Anti-condensation control method for air conditioner and air conditioner

Abstract

The invention provides an air conditioner anti-condensation control method and an air conditioner. The method comprises the steps that the absolute moisture content D and the dew point temperature Td of air are calculated according to the outdoor unit environment temperature Ta and the outdoor unit environment relative humidity phi so as to judge whether anti-condensation starting conditions are met or not, and when the anti-condensation starting conditions are met, the initial energy requirement Q of a compressor is determined according to the shutdown interval time m; the target parameters are periodically refreshed; the compressor refrigerating capacity q is obtained based on the target parameters, the actual dehumidification capacity Dx is determined based on the compressor refrigerating capacity q, and the dynamic dew point temperature Tdn is obtained according to the actual dehumidification capacity Dx; and updating the real-time compressor energy demand Qn and the anti-condensation operation time Hn based on the dynamic dew point temperature Tdn so as to adjust the rotating speed of the compressor. Under the condition that the indoor unit and the outdoor unit do not communicate with each other, the outdoor unit can perform fuzzy control to perform anti-condensation protection; and refrigeration load output adjustment can be carried out in real time according to different humidity, and it is guaranteed that condensation is avoided and rapid cooling can be achieved.

Description

Technical Field

[0001] This application relates to an anti-condensation control method, and more particularly to an anti-condensation control method and air conditioner for air conditioners, belonging to the technical field of anti-condensation control for air conditioners. Background Technology

[0002] When the ambient temperature and humidity are high, condensation and water droplets easily form on the outer surface of the indoor unit of an air conditioner near the air outlet. In severe cases, this can damage interior decoration and breed bacteria. The reason for condensation is that the air conditioner's cooling capacity is too high and the outlet air temperature is too low, causing the outer surface temperature of the outlet to cool below the air dew point temperature. The greater the temperature difference, the faster the condensation and the more water is condensed.

[0003] Currently, the industry's common method for preventing condensation control involves installing temperature and humidity sensors in the indoor unit. These sensors transmit indoor temperature and humidity data, as well as outlet air temperature, to the outdoor unit. The relationship between outlet air temperature and temperature / humidity data is then calculated to determine how to adjust the compressor output to prevent condensation. This method typically works with indoor and outdoor units equipped with baseband communication such as RS485 or current loops. It cannot be used on air conditioning units without baseband communication. When the outdoor unit lacks access to outlet air temperature and indoor temperature and humidity data, the risk of condensation in the indoor unit cannot be assessed. Summary of the Invention

[0004] In view of this, this application provides an air conditioner anti-condensation control method and an air conditioner to solve or alleviate the technical problems existing in the prior art, and at least provides a beneficial option.

[0005] The technical solution of this application embodiment is implemented as follows: an air conditioner anti-condensation control method includes the following steps: acquiring the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ, and calculating the absolute humidity D and dew point temperature Td based on the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ; determining whether the anti-condensation start-up conditions are met based on the absolute humidity D and the outdoor unit ambient relative humidity φ, so that when met, the initial energy demand Q of the compressor is determined based on the shutdown interval time m, and the target parameters are periodically refreshed; obtaining the compressor cooling capacity q based on the target parameters, determining the actual dehumidification capacity Dx based on the compressor cooling capacity q, and obtaining the dynamic dew point temperature Tdn based on the actual dehumidification capacity Dx; and updating the real-time compressor energy demand Qn and the anti-condensation running time Hn based on the dynamic dew point temperature Tdn, thereby adjusting the compressor speed.

[0006] A further preferred embodiment: the determination of whether the anti-condensation start-up condition is met includes: when the absolute humidity D of the air is greater than or equal to the first preset humidity D1 and the relative humidity φ of the outdoor unit environment is greater than or equal to the first preset relative humidity φ1, it is determined that the anti-condensation start-up condition is met.

[0007] A further preferred embodiment: determining the initial energy requirement Q of the compressor based on the shutdown interval time m includes: when the shutdown interval time m is less than the first preset shutdown interval time M1, the initial energy requirement Q of the compressor = Q. k1 When the shutdown interval m is greater than or equal to the first preset shutdown interval M1 and less than the second preset shutdown interval M2, the initial energy requirement of the compressor is Q = Q k2 When the shutdown interval m is greater than or equal to the second preset shutdown interval M2, and less than the third preset shutdown interval M3, the initial energy requirement of the compressor is Q = Q k3 When the shutdown interval m is greater than or equal to the fourth preset shutdown interval M4, the initial energy requirement of the compressor is Q = Q k4 .

