Indoor unit, air conditioner and control method of indoor unit and air conditioner

Abstract

An indoor unit comprises a machine shell, an air outlet, an indoor heat exchanger and a shielding component. The machine shell comprises an upper cover plate and a bottom plate which are oppositely arranged, and a first side plate connected with the upper cover plate and the bottom plate. The air outlet is formed in the first side plate; the indoor heat exchanger is located in the machine shell, the extending direction of the indoor heat exchanger is parallel to the extending direction of the air outlet, the length of the indoor heat exchanger is smaller than that of the air outlet, the first end of the indoor heat exchanger and the first end of the air outlet are located on the same side, and the second end of the indoor heat exchanger and the second end of the air outlet are located on the same side. An avoiding space exists between the first end of the indoor heat exchanger and the first end of the air outlet; the shielding component is connected with the first end of the indoor heat exchanger and the first end of the air outlet so that the avoiding space can be shielded and prevented from being exposed.

Description

Indoor unit, air conditioner and control method thereof

[0001] This application claims priority to Chinese patent applications with application number 202211273970.X, filed on October 18, 2022, application number 202222590935.2, filed on September 29, 2022, and application number 202211091531.7, filed on September 7, 2022, the entire contents of which are incorporated by reference into this application. Technical Field

[0002] The present disclosure relates to the technical field of household appliances, and in particular to an indoor unit, an air conditioner and a control method thereof. Background Art

[0003] In the spring and from mid-June to early July in southern my country, the temperature mostly remains between 20 and 30 degrees Celsius, but the humidity can reach over 80%. At this time, the temperature is relatively comfortable but the humidity is too high. Users have a strong demand for air conditioners that can achieve dehumidification without lowering the indoor temperature.

[0004] Summary of the Invention

[0005] On the one hand, an indoor unit is provided. The indoor unit includes a casing, an air outlet, an indoor heat exchanger, and a shielding component. The casing includes an upper cover plate and a bottom plate arranged opposite to each other, and a first side plate connected to the upper cover plate and the bottom plate; the air outlet is arranged on the first side plate; the indoor heat exchanger is located inside the casing, its extension direction is parallel to the extension direction of the air outlet and its length is less than the length of the air outlet; the first end of the indoor heat exchanger is located on the same side as the first end of the air outlet, the second end of the indoor heat exchanger is located on the same side as the second end of the air outlet, and there is an avoidance space between the first end of the indoor heat exchanger and the first end of the air outlet; the shielding component connects the first end of the indoor heat exchanger and the first end of the air outlet to shield the avoidance space from being exposed.

[0006] In another aspect, an air conditioner is provided, comprising the indoor unit as described above.

[0007] In yet another aspect, an air conditioner is provided. The air conditioner includes an indoor unit, an outdoor unit, and a circulation pipeline connecting the indoor and outdoor units. The indoor unit includes a first indoor unit, the first indoor unit including a first indoor heat exchanger, a first electronic expansion valve, a second indoor heat exchanger, the second electronic expansion valve, and a first blowing device, wherein the second end of the first indoor heat exchanger is connected in series with the first electronic expansion valve, the second indoor heat exchanger, and the first end of the second electronic expansion valve, respectively; the first blowing device is configured to blow air toward the first indoor heat exchanger; the outdoor unit includes a compressor assembly, a first refrigerant flow direction switching device, a third electronic expansion valve, a first outdoor heat exchanger, and a second refrigerant flow direction switching device. The compressor assembly includes a compressor having an outlet and an inlet; the first refrigerant flow direction switching device includes a first port connected to the first end of the first indoor heat exchanger, a second port connected to the inlet, a third port connected to the outlet, and a fourth port; the second end of the first outdoor heat exchanger is connected to the second end of the second electronic expansion valve through the third electronic expansion valve; the second refrigerant flow direction switching device includes a fifth port connected to the inlet, a sixth port connected to the first end of the first outdoor heat exchanger, a seventh port connected to the outlet, and an eighth port connected to the fourth port.

[0008] In another aspect, a method for controlling an air conditioner is provided. The air conditioner is the air conditioner described above; the method includes: the controller obtaining a first exhaust pressure value of the compressor at a first moment via the pressure sensor; the controller determining a maximum target pressure value from a first target pressure value and a second target pressure value, wherein the first target pressure value is a target exhaust pressure value of the compressor when the first indoor unit operates in a first mode, and the second target pressure value is a target exhaust pressure value of the compressor when the second indoor unit operates in a second mode; the controller calculating a pressure deviation between the maximum target pressure value and the first exhaust pressure value; and the controller adjusting a gear position of the outdoor fan based on the pressure deviation so that the exhaust pressure value of the compressor reaches the maximum target pressure value. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] To more clearly illustrate the technical solutions of the present disclosure, the following briefly introduces the drawings required for use in some embodiments of the present disclosure. Obviously, the drawings described below are only drawings of some embodiments of the present disclosure, and those skilled in the art can also derive other drawings based on these drawings. Furthermore, the drawings described below are schematic diagrams and are not intended to limit the actual dimensions of the products, actual processes of the methods, actual timing of signals, and the like involved in the embodiments of the present disclosure.

[0010] FIG1 is a perspective view of an indoor unit of an air conditioner with a non-cooling and dehumidifying function according to some embodiments, with a shielding component removed;

[0011] FIG2 is a perspective view of an indoor unit according to some embodiments;

[0012] FIG3 is a top view of FIG2 ;

[0013] FIG4 is a cross-sectional view of the cross-sectional view taken along line BB in FIG3 rotated 90° clockwise;

[0014] FIG5 is an enlarged view of portion C of FIG4 ;

[0015] FIG6 is an enlarged view of portion A of FIG2 ;

[0016] FIG7 is a perspective view of a heat exchanger of an indoor unit equipped with components of a non-cooling dehumidification system according to some embodiments;

[0017] FIG8 is a perspective view of a shielding component of an indoor unit according to some embodiments;

[0018] FIG9 is a perspective view of an assembly structure of a heat exchanger and a shielding component of an indoor unit according to some embodiments;

[0019] FIG10 is a perspective view of the assembly structure of the heat exchanger and the shielding component of the indoor unit according to some embodiments from another perspective;

[0020] FIG11 is a structural diagram of an assembly of an upper cover foam layer and a shielding component of an indoor unit according to some embodiments;

[0021] FIG12 is an enlarged view of portion D of FIG11 ;

[0022] FIG13 is a structural diagram of an air conditioner of related art;

[0023] FIG14 is a structural diagram of an air conditioner according to some embodiments;

[0024] FIG15 is a circuit connection diagram of an air conditioner according to some embodiments;

[0025] FIG16 is a diagram illustrating an operation cycle structure of an air conditioner according to some embodiments;

[0026] FIG17 is a pressure-enthalpy diagram of a non-cooling dehumidification mode of an air conditioner according to some embodiments;

[0027] FIG18 is a diagram illustrating another operation cycle structure of an air conditioner according to some embodiments;

[0028] FIG19 is a pressure-enthalpy diagram of a cooling and dehumidification mode of an air conditioner according to some embodiments;

[0029] FIG20 is a diagram illustrating another operation cycle structure of an air conditioner according to some embodiments;

[0030] FIG21 is a diagram illustrating another operation cycle structure of an air conditioner according to some embodiments;

[0031] FIG22 is a diagram illustrating another operation cycle structure of an air conditioner according to some embodiments;

[0032] FIG23 is a diagram illustrating another operation cycle structure of an air conditioner according to some embodiments;

[0033] FIG24 is a pressure-enthalpy diagram of another air conditioner in a non-cooling dehumidification mode according to some embodiments;

[0034] FIG25 is a diagram showing the main components of an air conditioner according to some embodiments;

[0035] FIG26 is a flow chart of a method for controlling an air conditioner according to some embodiments;

[0036] FIG27 is a logic flow diagram of a method for controlling an air conditioner according to some embodiments;

[0037] FIG28 is a block diagram illustrating a hardware configuration of a controller of an air conditioner according to some embodiments.

[0038] In the accompanying drawings, 1000 - air conditioner;

[0039] 100 - outdoor unit; 110 - compressor; 111 - return air port; 112 - exhaust port; 120 - outdoor heat exchanger; 121 - first outdoor heat exchanger; 130 - gas-liquid separator; 131 - first port of gas-liquid separator 130; 132 - second port of gas-liquid separator 130; 140 - oil separator; 141 - first port of oil separator 140; 142 - second port of oil separator 140; 143 - third port of oil separator 140; 150 - three-way valve; 160 - four-way valve; 170 - refrigerant flow direction switching device; 171 - first refrigerant flow direction switching device; 172 - second refrigerant flow direction switching device; 173 - third refrigerant flow direction switching device;

[0040] 200 - indoor unit; 201 - first indoor unit; 11 - first indoor temperature sensor; 12 - second indoor temperature sensor; 13 - third indoor temperature sensor; 51 - first inlet air temperature sensor; 202 - second indoor unit; 14 - fourth indoor temperature sensor; 15 - fifth indoor temperature sensor; 16 - sixth indoor temperature sensor; 52 - second inlet air temperature sensor; 210 - indoor heat exchanger; 211 - first end of indoor heat exchanger; 212 - second end of indoor heat exchanger; 213 - plastic end plate; 214 - first indoor heat exchanger; 215 - second indoor heat exchanger; 220 - housing; 221 - upper cover; 2211 - upper cover body; 2212 - upper cover foam layer; 2212A - straight portion; 2212B - inclined portion; 2212C - positioning portion; 222 - bottom plate; 223 - air outlet; 2231-first end of air outlet; 2232-second end of air outlet; 224-first side panel; 225-second side panel; 226-third side panel; 227-fourth side panel; 230-water tray; 231-bottom plate of water tray; 232-first water tray side panel; A-avoidance space; 240-shielding component; 241-first shielding part; 2410-shielding part body; 2411-first Supporting portion; 2412 - second supporting portion; 2413 - inserting portion; 2414 - connecting portion; 2414A - first connecting portion; 2414B - second connecting portion; 242 - second shielding portion; 2421 - third supporting portion; 2422 - fourth supporting portion; 2423 - through portion; 250 - connecting end plate; 251 - first blowing device; 252 - second blowing device; 253 - third blowing device;

