Air conditioner control method and device, air conditioner, storage medium and program product

Abstract

The invention discloses an air conditioner control method and device, an air conditioner, a storage medium and a computer program product. The air conditioner is provided with an inner fan, a first indoor heat exchanger and a second indoor heat exchanger, the first indoor heat exchanger and the second indoor heat exchanger are connected in parallel, and a first branch throttling component and a second branch throttling component are arranged between the two indoor heat exchangers and an air conditioner throttling component respectively; the method comprises the following steps: determining a PD feedback control strategy or a thermal load and wet load control strategy to control the operation frequency of a compressor according to the indoor dry-bulb temperature; according to the indoor dew-point temperature, a PD feedback control strategy or a thermal load and wet load control strategy is determined to control the rotating speed of an inner fan; and according to the air suction superheat degree of the first indoor heat exchanger and the air suction superheat degree of the second indoor heat exchanger, a PD feedback control strategy or a fitting formula control strategy is determined, and the opening degree of the first branch throttling component and the opening degree of the second throttling component are controlled. According to the scheme, the operation of the air conditioner is controlled by combining PD feedback and a heat and humidity load control strategy, and accurate temperature and humidity control and stable and efficient operation of the system are guaranteed.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioners, and specifically relates to a control method and device for an air conditioner, an air conditioner, a storage medium and a computer program product. Background Art

[0002] For air conditioning that controls both temperature and humidity, a one-to-many parallel air conditioning system has better energy efficiency than a conventional air conditioning system with one outdoor unit and one indoor unit. Related solutions have proposed air conditioning temperature and humidity control methods such as artificial intelligence neural network control method based on load model and PID type fuzzy logic control method based on weight rule table, but these methods are limited to conventional air conditioning systems and are not applicable to parallel air conditioning systems.

[0003] The above contents are only used to assist in understanding the technical solution of the present invention and do not constitute an admission that the above contents are prior art. Summary of the invention

[0004] The object of the present invention is to provide an air conditioning control method, device, air conditioning, storage medium and computer program product to solve the problem that the parallel air conditioning system in the related scheme cannot effectively control temperature and humidity at the same time, so as to achieve the effect of controlling the operating status of the compressor, internal fan and throttling components in the parallel air conditioning system by combining PD feedback and heat and humidity load control strategy, and ensuring the system accurately controls temperature and humidity and operates stably and efficiently.

[0005] The present invention provides a control method for an air conditioner, wherein the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; indoor fans are arranged at the first heat exchanger and the second indoor heat exchanger; the method comprises: after the air conditioner starts to run, obtaining the indoor dry-bulb temperature, the indoor dew-point temperature, the suction superheat of the first indoor heat exchanger, and the suction superheat of the second indoor heat exchanger; determining a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the size of the indoor dry-bulb temperature to control the operation of the compressor; determining a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the size of the indoor dew-point temperature A control strategy for controlling the rotation speed of the indoor fan to control the operation of the indoor fan; according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component are respectively determined to control the operation of the first branch throttling component and the second throttling component; wherein, the control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the rotation speed of the indoor fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

[0006] In some embodiments, the PD feedback control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula, controlling the operation of the indoor fan according to the result of calculating the speed of the indoor fan according to the second formula, controlling the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula, and controlling the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula; the heat load and wet load control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula, and controlling the operation of the indoor fan according to the result of calculating the speed of the indoor fan according to the sixth formula; determining the control strategy for controlling the operating frequency of the compressor of the air conditioner according to the size of the indoor dry-bulb temperature, including: judging the size of the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is less than the first temperature difference, then the control strategy for controlling the operating frequency of the compressor of the air conditioner is the PD feedback control according to the first formula. The result of the operating frequency of the compressor controls the operation of the compressor; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is greater than or equal to the first temperature difference, the control strategy for controlling the operating frequency of the compressor of the air conditioner is the result of calculating the operating frequency of the compressor according to the fifth formula in the heat load and wet load control to control the operation of the compressor; and / or, the control strategy for controlling the speed of the indoor fan is determined according to the size of the indoor dew point temperature, including: judging the size of the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is less than the second temperature difference, the control strategy for controlling the speed of the indoor fan is the result of calculating the speed of the indoor fan according to the second formula in the PD feedback control to control the operation of the indoor fan; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is greater than or equal to the second temperature difference, the control strategy for controlling the speed of the indoor fan is the result of calculating the speed of the indoor fan according to the sixth formula in the heat load and wet load control to control the operation of the indoor fan.

[0007] In some embodiments, according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component are respectively determined, including: judging the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat, if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is to control the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is the fitting formula control strategy; and / or, judging the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat The absolute value of the value; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is less than the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is to control the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is greater than or equal to the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is the fitting formula control strategy; wherein, the fitting formula control strategy for controlling the opening of the first branch throttling component and the opening of the second branch throttling component is the same; the fitting formula control strategy is to obtain the mass flow of the first branch throttling component and the second branch throttling component according to the seventh calculation formula, and obtain the opening of the first branch throttling component and the opening of the second branch throttling component according to the corresponding relationship between the preset mass flow and the opening; the seventh calculation formula is:

[0008] Mr=f(F, etav, tsuc_obj, tevap);

[0009] In the formula, Mr is the mass flow rate of the first branch throttling component and the second branch throttling component; F is the operating frequency of the compressor; ηv is the volumetric efficiency; if Mr is the mass flow rate of the first branch throttling component, tsuc_obj is the target suction superheat of the first indoor heat exchanger, and tevap is the evaporation temperature of the first indoor heat exchanger; if Mr is the mass flow rate of the second branch throttling component, tsuc_obj is the target suction superheat of the second indoor heat exchanger, and tevap is the evaporation temperature of the second indoor heat exchanger.

[0010] In some embodiments, the first formula is:

[0011] F(n+1)=F(n)+Kd*(Kp1*△Tdr+Ki1*δTdr)+Kw*(Kp2*△Tdp+Ki1*δTdp);

[0012] The second formula is:

[0013] C(n+1)=C(n)+Kp2*ΔTdp+Ki2*δTdp;

[0014] In the formula, F(n+1) and F(n) are the operating frequencies of the compressors, C(n+1) and C(n) are the speeds of the indoor fans, and n is the cycle number; △Tdr is the difference between the indoor dry-bulb temperature and the indoor set temperature; δTdr is the deviation rate between the indoor dry-bulb temperature and the indoor set temperature; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature; Kd, Kp1, Kp2, Ki1, Ki2, and Kw are all coefficients.

[0015] In some embodiments, the third formula is:

[0016] B1(n+1)=B1(n)+Kp3*Δsh1+Ki3*δsh1;

[0017] The fourth formula is:

[0018] B2(n+1)=B2(n)+Kp4*Δsh2+Ki4*δsh2;

[0019] In the formula, B1(n) and B1(n+1) are the openings of the first branch throttling component, B2(n) and B2(n+1) are the openings of the second branch throttling component, and n is the cycle number; △sh1 is the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat; δsh1 is the deviation rate between the suction superheat of the first indoor heat exchanger and the first set suction superheat; △sh2 is the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; δsh2 is the deviation rate between the suction superheat of the second indoor heat exchanger and the second set suction superheat; Kp3, Ki3, Kp4, and Ki4 are all coefficients.

[0020] In some implementations, the fifth formula is:

[0021] F0=z1+a1*Qtot+b1*SHR+c1*Qtot 2 +d1*SHR 2 +e1*Qtot*SHR;

[0022] The sixth formula is:

[0023] C0=z2+a2*Qtot+b2*SHR+c2*Qtot 2 +d2*SHR 2 +e2*Qtot*SHR;

[0024] In the formula, F0 is the operating frequency of the compressor; C0 is the speed of the indoor fan; z1, a1, b1, c1, d1, e1, z2, a2, b2, c2, d2, and e2 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; Qsen is the heat load.