[0008] Further preferably: the target parameters include at least the evaporation temperature Te, the condenser outlet temperature Tc, the evaporation pressure Pe, and the condensation pressure Pc; obtaining the compressor cooling capacity q based on the target parameters includes: determining the evaporator outlet enthalpy h0 and the evaporator inlet enthalpy h based on the target parameters. i .

[0009] A further preferred embodiment: obtaining the compressor cooling capacity q based on the target parameter includes: based on the compressor displacement C v Compressor speed R, evaporator outlet refrigerant density ρ, compressor volumetric efficiency η v Enthalpy at evaporator outlet h0 and enthalpy at evaporator inlet h i The compressor's cooling capacity q = C was calculated. v ·R·ρ·η v ·(h0-h i ).

[0010] A further preferred embodiment: determining the actual dehumidification capacity Dx based on the compressor's cooling capacity q includes: using the minimum airflow correction factor K and the compressor's rated displacement C. w The calculated air volume Fm = K·C w The preset sensible heat ratio X is calculated based on the compressor's cooling capacity q. The latent heat and sensible heat are calculated based on the preset sensible heat ratio X. The dehumidification capacity dx is calculated by combining the air volume Fm, the outdoor unit ambient temperature Ta, and the outdoor unit ambient relative humidity φ. The actual dehumidification capacity Dx = dx × v is calculated by using the correction coefficient v.

[0011] A further preferred embodiment: obtaining the dynamic dew point temperature Tdn based on the actual dehumidification amount Dx includes: obtaining the total air mass by combining the room volume L and the air volume Fm, and obtaining the dynamic dew point temperature Tdn based on the total air mass and the actual dehumidification amount Dx.

[0012] A further preferred method: updating the real-time compressor energy demand Qn and anti-condensation operating time Hn based on the dynamic dew point temperature Tdn includes: calculating the anti-condensation operating time Hn = (a·q) / (ΔTde) based on the first coefficient value a, the compressor cooling capacity q, the dynamic dew point temperature Tdn, and the estimated air outlet temperature To of the indoor unit. 2 Where ΔTde=Tdn-To; according to the compressor energy requirement Q in the (n-1)th cycle. (n-1) The compressor energy demand Qn = Q is obtained by calculating the real-time compressor energy demand change ΔQn. (n-1) +ΔQn; where ΔQn=(ΔTde1-ΔTde2) / a·100%, ΔTde1 represents ΔTde in the nth period, and ΔTde2 represents ΔTde in the (n-1)th period.

[0013] Further preferred embodiment: also includes: calculating the estimated air outlet temperature To of the indoor unit; wherein: calculating the evaporator outlet temperature Teo=Ts-Tx based on the compressor suction temperature Ts and the superheat correction value Tx, and calculating the estimated air outlet temperature To of the indoor unit in combination with the air volume Fm, the compressor cooling capacity q and the air property parameters.

[0014] Based on the same concept, this application also provides an air conditioner that uses the above-described air conditioner anti-condensation control method to reduce the frequency to decrease cooling capacity or increase the frequency to increase cooling capacity.

[0015] The embodiments of this application, due to the adoption of the above technical solutions, have the following advantages:

[0016] This application enables the outdoor unit to perform fuzzy control for anti-condensation protection even when there is no communication between the indoor and outdoor units; it can also adjust the cooling load output in real time according to different humidity levels to ensure that condensation does not occur and that the temperature can be dropped quickly.

[0017] The above overview is for illustrative purposes only and is not intended to be limiting in any way. In addition to the illustrative aspects, embodiments, and features described above, further aspects, embodiments, and features of this application will become readily apparent from the accompanying drawings and the following detailed description. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a flowchart of the air conditioner anti-condensation control method described in this application.

[0020] Figure 2 This is a frame diagram of the air conditioner described in this application. Detailed Implementation

[0021] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit or scope of this application. Therefore, the drawings and description are considered to be exemplary in nature and not restrictive.

[0022] The embodiments of this application will now be described in detail with reference to the accompanying drawings.