[0041] 300-expansion valve; 310-outdoor electronic expansion valve; 320-indoor electronic expansion valve; 321-first electronic expansion valve; 322-second electronic expansion valve; 311-third electronic expansion valve; 323-fourth electronic expansion valve; 324-fifth indoor expansion valve; 312-sixth electronic expansion valve;

[0042] 400-system parts;

[0043] 500-controller;

[0044] 600 - solenoid valve; 601 - first end of the solenoid valve 600; 602 - second end of the solenoid valve 600;

[0045] 001 - first connection port; 002 - second connection port; 003 - third connection port; 20 - compressor assembly; 21 - inlet; 22 - outlet; 23 - oil return capillary; 24 - one-way valve;

[0046] E-screw hole; F-screw hole; G-screw hole; H-screw hole; M-first port; N-second port; O-third port; P-fourth port; R-fifth port; S-sixth port; T-seventh port; U-eighth port; I-ninth port; K-tenth port; Y-eleventh port; Z-twelfth port;

[0047] Pd-exhaust pressure value; Pd01-first exhaust pressure value; Pd02-second exhaust pressure value; Pd1-first saturation pressure value; Pd2-second saturation pressure value;

[0048] Pdset-target pressure value; Pdset1(1)-first target pressure value; Pdset2(1)-second target pressure value; Pdset1(2)-third target pressure value; Pdset2(2)-fourth target pressure value;

[0049] ΔPd2-pressure deviation value;

[0050] Ti-indoor ambient temperature; Ti1-first ambient temperature; Ti2-second ambient temperature; Ts-preset temperature;

[0051] ΔT-temperature difference; ΔT1-first temperature difference; ΔT2-second temperature difference; X-temperature difference change rate. DETAILED DESCRIPTION

[0052] The following will be combined with the accompanying drawings to clearly and completely describe the technical solutions in some embodiments of the present disclosure. Obviously, the embodiments described are only some embodiments of the present disclosure, not all embodiments. Based on the embodiments provided by the present disclosure, all other embodiments obtained by ordinary technicians in this field are within the scope of protection of the present disclosure.

[0053] Unless the context requires otherwise, throughout the specification and claims, the term "comprise" and its other forms, such as the third person singular form "comprises" and the present participle form "comprising", are to be interpreted as open and inclusive, that is, "including, but not limited to". In the description of the specification, the terms "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific example" or "some examples" are intended to indicate that the particular features, structures, materials or characteristics associated with the embodiment or example are included in at least one embodiment or example of the present disclosure. The schematic representation of the above terms does not necessarily refer to the same embodiment or example. In addition, the particular features, structures, materials or characteristics may be included in any one or more embodiments or examples in any appropriate manner.

[0054] In the following, the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.

[0055] When describing some embodiments, the expressions "coupled" and "connected" and their derivatives are used. For example, when describing some embodiments, the term "connected" may be used to indicate that two or more components are in direct physical or electrical contact with each other. For another example, when describing some embodiments, the term "coupled" may be used to indicate that two or more components are in direct physical or electrical contact. However, the term "coupled" or "communicatively coupled" may also refer to two or more components that are not in direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the contents of this document.

[0056] “At least one of A, B and C” has the same meaning as “at least one of A, B or C” and both include the following combinations of A, B and C: A only, B only, C only, the combination of A and B, the combination of A and C, the combination of B and C, and the combination of A, B and C.

[0057] “A and / or B” includes the following three combinations: A only, B only, and a combination of A and B.

[0058] The use of "adapted to" or "configured to" herein is intended to be open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.

[0059] Additionally, the use of “based on” is meant to be open and inclusive, as a process, step, calculation, or other action “based on” one or more stated conditions or values ​​may, in practice, be based on additional conditions or values ​​beyond those stated.

[0060] As used herein, "about," "substantially," or "approximately" includes the stated value and an average value that is within an acceptable range of deviation from the particular value as determined by one of ordinary skill in the art taking into account the measurements in question and the errors associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0061] FIG14 is a structural diagram of an air conditioner according to some embodiments. As shown in FIG14 , the air conditioner 1000 includes a compressor 110 , an outdoor heat exchanger 120 , an indoor heat exchanger 210 , and an expansion valve 300 .

[0062] The air conditioner 1000 includes an outdoor unit 100 and an indoor unit 200. The outdoor unit 100 includes a compressor 110 and an outdoor heat exchanger 120, and the indoor unit 200 includes an indoor heat exchanger 210. The expansion valve 300 may be provided in the outdoor unit 100 or the indoor unit 200.

[0063] The compressor 110, the condenser (the indoor heat exchanger 210 or the outdoor heat exchanger 120), the expansion valve 300, and the evaporator (the outdoor heat exchanger 120 or the indoor heat exchanger 210) perform the refrigerant cycle of the air conditioner 1000. The refrigerant cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and circulates the refrigerant to the conditioned side.

[0064] The indoor heat exchanger 210 is configured to exchange heat between indoor air and the refrigerant flowing through the indoor heat exchanger 210. For example, when the air conditioner 1000 is operating in cooling mode, the indoor heat exchanger 210 operates as an evaporator, causing the refrigerant, after dissipating heat through the outdoor heat exchanger 120, to absorb heat from the indoor air through the indoor heat exchanger 210 and evaporate. When the air conditioner 1000 is in heating mode, the indoor heat exchanger 210 operates as a condenser, causing the refrigerant, after absorbing heat through the outdoor heat exchanger 210, to dissipate the heat to the indoor air through the indoor heat exchanger 210 and condense.

[0065] The expansion valve 300 is connected between the outdoor heat exchanger 120 and the indoor heat exchanger 210. The opening of the expansion valve 300 regulates the pressure of the refrigerant flowing through the outdoor heat exchanger 120 and the indoor heat exchanger 210, thereby adjusting the refrigerant flow rate between the outdoor heat exchanger 120 and the indoor heat exchanger 210. The flow rate and pressure of the refrigerant flowing between the outdoor heat exchanger 120 and the indoor heat exchanger 210 will affect the heat exchange performance of the outdoor heat exchanger 120 and the indoor heat exchanger 210. The expansion valve 300 can be an electronic valve. The opening of the expansion valve 300 is adjustable to control the flow rate and pressure of the refrigerant flowing through the expansion valve 300.

[0066] Compressor 110 compresses the low-temperature, low-pressure gas-phase refrigerant and discharges the compressed high-temperature, high-pressure gas-phase refrigerant, which then flows into the condenser. The condenser condenses the high-temperature, high-pressure gas-phase refrigerant into a high-pressure liquid-phase refrigerant, releasing heat into the surrounding environment during the condensation process. The expansion valve 300 expands the high-pressure liquid-phase refrigerant into a low-pressure gas-liquid two-phase refrigerant. The evaporator absorbs heat from the surrounding environment and evaporates the low-pressure gas-liquid two-phase refrigerant to form a low-temperature, low-pressure gas-phase refrigerant, which then returns to compressor 110.

[0067] In order to enable conventional two-pipe air conditioners to have the function of dehumidification without cooling (that is, dehumidification without lowering the indoor temperature), it is necessary to add system parts to the piping end of the indoor heat exchanger, such as a dehumidification solenoid valve and corresponding piping lines. While ensuring that the size of the indoor unit remains unchanged, in order to install the system parts to the piping end of the indoor heat exchanger, the length of the indoor heat exchanger needs to be shortened accordingly to reserve space for the system parts. At this time, the length of the indoor heat exchanger is shorter than the length of the air outlet, and there is an exposed area between the indoor heat exchanger and the air outlet. The exposed area has low wind resistance, and the air outlet of the air conditioner will preferentially flow out from this area instead of passing through the indoor heat exchanger, causing the entire machine to leak air from this area, thereby affecting the performance of the air conditioner.

[0068] In the related art, the length of the air outlet is usually shortened accordingly to solve the problem of the exposed area between the indoor heat exchanger and the air outlet, but the shortened length of the air outlet will affect the versatility of on-site installation of the air conditioner. To this end, some embodiments of the present disclosure provide an indoor unit that can avoid the exposed area between the indoor heat exchanger and the air outlet, while not affecting the versatility of on-site installation of the air conditioner. Figure 1 is a three-dimensional view of an indoor unit of an air conditioner with a non-cooling and dehumidifying function according to some embodiments, with the shielding components removed; Figure 2 is a three-dimensional view of the indoor unit according to some embodiments; Figure 3 is a top view of Figure 2; Figure 4 is a cross-sectional view of the BB cross-sectional view of Figure 3 rotated 90° clockwise; and Figure 5 is an enlarged view of part C of Figure 4. In some embodiments, as shown in Figures 1 to 4, the indoor unit 200 includes an indoor heat exchanger 210, a casing 220, and other structural components, such as a fan assembly. The housing 220 includes an upper cover 221, a bottom plate 222, an air outlet 223, and circumferential side panels. The circumferential side panels are formed by four side panels: a first side panel 224, a second side panel 225, a third side panel 226, and a fourth side panel 227, which are connected in sequence. In some embodiments, the housing 220 is a rectangular parallelepiped, with the upper cover 221, bottom plate 222, and circumferential side panels all being rectangular. The air outlet 223 is provided on the first side panel 224 and includes a first end 2231 and a second end 2232. The length of the air outlet 223 is aligned with the length of the first side panel 224, and the length of the air outlet 223 is less than that of the first side panel 224.