[0025] Matching the above method, the present invention provides a control device for an air conditioner on the other hand, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; indoor fans are arranged at the first heat exchanger and the second indoor heat exchanger; the device comprises: an acquisition unit, configured to acquire the indoor dry-bulb temperature, the indoor dew point temperature, the suction superheat of the first indoor heat exchanger, and the suction superheat of the second indoor heat exchanger after the air conditioner starts to run; a control unit, configured to determine a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the size of the indoor dry-bulb temperature, so as to control the operation of the compressor; the control unit is configured to A control strategy for controlling the rotational speed of the indoor fan is determined according to the size of the indoor dew point temperature, so as to control the operation of the indoor fan; the control unit is configured to determine the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component respectively according to the size of the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, so as to control the operation of the first branch throttling component and the second throttling component; wherein, the control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the rotational speed of the indoor fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

[0026] In some embodiments, the PD feedback control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula, controlling the operation of the indoor fan according to the result of calculating the speed of the indoor fan according to the second formula, controlling the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula, and controlling the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula; the heat load and wet load control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula, and controlling the operation of the indoor fan according to the result of calculating the speed of the indoor fan according to the sixth formula; the control unit determines the control strategy for controlling the operating frequency of the compressor of the air conditioner according to the size of the indoor dry-bulb temperature, including: judging the size of the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is less than the first temperature difference, then the control strategy for controlling the operating frequency of the compressor of the air conditioner is the control strategy calculated according to the first formula in the PD feedback control. The result of the operating frequency of the compressor controls the operation of the compressor; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is greater than or equal to the first temperature difference, the control strategy for controlling the operating frequency of the compressor of the air conditioner is to control the operation of the compressor by calculating the operating frequency of the compressor according to the fifth formula in the heat load and wet load control; and / or, the control unit determines the control strategy for controlling the speed of the indoor fan according to the size of the indoor dew point temperature, including: judging the size of the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is less than the second temperature difference, the control strategy for controlling the speed of the indoor fan is to control the operation of the indoor fan by calculating the speed of the indoor fan according to the second formula in the PD feedback control; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is greater than or equal to the second temperature difference, the control strategy for controlling the speed of the indoor fan is to control the operation of the indoor fan by calculating the speed of the indoor fan according to the sixth formula in the heat load and wet load control.

[0027] In some embodiments, the control unit determines the control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component respectively according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, including: judging the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat, if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is to control the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is the fitting formula control strategy; and / or, judging the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat the size of the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is less than the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is to control the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is greater than or equal to the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is the fitting formula control strategy; wherein, the fitting formula control strategy for controlling the opening of the first branch throttling component and the opening of the second branch throttling component is the same; the fitting formula control strategy is to obtain the mass flow of the first branch throttling component and the second branch throttling component according to the seventh calculation formula, and obtain the opening of the first branch throttling component and the opening of the second branch throttling component according to the corresponding relationship between the preset mass flow and the opening; the seventh calculation formula is:

[0028] Mr=f(F, etav, tsuc_obj, tevap);

[0029] In the formula, Mr is the mass flow rate of the first branch throttling component and the second branch throttling component; F is the operating frequency of the compressor; ηv is the volumetric efficiency; if Mr is the mass flow rate of the first branch throttling component, tsuc_obj is the target suction superheat of the first indoor heat exchanger, and tevap is the evaporation temperature of the first indoor heat exchanger; if Mr is the mass flow rate of the second branch throttling component, tsuc_obj is the target suction superheat of the second indoor heat exchanger, and tevap is the evaporation temperature of the second indoor heat exchanger.

[0030] In some embodiments, the first formula is:

[0031] F(n+1)=F(n)+Kd*(Kp1*△Tdr+Ki1*δTdr)+Kw*(Kp2*△Tdp+Ki1*δTdp);

[0032] The second formula is:

[0033] C(n+1)=C(n)+Kp2*ΔTdp+Ki2*δTdp;

[0034] In the formula, F(n+1) and F(n) are the operating frequencies of the compressors, C(n+1) and C(n) are the speeds of the indoor fans, and n is the cycle number; △Tdr is the difference between the indoor dry-bulb temperature and the indoor set temperature; δTdr is the deviation rate between the indoor dry-bulb temperature and the indoor set temperature; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature; Kd, Kp1, Kp2, Ki1, Ki2, and Kw are all coefficients.

[0035] In some embodiments, the third formula is:

[0036] B1(n+1)=B1(n)+Kp3*Δsh1+Ki3*δsh1;

[0037] The fourth formula is:

[0038] B2(n+1)=B2(n)+Kp4*Δsh2+Ki4*δsh2;

[0039] In the formula, B1(n) and B1(n+1) are the openings of the first branch throttling component, B2(n) and B2(n+1) are the openings of the second branch throttling component, and n is the cycle number; △sh1 is the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat; δsh1 is the deviation rate between the suction superheat of the first indoor heat exchanger and the first set suction superheat; △sh2 is the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; δsh2 is the deviation rate between the suction superheat of the second indoor heat exchanger and the second set suction superheat; Kp3, Ki3, Kp4, and Ki4 are all coefficients.

[0040] In some implementations, the fifth formula is:

[0041] F0=z1+a1*Qtot+b1*SHR+c1*Qtot 2 +d1*SHR 2 +e1*Qtot*SHR;

[0042] The sixth formula is:

[0043] C0=z2+a2*Qtot+b2*SHR+c2*Qtot 2 +d2*SHR 2 +e2*Qtot*SHR;

[0044] In the formula, F0 is the operating frequency of the compressor; C0 is the speed of the indoor fan; z1, a1, b1, c1, d1, e1, z2, a2, b2, c2, d2, and e2 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; Qsen is the heat load.

[0045] Matching the above device, the present invention provides an air conditioner on another aspect, including: the control device of the air conditioner mentioned above.

[0046] In accordance with the above method, the present invention provides a storage medium on another aspect, wherein the storage medium includes a stored program, wherein when the program is running, the device where the storage medium is located is controlled to execute the above-mentioned air conditioning control method.

[0047] In accordance with the above method, the present invention provides a computer program product on another aspect, wherein the computer program product includes a computer program, and when the computer program product is processed and executed, the steps of the above air conditioner control method are implemented.

[0048] According to the scheme of the present invention, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger connected in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0049] Other features and advantages of the present invention will be set forth in the description which follows, and in part will be apparent from the description, or may be learned by practice of the present invention.

[0050] The technical solution of the present invention is further described in detail below through the accompanying drawings and embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] Figure 1 A schematic diagram of a flow chart of an embodiment of a method for controlling an air conditioner of the present invention;

[0052] Figure 2 A schematic structural diagram of an embodiment of a control device for an air conditioner of the present invention;

[0053] Figure 3 It is a structural schematic diagram of the air conditioning system of the present invention;

[0054] Figure 4 FIG. 4 is a flow chart of another embodiment of the air conditioner control method of the present invention.

[0055] In conjunction with the accompanying drawings, the reference numerals in the embodiments of the present invention are as follows:

[0056] 10-compressor; 11-first air intake port of compressor; 12-second air intake port of compressor; 13-third air intake port of compressor; 14-exhaust port of compressor; 20-outdoor heat exchanger; 31-first-stage electronic expansion valve; 40-flash device; 32-first-second-stage electronic expansion valve; 33-second-second-stage electronic expansion valve; 51-first indoor heat exchanger; 52-second indoor heat exchanger; 102-acquisition unit; 104-control unit. DETAILED DESCRIPTION

[0057] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the specific embodiments of the present invention and the corresponding drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0058] According to an embodiment of the present invention, a control method for an air conditioner is provided, wherein the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; and indoor fans are arranged at the first heat exchanger and the second indoor heat exchanger.