[0023] like Figure 1 As shown in the figure, this application provides an air conditioner anti-condensation control method, including the following steps: obtaining the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ, and calculating the absolute humidity D and dew point temperature Td based on the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ; determining whether the anti-condensation start-up conditions are met based on the absolute humidity D and the outdoor unit ambient relative humidity φ, so that when they are met, the initial energy demand Q of the compressor is determined based on the shutdown interval time m, and the target parameters are periodically refreshed; obtaining the compressor cooling capacity q based on the target parameters, determining the actual dehumidification capacity Dx based on the compressor cooling capacity q, and obtaining the dynamic dew point temperature Tdn based on the actual dehumidification capacity Dx; and updating the real-time compressor energy demand Qn and the anti-condensation running time Hn based on the dynamic dew point temperature Tdn, thereby adjusting the compressor speed.

[0024] A further preferred embodiment: the determination of whether the anti-condensation start-up condition is met includes: when the absolute humidity D of the air is greater than or equal to the first preset humidity D1 and the relative humidity φ of the outdoor unit environment is greater than or equal to the first preset relative humidity φ1, it is determined that the anti-condensation start-up condition is met.

[0025] A further preferred embodiment: determining the initial energy requirement Q of the compressor based on the shutdown interval time m includes: when the shutdown interval time m is less than the first preset shutdown interval time M1, the initial energy requirement Q of the compressor = Q. k1 When the shutdown interval m is greater than or equal to the first preset shutdown interval M1 and less than the second preset shutdown interval M2, the initial energy requirement of the compressor is Q = Q k2 When the shutdown interval m is greater than or equal to the second preset shutdown interval M2, and less than the third preset shutdown interval M3, the initial energy requirement of the compressor is Q = Q k3 When the shutdown interval m is greater than or equal to the fourth preset shutdown interval M4, the initial energy requirement of the compressor is Q = Q k4 .

[0026] Further preferably: the target parameters include at least the evaporation temperature Te, the condenser outlet temperature Tc, the evaporation pressure Pe, and the condensation pressure Pc; obtaining the compressor cooling capacity q based on the target parameters includes: determining the evaporator outlet enthalpy h0 and the evaporator inlet enthalpy h based on the target parameters. i .

[0027] A further preferred embodiment: obtaining the compressor cooling capacity q based on the target parameter includes: based on the compressor displacement C v Compressor speed R, evaporator outlet refrigerant density ρ, compressor volumetric efficiency η v Enthalpy at evaporator outlet h0 and enthalpy at evaporator inlet h i The compressor's cooling capacity q = C was calculated. v ·R·ρ·η v ·(h0-h i ).

[0028] A further preferred embodiment: determining the actual dehumidification capacity Dx based on the compressor's cooling capacity q includes: using the minimum airflow correction factor K and the compressor's rated displacement C. w The calculated air volume Fm = K·C w The preset sensible heat ratio X is calculated based on the compressor's cooling capacity q. The latent heat and sensible heat are calculated based on the preset sensible heat ratio X. The dehumidification capacity dx is calculated by combining the air volume Fm, the outdoor unit ambient temperature Ta, and the outdoor unit ambient relative humidity φ. The actual dehumidification capacity Dx = dx × v is calculated by using the correction coefficient v.

[0029] A further preferred embodiment: obtaining the dynamic dew point temperature Tdn based on the actual dehumidification amount Dx includes: obtaining the total air mass by combining the room volume L and the air volume Fm, and obtaining the dynamic dew point temperature Tdn based on the total air mass and the actual dehumidification amount Dx.

[0030] A further preferred method: updating the real-time compressor energy demand Qn and anti-condensation operating time Hn based on the dynamic dew point temperature Tdn includes: calculating the anti-condensation operating time Hn = (a·q) / (ΔTde) based on the first coefficient value a, the compressor cooling capacity q, the dynamic dew point temperature Tdn, and the estimated air outlet temperature To of the indoor unit. 2 Where ΔTde=Tdn-To; according to the compressor energy requirement Q in the (n-1)th cycle. (n-1) The compressor energy demand Qn = Q is obtained by calculating the real-time compressor energy demand change ΔQn. (n-1) +ΔQn; where ΔQn=(ΔTde1-ΔTde2) / a·100%, ΔTde1 represents ΔTde in the nth period, and ΔTde2 represents ΔTde in the (n-1)th period.

[0031] Further preferred embodiment: also includes: calculating the estimated air outlet temperature To of the indoor unit; wherein: calculating the evaporator outlet temperature Teo=Ts-Tx based on the compressor suction temperature Ts and the superheat correction value Tx, and calculating the estimated air outlet temperature To of the indoor unit in combination with the air volume Fm, the compressor cooling capacity q and the air property parameters.