[0069] In some embodiments, to improve the thermal insulation performance of the casing 220 of the indoor unit 200 and reduce heat transfer, the upper cover 221 typically includes a metal upper cover body 2211 and an upper cover foam layer 2212 that protrudes from the upper cover body 2211 toward the interior of the indoor unit 200. The upper cover foam layer 2212 includes a straight portion 2212A parallel to the bottom plate 222 and an inclined portion 2212B inclined toward the bottom plate 222. The inclined portion 2212B is located near the air outlet 223 and on the same side as the air outlet 223. The inclined portion 2212B is configured to guide the outlet airflow toward the air outlet 223, thereby increasing the air output of the indoor unit 200.

[0070] The indoor heat exchanger 210 is located inside the housing 220 near the air outlet 223 and includes a first end 211 and a second end 212. The first end 211 serves as the piping end of the indoor heat exchanger 210, while the second end 212 corresponds to the other end of the indoor heat exchanger 210. The length of the indoor heat exchanger 210 aligns with the length of the air outlet 223, and the length of the indoor heat exchanger 210 is shorter than that of the air outlet 223. The first end 211 and the first end 2231 of the air outlet are located on the same side, while the second end 212 and the second end 2232 of the air outlet are located on the same side. The second end 212 and the second end 2232 of the air outlet are tightly connected to ensure that this end is as closed as possible to prevent air leakage. There is an avoidance space A (see FIG. 1 ) between the first end 211 of the indoor heat exchanger and the first end 2231 of the air outlet to reserve space for other components.

[0071] In some embodiments, as shown in Figure 1 , the indoor unit 200 further includes a system component 400. The system component 400 is disposed at the first end 211 of the indoor heat exchanger and is located in the avoidance space A. For example, the system component 400 includes a dehumidification solenoid valve and corresponding piping.

[0072] As shown in Figures 4 and 5 , the indoor unit 200 also includes a water pan 230. The water pan 230 is located within the housing 220 and below the indoor heat exchanger 210 (i.e., on the side of the indoor heat exchanger 210 near the bottom plate 222). It has a tray-shaped structure with an opening toward the upper cover 221 and is configured to collect condensed water from the indoor heat exchanger 210. The water pan 230 includes a bottom plate 231 and circumferential side plates. The side plates include a first side plate 232 and three other side plates. The first side plate 232 is located near and parallel to the first side plate 224 of the indoor unit 200.

[0073] Figure 6 is an enlarged view of part A of Figure 2; Figure 7 is a stereoscopic view of an indoor heat exchanger equipped with non-cooling dehumidification system parts according to some embodiments; Figure 8 is a stereoscopic view of a shielding component of an indoor unit according to some embodiments; Figure 9 is a stereoscopic view of the assembly structure of the indoor heat exchanger and the shielding component from one perspective according to some embodiments; Figure 10 is a stereoscopic view of the assembly structure of the indoor heat exchanger and the shielding component from another perspective according to some embodiments; Figure 11 is a schematic diagram of the assembly structure of the upper cover foam layer and the shielding component of the indoor unit according to some embodiments; Figure 12 is an enlarged view of part D of Figure 11.

[0074] As shown in FIG. 2 , FIG. 6 and FIG. 7 , in some embodiments, the indoor unit 200 further includes a shielding component 240 .

[0075] The shielding member 240 connects the indoor heat exchanger first end 211 and the air outlet first end 2231 and is configured to shield the escape space A, preventing it from being exposed. This prevents air leakage from the escape space A during air delivery from the air conditioner 1000, which could affect the performance of the air conditioner 1000. Furthermore, since the length of the air outlet 223 does not need to be adjusted, the on-site installation versatility of the air conditioner 1000 is not affected. Furthermore, the shielding member 240 can also be used to secure the indoor heat exchanger first end 211, eliminating the need for a separate securing structure for the shortened indoor heat exchanger first end 211 and reducing the cost of the air conditioner 1000.

[0076] In some embodiments, the indoor heat exchanger 210 further includes a plastic end plate 213 (as shown in FIG7 ), which is arranged at the second end 212 of the indoor heat exchanger. The indoor unit 200 further includes a plastic fixing member (not shown in the figure), which is arranged on the fourth side panel 227. The plastic end plate 213 is clamped in the plastic fixing member, thereby achieving the fixation of the second end 212 of the indoor heat exchanger in the casing 220.

[0077] In some embodiments of the present disclosure, since the indoor heat exchanger 210 and the air outlet 223 are not on the same plane, and the indoor heat exchanger 210 is recessed toward the interior of the indoor unit 200 relative to the air outlet 223, there is a gap in the avoidance space A in the length direction parallel to the air outlet 223, and there is also a gap in the direction perpendicular to the first side panel 224.

[0078] As shown in Figures 6, 8, and 10, the shielding member 240 includes a first shielding portion 241 and a second shielding portion 242. The first shielding portion 241 is arranged parallel to the air outlet 223, that is, parallel to the first side panel 224, and is fixedly connected to the first side panel 224, thereby blocking the gap in the avoidance space A along the length of the air outlet 223. The second shielding portion 242 is arranged perpendicular to the air outlet 223, that is, perpendicular to the first side panel 224, and is fixedly connected to the first end 211 of the indoor heat exchanger, thereby blocking the gap in the avoidance space A along a direction perpendicular to the first side panel 224. In this way, the shielding member 240 can effectively shield the avoidance space A and minimize air leakage.

[0079] As shown in Figures 4, 5 and 8, in some embodiments of the present disclosure, the first shielding portion 241 of the shielding component 240 includes a shielding portion main body 2410, a first support portion 2411 and a second support portion 2412. The first support portion 2411 is arranged at one end of the shielding portion main body 2410 close to the upper cover plate 221, and rests on the inclined portion 2212B of the upper cover plate foam layer 2212. The second support portion 2412 is arranged at one end of the shielding portion main body 2410 close to the bottom plate 222, and rests on the surface of the first water receiving tray side plate 232 close to the upper cover plate 221, and is in contact with the first water receiving tray side plate 232. The second shielding portion 242 of the shielding member 240 includes a third support portion 2421 and a fourth support portion 2422. The third support portion 2421 abuts against the upper cover 221 and includes a first support section 2421A parallel to the upper cover 221 and a second support section 2421B inclined therefrom. The fourth support portion 2422 abuts against the surface of the water tray bottom plate 231 proximal to the upper cover 221 and is in contact with the water tray bottom plate 231. This allows the upper cover 221 and water tray 230 of the indoor unit 200 to position and limit the shielding member 240 from above and below, making it more stable and reliable, thereby improving the installation stability and shielding reliability of the shielding member 240.

[0080] In some embodiments of the present disclosure, the first support portion 2411 has an inclination angle that matches the inclined portion 2212B of the upper cover foam layer 2212. That is, the first support portion 2411 is also inclined and fits snugly with the inclined portion 2212B of the upper cover foam layer 2212. The third support portion 2421 includes a first support sub-portion 2421A that fits snugly with the straight portion 2212A and a second support sub-portion 2421B that fits snugly with the inclined portion 2212B. Furthermore, because the first shielding portion 241 and the second shielding portion 242 fit snugly with the first water tray side panel 232 and the water tray bottom panel 231, respectively, the gaps between adjacent structural components are minimized, thereby improving the tightness of the shielding member 240.

[0081] As shown in Figures 11 and 12, the upper cover foam layer 2212 also includes a positioning portion 2212C, which is arranged on the inclined portion 2212B and protrudes toward the side where the bottom plate 222 is located. One side edge of the first support portion 2411 rests on the positioning portion 2212C, further improving the positioning effect of the shielding component 240.

[0082] As shown in Figures 5 and 8, in some embodiments of the present disclosure, the first shielding portion 241 of the shielding component 240 further includes an inserting portion 2413. The inserting portion 2413 is connected to the second supporting portion 2412 and is perpendicular to the second supporting portion 2412. The second supporting portion 2412 is arranged parallel to the bottom plate 222, and the inserting portion 2413 is arranged perpendicular to the bottom plate 222. An assembly gap is provided between the first water receiving tray side plate 232 of the water receiving tray 230 and the first side plate 224 of the housing 220, and the inserting portion 2413 is inserted into the assembly gap. The first shielding portion 241 is inserted into the gap through the inserting portion 2413, which can improve the support and limiting effect on the shielding component 240 and improve the tightness of the shielding of the shielding component 240.

[0083] As shown in Figures 6 and 8, in some embodiments of the present disclosure, the first shielding portion 241 further includes a connecting portion 2414. The connecting portion 2414 is disposed at one end of the shielding portion body 2410 away from the second shielding portion 242, is folded toward the outside of the housing 220 relative to the shielding portion body 2410, and is configured to be fixedly connected to the first side panel 224 of the housing 220. The connecting portion 2414 includes a first connecting portion 2414A and a second connecting portion 2414B. The first connecting portion 2414A and the second connecting portion 2414B are perpendicular to each other, and the second connecting portion 2414B is in contact with the first side panel 224 and is fixedly connected to the first side panel 224.

[0084] In order to install the fixed shielding component 240 while ensuring the original assembly structure of the whole machine as much as possible, in some embodiments of the present disclosure, the first side panel 224 includes a screw hole E (before the indoor heat exchanger 210 is shortened, the screw hole E is used to fix the first end 211 of the indoor heat exchanger), and the second connection part 2414B includes a screw hole F. The screw hole E and the screw hole F are arranged accordingly. The screw hole E and the screw hole F are connected by screws, so that the second connection part 2414B is connected to the first side panel 224, without the need to add an additional connection structure or consider the assembly position.