[0059] The system structure of air conditioning is as follows Figure 3As shown, the throttling component of the air conditioner is a first-stage electronic expansion valve 31, the first branch throttling component is a first-stage electronic expansion valve 32, and the second branch throttling component is a second-stage electronic expansion valve 33. Specifically, the pipeline at the exhaust port 14 of the compressor 10 of the air conditioner passes through the outdoor heat exchanger 20 and the first-stage electronic expansion valve 31 in sequence and is connected to the flasher 40. The flasher 40 has two refrigerant outlets, one of which is connected to the third air intake port 13 of the compressor, and the other refrigerant outlet is connected to the compressor with a first branch and a second branch in parallel. On the first branch, along the direction from the flasher 40 to the compressor 10, the first-stage electronic expansion valve 32 and the first indoor heat exchanger 51 are arranged in sequence, and finally connected to the first air intake port 11 of the compressor. On the second branch, along the direction from the flasher 40 to the compressor 10, the second-stage electronic expansion valve 33 and the second indoor heat exchanger 52 are arranged in sequence, and finally connected to the second air intake port 12 of the compressor.

[0060] The first indoor heat exchanger and the second indoor heat exchanger are placed side by side in the same air duct, and have an upstream and downstream relationship. Figure 3 In the embodiment, the first indoor heat exchanger 51 is at an upstream position and the second indoor heat exchanger 52 is at a downstream position.

[0061] like Figure 1 The flowchart of an embodiment of the method of the present invention is shown in FIG. The air conditioner control method may include: steps S110 to S140.

[0062] In step S110, after the air conditioner starts to operate, the indoor dry-bulb temperature, the indoor dew point temperature, the suction superheat of the first indoor heat exchanger, and the suction superheat of the second indoor heat exchanger are obtained.

[0063] In step S120, a control strategy for controlling the operating frequency of the compressor of the air conditioner is determined according to the indoor dry-bulb temperature to control the operation of the compressor.

[0064] In step S130, a control strategy for controlling the rotation speed of the indoor fan is determined according to the indoor dew point temperature to control the operation of the indoor fan.

[0065] At step S140, control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component are determined respectively according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, so as to control the operation of the first branch throttling component and the second throttling component.

[0066] The control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the speed of the internal fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

[0067] The operation of the air conditioner is divided into the first stage and the second stage. In the first stage, the air conditioner obtains the operating parameters of the air conditioner according to the preset calculation formula based on the collected temperature, humidity, and suction superheat data, and controls the compressor operating frequency, internal fan speed, and the opening of the throttling component. In the second stage, the operating parameters are calculated based on the PD feedback control, and the two indoor heat exchangers are coupled to process the sensible heat load and latent heat load, so as to achieve the purpose of accurately controlling temperature and humidity and maintaining the efficient operation of the air conditioning system. Among them, for the compressor, internal fan, and throttling component, the judgment conditions for choosing to execute the first stage or the second stage are different.

[0068] The first-stage electronic expansion valve and the second-stage electronic expansion valve are linked to each other. Specifically, the refrigerant mass flow rate of the first-stage electronic expansion valve is calculated based on the refrigerant mass flow rate of the first-stage electronic expansion valve and the second-stage electronic expansion valve, and is converted into an opening value based on the relationship between the mass flow rate and the opening degree. The first-stage electronic expansion valve is controlled based on the opening value. The calculation formula is:

[0069] Mr_m=(Mr1+Mr2) / (1-x_ft).

[0070] In the formula, Mr_m is the mass flow rate of the first-stage electronic expansion valve; Mr1 is the mass flow rate of the first and second-stage electronic expansion valves; Mr2 is the mass flow rate of the second and second-stage electronic expansion valves; x_ft is the first-stage throttling flash dryness, and the calculation formula is as follows:

[0071] x_ft=i*(t_c_o-t_ft_target) / (jk*t_ft_target).

[0072] In the formula, i, j, and k are pre-stored coefficients determined by experiments; t_c_o is the condenser outlet temperature; t_ft_target is the target value of the intermediate temperature of the first-stage electronic expansion valve opening, and the calculation formula is as follows:

[0073] t_ft_target=m*tc_o+n*(tevap1+tevap2).

[0074] In the formula, m and n are pre-stored coefficients determined by experiments; tc_o is the condenser outlet temperature; tevap1 is the evaporation temperature of the first indoor heat exchanger; tevap2 is the evaporation temperature of the second indoor heat exchanger. Among them, the high-pressure circuit parameters include the condenser outlet temperature tc_o, and the low-pressure circuit parameters include the evaporation temperature tevap1 of the first indoor heat exchanger and the evaporation temperature tevap2 of the second indoor heat exchanger.

[0075] By determining the intermediate temperature target value of the opening of the first-stage electronic expansion valve according to the evaporation temperature of all indoor heat exchangers in the parallel air-conditioning system, and combining the mass flow rate of all second-stage electronic expansion valves, the opening of the first-stage electronic expansion valve is obtained, thereby improving the temperature and humidity control effect of the parallel air-conditioning system and enhancing the energy efficiency performance of the system.

[0076] In some embodiments, the PD feedback control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula, controlling the operation of the internal fan according to the result of calculating the speed of the internal fan according to the second formula, controlling the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula, and controlling the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula; the heat load and wet load control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula, and controlling the operation of the internal fan according to the result of calculating the speed of the internal fan according to the sixth formula.

[0077] In some embodiments, in step S120, the specific process of determining the operating frequency control strategy of controlling the compressor of the air conditioner according to the size of the indoor dry-bulb temperature includes: judging the size of the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is less than the first temperature difference, then the operating frequency control strategy of controlling the compressor of the air conditioner is to control the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula in the PD feedback control; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is greater than or equal to the first temperature difference, then the operating frequency control strategy of controlling the compressor of the air conditioner is to control the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula in the heat load and wet load control.

[0078] For the control of the compressor operating frequency, after the air conditioner is turned on, the compressor operating frequency is first controlled according to the first stage, and then whether to execute the second stage control is determined according to the size of the indoor dry bulb temperature Tin. The first stage is controlled according to the heat load and wet load, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first stage and the second stage is whether the indoor dry bulb temperature Tin reaches the indoor set temperature T_set. The indoor set temperature T_set is set by the user. The first temperature difference is used to determine whether the indoor dry bulb temperature Tin is significantly different from the indoor set temperature T_set, and can be set to 1.5°C. When |Tin-T_set|<1.5°C, the indoor dry bulb temperature Tin is slightly different from the indoor set temperature T_set, and it is considered that the indoor dry bulb temperature Tin meets the threshold interval and meets the conditions for PD feedback control; when |Tin-T_set|≥1.5°C, the first stage control continues.

[0079] The first formula is:

[0080] F(n+1)=F(n)+Kd*(Kp1*ΔTdr+Ki1*δTdr)+Kw*(Kp2*ΔTdp+Ki1*δTdp).

[0081] In the formula, F(n+1) and F(n) are the operating frequencies of the compressor, n is the cycle number; △Tdr is the difference between the indoor dry-bulb temperature and the indoor set temperature, that is, △Tdr=|Tin-T_set|; δTdr is the deviation rate between the indoor dry-bulb temperature and the indoor set temperature, that is, δTdr=△Tdr / T_set; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature, that is, △Tdp=|Tdp-Tdp_set|; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature, that is, δTdp=△Tdp / Tdp_set; Kd, Kp1, Ki1, and Kw are coefficients.

