation temperature is corrected and controlled according to the temperature difference DeltaT, or the evaporation temperature is corrected and controlled according to the temperature difference DeltaT and the change rate of the air inlet temperature.
Specifically, the temperature difference delta T between the air outlet temperature T Air outlet and the dehumidification setting temperature T Setting up is judged, and if the temperature difference delta T between the air outlet temperature and the dehumidification setting temperature is within the range of [ [ delta ] T1, [ delta ] T2], the current running state is kept unchanged; otherwise, the air conditioner evaporating temperature correction control is entered. The dehumidification setting temperature T Setting up is an indoor environment comfort temperature in a dehumidification mode, and can be 24-26 ℃ for example. The first preset temperature difference DeltaT 1 can be, for example, -2-0 ℃; the second preset temperature difference DeltaT 2 may be, for example, 0 ℃ to 2 ℃.
In one embodiment, the evaporation temperature is controlled by correcting the evaporation temperature according to the temperature difference Δt. Specifically, if the temperature difference Δt is smaller than a first preset temperature difference Δt1, correcting an evaporation temperature of the air conditioner by reducing a compressor frequency; and if the temperature difference delta T is larger than a second preset temperature difference delta T2, correcting the evaporation temperature of the air conditioner by increasing the frequency of the compressor.
If T Air outlet -T Setting up < [ delta ] T1, indicating that the temperature of the air outlet is lower than the comfortable interval of the set temperature, the tube temperature of the indoor heat exchanger is relatively low, and the evaporation temperature can be corrected by reducing the frequency of the compressor; if T Air outlet -T Setting up >. DELTA.T2, it indicates a comfortable interval where the outlet air temperature is higher than the set temperature, the indoor heat exchanger tube temperature is relatively high, and the evaporating temperature can be corrected by raising the compressor frequency.
In another embodiment, the correction control of the evaporation temperature is performed according to the temperature difference Δt and the change rate of the intake air temperature. Specifically, according to the temperature difference DeltaT and the change rate of the inlet air temperature, determining an evaporation temperature change value Delta tevp according to a preset rule; and correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature change value delta tevp.
In one specific embodiment, the evaporation temperature change value Delta tevp is determined according to the following formula according to the temperature difference DeltaT and the change rate of the inlet air temperature,
△tevp=a1(T Air outlet -T Setting up )+b1△T Air inlet /△S+c1
Wherein Δt evp represents an evaporation temperature variation value, T Air outlet represents an air outlet temperature, T Setting up represents a dehumidification set temperature, Δt Air inlet /Δsrepresents an air inlet temperature variation rate in Δs time, that is, a ratio of a temperature difference Δt Air inlet between an air inlet temperature at time i and an air inlet temperature at time j and a time interval Δs (Δs=i-j), and a1, b1, and c1 are fitting coefficients, respectively, which can be determined in advance through experimental tests according to actual measurement values.
After determining the evaporation temperature variation delta tevp, correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature variation delta tevp, wherein the corrected evaporation temperature t evp Correction is equal to the sum of the initial evaporation temperature tevp Initial initiation and the evaporation temperature variation delta tevp, namely
tevp Correction = tevp Initial initiation +△tevp。
After the corrected evaporating temperature is obtained, the air conditioner operates according to the corrected evaporating temperature, and particularly, the air conditioner can be controlled to operate according to the corrected evaporating temperature t evp Correction by adjusting the frequency of the compressor. For example, the compressor frequency is increased or decreased according to the difference between the current actual evaporation temperature and the corrected evaporation temperature T evp Correction , so that the difference Δt between the outlet air temperature of the air conditioner and the dehumidification setting temperature is between [ Δt1, Δt2 ].
By correcting the evaporation temperature in the specific embodiment, the difference delta T between the air outlet temperature and the dehumidification setting temperature is ensured to be between [ deltaT 1 and delta T2), and the comfort of a user can be met while the dehumidification effect is ensured.
The present invention also provides a storage medium corresponding to the dehumidification control method of an air conditioner, having stored thereon a computer program which when executed by a processor implements the steps of any of the methods described above.
The invention also provides an air conditioner corresponding to the dehumidification control method of the air conditioner, which comprises a processor, a memory and a computer program stored on the memory and capable of running on the processor, wherein the processor executes the program to realize the steps of any one of the methods.
The invention also provides an air conditioner corresponding to the dehumidification control device of the air conditioner, which comprises any one of the dehumidification control devices of the air conditioner.
The invention also provides a computer program product corresponding to the dehumidification control method of an air conditioner, which when being executed by a processor, realizes the steps of any one of the methods.