[0085] Also to improve the tightness of the shielding, as shown in Figures 7 to 10, the second shielding portion 242 of the shielding component 240 also includes a through portion 2423. The through portion 2423 is configured to avoid the system parts 400 at the first end 211 of the indoor heat exchanger. The second shielding portion 242 is in contact with the end face of the first end 211 of the indoor heat exchanger, and the contour shape of the through portion 2423 is closely adapted to the cross-sectional contour shape of the indoor heat exchanger 210 to effectively avoid the relevant piping structure. For example, the cross-section of the indoor heat exchanger 210 is V-shaped, and the through portion 2423 is approximately V-shaped. In the present disclosure, the indoor heat exchanger 210 is not limited to a V-shape. When using other forms of indoor heat exchangers 210, it is only necessary to change the shape of the through portion 2423 of the second shielding portion 242 accordingly.

[0086] In some embodiments of the present disclosure, the indoor unit 200 further includes a connecting end plate 250, which is disposed at the first end 211 of the indoor heat exchanger and is configured to connect the first end 211 of the indoor heat exchanger to the second shielding portion 242. The connecting end plate 250 includes a plurality of screw holes G disposed at an edge of the connecting end plate 250. Correspondingly, the second shielding portion 242 includes a plurality of screw holes H disposed at an edge of the through portion 2423. The first end 211 of the indoor heat exchanger 210 and the second shielding portion 242 are connected by screws.

[0087] In some embodiments of the present disclosure, during the production and assembly process, the indoor unit 200 is assembled in an inverted manner. This means that the indoor unit 200 is flipped upside down, with the upper cover 221 of the housing 220 facing downward and the bottom plate 222 facing upward. During assembly, the shielding component 240 can be connected to the indoor heat exchanger 210 before the indoor unit 200 is installed as a whole. One end of the first shielding portion 241 and the second shielding portion 242 rests on the inclined portion 2212B of the upper cover foam layer 2212, while the other ends of the first shielding portion 241 and the second shielding portion 242 rest on the water receiving tray 230. This can position and support the entire assembly consisting of the indoor heat exchanger 210 and the shielding component 240, thereby improving assembly efficiency. The positioning portion 2212C can also improve the positioning of the entire assembly consisting of the indoor heat exchanger 210 and the shielding component 240.

[0088] In some embodiments of the present disclosure, the shielding member 240 is a unitary metal plate structure formed by bending, which is easy to process and has high structural strength. In other embodiments of the present disclosure, the shielding member 240 can also be composed of a first shielding portion 241 and a second shielding portion 242 connected by welding or other structural forms, or can be an integral injection molded part, which is not limited by the present disclosure.

[0089] Figure 13 is a structural diagram of an air conditioner in the related art. As shown in Figure 13, in the related art, a two-pipe air conditioner includes: an outdoor unit 100 and a plurality of indoor units 200 connected to the outdoor unit 100; wherein the plurality of indoor units 200 are connected in parallel, and the outdoor unit 100 is connected to the plurality of indoor units 200 connected in parallel through a first connection port 001 and a third connection port 003.

[0090] The outdoor unit 100 includes a compressor 110, an outdoor heat exchanger 120, a gas-liquid separator 130, an oil separator 140, a plurality of parallel refrigerant heat exchange pipelines, a three-way valve 150, a four-way valve 160, and an outdoor electronic expansion valve 310. Each refrigerant heat exchange pipeline between the oil separator 140 and the three-way valve 150 is sequentially connected to a four-way valve 160, the outdoor heat exchanger 120, and the outdoor electronic expansion valve 310. The four-way valve 160 is configured to switch the flow direction of the refrigerant in the refrigerant circuit so that the air conditioner 1000 operates in either a cooling mode or a heating mode.

[0091] The indoor unit 200 includes an indoor heat exchanger 210 and an indoor electronic expansion valve 320. One end of the indoor heat exchanger 210 is connected to one end of the indoor electronic expansion valve 320. The other end of the indoor heat exchanger 210 is connected to one end of multiple parallel refrigerant heat exchange pipelines (in Figure 13, this is the end where the four-way valve 160 is located) via a first connection port 001. The other end of the indoor electronic expansion valve 320 is connected to the other end of the multiple parallel refrigerant heat exchange pipelines (in Figure 13, this is the end where the three-way valve 150 is located) via a third connection port 003. The refrigerant heat exchange pipelines in the two-pipe air conditioner during cooling operation are the same as those used in heating mode.

[0092] In the related art, the indoor unit of a two-pipe air conditioner generally only includes one indoor heat exchanger, so the operating modes are limited to heating operation mode, cooling operation mode and dehumidification operation mode. However, the above-mentioned multiple operation modes cannot meet the actual needs of users. For example, for some areas with rainy season, after entering the rainy season, the indoor and outdoor temperatures are generally low (usually below 20 degrees Celsius). If the user uses a two-pipe air conditioner to run the dehumidification operation mode to dehumidify the air, the following problem will arise: the current two-pipe air conditioner will cause the indoor temperature to drop during dehumidification operation. At this time, the more the air conditioner runs in the dehumidification operation mode, the colder it will become, which seriously damages the user's comfort.

[0093] In some embodiments, a three-pipe air conditioner is a single outdoor unit connected to multiple indoor units. For example, one outdoor unit is connected to two indoor units, one of which can operate in heating mode and the other in dehumidification mode. Therefore, a three-pipe air conditioner can achieve dehumidification without lowering the indoor temperature. However, three-pipe air conditioners generally suffer from numerous drawbacks, such as inconvenient installation and poor operational stability. For example, three-pipe air conditioners typically use long piping during installation. When installation space is limited, there is a large height difference between the indoor unit 200 and the outdoor unit 100, which can cause installation difficulties. For example, a three-pipe air conditioner typically has numerous piping nodes. If a problem occurs in one of these nodes, the three-pipe air conditioner may not operate properly, resulting in poor operational stability. Furthermore, a three-pipe air conditioner typically contains a large amount of refrigerant, which can reduce compressor reliability, lead to poor air conditioner operational stability, and result in low user satisfaction.

[0094] To solve the above problems, the present disclosure provides an air conditioner 1000. The air conditioner 1000 includes four operating modes, namely a heating operating mode, a non-cooling and dehumidifying operating mode, a cooling operating mode, and a cooling and dehumidifying operating mode. The heating operating mode indicates that the air conditioner 1000 heats the indoor environment, and the cooling operating mode indicates that the air conditioner 1000 cools the indoor environment. The non-cooling and dehumidifying operating mode indicates that the air conditioner 1000 does not lower the indoor temperature while dehumidifying the indoor environment. The cooling and dehumidifying operating mode indicates that the air conditioner 1000 dehumidifies the indoor environment while lowering the indoor temperature.

[0095] FIG14 is a block diagram of an air conditioner according to some embodiments of the present disclosure. As shown in FIG14 , the air conditioner 1000 includes at least one indoor unit 200, an outdoor unit 100, and a circulation pipeline. The circulation pipeline is configured to connect the at least one indoor unit 200 and the outdoor unit 100 to form a circulation loop. The present disclosure does not limit the number of indoor units 200; the number may be one or more.

[0096] The air conditioner 1000 includes one indoor unit 200 , namely the first indoor unit 201 , as an example for description.

[0097] In some embodiments of the present disclosure, the first indoor unit 201 includes two indoor heat exchangers 210, two indoor electronic expansion valves 320, and a first blowing device 251. The two indoor heat exchangers 210 are respectively a first indoor heat exchanger 214 and a second indoor heat exchanger 215, and the two indoor electronic expansion valves 320 are respectively a first electronic expansion valve 321 and a second electronic expansion valve 322. As shown in FIG14 , the first indoor heat exchanger 214, the first electronic expansion valve 321, the second indoor heat exchanger 215, and the second electronic expansion valve 322 are connected in series. In some embodiments of the present disclosure, the indoor heat exchanger 210 in the air conditioner 1000 is affected by the flow direction of the refrigerant, and the first indoor heat exchanger 214 and the second indoor heat exchanger 215 can be used as a condenser or an evaporator, respectively.

[0098] The first blowing device 251 is configured to blow air toward the first indoor heat exchanger 214, with the air outlet side of the first blowing device 251 facing the first indoor heat exchanger 214. This can improve the heat exchange efficiency between the first indoor heat exchanger 214 and the indoor air. The first blowing device 251 can be a fan, a blower, etc., which is not limited in this disclosure. In some embodiments of the present disclosure, the outdoor unit 100 of the air conditioner 1000 includes a compressor assembly 20, an outdoor heat exchanger 120 (i.e., a first outdoor heat exchanger 121), two refrigerant flow direction switching devices 170, a second blowing device 252, and an outdoor electronic expansion valve 310 (i.e., a third electronic expansion valve 311). The two refrigerant flow direction switching devices 170 are the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172. The second blowing device 252 is configured to blow air toward the first outdoor heat exchanger 121, with the air outlet side of the second blowing device 252 facing the first outdoor heat exchanger 121.

[0099] As shown in Figure 14, the compressor assembly 20 includes an inlet 21, an outlet 22, a gas-liquid separator 130, a compressor 110, an oil separator 140, an oil return capillary tube 23, and a one-way valve 24. The inlet 21 is the first port 131 of the gas-liquid separator 130. The second port 132 of the gas-liquid separator 130 is connected to the gas return port 111 of the compressor 110. The exhaust port 112 of the compressor 110 is connected to the first port 141 of the oil separator 140. The second port 142 of the oil separator 140 is connected to the one-way valve 24. The outlet 22 is provided in a connecting line on the side of the one-way valve 24 away from the oil separator 140. The third port 143 of the oil separator 140 is connected to the second port 132 of the gas-liquid separator 130 via the oil return capillary tube 23.