[0082] The fifth formula is:

[0083] F0=z1+a1*Qtot+b1*SHR+c1*Qtot 2 +d1*SHR 2 +e1*Qtot*SHR.

[0084] In the formula, F0 is the operating frequency of the compressor; z1, a1, b1, c1, d1, and e1 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; and Qsen is the heat load.

[0085] When the air conditioner stably controls temperature and humidity, the indoor heat load Qsen is equal to the sensible heat output by the air conditioner, and the indoor humidity load Qlat is equal to the latent heat output by the air conditioner. Therefore, the total cooling capacity of the air conditioner Qtot = sensible heat + latent heat = Qsen + Qlat. The calculation formula for heat load Qsen is:

[0086] Qsen=a3*(Tin-T_set)+b3*Tout+c3;

[0087] The calculation formula for wet load Qlat is:

[0088] Qlat=a4*(Tdp-Tdp_set)+b4*Tout+c4;

[0089] In the formula, a3, a4, b3, b4, c3, and c4 are coefficients determined by experiments; Tin is the indoor dry bulb temperature; Tin_set is the indoor set temperature; Tout is the outdoor ambient temperature; Tdp is the indoor dew point temperature; Tdp_set is the indoor set dew point temperature, which can be calculated by the wet air state parameter theory based on the indoor set temperature T_set and the set relative humidity RH_set. It should be noted that the method of calculating heat load and wet load is not limited to the above formula, and heat load and wet load can also be calculated based on other empirical formulas, experimental fitting formulas, big data and large model fitting formulas and other algorithms.

[0090] In some embodiments, in step S130, the specific process of determining the control strategy for controlling the rotational speed of the indoor fan according to the size of the indoor dew point temperature includes: judging the size of the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is less than the second temperature difference, then the control strategy for controlling the rotational speed of the indoor fan is to control the operation of the indoor fan by calculating the rotational speed of the indoor fan according to the second formula in the PD feedback control; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is greater than or equal to the second temperature difference, then the control strategy for controlling the rotational speed of the indoor fan is to control the operation of the indoor fan by calculating the rotational speed of the indoor fan according to the sixth formula in the heat load and moisture load control.

[0091] The indoor set dew point temperature Tdp_set can be calculated by the wet air state parameter theory based on the indoor set temperature T_set and the set relative humidity RH_set. The indoor dew point temperature Tdp can be calculated based on the indoor environment dry bulb temperature Tin, the indoor relative humidity RH, and the outdoor environment temperature Tout. After the air conditioner is turned on, the speed of the indoor fan is first controlled according to the first stage, and then the second stage of control is determined according to the size of the indoor dew point temperature Tdp. The first stage is controlled according to the heat load and the wet load, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first stage and the second stage is whether the indoor dew point temperature Tdp reaches the indoor set dew point temperature Tdp_set. The second temperature difference is used to determine whether the indoor dew point temperature Tdp is significantly different from the indoor set dew point temperature Tdp_set, which can be set to 1°C. When |Tdp-Tdp_set|<1℃, the difference between the indoor dew point temperature Tdp and the indoor set dew point temperature Tdp_set is small. It is considered that the indoor dew point temperature Tdp meets the threshold range and meets the conditions for PD feedback control; when |Tdp-Tdp_set|≥1℃, the first stage of control will continue.

[0092] The second formula is:

[0093] C(n+1)=C(n)+Kp2*ΔTdp+Ki2*δTdp.

[0094] In the formula, C(n+1) and C(n) are the speeds of the indoor fans, n is the cycle number; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature; Kp2 and Ki2 are coefficients.

[0095] The sixth formula is:

[0096] C0=z2+a2*Qtot+b2*SHR+c2*Qtot 2 +d2*SHR 2 +e2*Qtot*SHR.

[0097] In the formula, C0 is the rotation speed of the indoor fan; z2, a2, b2, c2, d2, and e2 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; and Qsen is the heat load.

[0098] In some embodiments, in step S140, the specific process of determining the control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component respectively according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger includes: judging the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is to control the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is the fitting formula control strategy. And, determine the size of the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the second branch throttling component is the PD feedback control in which the result of calculating the opening of the second branch throttling component according to the fourth formula controls the operation of the second branch throttling component; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the second branch throttling component is the fitting formula control strategy.

[0099] The third formula is:

[0100] B1(n+1)=B1(n)+Kp3*Δsh1+Ki3*δsh1.

[0101] The fourth formula is:

[0102] B2(n+1)=B2(n)+Kp4*Δsh2+Ki4*δsh2.

[0103] In the formula, B1(n) and B1(n+1) are the openings of the first branch throttling component, B2(n) and B2(n+1) are the openings of the second branch throttling component, and n is the cycle number; △sh1 is the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat, that is, △sh1=|sh_obj1-sh_1|; δsh1 is the deviation rate between the suction superheat of the first indoor heat exchanger and the first set suction superheat, that is, δsh1=△sh1 / sh_1; △sh2 is the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat, that is, △sh1=|sh_obj2-sh_2|; δsh2 is the deviation rate between the suction superheat of the second indoor heat exchanger and the second set suction superheat, that is, δsh2=△sh2 / sh_2; Kp3, Ki3, Kp4, and Ki4 are all coefficients.

[0104] The fitting formula control strategy for controlling the opening of the first branch throttling component and the opening of the second branch throttling component is the same; the fitting formula control strategy is to obtain the mass flow of the first branch throttling component and the second branch throttling component according to the seventh calculation formula, and obtain the opening of the first branch throttling component and the opening of the second branch throttling component according to the preset corresponding relationship between the mass flow and the opening; the seventh calculation formula is:

[0105] Mr=f(F, etav, tsuc_obj, tevap);

[0106] In the formula, Mr is the mass flow rate of the first branch throttling component and the second branch throttling component; F is the operating frequency of the compressor; ηv is the volumetric efficiency; if Mr is the mass flow rate of the first branch throttling component, tsuc_obj is the target suction superheat of the first indoor heat exchanger, and tevap is the evaporation temperature of the first indoor heat exchanger; if Mr is the mass flow rate of the second branch throttling component, tsuc_obj is the target suction superheat of the second indoor heat exchanger, and tevap is the evaporation temperature of the second indoor heat exchanger.

[0107] For the opening control of the first and second level electronic expansion valves and the second level electronic expansion valve, after the air conditioner is turned on, the opening is first controlled according to the first stage, and then the second stage control is determined according to the suction superheat of the indoor heat exchanger directly connected to the second level electronic expansion valve. The first stage is controlled according to the fitting formula, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first and second stages is whether the suction superheat reaches the set suction superheat. The preset suction superheat difference Δsh is used to determine whether the suction superheat is significantly different from the set suction superheat. Taking the first and second level electronic expansion valves as an example, the suction superheat of the first indoor heat exchanger is sh_obj1, and the corresponding set suction superheat is sh_1. When |sh_obj1-sh_1|<Δsh, the difference between the suction superheat and the set suction superheat is small. It is considered that the suction superheat meets the threshold range, and the first and second level electronic expansion valves meet the conditions for PD feedback control; when |sh_obj1-sh_1|≥Δsh, the first stage of control continues to be executed.

[0108] Figure 4 FIG. 1 is a flow chart of another embodiment of the air conditioner control method of the present invention. Figure 4 As shown, including:

[0109] Step 1: Obtain the set values ​​of indoor dry bulb temperature and indoor relative humidity, and calculate the set value of indoor dew point temperature. Obtain the current values ​​of indoor dry bulb temperature, indoor relative humidity, and outdoor ambient temperature, and calculate the current value of indoor dew point temperature. Estimate the indoor heat load and wet load based on the set values ​​of indoor dry bulb temperature and indoor dew point temperature and the current values ​​of indoor dry bulb temperature, indoor dew point temperature, and outdoor ambient temperature. Determine the initial operating parameters of the air conditioner based on the indoor heat load and wet load.