[0032] Based on the same concept, such as Figure 2 As shown, this application also provides an air conditioner that uses the above-described air conditioner anti-condensation control method to reduce the cooling capacity by lowering the frequency or increasing the cooling capacity by raising the frequency.

[0033] This application is in operation:

[0034] Assuming the first preset moisture content D1 = 13 g / kg, the first preset relative humidity φ1 = 70%, and M1~M4 = (10, 20, 30, 40), the initial energy required by the first to fourth preset compressors is Q. k1 ~Q k4 = (50%, 60%, 70%, 80%), the first to fourth preset coefficient values ​​a1~a4 = (0.5, 0.7, 1.1, 1.6), the first to third preset Δte thresholds b1~b3 = (0, 1, 3), H = 90min.

[0035] When the outdoor unit receives the cooling start signal, it determines whether the absolute humidity of the air D≥13g / kg and the relative humidity of the outdoor unit environment φ≥70%. If the conditions are met, it enters the anti-condensation fuzzy control program.

[0036] First, read the outdoor ambient temperature Ta and relative humidity φ detected by the temperature and humidity sensor at the current moment, calculate the absolute humidity D and dew point temperature Td, and assign them as initial values ​​to participate in the calculation of other initial parameters.

[0037] For example, at this time, the outdoor unit ambient temperature Ta = 28℃, φ = 70%, and the calculated D = 16.88g / kg, Td = 22℃. At this time, D and φ meet the conditions for entering the anti-condensation fuzzy control program. The time m since the last shutdown is determined. For example, m = 15min. According to the table below, the initial energy requirement of the compressor is 60%. The initial running time H can be any number greater than 0. In this calculation, it is preset to 90min. Start the cooling operation.

[0038] Downtime interval m (min) The initial energy requirement of the compressor is Q (%) m < M1 <![CDATA[Q k1 ]]> M1≤m<M2 <![CDATA[Q k2 ]]> M2≤m<M3 <![CDATA[Q k3 ]]> m≥M3 <![CDATA[Q k4 ]]>

[0039] Among them, M1~M3: the first to third preset shutdown interval times.

[0040] After startup, parameters are refreshed every 5 minutes. After 15 minutes of operation, energy demand adjustment begins. In the first cycle (5 minutes), Pe = 11.07 bar, and the software, based on the physical property parameter table, finds Te3 = 10℃. Similarly, in the second cycle (10 minutes), Pe = 10.91 bar, Te2 = 9.5℃. In the third cycle (15 minutes), Pe = 10.43 bar, Te1 = 8℃. The calculated difference between the evaporation temperature of this cycle and the previous cycle is ΔTe1 = Te1 - Te2 = -1.5℃, and the difference between the evaporation temperature of the previous cycle and the cycle before that is ΔTe2 = Te2 - Te3 = -0.5℃.

[0041] The calculation period for the evaporation temperature Te is the first preset time C1.

[0042] Change in Te per 5 minutes ΔTe (°C) coefficient a ΔTe<b1 a1 b1≤ΔTe<b2 a2 b2≤ΔTe<b3 a3 ΔTe≥b3 a4

[0043] Calculate the dehumidification capacity to determine the latest room air dew point temperature.

[0044] First, calculate the theoretical cooling capacity q of the compressor. Assuming the air conditioning system uses R32 refrigerant and the rated cooling capacity of the unit is Cw (taken as 17kW), taking the first cycle as an example, for instance, Pc = 28bar, and the compressor displacement C... v =40cm 3 The compressor speed R = 2400 rpm, the condenser outlet temperature Tc = 40℃, and the minimum air volume correction coefficient K is taken as 8. According to empirical data, the sensible heat ratio X of the air conditioning cooling capacity under high temperature and high humidity conditions is generally 0.42 to 0.48%. The control method of this invention selects 0.45, which has sufficient accuracy to calculate the relevant parameters.