[0100] The gas-liquid separator 130 is configured to adopt the principles of centrifugal separation and wire mesh filtration to filter the liquid refrigerant that has not been completely evaporated in the gaseous refrigerant returned to the compressor 110 .

[0101] In some embodiments, since the gas-phase refrigerant compressed by the compressor 110 has a fast flow rate and high temperature when discharged, part of the compressor oil forms oil vapor and oil droplets due to the high temperature and is discharged together with the gas-phase refrigerant. The oil separator 140 is configured to separate the compressor oil in the high-temperature and high-pressure gas-phase refrigerant discharged by the compressor 110 under the action of gravity according to the oil separation principle of reducing the air flow velocity and changing the air flow direction, so as to ensure the safe and efficient operation of the device.

[0102] In some embodiments of the present disclosure, the refrigerant flow direction switching device 170 can be a three-way valve or a four-way valve, and the structures of the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172 can be the same or different, which is not limited by the present disclosure.

[0103] Since the four-way valve has the advantages of quick opening and closing, simple structure, small size, light weight, easy maintenance, no restrictions on installation direction, and the flow direction of the medium can be switched arbitrarily, some embodiments of the present disclosure are described as the refrigerant flow direction switching device 170 being a four-way valve.

[0104] At this time, the first refrigerant flow direction switching device 171 includes a first port M, a second port N, a third port O, and a fourth port P. The first port M is connected to one end of the first indoor heat exchanger 214, the second port N is connected to the inlet 21, the third port O is connected to the outlet 22, and the fourth port P is connected to the second refrigerant flow direction switching device 172 via a connecting port. The second refrigerant flow direction switching device 172 includes a fifth port R, a sixth port S, a seventh port T, and an eighth port U. The fifth port R is connected to the inlet 21, the sixth port S is connected to the first outdoor heat exchanger 121, the seventh port T is connected to the outlet 22, and the eighth port U is connected to the fourth port P via a connecting port. Both the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172 can achieve switching between ports. For example, the connection between the first port M and the second port N can be switched to the connection between the second port N and the third port O.

[0105] Figure 15 is a circuit connection relationship diagram of an air conditioner according to some embodiments. As shown in Figure 15, in some embodiments of the present disclosure, the air conditioner 1000 also includes a controller 500, which is electrically connected to both the indoor unit 200 and the outdoor unit 100 and is configured to control the start or stop of the indoor unit 200 and the outdoor unit 100.

[0106] In this way, the controller 500 can be used as a hub to control the operation of the air conditioner 1000, which is beneficial to the stable operation of the air conditioner 1000.

[0107] In some embodiments of the present disclosure, the controller 500 of the air conditioner 1000 adjusts the first indoor heat exchanger 214, the second indoor heat exchanger 215, and the first outdoor heat exchanger 121 to function as a condenser or an evaporator by controlling the connection status of the ports of the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172, the opening of the expansion valve 300, and the power of the first blowing device 251. This ensures that the indoor temperature does not drop when the air conditioner 1000 is operating in the dehumidification mode, thereby improving user comfort and enhancing the user experience.

[0108] FIG16 is a diagram illustrating an operating cycle of an air conditioner according to some embodiments. As shown in FIG16 , when the air conditioner 1000 is operating in heating mode, the controller 500 controls the first refrigerant flow direction switching device 171 so that the first port M is connected to the third port O, and the second port N is connected to the fourth port P. The controller 500 controls the second refrigerant flow direction switching device 172 so that the fifth port R is connected to the sixth port S, and the seventh port T is connected to the eighth port U. The fourth port P and the eighth port U are blocked to prevent refrigerant leakage. The controller 500 controls the first electronic expansion valve 321 to fully open, and controls the speed of the first blowing device 251 to a first preset value.

[0109] At this time, the first indoor heat exchanger 214 and the second indoor heat exchanger 215 function as condensers, and the first outdoor heat exchanger 121 functions as an evaporator. Since the condenser dissipates heat during condensation, both indoor heat exchangers 210 dissipate heat during operation, and the air conditioner operates in heating mode.

[0110] The compressor 110 compresses the low-temperature, low-pressure gas-phase refrigerant and discharges the compressed high-temperature, high-pressure gas-phase refrigerant to the oil separator 140 through the exhaust port 112. After the oil separator 140 separates the high-temperature, high-pressure gas-phase refrigerant and part of the compressor oil, the compressor oil flows back to the compressor 110, and the high-temperature, high-pressure gas-phase refrigerant flows out and passes through the one-way valve 24, the first refrigerant flow direction switching device 171, the first connection port 001, and the second connection port 002 in sequence to enter the first indoor heat exchanger 214. The high-temperature, high-pressure gas-phase refrigerant passes through the first indoor heat exchanger 214 and is condensed into a medium-temperature, high-pressure liquid-phase refrigerant under the action of the first blowing device 251. It is further condensed into a medium-temperature, high-pressure liquid-phase refrigerant in the second indoor heat exchanger 215. The medium-temperature, high-pressure liquid-phase refrigerant passes through the second electronic After expansion, the expansion valve 322 becomes a medium-temperature and medium-pressure liquid refrigerant. The medium-temperature and medium-pressure liquid refrigerant passes through the third connection port 003 and the fourth connection port 004 in sequence and enters the third electronic expansion valve 311. After further expansion through the third electronic expansion valve 311, it becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant. The low-temperature and low-pressure gas-liquid two-phase refrigerant evaporates into a low-temperature and low-pressure gas-phase refrigerant through the first outdoor heat exchanger 121. The low-temperature and low-pressure gas-phase refrigerant finally passes through the second refrigerant flow direction switching device 172 and flows into the gas-liquid separator 130. The gas-liquid separator 130 filters the liquid-phase refrigerant that has not been completely evaporated again. Finally, the gas-phase refrigerant in a low-temperature and low-pressure state returns to the compressor 110 through the return air port 111, thereby completing the circulation of the refrigerant during the heating operation mode of the air conditioner 1000.

[0111] When the air conditioner 1000 operates in the non-cooling and dehumidifying operation mode, the refrigerant flow direction of the air conditioner and the connection method of each port of the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172 are consistent with those when the air conditioner is in the heating operation mode, please refer to Figure 16.

[0112] The controller 500 controls the second electronic expansion valve 322 and the third electronic expansion valve 311 to be fully open, and controls the rotation speed of the first blowing device 251 to a second preset value, which is greater than the first preset value, to ensure that in the non-cooling and dehumidification mode, the high-temperature and high-pressure gas-phase refrigerant can be fully condensed into medium-temperature and high-pressure liquid-phase refrigerant when passing through the first indoor heat exchanger 214.

[0113] At this time, the first indoor heat exchanger 214 functions as a condenser, and the second indoor heat exchanger 215 and the first outdoor heat exchanger 121 function as an evaporator.

[0114] After the refrigerant enters the first indoor heat exchanger 214 from the compressor 110, the high-temperature and high-pressure gas-phase refrigerant passes through the first indoor heat exchanger 214 and is condensed into a medium-temperature and high-pressure liquid-phase refrigerant under the action of the first blowing device 251. The medium-temperature and high-pressure liquid-phase refrigerant expands into a low-temperature and low-pressure liquid-phase refrigerant through the first electronic expansion valve 321. The low-temperature and low-pressure liquid-phase refrigerant evaporates into a low-temperature and low-pressure gas-liquid two-phase refrigerant through the second indoor heat exchanger 215. The low-temperature and low-pressure gas-liquid two-phase refrigerant flows out through the second electronic expansion valve 322, and the process is repeated in sequence. It flows into the first outdoor heat exchanger 121 through the third connection port 003, the fourth connection port 004, and the third electronic expansion valve 311, and is further evaporated into a low-temperature and low-pressure gas-phase refrigerant through the first outdoor heat exchanger 121. The low-temperature and low-pressure gas-phase refrigerant flows into the gas-liquid separator 130 through the second refrigerant flow direction switching device 172, and the low-temperature and low-pressure gas-phase refrigerant flowing out of the gas-liquid separator 130 enters the compressor 110, thus completing the refrigerant circulation when the air conditioner 1000 is operating in the non-cooling and dehumidification operation mode.

[0115] It is understood that when the air conditioner 1000 is operating in the non-cooling and dehumidifying mode, the rotational speed of the first blowing device 251 is greater than the rotational speed of the first blowing device 251 when the air conditioner 1000 is operating in the heating mode. Therefore, when the air conditioner 1000 is operating in the non-cooling and dehumidifying mode, the effect of the first indoor heat exchanger 214 acting as a condenser on refrigerant condensation is equivalent to the combined effect of the first indoor heat exchanger 214 and the second indoor heat exchanger 215 acting as condensers on refrigerant condensation when the air conditioner 1000 is operating in the heating mode. When the air conditioner 1000 is operating in the non-cooling and dehumidifying mode, the combined effect of the second indoor heat exchanger 215 and the first outdoor heat exchanger 121 acting as evaporators on refrigerant evaporation is equivalent to the effect of the first outdoor heat exchanger 121 acting as an evaporator on refrigerant evaporation when the air conditioner 1000 is operating in the heating mode.