[0110] Step 2: Perform PD control feedback to adjust the air conditioning operating parameters to stabilize temperature and humidity control according to the set values ​​and current values ​​of the indoor dry-bulb temperature and indoor dew point temperature.

[0111] Step 3: The opening of the first-stage throttling electronic expansion valve is controlled by the intermediate target temperature, which is calculated by an empirical formula. The empirical formula needs to obtain the characteristic parameters of the high-pressure circuit and the low-pressure circuit of the system; the opening of the second-stage throttling electronic expansion valve includes two parts: the calculated value and the feedback control. The calculated value empirical formula needs to obtain the characteristic parameters of the compressor, the pre-stored characteristic parameters of the electronic expansion valve, and the various state parameters of the system. The feedback control is realized by the preset suction target superheat.

[0112] According to the technical solution of this embodiment, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0113] According to an embodiment of the present invention, a control device for an air conditioner corresponding to the control method for an air conditioner is also provided. The air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; and an internal fan is arranged at the first heat exchanger and the second indoor heat exchanger.

[0114] The system structure of air conditioning is as follows Figure 3 As shown, the throttling component of the air conditioner is a first-stage electronic expansion valve 31, the first branch throttling component is a first-stage electronic expansion valve 32, and the second branch throttling component is a second-stage electronic expansion valve 33. Specifically, the pipeline at the exhaust port 14 of the compressor 10 of the air conditioner passes through the outdoor heat exchanger 20 and the first-stage electronic expansion valve 31 in sequence and is connected to the flasher 40. The flasher 40 has two refrigerant outlets, one of which is connected to the third air intake port 13 of the compressor, and the other refrigerant outlet is connected to the compressor with a first branch and a second branch in parallel. On the first branch, along the direction from the flasher 40 to the compressor 10, the first-stage electronic expansion valve 32 and the first indoor heat exchanger 51 are arranged in sequence, and finally connected to the first air intake port 11 of the compressor. On the second branch, along the direction from the flasher 40 to the compressor 10, the second-stage electronic expansion valve 33 and the second indoor heat exchanger 52 are arranged in sequence, and finally connected to the second air intake port 12 of the compressor.

[0115] The first indoor heat exchanger and the second indoor heat exchanger are placed side by side in the same air duct, and have an upstream and downstream relationship. Figure 3 In the embodiment, the first indoor heat exchanger 51 is at an upstream position and the second indoor heat exchanger 52 is at a downstream position.

[0116] See also Figure 2 The schematic diagram of the structure of an embodiment of the device of the present invention is shown. The control device of the air conditioner may include: an acquisition unit 102 and a control unit 104.

[0117] The acquisition unit 102 is configured to acquire the indoor dry bulb temperature, the indoor dew point temperature, the suction superheat of the first indoor heat exchanger, and the suction superheat of the second indoor heat exchanger after the air conditioner starts to operate. The specific functions and processing of the acquisition unit 102 refer to step S110.

[0118] The control unit 104 is configured to determine a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the indoor dry-bulb temperature, so as to control the operation of the compressor. The specific functions and processing of the control unit 104 refer to step S120.

[0119] The control unit 104 is further configured to determine a control strategy for controlling the rotation speed of the indoor fan according to the indoor dew point temperature, so as to control the operation of the indoor fan. The specific functions and processing of the control unit 104 refer to step S130.

[0120] The control unit 104 is further configured to determine a control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component, respectively, according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, so as to control the operation of the first branch throttling component and the second throttling component. The specific functions and processing of the control unit 104 refer to step S140.

[0121] The control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the speed of the internal fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

[0122] The operation of the air conditioner is divided into the first stage and the second stage. In the first stage, the air conditioner obtains the operating parameters of the air conditioner according to the preset calculation formula based on the collected temperature, humidity, and suction superheat data, and controls the compressor operating frequency, internal fan speed, and the opening of the throttling component. In the second stage, the operating parameters are calculated based on the PD feedback control, and the two indoor heat exchangers are coupled to process the sensible heat load and latent heat load, so as to achieve the purpose of accurately controlling temperature and humidity and maintaining the efficient operation of the air conditioning system. Among them, for the compressor, internal fan, and throttling component, the judgment conditions for choosing to execute the first stage or the second stage are different.

[0123] The first-stage electronic expansion valve and the second-stage electronic expansion valve are linked to each other. Specifically, the refrigerant mass flow rate of the first-stage electronic expansion valve is calculated based on the refrigerant mass flow rate of the first-stage electronic expansion valve and the second-stage electronic expansion valve, and is converted into an opening value based on the relationship between the mass flow rate and the opening degree. The first-stage electronic expansion valve is controlled based on the opening value. The calculation formula is:

[0124] Mr_m=(Mr1+Mr2) / (1-x_ft).

[0125] In the formula, Mr_m is the mass flow rate of the first-stage electronic expansion valve; Mr1 is the mass flow rate of the first and second-stage electronic expansion valves; Mr2 is the mass flow rate of the second and second-stage electronic expansion valves; x_ft is the first-stage throttling flash dryness, and the calculation formula is as follows:

[0126] x_ft=i*(t_c_o-t_ft_target) / (jk*t_ft_target).

[0127] In the formula, i, j, and k are pre-stored coefficients determined by experiments; t_c_o is the condenser outlet temperature, and t_ft_target is the target value of the intermediate temperature of the first-stage electronic expansion valve opening. The calculation formula is as follows:

[0128] t_ft_target=m*tc_o+n*(tevap1+tevap2).

[0129] In the formula, m and n are pre-stored coefficients determined by experiments; tc_o is the condenser outlet temperature; tevap1 is the evaporation temperature of the first indoor heat exchanger; tevap2 is the evaporation temperature of the second indoor heat exchanger. Among them, the high-pressure circuit parameters include the condenser outlet temperature tc_o, and the low-pressure circuit parameters include the evaporation temperature tevap1 of the first indoor heat exchanger and the evaporation temperature tevap2 of the second indoor heat exchanger.

[0130] By determining the intermediate temperature target value of the opening of the first-stage electronic expansion valve according to the evaporation temperature of all indoor heat exchangers in the parallel air-conditioning system, and combining the mass flow rate of all second-stage electronic expansion valves, the opening of the first-stage electronic expansion valve is obtained, thereby improving the temperature and humidity control effect of the parallel air-conditioning system and enhancing the energy efficiency performance of the system.

[0131] In some embodiments, the PD feedback control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula, controlling the operation of the internal fan according to the result of calculating the speed of the internal fan according to the second formula, controlling the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula, and controlling the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula; the heat load and wet load control strategy includes: controlling the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula, and controlling the operation of the internal fan according to the result of calculating the speed of the internal fan according to the sixth formula.

[0132] In some embodiments, the control unit 104 determines the specific process of the operating frequency control strategy of controlling the compressor of the air conditioner according to the size of the indoor dry-bulb temperature, including: judging the size of the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is less than the first temperature difference, then the operating frequency control strategy of controlling the compressor of the air conditioner is to control the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the first formula in the PD feedback control; if the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is greater than or equal to the first temperature difference, then the operating frequency control strategy of controlling the compressor of the air conditioner is to control the operation of the compressor according to the result of calculating the operating frequency of the compressor according to the fifth formula in the heat load and wet load control.