According to the scheme provided by the invention, the relation between the evaporation temperature and the dehumidification amount of the air conditioner is determined by combining the performance curve of the compressor, the dehumidification evaporation temperature with the maximum dehumidification amount is determined as the dehumidification evaporation temperature, and the operation of the air conditioner is controlled according to the determined initial evaporation temperature, so that the dehumidification efficiency can be improved.
According to the scheme provided by the invention, the evaporation temperature is corrected according to the temperature difference between the air outlet temperature and the dehumidification set temperature, so that the difference between the air outlet temperature and the dehumidification set temperature is ensured to be within a certain temperature difference range, and the comfort level of a user can be met while the dehumidification effect is ensured.
The proposal in the related art mostly determines the target moisture content according to the set indoor temperature and indoor humidity, and enters different dehumidification modes according to the relative sizes of the current moisture content and the target moisture content, and theoretical analysis is carried out without combining the dehumidification characteristics of the air conditioner and the air treatment process, and the method is judged only according to the environmental parameters and the preset target parameters, so that the control method is relatively simple and lacks theoretical support.
According to the invention, through analyzing the dehumidification characteristic of the air conditioner and the air treatment process of the indoor heat exchanger, the correlation between the evaporation temperature and the dehumidification amount of the air conditioner is determined, so that the dehumidification effect is ensured, and the comfort level of a user is met.
According to the scheme provided by the invention, the environment parameters (indoor dry bulb temperature and wet bulb temperature) and the system parameters (air conditioner dehumidification set temperature, air inlet temperature, air outlet temperature, condensation temperature and evaporation temperature) are monitored and recorded in real time in the air conditioner dehumidification operation process, the current preset initial evaporation temperature is determined through the maximum program of the theoretical dehumidification amount of the air conditioner, and the evaporation temperature correction is performed according to the difference value between the air outlet temperature and the dehumidification set temperature and the change rate of the air inlet temperature, so that the user comfort level is met while the dehumidification effect is ensured.
The functions described herein may be implemented in hardware, software executed by a processor, firmware, or any combination thereof. If implemented in software that is executed by a processor, the functions may be stored on or transmitted over as one or more instructions or code on a computer-readable medium. Other examples and implementations are within the scope and spirit of the invention and the appended claims. For example, due to the nature of software, the functions described above may be implemented using software executed by a processor, hardware, firmware, hardwired, or a combination of any of these. In addition, each functional unit may be integrated in one processing unit, each unit may exist alone physically, or two or more units may be integrated in one unit.
In the several embodiments provided in the present application, it should be understood that the disclosed technology may be implemented in other manners. The above-described embodiments of the apparatus are merely exemplary, and the division of the units, for example, may be a logic function division, and may be implemented in another manner, for example, a plurality of units or components may be combined or may be integrated into another system, or some features may be omitted, or not performed. Alternatively, the coupling or direct coupling or communication connection shown or discussed with each other may be through some interfaces, units or modules, or may be in electrical or other forms.
The units described as separate components may or may not be physically separate, and components as control devices may or may not be physical units, may be located in one place, or may be distributed over a plurality of units. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.
The integrated units, if implemented in the form of software functional units and sold or used as stand-alone products, may be stored in a computer readable storage medium. Based on such understanding, the technical solution of the present invention may be embodied in essence or a part contributing to the related art or all or part of the technical solution, in the form of a software product stored in a storage medium, including several instructions for causing a computer device (which may be a personal computer, a server or a network device, etc.) to perform all or part of the steps of the method according to the embodiments of the present invention. And the aforementioned storage medium includes: a U-disk, a Read-Only Memory (ROM), a random access Memory (RAM, randomAccess Memory), a removable hard disk, a magnetic disk, or an optical disk, or other various media capable of storing program codes.
The above description is only an example of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the scope of the claims of the present invention.

Claims (9)

1. A dehumidification control method of an air conditioner, comprising:
detecting current indoor environment parameters and system parameters of the air conditioner when the air conditioner is in dehumidification operation; the indoor environment parameters include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner comprise: condensing temperature;
according to the current indoor dry bulb temperature and the indoor wet bulb temperature, determining the evaporation temperature corresponding to the current maximum dehumidification amount by combining the compressor performance curve corresponding to the current condensation temperature, and taking the evaporation temperature as the initial evaporation temperature of the air conditioner;
and controlling the air conditioner to operate according to the determined initial evaporation temperature.
2. The method as recited in claim 1, further comprising: and performing correction control of the evaporating temperature according to the difference value between the air outlet temperature and the dehumidification set temperature of the air conditioner, wherein the correction control comprises the following steps:
Judging whether the temperature difference between the air outlet temperature and the dehumidification set temperature is larger than or equal to a first preset temperature difference and smaller than or equal to a second preset temperature difference;
if the temperature difference value is larger than or equal to the first preset temperature difference value and smaller than or equal to the second preset temperature difference value, the current running state is kept to run;
If the temperature difference is smaller than the first preset temperature difference or larger than the second preset temperature difference, the evaporation temperature is corrected and controlled according to the temperature difference, or the evaporation temperature is corrected and controlled according to the temperature difference and the change rate of the air inlet temperature.