[0116] Figure 17 is a pressure-enthalpy diagram of the non-cooling and dehumidification operation mode of the air conditioner according to some embodiments. As shown in Figure 17, state point a is the state before the refrigerant enters the first heat exchanger 214, and state point b is the state after the refrigerant is condensed through the first heat exchanger 214. The state changes of the refrigerant during the condensation process through the first indoor heat exchanger 214 are shown between state point a and state point b; state point c is the state of the refrigerant before entering the second indoor heat exchanger 215 after expansion through the first electronic expansion valve 321, state point d is the state after the refrigerant evaporates through the second indoor heat exchanger 215, and the state changes between state point c and state point d are during the evaporation process of the refrigerant through the second indoor heat exchanger 215; state point e is the state after the refrigerant evaporates again through the first outdoor heat exchanger 121, and the state changes between state point d and state point e are during the evaporation process of the refrigerant through the first outdoor heat exchanger 121.

[0117] Among them, the enthalpy value corresponding to state point a is h4, the enthalpy values ​​corresponding to state points b and c are h1, the enthalpy value corresponding to state d is point h2, and the enthalpy value corresponding to state point e is h3; during the operation of air conditioner 1000, the amount of refrigerant circulating in the system is m.

[0118] The heat released into the air when the refrigerant passes through the first indoor heat exchanger 214 and condenses can be calculated using Formula 1: cond =(h4-h1)×m Formula 1

[0119] The heat absorbed from the air when the refrigerant evaporates through the second indoor heat exchanger 215 can be calculated using Formula 2: evap =(h2-h1)×m Formula 2

[0120] The heat absorbed from the air when the refrigerant evaporates through the first outdoor heat exchanger 121 can be calculated using Formula 3: evap_out =(h3-h2)×m Formula 3

[0121] The power consumption of the compressor 110 can be calculated using Formula 4: W = (h4 - h3) × m Formula 4

[0122] When the refrigerant passes through the first indoor heat exchanger 214 and condenses, the heat Q released in the air cond , the refrigerant absorbs heat Q from the air when evaporating through the second indoor heat exchanger 215 evap , the refrigerant absorbs heat Q from the air when evaporating through the first outdoor heat exchanger 121 evap_out The relationship between the power consumption W of the compressor 110 is shown in Formula 5: cond =Q evap +Q evap_out +W Formula 5

[0123] At this time, the heat released by the refrigerant after condensation in the first indoor heat exchanger 214 is greater than the heat absorbed by the refrigerant after evaporation in the second indoor heat exchanger 215, that is, Q cond >Q evap Therefore, when the air conditioner 1000 is operated in the non-cooling and dehumidifying mode, the temperature of the indoor air will rise while the humidity decreases.

[0124] FIG18 is a diagram illustrating another air conditioner operating cycle according to some embodiments. As shown in FIG18 , when the air conditioner 1000 is operating in cooling mode, the controller 500 is configured to control the first port M of the first refrigerant flow direction switching device 171 to communicate with the second port N, and the third port O to communicate with the fourth port P; the sixth port S of the second refrigerant flow direction switching device 172 to communicate with the seventh port T, and the fifth port R to communicate with the eighth port U, with the fourth port P and the eighth port U blocked. The first electronic expansion valve 321 is fully opened, and the speed of the second blowing device 252 is controlled to a third preset value.

[0125] At this time, the first outdoor heat exchanger 121 acts as a condenser, and the first indoor heat exchanger 214 and the second indoor heat exchanger 215 act as evaporators. Since the evaporator absorbs heat during evaporation, both indoor heat exchangers 210 absorb heat during operation, and the air conditioner 1000 operates in cooling mode.

[0126] The low-temperature and low-pressure gas-phase refrigerant is compressed by the compressor 110 and becomes a high-temperature and high-pressure gas-phase refrigerant. After the high-temperature and high-pressure gas-phase refrigerant flows out, it enters the first outdoor heat exchanger 121 through the one-way valve 24 and the second refrigerant flow switching device 172. The high-temperature and high-pressure gas-phase refrigerant passes through the first outdoor heat exchanger 121 and is condensed into a medium-temperature and high-pressure liquid-phase refrigerant under the action of the second blowing device 252. The medium-temperature and high-pressure liquid-phase refrigerant is expanded by the third electronic expansion valve 311 and becomes a medium-temperature and medium-pressure gas-liquid two-phase refrigerant. The medium-temperature and medium-pressure gas-liquid two-phase refrigerant passes through the fourth connection port 004 and the third connection port 003 in turn and enters the second electronic The expansion valve 322, after being expanded again by the second electronic expansion valve 322, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant. The low-temperature and low-pressure gas-liquid two-phase refrigerant evaporates into a low-temperature and low-pressure gas-phase refrigerant through the second indoor heat exchanger 215 and the first indoor heat exchanger 214. The low-temperature and low-pressure gas-phase refrigerant flows into the gas-liquid separator 130 through the second connection port 002, the first connection port 001 and the first refrigerant flow direction switching device 171 in turn, and finally the gas-phase refrigerant in a low-temperature and low-pressure state returns to the compressor 110 through the return air port 111, thereby completing the circulation of the refrigerant during the refrigeration operation cycle of the air conditioner 1000.

[0127] When the air conditioner 1000 operates in the cooling and dehumidification mode, the refrigerant flow direction in the air conditioner and the connection mode of each port of the first refrigerant flow direction switching device 171 and the second refrigerant flow direction switching device 172 are consistent with those when the air conditioner is in the cooling mode, please refer to Figure 18.

[0128] The controller 500 controls the second electronic expansion valve 322 and the third electronic expansion valve 311 to be fully open, and controls the rotation speed of the second blowing device 252 to a fourth preset value, which is smaller than the third preset value.

[0129] At this time, the first outdoor heat exchanger 121 and the second indoor heat exchanger 215 function as condensers, and the first indoor heat exchanger 214 functions as an evaporator.

[0130] After the refrigerant enters the first outdoor heat exchanger 121 from the compressor 110, the high-temperature and high-pressure gas-phase refrigerant passes through the first outdoor heat exchanger 121 and is condensed into a medium-temperature and high-pressure gas-liquid two-phase refrigerant under the action of the second blowing device 252. The medium-temperature and high-pressure gas-liquid two-phase refrigerant flows out through the third electronic expansion valve 311 and flows into the second indoor heat exchanger 215 through the fourth connection port 004, the third connection port 003 and the second electronic expansion valve 322 in sequence. The medium-temperature and high-pressure gas-liquid two-phase refrigerant is condensed into a medium-temperature and high-pressure liquid-phase refrigerant through the second indoor heat exchanger 215. The medium-temperature and high-pressure The liquid refrigerant is expanded by the first electronic expansion valve 321 and becomes a medium-temperature, low-pressure gas-liquid two-phase refrigerant. The medium-temperature, low-pressure gas-liquid two-phase refrigerant is evaporated into a low-temperature, low-pressure gas-phase refrigerant by the first indoor heat exchanger 214. The low-temperature, low-pressure gas-phase refrigerant flows into the gas-liquid separator 203 in sequence through the second connection port 002, the first connection port 001 and the first refrigerant flow direction switch 171. Finally, the gas-phase refrigerant in a low-temperature, low-pressure state returns to the compressor 110 through the return air port 111, thereby completing the refrigerant circulation of the air conditioner 1000 during the cooling and dehumidification operation mode.

[0131] It is understood that when the air conditioner 1000 operates in the cooling and dehumidification mode, the rotational speed of the second blowing device 252 is lower than the rotational speed of the second blowing device 252 when the air conditioner 1000 operates in the cooling and dehumidification mode. Therefore, when the air conditioner 1000 operates in the cooling and dehumidification mode, the effect of the first indoor heat exchanger 214 acting as an evaporator on the evaporation of the refrigerant is equivalent to the combined effect of the first indoor heat exchanger 214 and the second indoor heat exchanger 215 on the evaporation of the refrigerant when the air conditioner 1000 operates in the cooling mode. When the air conditioner 1000 operates in the cooling and dehumidification mode, the combined effect of the second indoor heat exchanger 215 and the first outdoor heat exchanger 121 acting as condensers on the condensation of the refrigerant is equivalent to the effect of the first outdoor heat exchanger 121 acting as a condenser on the condensation of the refrigerant when the air conditioner 1000 operates in the cooling mode.

[0132] Figure 19 is a pressure-enthalpy diagram of the cooling and dehumidification mode of the air conditioner according to some embodiments. As shown in Figure 19, state point a is the state of the refrigerant before entering the first outdoor heat exchanger 121, state point b is the state of the refrigerant after condensing through the first outdoor heat exchanger 121, and the state between state point a and state point b is the state change of the refrigerant during the condensation process through the first outdoor heat exchanger 121; state point c is the state of the refrigerant after condensing through the second indoor heat exchanger 215, and the state between state point b and state point c is the state change of the refrigerant during the condensation process through the second indoor heat exchanger 322; state point d is the state of the refrigerant after expansion through the third electronic expansion valve 311, state point e is the state of the refrigerant after expansion through the first electronic expansion valve 321, state point f is the state of the refrigerant after evaporation through the first indoor heat exchanger 214, and the state between state point d is the state change of the refrigerant during the condensation process through the second indoor heat exchanger 215; between state point e and state point f is the state change of the refrigerant during the evaporation process through the first indoor heat exchanger 214.

[0133] The enthalpy value corresponding to state point a is h4, the enthalpy value corresponding to state point b is h2, the enthalpy value corresponding to state point c is h1, the enthalpy value corresponding to state point d is h1, the enthalpy value corresponding to state point e is h1, and the enthalpy value corresponding to state point f is h3. During the operation of the air conditioner 1000, the amount of refrigerant circulating in the system is m.

[0134] The heat released into the air when the refrigerant passes through the second indoor heat exchanger 215 and condenses can be calculated using Formula 6: cond =(h2-h1)×m Formula 6

[0135] The heat absorbed from the air when the refrigerant evaporates through the first indoor heat exchanger 214 can be calculated using Formula 7: evap =(h3-h1)×m Formula 7

[0136] Since h3>h2, the heat absorbed by the refrigerant after evaporation through the first indoor heat exchanger 214 is greater than the heat released by the refrigerant after condensation through the second indoor heat exchanger 215, that is, Q evap >Q cond Therefore, when the air conditioner 1000 operates in the cooling and dehumidification mode, the temperature of the indoor air will decrease while the humidity decreases.