[0133] For the control of the compressor operating frequency, after the air conditioner is turned on, the compressor operating frequency is first controlled according to the first stage, and then whether to execute the second stage control is determined according to the size of the indoor dry bulb temperature Tin. The first stage is controlled according to the heat load and wet load, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first stage and the second stage is whether the indoor dry bulb temperature Tin reaches the indoor set temperature T_set. The indoor set temperature T_set is set by the user. The first temperature difference is used to determine whether the indoor dry bulb temperature Tin is significantly different from the indoor set temperature T_set, and can be set to 1.5°C. When |Tin-T_set|<1.5°C, the indoor dry bulb temperature Tin is slightly different from the indoor set temperature T_set, and it is considered that the indoor dry bulb temperature Tin meets the threshold interval and meets the conditions for PD feedback control; when |Tin-T_set|≥1.5°C, the first stage control continues.

[0134] The first formula is:

[0135] F(n+1)=F(n)+Kd*(Kp1*ΔTdr+Ki1*δTdr)+Kw*(Kp2*ΔTdp+Ki1*δTdp).

[0136] In the formula, F(n+1) and F(n) are the operating frequencies of the compressor, n is the cycle number; △Tdr is the difference between the indoor dry-bulb temperature and the indoor set temperature, that is, △Tdr=|Tin-T_set|; δTdr is the deviation rate between the indoor dry-bulb temperature and the indoor set temperature, that is, δTdr=△Tdr / T_set; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature, that is, △Tdp=|Tdp-Tdp_set|; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature, that is, δTdp=△Tdp / Tdp_set; Kd, Kp1, Ki1, and Kw are coefficients.

[0137] The fifth formula is:

[0138] F0=z1+a1*Qtot+b1*SHR+c1*Qtot 2 +d1*SHR 2 +e1*Qtot*SHR.

[0139] In the formula, F0 is the operating frequency of the compressor; z1, a1, b1, c1, d1, and e1 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; and Qsen is the heat load.

[0140] When the air conditioner stably controls temperature and humidity, the indoor heat load Qsen is equal to the sensible heat output by the air conditioner, and the indoor humidity load Qlat is equal to the latent heat output by the air conditioner. Therefore, the total cooling capacity of the air conditioner Qtot = sensible heat + latent heat = Qsen + Qlat. The calculation formula for heat load Qsen is:

[0141] Qsen=a3*(Tin-T_set)+b3*Tout+c3;

[0142] The calculation formula for wet load Qlat is:

[0143] Qlat=a4*(Tdp-Tdp_set)+b4*Tout+c4;

[0144] In the formula, a3, a4, b3, b4, c3, and c4 are coefficients determined by experiments; Tin is the indoor dry bulb temperature; Tin_set is the indoor set temperature; Tout is the outdoor ambient temperature; Tdp is the indoor dew point temperature; Tdp_set is the indoor set dew point temperature, which can be calculated by the wet air state parameter theory based on the indoor set temperature T_set and the set relative humidity RH_set. It should be noted that the method of calculating heat load and wet load is not limited to the above formula, and heat load and wet load can also be calculated based on other empirical formulas, experimental fitting formulas, big data and large model fitting formulas and other algorithms.

[0145] In some embodiments, the control unit 104 determines the specific process of the control strategy for controlling the rotational speed of the indoor fan according to the size of the indoor dew point temperature, including: judging the size of the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is less than the second temperature difference, then the control strategy for controlling the rotational speed of the indoor fan is to control the operation of the indoor fan by calculating the rotational speed of the indoor fan according to the second formula in the PD feedback control; if the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is greater than or equal to the second temperature difference, then the control strategy for controlling the rotational speed of the indoor fan is to control the operation of the indoor fan by calculating the rotational speed of the indoor fan according to the sixth formula in the heat load and moisture load control.

[0146] The indoor set dew point temperature Tdp_set can be calculated by the wet air state parameter theory based on the indoor set temperature T_set and the set relative humidity RH_set. The indoor dew point temperature Tdp can be calculated based on the indoor environment dry bulb temperature Tin, the indoor relative humidity RH, and the outdoor environment temperature Tout. After the air conditioner is turned on, the speed of the indoor fan is first controlled according to the first stage, and then the second stage of control is determined according to the size of the indoor dew point temperature Tdp. The first stage is controlled according to the heat load and the wet load, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first stage and the second stage is whether the indoor dew point temperature Tdp reaches the indoor set dew point temperature Tdp_set. The second temperature difference is used to determine whether the indoor dew point temperature Tdp is significantly different from the indoor set dew point temperature Tdp_set, which can be set to 1°C. When |Tdp-Tdp_set|<1℃, the difference between the indoor dew point temperature Tdp and the indoor set dew point temperature Tdp_set is small. It is considered that the indoor dew point temperature Tdp meets the threshold range and meets the conditions for PD feedback control; when |Tdp-Tdp_set|≥1℃, the first stage of control will continue.

[0147] The second formula is:

[0148] C(n+1)=C(n)+Kp2*ΔTdp+Ki2*δTdp.

[0149] In the formula, C(n+1) and C(n) are the speeds of the indoor fans, n is the cycle number; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature; Kp2 and Ki2 are coefficients.

[0150] The sixth formula is:

[0151] C0=z2+a2*Qtot+b2*SHR+c2*Qtot 2 +d2*SHR 2 +e2*Qtot*SHR.

[0152] In the formula, C0 is the rotation speed of the indoor fan; z2, a2, b2, c2, d2, and e2 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; and Qsen is the heat load.

[0153] In some embodiments, the control unit 104 determines the specific process of the control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, respectively, including: judging the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is to control the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula in the PD feedback control; if the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the first branch throttling component is the fitting formula control strategy. And, determine the size of the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is less than the preset suction superheat difference, then the control strategy for controlling the opening of the second branch throttling component is the PD feedback control in which the result of calculating the opening of the second branch throttling component according to the fourth formula controls the operation of the second branch throttling component; if the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is greater than or equal to the preset suction superheat difference, then the control strategy for controlling the opening of the second branch throttling component is the fitting formula control strategy.

[0154] The third formula is:

[0155] B1(n+1)=B1(n)+Kp3*Δsh1+Ki3*δsh1.

[0156] The fourth formula is:

[0157] B2(n+1)=B2(n)+Kp4*Δsh2+Ki4*δsh2.

[0158] In the formula, B1(n) and B1(n+1) are the openings of the first branch throttling component, B2(n) and B2(n+1) are the openings of the second branch throttling component, and n is the cycle number; △sh1 is the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat, that is, △sh1=|sh_obj1-sh_1|; δsh1 is the deviation rate between the suction superheat of the first indoor heat exchanger and the first set suction superheat, that is, δsh1=△sh1 / sh_1; △sh2 is the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat, that is, △sh1=|sh_obj2-sh_2|; δsh2 is the deviation rate between the suction superheat of the second indoor heat exchanger and the second set suction superheat, that is, δsh2=△sh2 / sh_2; Kp3, Ki3, Kp4, and Ki4 are all coefficients.

[0159] The fitting formula control strategy for controlling the opening of the first branch throttling component and the opening of the second branch throttling component is the same; the fitting formula control strategy is to obtain the mass flow of the first branch throttling component and the second branch throttling component according to the seventh calculation formula, and obtain the opening of the first branch throttling component and the opening of the second branch throttling component according to the preset corresponding relationship between the mass flow and the opening; the seventh calculation formula is:

[0160] Mr=f(F, etav, tsuc_obj, tevap);

[0161] In the formula, Mr is the mass flow rate of the first branch throttling component and the second branch throttling component; F is the operating frequency of the compressor; ηv is the volumetric efficiency; if Mr is the mass flow rate of the first branch throttling component, tsuc_obj is the target suction superheat of the first indoor heat exchanger, and tevap is the evaporation temperature of the first indoor heat exchanger; if Mr is the mass flow rate of the second branch throttling component, tsuc_obj is the target suction superheat of the second indoor heat exchanger, and tevap is the evaporation temperature of the second indoor heat exchanger.