3. The method of claim 2, wherein the step of determining the position of the substrate comprises,
And performing correction control of the evaporating temperature according to the temperature difference value, comprising:
if the temperature difference is smaller than the first preset temperature difference, correcting the evaporation temperature of the air conditioner by reducing the frequency of the compressor;
If the temperature difference is larger than a second preset temperature difference, correcting the evaporating temperature of the air conditioner by increasing the frequency of the compressor;
and/or the number of the groups of groups,
And carrying out correction control on the evaporating temperature according to the temperature difference and the change rate of the inlet air temperature, wherein the correction control comprises the following steps:
Determining an evaporation temperature change value according to a preset rule according to the temperature difference value and the change rate of the inlet air temperature;
and correcting the evaporation temperature according to the initial evaporation temperature and the evaporation temperature variation value.
4. A method according to claim 3, wherein determining the evaporation temperature variation value Δ tevp according to a preset rule based on the temperature difference Δt and the rate of change of the intake air temperature comprises: according to the temperature difference and the change rate of the inlet air temperature, determining an evaporation temperature change value delta tevp according to the following formula:
△tevp=a1(T Air outlet -T Setting up )+b1△T Air inlet /△S+c1
Wherein Δt evp represents an evaporation temperature change value, T Air outlet represents an air outlet temperature, T Setting up represents a dehumidification set temperature, Δt Air inlet /. DELTA.S represents a change rate of an air inlet temperature in the DeltaS time, and a1, b1, c1 are fitting coefficients.
5. A dehumidification control device of an air conditioner, comprising:
The detection unit is used for detecting the current indoor environment parameters and the system parameters of the air conditioner when the air conditioner is in dehumidification operation; the indoor environment parameters include: indoor dry bulb temperature and indoor wet bulb temperature; the system parameters of the air conditioner comprise: condensing temperature;
The determining unit is used for determining the evaporation temperature corresponding to the current maximum dehumidification amount according to the current indoor dry bulb temperature and the indoor wet bulb temperature detected by the detecting unit and in combination with a compressor performance curve corresponding to the current condensation temperature, and taking the evaporation temperature as the initial evaporation temperature of the air conditioner;
and the control unit is used for controlling the air conditioner to operate according to the determined initial evaporation temperature.
6. A storage medium having stored thereon a computer program which when executed by a processor performs the steps of the method of any of claims 1-4.
7. An air conditioner comprising a processor, a memory and a computer program stored on the memory and executable on the processor, the processor implementing the steps of the method of any one of claims 1 to 4 when the program is executed by the processor.
8. An air conditioner comprising the dehumidification control device according to claim 5.
9. A computer program product comprising a computer program which, when executed by a processor, implements the steps of the method of any of claims 1-4.
CN202410460000.3A 2024-04-17 2024-04-17 Air conditioner, dehumidification control method and device thereof, storage medium and program product Pending CN118066665A (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105115212A (en) * 2015-07-28 2015-12-02 中国计量学院 Control method capable of controlling evaporating temperature of dehumidifier
CN112880034A (en) * 2021-03-25 2021-06-01 浙江星光电科智能家居科技有限公司 Fresh air temperature and humidity control system, fresh air conditioner and fresh air dehumidification temperature control method
KR20220036260A (en) * 2020-09-15 2022-03-22 현대자동차주식회사 Vehicle thermal management system
CN114754468A (en) * 2022-04-25 2022-07-15 宁波奥克斯电气股份有限公司 Control method and control device of air conditioner, air conditioner and readable storage medium
CN117190337A (en) * 2022-05-30 2023-12-08 广东美的制冷设备有限公司 Dehumidification control method and device for air conditioner, air conditioner and storage medium

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105115212A (en) * 2015-07-28 2015-12-02 中国计量学院 Control method capable of controlling evaporating temperature of dehumidifier
KR20220036260A (en) * 2020-09-15 2022-03-22 현대자동차주식회사 Vehicle thermal management system
CN112880034A (en) * 2021-03-25 2021-06-01 浙江星光电科智能家居科技有限公司 Fresh air temperature and humidity control system, fresh air conditioner and fresh air dehumidification temperature control method
CN114754468A (en) * 2022-04-25 2022-07-15 宁波奥克斯电气股份有限公司 Control method and control device of air conditioner, air conditioner and readable storage medium
CN117190337A (en) * 2022-05-30 2023-12-08 广东美的制冷设备有限公司 Dehumidification control method and device for air conditioner, air conditioner and storage medium

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