[0137] In some other embodiments of the present disclosure, the air conditioner 1000 includes two indoor units 200 (a first indoor unit 201 and a second indoor unit 202 ).

[0138] Figure 20 is a diagram of another air conditioner operating cycle according to some embodiments, and Figure 21 is a diagram of another air conditioner operating cycle structure according to some embodiments. As shown in Figures 20 and 21, in some other embodiments of the present disclosure, the air conditioner 1000 further includes a second indoor unit 202, which includes a third indoor heat exchanger 216, a fourth electronic expansion valve 323, a fourth indoor heat exchanger 217, and a fifth electronic expansion valve 324. The third indoor heat exchanger 216 is connected in series with the fourth electronic expansion valve 323, the fourth indoor heat exchanger 217, and the fifth electronic expansion valve 324.

[0139] The second indoor unit 202 is connected in parallel with the first indoor unit 201, and the two indoor units 200 are respectively connected in series with the outdoor unit 100. It should be noted that when the air conditioner 1000 operates in any of the four modes, the refrigerant flowing from the outdoor unit 100 to the two indoor units 200 flows through the second connection port 002 or the third connection port 003 and then flows through the refrigerant pipeline to the first indoor unit 201 and the second indoor unit 202 respectively. The refrigerant flowing from the two indoor units 200 to the outdoor unit 100 is the refrigerant in the first indoor unit 201 and the second indoor unit 202 merged and then flows into the outdoor unit 100 through the refrigerant pipeline.

[0140] In other embodiments of the present disclosure, the outdoor unit 100 of the air conditioner 1000 includes one or more outdoor heat exchangers 120. Multiple outdoor heat exchangers 120 are connected in parallel. Multiple outdoor heat exchangers 120 can improve the cooling or heating performance of the air conditioner 1000. This disclosure uses an example in which the outdoor unit 100 includes two outdoor heat exchangers 120. In this case, the outdoor unit 200 also includes a second outdoor heat exchanger 122, a sixth electronic expansion valve 312, a third blowing device 253, and a third refrigerant flow direction switching device 173.

[0141] The third refrigerant flow direction switching device 173 can be a three-way valve or a four-way valve. This disclosure uses a four-way valve as an example for explanation. The third refrigerant flow direction switching device 173 includes a ninth port I, a tenth port K, an eleventh port Y, and a twelfth port Z. The ninth port I of the third refrigerant flow direction switching device 173 is connected to the inlet 21, the tenth port K is connected to the second outdoor heat exchanger 122, the eleventh port Y is connected to the outlet 22, and the twelfth port Z is connected to the sixth port S of the second refrigerant flow direction switching device 172. The second outdoor unit 202 is connected to the two indoor units 200 via the sixth electronic expansion valve 312. The third blowing device 253 is configured to blow air toward the second outdoor heat exchanger 122, with the air outlet side of the third blowing device 253 facing the second outdoor heat exchanger 122.

[0142] As shown in FIG20 , when the air conditioner 1000 is operating in the heating mode and / or the non-cooling and dehumidifying mode, the controller 500 is configured to connect the ninth port I to the tenth port K, while the remaining ports are blocked. The refrigerant flowing out of the two indoor units 200 is split after passing through the connecting ports. A portion of the refrigerant flows sequentially through the third electronic expansion valve 311, the first outdoor heat exchanger 121, and the second refrigerant flow direction switching device 172 into the gas-liquid separator 130, while another portion of the refrigerant flows sequentially through the sixth electronic expansion valve 312, the second outdoor heat exchanger 122, and the third refrigerant flow direction switching device 173 into the gas-liquid separator 130.

[0143] As shown in Figure 21, when the air conditioner 1000 is operating in cooling mode or cooling and dehumidification mode, the controller 500 is configured to connect the tenth port K to the eleventh port Y, while the remaining ports are blocked. The refrigerant flowing out of the oil separator 140 is split after passing through the one-way valve 24. A portion of the refrigerant flows through the first outdoor heat exchanger 121 and the third electronic expansion valve 311 into the two indoor units 200, while the remaining portion flows through the second outdoor heat exchanger 122 and the sixth electronic expansion valve 312 into the two indoor units 200.

[0144] In some embodiments of the present disclosure, when the air conditioner 1000 operates in a non-cooling and dehumidification mode, only part of the outdoor heat exchanger 120 can be operated to reduce the energy consumption of the air conditioner 1000. For example, as shown in Figure 22, only the first outdoor heat exchanger 121 is operated, and the sixth electronic expansion valve 312 is closed and the third electronic expansion valve 311 is opened. The operating cycle of the refrigerant of the air conditioner 1000 can be as shown in the operating state when the second outdoor heat exchanger 122 is removed in Figure 21, which will not be repeated in this disclosure.

[0145] Figure 23 is another air conditioner operation cycle structure diagram according to some embodiments. As shown in Figure 23, in order to further reduce the energy consumption of the air conditioner 1000, in some embodiments of the present disclosure, the air conditioner 1000 also includes a solenoid valve 600, and the first end 601 of the solenoid valve 600 is connected to the second end 3222 of the second electronic expansion valve 322, and the second end 602 of the solenoid valve 600 is connected to the inlet 21.

[0146] When the air conditioner 1000 is operating in the non-cooling and dehumidifying mode, the controller 500 is configured to close the third electronic expansion valve 311 and open the solenoid valve 600. At this point, the first port M of the first refrigerant flow direction switching device 171 is connected to the third port O, and the second electronic expansion valve 322 and the fifth electronic expansion valve 324 are both fully open.

[0147] The low-temperature, low-pressure gas-phase refrigerant is compressed by the compressor 110 and becomes a high-temperature, high-pressure gas-phase refrigerant that flows out. The high-temperature, high-pressure gas-phase refrigerant is divided into two parts after passing through the one-way valve 24, the first refrigerant flow direction switching device 171, the first connection port 001 and the second connection port 002 in sequence. A part of the high-temperature, high-pressure gas-phase refrigerant is condensed into a medium-temperature, high-pressure liquid-phase refrigerant through the first indoor heat exchanger 214. The medium-temperature, medium-pressure liquid-phase refrigerant is expanded through the first electronic expansion valve 321 and becomes a low-temperature, low-pressure liquid-phase refrigerant. The low-temperature, low-pressure liquid-phase refrigerant is evaporated through the second indoor heat exchanger 215 and becomes a low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant flows out from the second electronic expansion valve 322. Another part of the high-temperature, high-pressure gas-phase refrigerant passes through the third indoor heat exchanger 2 16 is condensed into a medium-temperature and high-pressure liquid-phase refrigerant, and the medium-temperature and medium-pressure liquid-phase refrigerant is expanded into a low-temperature and low-pressure gas-liquid two-phase refrigerant through the fourth electronic expansion valve 323. The low-temperature and low-pressure gas-liquid two-phase refrigerant evaporates into a low-temperature and low-pressure gas-phase refrigerant through the fourth indoor heat exchanger 217, and the low-temperature and low-pressure gas-phase refrigerant flows out from the fifth electronic expansion valve 324; the low-temperature and low-pressure gas-phase refrigerants flowing out of the second electronic expansion valve 322 and the fifth electronic expansion valve 324 are merged and flow into the gas-liquid separator 130 through the third connection port 003, the fourth connection port 004 and the solenoid valve 600 in sequence. The gas-liquid separator 130 filters the liquid-phase refrigerant that has not been completely evaporated again, and finally the gas-phase refrigerant in a low-temperature and low-pressure state returns to the compressor 110 through the return air port 111.

[0148] At this time, the outdoor heat exchanger 120 can complete the dehumidification and heating of the indoor air without working, reducing the energy consumption of the air conditioner 1000.

[0149] Figure 24 is a pressure-enthalpy diagram of the non-cooling and dehumidification operation mode of another air conditioner according to some embodiments. As shown in Figure 24, state point a is the state of the refrigerant before entering the first indoor heat exchanger 214, and state point b is the state of the refrigerant after condensing through the first indoor heat exchanger 214. The state between state point a and state point b is the state change of the refrigerant during the condensation process of the first indoor heat exchanger 214; state point c is the state of the refrigerant before entering the second indoor heat exchanger 215, and state point d is the state of the refrigerant after evaporating through the second indoor heat exchanger 215. The state between state point c and state point d is the state change of the refrigerant during the evaporation process of the second indoor heat exchanger 215.

[0150] The enthalpy value corresponding to state point a is h3, the enthalpy values ​​corresponding to state points b and c are h1, and the enthalpy value corresponding to state point d is h2; during the operation of the air conditioner 1000, the amount of refrigerant circulating in the system is m.

[0151] The heat released into the air when the refrigerant passes through the first indoor heat exchanger 214 and condenses can be calculated using Formula 8: cond=(h3-h1)×m Formula 8

[0152] The heat absorbed from the air when the refrigerant evaporates through the second indoor heat exchanger 215 can be calculated using Formula 9: evap =(h2-h1)×m Formula 9

[0153] The power consumption of the compressor 110 can be calculated using Formula 10: W = (h3 - h2) × m Formula 10

[0154] When the refrigerant passes through the first indoor heat exchanger 214 and condenses, the heat Q released in the air cond , the refrigerant absorbs heat Q from the air when evaporating through the second indoor heat exchanger 215 evap The relationship between the power consumption W of the compressor 110 is shown in Formula 11: cond =Q evap +W Formula 11

[0155] In this way, the heat absorbed by the refrigerant after evaporation through the second indoor heat exchanger 215 is less than the heat released by the refrigerant after condensation through the first indoor heat exchanger 214, that is, Q evap <Q cond Therefore, when the air conditioner 1000 is operated in the non-cooling and dehumidifying mode, the indoor air is condensed through the first indoor heat exchanger 214 and evaporated through the second indoor heat exchanger 215. The refrigerant does not absorb heat from the outdoor heat exchanger 120, and the temperature of the indoor air will rise slightly while the humidity decreases.