[0162] For the opening control of the first and second level electronic expansion valves and the second level electronic expansion valve, after the air conditioner is turned on, the opening is first controlled according to the first stage, and then the second stage control is determined according to the suction superheat of the indoor heat exchanger directly connected to the second level electronic expansion valve. The first stage is controlled according to the fitting formula, and the second stage is controlled according to the PD feedback. The second stage is a precise temperature and humidity control logic. The difference between the first and second stages is whether the suction superheat reaches the set suction superheat. The preset suction superheat difference Δsh is used to determine whether the suction superheat is significantly different from the set suction superheat. Taking the first and second level electronic expansion valves as an example, the suction superheat of the first indoor heat exchanger is sh_obj1, and the corresponding set suction superheat is sh_1. When |sh_obj1-sh_1|<Δsh, the difference between the suction superheat and the set suction superheat is small. It is considered that the suction superheat meets the threshold range, and the first and second level electronic expansion valves meet the conditions for PD feedback control; when |sh_obj1-sh_1|≥Δsh, the first stage of control continues to be executed.

[0163] Figure 4 FIG. 1 is a flow chart of another embodiment of the air conditioner control method of the present invention. Figure 4 As shown, including:

[0164] Step 1: Obtain the set values ​​of indoor dry bulb temperature and indoor relative humidity, and calculate the set value of indoor dew point temperature. Obtain the current values ​​of indoor dry bulb temperature, indoor relative humidity, and outdoor ambient temperature, and calculate the current value of indoor dew point temperature. Estimate the indoor heat load and wet load based on the set values ​​of indoor dry bulb temperature and indoor dew point temperature and the current values ​​of indoor dry bulb temperature, indoor dew point temperature, and outdoor ambient temperature. Determine the initial operating parameters of the air conditioner based on the indoor heat load and wet load.

[0165] Step 2: Perform PD control feedback to adjust the air conditioning operating parameters to stabilize temperature and humidity control according to the set values ​​and current values ​​of the indoor dry-bulb temperature and indoor dew point temperature.

[0166] Step 3: The opening of the first-stage throttling electronic expansion valve is controlled by the intermediate target temperature, which is calculated by an empirical formula. The empirical formula needs to obtain the characteristic parameters of the high-pressure circuit and the low-pressure circuit of the system; the opening of the second-stage throttling electronic expansion valve includes two parts: the calculated value and the feedback control. The calculated value empirical formula needs to obtain the characteristic parameters of the compressor, the pre-stored characteristic parameters of the electronic expansion valve, and the various state parameters of the system. The feedback control is realized by the preset suction target superheat.

[0167] Since the processing and functions implemented by the device of this embodiment basically correspond to the embodiments, principles and examples of the aforementioned method, for the details not fully described in this embodiment, please refer to the relevant descriptions in the aforementioned embodiments, and no further elaboration will be made here.

[0168] According to the technical solution of the present invention, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0169] According to an embodiment of the present invention, an air conditioner corresponding to the control device of the air conditioner is also provided. The air conditioner may include: the control device of the air conditioner described above.

[0170] Since the processing and functions implemented by the air conditioner of this embodiment basically correspond to the embodiments, principles and examples of the aforementioned devices, for the details not fully described in this embodiment, please refer to the relevant descriptions in the aforementioned embodiments and will not be repeated here.

[0171] According to the technical solution of the present invention, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0172] According to an embodiment of the present invention, a storage medium corresponding to the air conditioner control method is also provided, wherein the storage medium includes a stored program, wherein when the program is running, the device where the storage medium is located is controlled to execute the air conditioner control method described above.

[0173] Since the processing and functions implemented by the storage medium of this embodiment basically correspond to the embodiments, principles and examples of the aforementioned method, for the details not fully described in this embodiment, please refer to the relevant descriptions in the aforementioned embodiments, and no further elaboration will be made here.

[0174] According to the technical solution of the present invention, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0175] According to an embodiment of the present invention, a computer program product corresponding to the air conditioner control method is also provided, wherein the computer program product comprises a computer program, and when the computer program product is processed and executed, the steps of the air conditioner control method are implemented.

[0176] Since the processing and functions implemented by the computer program product of this embodiment basically correspond to the embodiments, principles and examples of the aforementioned method, for the details not fully described in this embodiment, please refer to the relevant descriptions in the aforementioned embodiments and will not be repeated here.

[0177] According to the technical solution of the present invention, the air conditioner has a first indoor heat exchanger and a second indoor heat exchanger in parallel, a first branch throttling component is provided between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is provided between the second indoor heat exchanger and the throttling component of the air conditioner; after the air conditioner starts to operate, the control strategy for determining the compressor operating frequency according to the indoor dry-bulb temperature is a PD feedback control strategy or a heat load and wet load control strategy, the control strategy for determining the internal fan speed according to the indoor dew point temperature is a PD feedback control strategy or a heat load and wet load control strategy, and the control strategy for determining the opening of the first branch throttling component and the opening of the second branch throttling component respectively according to the suction superheat of the first indoor heat exchanger and the second indoor heat exchanger is a PD feedback control strategy or a fitting formula control strategy. Thus, by combining PD feedback control and heat and wet load control, the operating states of the compressor, the internal fan, and the throttling component in the parallel air conditioning system are controlled to ensure that the system accurately controls temperature and humidity and operates stably and efficiently.

[0178] In summary, it is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0179] The above description is only an embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent substitution, improvement, etc. made within the spirit and principle of the present invention shall be included in the scope of the claims of the present invention.

Claims

1. A method for controlling an air conditioner, characterized in that: The air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; an internal fan is arranged at the first heat exchanger and the second indoor heat exchanger; The method comprises: After the air conditioner starts to run, obtaining the indoor dry-bulb temperature, the indoor dew point temperature, the suction superheat of the first indoor heat exchanger, and the suction superheat of the second indoor heat exchanger; Determining a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the indoor dry-bulb temperature to control the operation of the compressor; Determining a control strategy for controlling the rotation speed of the indoor fan according to the indoor dew point temperature to control the operation of the indoor fan; According to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, respectively determine the control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component, so as to control the operation of the first branch throttling component and the second throttling component; Among them, the control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the speed of the internal fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

2. The air conditioner control method according to claim 1, characterized in that: The PD feedback control strategy includes: controlling the operation of the compressor by calculating the operating frequency of the compressor according to the first formula, controlling the operation of the indoor fan by calculating the speed of the indoor fan according to the second formula, controlling the operation of the first branch throttling component by calculating the opening of the first branch throttling component according to the third formula, and controlling the operation of the second branch throttling component by calculating the opening of the second branch throttling component according to the fourth formula; The heat load and wet load control strategy includes: controlling the operation of the compressor by calculating the operating frequency of the compressor according to the fifth formula, and controlling the operation of the indoor fan by calculating the speed of the indoor fan according to the sixth formula; The control strategy for controlling the operating frequency of the compressor of the air conditioner is determined according to the indoor dry-bulb temperature, including: Determine the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature; If the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is less than the first temperature difference, the operating frequency control strategy of the compressor of the air conditioner is to control the operation of the compressor by calculating the operating frequency of the compressor according to the first formula in the PD feedback control; If the absolute value of the difference between the indoor dry-bulb temperature and the indoor set temperature is greater than or equal to the first temperature difference, the operating frequency control strategy of the compressor of the air conditioner is to control the operation of the compressor by calculating the operating frequency of the compressor according to the fifth formula in the heat load and wet load control; and / or, The control strategy for controlling the rotation speed of the indoor fan is determined according to the indoor dew point temperature, including: Determining the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature; If the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is less than the second temperature difference, the control strategy for controlling the rotation speed of the indoor fan is to control the operation of the indoor fan by calculating the rotation speed of the indoor fan according to the second formula in the PD feedback control; If the absolute value of the difference between the indoor dew point temperature and the indoor set dew point temperature is greater than or equal to the second temperature difference, the control strategy for controlling the speed of the indoor fan is to control the operation of the indoor fan according to the result of calculating the speed of the indoor fan according to the sixth formula in the heat load and wet load control.