[0045] The selection rule for the evaporator outlet superheat correction factor Tx is as follows: assuming the indoor and outdoor units of this model use normal-length connecting pipes, and the expected heat loss from the connecting pipes is 3℃, then Tx equals 3℃. Assuming the compressor suction temperature Ts = 15℃, the evaporator outlet temperature Teo = 15 - 3 = 12℃. The enthalpy values ​​h at the evaporator inlet and outlet can be obtained from the built-in refrigerant property parameters in the query program, which include Pc, Pe, Tc, evaporation temperature (the outdoor unit can convert the pressure value detected by the low-pressure sensor into saturation temperature), Te, Teo, and Ts. i =275.35 kJ / kg, h0 = 519.07 kJ / kg, refrigerant density at evaporator outlet ρ = 29.77 kg / m³ 3 Compressor volumetric efficiency η v Taking 0.9, we can derive q = C v ·R·ρ·η v ·(h0-h i=29.77*0.9*40 / 1000*2400*60*(519.07-275.35) / 1000 = 10.45kw. From the sensible heat ratio X = 0.45, we can get the latent heat = 10.45*(1-0.45) = 5.75kw, and the sensible heat = 10.45*0.35 = 3.66kw.

[0046] The calculated dehumidification capacity of the air conditioning unit for the first cycle, dx = 0.665 kg, and the outlet air temperature To = 21.1℃ can be calculated from the latent heat, sensible heat, initial temperature and humidity parameters Ta and φ, and the humid air property parameters built into the air volume Fm query program. Since the indoor air state changes dynamically, the actual dehumidification capacity will be less than dx, so a correction coefficient v needs to be introduced. Assuming that it is 0.75 for this operating condition, the actual dehumidification capacity can be approximated, i.e., Dx = 0.665 * 0.75 = 0.5 kg.

[0047] During unit installation, the installer needs to input the room's internal volume into the outdoor unit. If this is not input, the preset volume L in the program will be used. Assuming the installer did not input this volume, L = 17 * 21 = 357 m³. 3 From the above, we can see that the air volume Fm = 17 / 0.008 = 2125m³. 3 / h, then the air replacement rate for the first cycle is 177m³. 3 That is, the replacement rate is (177 / 357)% = 49.6%.

[0048] At the end of the first cycle, To = 21.1℃. Since cooling is a dynamic process and fuzzy control does not require high precision, the program simulates the cooling process as a linear process. That is, the outlet air temperature of the whole process is the average of the initial and final values, i.e. (28 + 21.1) / 2 = 24.55℃.

[0049] Since the replacement rate is 49.6%, it means that 49.6% of the 28°C air was replaced with 24.55°C air. Therefore, the air temperature at the end of the first cycle after mixing is (24.55*177+28*180) / 357=26.29°C.

[0050] Using the air density value under standard conditions (20℃, 1 atm) as the calculation value, the total air mass of the room is calculated to be 360kg. The initial total air moisture content is 360kg*16.88g / kg / 1000=6048g. The dehumidification amount for the first cycle was previously calculated to be 0.5kg, and the remaining moisture content is 6.048kg-0.5kg=5548g.

[0051] At the end of the first cycle, the air moisture content D1 = 5548g / 360kg = 15.411g / kg. The room air dynamic dew point temperature Td1 = 20.57℃ is calculated from the air property parameter table built into the D1 and To1 data query program.

[0052] At this point, all parameters involved in the calculation of Qn and Hn have been obtained. Similarly, all parameters in the nth cycle can be calculated using the above method. After calculating Qn and Hn, the compressor energy requirement is updated, that is, the frequency is reduced to decrease the cooling capacity or the frequency is increased to increase the cooling capacity.

[0053] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this application, and these should all be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A method for preventing condensation in an air conditioner, characterized in that, Includes the following steps: Obtain the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ, and calculate the absolute humidity D and dew point temperature Td based on the outdoor unit ambient temperature Ta and the outdoor unit ambient relative humidity φ; Based on the absolute humidity D of the air and the relative humidity φ of the outdoor unit environment, it is determined whether the anti-condensation start-up conditions are met. When they are met, the initial energy requirement Q of the compressor is determined based on the shutdown interval time m, and the target parameters are periodically refreshed. The compressor cooling capacity q is obtained based on the target parameters, the actual dehumidification capacity Dx is determined based on the compressor cooling capacity q, and the dynamic dew point temperature Tdn is obtained based on the actual dehumidification capacity Dx. And based on the dynamic dew point temperature Tdn, the real-time compressor energy demand Qn and anti-condensation running time Hn are updated, thereby adjusting the compressor speed.