3. The air conditioner control method according to claim 2, characterized in that: According to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, a control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component is determined respectively, including: Determine the absolute value of the difference between the suction air superheat of the first indoor heat exchanger and the first set suction air superheat, If the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is less than the preset suction superheat difference, the control strategy for controlling the opening of the first branch throttling component is to control the operation of the first branch throttling component according to the result of calculating the opening of the first branch throttling component according to the third formula in the PD feedback control; If the absolute value of the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat is greater than or equal to the preset suction superheat difference, the control strategy for controlling the opening of the first branch throttling component is the fitting formula control strategy; and / or, Determining the magnitude of the absolute value of the difference between the suction air superheat of the second indoor heat exchanger and a second set suction air superheat; If the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is less than the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is to control the operation of the second branch throttling component according to the result of calculating the opening of the second branch throttling component according to the fourth formula in the PD feedback control; If the absolute value of the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat is greater than or equal to the preset suction superheat difference, the control strategy for controlling the opening of the second branch throttling component is the fitting formula control strategy; Among them, the fitting formula control strategy for controlling the opening of the first branch throttling component and the opening of the second branch throttling component is the same; the fitting formula control strategy is to obtain the mass flow of the first branch throttling component and the second branch throttling component according to the seventh calculation formula, and obtain the opening of the first branch throttling component and the opening of the second branch throttling component according to the preset corresponding relationship between the mass flow and the opening; the seventh calculation formula is: Mr=f(F, etav, tsuc_obj, tevap); In the formula, Mr is the mass flow rate of the first branch throttling component and the second branch throttling component; F is the operating frequency of the compressor; ηv is the volumetric efficiency; if Mr is the mass flow rate of the first branch throttling component, tsuc_obj is the target suction superheat of the first indoor heat exchanger, and tevap is the evaporation temperature of the first indoor heat exchanger; if Mr is the mass flow rate of the second branch throttling component, tsuc_obj is the target suction superheat of the second indoor heat exchanger, and tevap is the evaporation temperature of the second indoor heat exchanger.

4. The air conditioner control method according to claim 2, characterized in that: The first formula is: F(n+1)=F(n)+Kd*(Kp1*△Tdr+Ki1*δTdr)+Kw*(Kp2*△Tdp+Ki1*δTdp); The second formula is: C(n+1)=C(n)+Kp2*ΔTdp+Ki2*δTdp; In the formula, F(n+1) and F(n) are the operating frequencies of the compressors, C(n+1) and C(n) are the speeds of the indoor fans, and n is the cycle number; △Tdr is the difference between the indoor dry-bulb temperature and the indoor set temperature; δTdr is the deviation rate between the indoor dry-bulb temperature and the indoor set temperature; △Tdp is the difference between the indoor dew point temperature and the indoor target dew point temperature; δTdp is the deviation rate between the indoor dew point temperature and the indoor target dew point temperature; Kd, Kp1, Kp2, Ki1, Ki2, and Kw are all coefficients.

5. The air conditioner control method according to claim 2 or 3, characterized in that: The third formula is: B1(n+1)=B1(n)+Kp3*Δsh1+Ki3*δsh1; The fourth formula is: B2(n+1)=B2(n)+Kp4*Δsh2+Ki4*δsh2; In the formula, B1(n) and B1(n+1) are the openings of the first branch throttling component, B2(n) and B2(n+1) are the openings of the second branch throttling component, and n is the cycle number; △sh1 is the difference between the suction superheat of the first indoor heat exchanger and the first set suction superheat; δsh1 is the deviation rate between the suction superheat of the first indoor heat exchanger and the first set suction superheat; △sh2 is the difference between the suction superheat of the second indoor heat exchanger and the second set suction superheat; δsh2 is the deviation rate between the suction superheat of the second indoor heat exchanger and the second set suction superheat; Kp3, Ki3, Kp4, and Ki4 are all coefficients.

6. The air conditioner control method according to claim 2, characterized in that: The fifth formula is: F0=z1+a1*Qtot+b1*SHR+c1*Qtot 2 +d1*SHR 2 +e1*Qtot*SHR; The sixth formula is: <h2 style=";text-align:left;direction:ltr">C0 = z2 + a2 * Qtot + b2 * SHR + c2 * Qtot<h2 style=";text-align:left;direction:ltr"> 2 <h2 style=";text-align:left;direction:ltr"> +d2*SHR<h2 style=";text-align:left;direction:ltr"> 2 <h2 style=";text-align:left;direction:ltr"> +e2*Qtot*SHR; In the formula, F0 is the operating frequency of the compressor; C0 is the speed of the indoor fan; z1, a1, b1, c1, d1, e1, z2, a2, b2, c2, d2, and e2 are all coefficients; Qtot is the total cooling capacity of the air conditioner, Qtot=Qlat+Qsen; SHR is the sensible heat ratio; SHR=Qsen / Qtot; Qlat is the wet load; Qsen is the heat load.

7. A control device for an air conditioner, characterized in that: The air conditioner has a first indoor heat exchanger and a second indoor heat exchanger arranged in parallel; a first branch throttling component is arranged between the first indoor heat exchanger and the throttling component of the air conditioner, and a second branch throttling component is arranged between the second indoor heat exchanger and the throttling component of the air conditioner; an internal fan is arranged at the first heat exchanger and the second indoor heat exchanger; The device comprises: an acquisition unit configured to acquire, after the air conditioner starts to operate, an indoor dry-bulb temperature, an indoor dew point temperature, an air suction superheat of the first indoor heat exchanger, and an air suction superheat of the second indoor heat exchanger; A control unit configured to determine a control strategy for controlling the operating frequency of the compressor of the air conditioner according to the indoor dry-bulb temperature, so as to control the operation of the compressor; The control unit is configured to determine a control strategy for controlling the rotation speed of the indoor fan according to the indoor dew point temperature, so as to control the operation of the indoor fan; The control unit is configured to determine a control strategy for controlling the opening of the first branch throttling component and the opening of the second throttling component according to the suction superheat of the first indoor heat exchanger and the suction superheat of the second indoor heat exchanger, respectively, so as to control the operation of the first branch throttling component and the second throttling component; Among them, the control strategies for controlling the operating frequency of the compressor of the air conditioner include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the speed of the internal fan include: PD feedback control strategy, heat load and wet load control strategy; the control strategies for controlling the opening of the first branch throttling component and the opening of the second throttling component include: PD feedback control strategy, fitting formula control strategy.

8. An air conditioner, characterized in that: include: The air conditioner control device as claimed in claim 7.

9. A storage medium, characterized in that: The storage medium includes a stored program, wherein when the program is executed, the device where the storage medium is located is controlled to execute the air conditioner control method according to any one of claims 1 to 6.

10. A computer program product, comprising a computer program, characterized in that When the computer program is executed by a processor, the steps of the method according to any one of claims 1 to 6 are implemented.

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