2. The air conditioner anti-condensation control method according to claim 1, characterized in that, The determination of whether the anti-condensation activation conditions are met includes: When the absolute humidity D of the air is greater than or equal to the first preset humidity D1 and the relative humidity φ of the outdoor unit environment is greater than or equal to the first preset relative humidity φ1, the anti-condensation start-up condition is determined to be met.

3. The air conditioner anti-condensation control method according to claim 1, characterized in that, The determination of the compressor's initial energy requirement Q based on the downtime m includes: When the shutdown interval m is less than the first preset shutdown interval M1, the initial energy requirement of the compressor is Q = Q k1 ; When the shutdown interval m is greater than or equal to the first preset shutdown interval M1, and less than the second preset shutdown interval M2, the initial energy requirement of the compressor is Q = Q k2 ; When the shutdown interval m is greater than or equal to the second preset shutdown interval M2, and less than the third preset shutdown interval M3, the initial energy requirement of the compressor is Q = Q k3 ; When the shutdown interval m is greater than or equal to the fourth preset shutdown interval M4, the initial energy requirement of the compressor is Q = Q k4 .

4. The air conditioner anti-condensation control method according to claim 1, characterized in that, The target parameters include at least the evaporation temperature Te, the condenser outlet temperature Tc, the evaporation pressure Pe, and the condensation pressure Pc; obtaining the compressor cooling capacity q based on the target parameters includes: Based on the target parameters, determine the evaporator outlet enthalpy h0 and the evaporator inlet enthalpy h i .

5. The air conditioner anti-condensation control method according to claim 4, characterized in that, The process of obtaining the compressor cooling capacity q based on the target parameter includes: According to the compressor displacement C v Compressor speed R, evaporator outlet refrigerant density ρ, compressor volumetric efficiency η v Enthalpy at evaporator outlet h0 and enthalpy at evaporator inlet h i The compressor's cooling capacity q = C was calculated. v ·R·ρ·η v ·(h0-h i ).

6. The air conditioner anti-condensation control method according to claim 5, characterized in that, The determination of the actual dehumidification capacity Dx based on the compressor's cooling capacity q includes: Based on the minimum air volume correction factor K and the compressor rated displacement C w The calculated air volume Fm = K·C w ; The preset sensible heat ratio X is calculated based on the compressor cooling capacity q. The latent heat and sensible heat are calculated based on the preset sensible heat ratio X. The dehumidification capacity dx is calculated by combining the air volume Fm, the outdoor unit ambient temperature Ta, and the outdoor unit ambient relative humidity φ. The actual dehumidification capacity Dx = dx × v is calculated using the correction factor v.

7. The air conditioner anti-condensation control method according to claim 6, characterized in that, The step of obtaining the dynamic dew point temperature Tdn based on the actual dehumidification capacity Dx includes: The total air mass is obtained by combining the room volume L and the air volume Fm, and the dynamic dew point temperature Tdn is obtained based on the total air mass and the actual dehumidification capacity Dx.

8. The air conditioner anti-condensation control method according to claim 7, characterized in that, The real-time compressor energy demand Qn and anti-condensation operating time Hn are updated based on the dynamic dew point temperature Tdn, including: The anti-condensation operating time Hn = (a·q) / (ΔTde) is calculated based on the first coefficient value a, the compressor cooling capacity q, the dynamic dew point temperature Tdn, and the estimated air outlet temperature To of the indoor unit. 2 Where ΔTde = Tdn - To; According to the compressor energy requirement Q in the (n-1)th cycle (n-1) The compressor energy demand Qn = Q is obtained by calculating the real-time compressor energy demand change ΔQn. (n-1) +ΔQn; where ΔQn=(ΔTde1-ΔTde2) / a·100%, ΔTde1 represents ΔTde in the nth period, and ΔTde2 represents ΔTde in the (n-1)th period.

9. The air conditioner anti-condensation control method according to claim 8, characterized in that, Also includes: The estimated outlet air temperature To of the indoor unit is calculated. This includes: The evaporator outlet temperature Teo = Ts - Tx is calculated based on the compressor suction temperature Ts and the superheat correction value Tx. The indoor unit's estimated outlet temperature To is then calculated by combining the air volume Fm, the compressor cooling capacity q, and air property parameters.

10. An air conditioner, characterized in that, The system employs the air conditioner anti-condensation control method as described in any one of claims 1-9, which reduces the cooling capacity by lowering the frequency or increases the cooling capacity by raising the frequency.

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