[0156] In some embodiments, as shown in FIG23 , when the air conditioner 1000 includes: a second outdoor heat exchanger 122 , a sixth electronic expansion valve 312 , a third blowing device 253 and a third refrigerant flow direction switching device 173 , the flow direction of the refrigerant can refer to FIG23 , and this disclosure will not elaborate on this.

[0157] In related art, the air conditioner 1000 detects the temperature and humidity of the space where the indoor unit is located to adjust the operating frequency of the compressor 110, the opening of the electronic expansion valve 300, and the gear position of the fan of the indoor unit 200 to control the refrigerant flow rate and the air outlet temperature of the indoor unit 200. This achieves variable frequency regulation of the air conditioner 1000, thereby changing the temperature and humidity of the space where the indoor unit 200 is located. However, when the indoor temperature and humidity vary significantly and there are no fixed target values ​​for temperature and humidity, the compressor 110 may operate at a fixed frequency, causing the user to experience a low perceived temperature despite the humidity not decreasing.

[0158] Based on this, the present disclosure provides a control method for an air conditioner 1000 , which realizes dual control of room temperature and humidity of a plurality of indoor units 200 by controlling the air conditioner 1000 .

[0159] Figure 25 is a diagram of the main components of an air conditioner according to some embodiments. As shown in Figure 25, the embodiment of the present disclosure provides an air conditioner 1000 and an operating mode control method of the air conditioner 1000. The air conditioner 1000 may include one outdoor unit 100 and two or more indoor units 200, and a controller 500 for controlling each indoor unit 200 and outdoor unit 100.

[0160] The outdoor unit 100 includes an outdoor heat exchanger 120 , namely a first outdoor heat exchanger 121 . The outdoor unit 100 also includes an outdoor fan 180 (ie, a second blowing device 252 ), a liquid-side stop valve 191 and a gas-side stop valve 192 .

[0161] The first indoor unit 201 further includes a first inlet air temperature sensor 51 , a first indoor temperature sensor 11 , a second indoor temperature sensor 12 and a third indoor temperature sensor 13 .

[0162] The second indoor unit 202 further includes a second inlet air temperature sensor 52 , a fourth indoor temperature sensor 14 , a fifth indoor temperature sensor 15 and a sixth indoor temperature sensor 16 .

[0163] FIG26 is a flow chart of a method for controlling an air conditioner according to some embodiments. As shown in FIG26 , the present disclosure provides a method for controlling an air conditioner 1000, comprising the following steps:

[0164] S101 : The controller 500 obtains a first exhaust pressure value Pd01 of the compressor 110 at a first moment through the pressure sensor 60 .

[0165] The first moment is any moment during the operation of the air conditioner 1000. The exhaust pressure value Pd of the compressor 110 refers to the pressure of the refrigerant gas in the exhaust pipe at the compressor exhaust port 112. The first exhaust pressure value Pd01 is the exhaust pressure value of the compressor 110 detected by the pressure sensor 60 at the first moment.

[0166] For example, the first moment may be the start time of the air conditioner 1000. When the user turns on the air conditioner 1000, the controller 500 may execute step S101 based on the operation mode selected by the user to obtain the first exhaust pressure value Pd01 of the compressor 110.

[0167] S102 : The controller 500 determines a maximum target pressure value from the first target pressure value Pdset1 ( 1 ) and the second target pressure value Pdset2 ( 1 ).

[0168] The target pressure value Pdset is a target exhaust pressure value of the compressor 110 when any one of the multiple indoor units 200 operates in any mode. The first target pressure value Pdset1(1) is a target exhaust pressure value of the compressor 110 at a first moment when the first indoor unit 201 of the multiple indoor units 200 operates in any mode. The second target pressure value Pdset2(1) is a target exhaust pressure value of the compressor 110 at a first moment when the second indoor unit 202 of the multiple indoor units 200 operates in any mode.

[0169] It should be noted that when the indoor unit 200 operates in the cooling operation mode, it has a fixed target pressure value Pdset. For example, when the first indoor unit 201 operates in the cooling operation mode, the first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment is 2.9Mpa. When the indoor unit 200 operates in the non-cooling and dehumidifying operation mode, the set target pressure value Pdset can be variable. For example, when the first indoor unit 201 operates in the non-cooling and dehumidifying operation mode, the first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment will change with the change of the indoor ambient temperature Ti, so that the re-determined target pressure value Pdset is more in line with the current environmental conditions of the first indoor unit 201.

[0170] When the controller 500 determines that the first target pressure value Pdset1(1) of the first indoor unit 201 is greater than or equal to the second target pressure value Pdset2(1) of the second indoor unit 202, the first target pressure value Pdset1(1) is determined as the maximum target pressure value. When the controller 500 determines that the first target pressure value Pdset1(1) of the first indoor unit 201 is less than the second target pressure value Pdset2(1) of the second indoor unit 202, the second target pressure value Pdset2(1) is determined as the maximum target pressure value.

[0171] In step S103 , the controller 500 calculates the pressure deviation value ΔPd2 .

[0172] The pressure deviation value ΔPd2 refers to the difference between the maximum target pressure value at any moment when the air conditioner 1000 is operating and the exhaust pressure value Pd of the compressor 110 at that moment.

[0173] For example, when the controller 500 determines that the first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment is greater than the second target pressure value Pdset2(2) of the second indoor unit 202, the maximum target pressure value is Pdset1(1), and the first exhaust pressure value of the compressor 110 at the first moment is Pd01. At this time, the relationship between the pressure deviation value ΔPd2 and the first exhaust pressure value Pd01 and the maximum target pressure value is: ΔPd2=Pdset1(1)-Pd01.

[0174] In step S104 , the controller 500 obtains the fan gear adjustment value of the outdoor fan 180 and adjusts the gear of the outdoor fan 180 .

[0175] The controller 500 searches for the fan gear adjustment value of the outdoor fan 180 in the preset correspondence table based on the pressure deviation value ΔPd2, and adjusts the gear of the outdoor fan 180 so that the exhaust pressure value Pd of the compressor 110 is adjusted from the first exhaust pressure value Pd01 at the first moment to the maximum target pressure value.

[0176] The preset correspondence table is a correspondence table between the pressure deviation value ΔPd2 and the fan gear adjustment value, which includes at least one pressure deviation value ΔPd2 between the maximum target pressure value of the indoor unit 200 at any moment and the exhaust pressure value Pd of the compressor 110 at that moment, and at least one fan gear adjustment value of the outdoor fan 180, and at least one pressure deviation value ΔPd2 has a correspondence with at least one fan gear adjustment value of the outdoor fan 180.

[0177] For example, when air conditioner 1000 begins operation, controller 500 obtains the outdoor ambient temperature and the frequency of compressor 110 at the time of operation start, and assigns an initial fan gear position to outdoor fan 180 based on the outdoor ambient temperature and the frequency of compressor 110. Controller 500 determines a pressure deviation value ΔPd2 and searches a preset correspondence table for a fan gear position adjustment value for outdoor fan 180 based on the pressure deviation value ΔPd2. Based on the searched fan gear position adjustment value, controller 500 adjusts the gear position of outdoor fan 180 according to the initial fan gear position, so that the exhaust pressure value Pd of compressor 110 is adjusted toward the maximum target pressure value.

[0178] It should be noted that in some embodiments of the present disclosure, when the exhaust pressure value Pd of the compressor 110 reaches the maximum target pressure value at any moment, it can be considered that the indoor ambient temperature Ti at that moment has reached the preset temperature Ts. At this time, the operation of the air conditioner 1000 reaches a dynamic balance. When there is no change in the preset temperature Ts or a sudden change in the indoor ambient temperature Ti, the maximum pressure value of the indoor unit 200 generally no longer changes with the change of time.

[0179] In some embodiments of the present disclosure, when the first indoor unit 201 and the second indoor unit 202 both operate in the cooling operation mode, the correspondence between the pressure deviation value ΔPd2 and the fan gear adjustment value is shown in Table 1, which is a preset correspondence table.

[0180] Table 1

[0181] For example, when the pressure deviation value ΔPd2 between the maximum target pressure value determined by the controller 500 and the first exhaust pressure value Pd01 of the compressor 110 is 0, based on the pressure deviation value ΔPd2=0 and Table 1, it can be determined that the fan gear adjustment value that needs to be adjusted for the outdoor fan 180 is 0, and at this time, the fan gear of the outdoor fan 180 does not need to be adjusted.

[0182] For example, the controller 500 determines that the pressure deviation value ΔPd2 between the maximum target pressure value of the indoor unit 200 at the first moment and the first exhaust pressure value Pd01 of the compressor 110 is -0.9. Then the controller 500 determines that the fan gear adjustment value that needs to be adjusted for the outdoor fan 180 is +3 based on the pressure deviation value ΔPd2=-0.9 and Table 1. At this time, the controller 500 increases the first fan gear of the outdoor fan 180 by 3 gears.

[0183] For example, the controller 500 determines that the pressure deviation ΔPd2 between the maximum target pressure value of the indoor unit 200 at the first moment of operation and the first exhaust pressure value Pd01 of the compressor 110 is 0.4. Based on the pressure deviation ΔPd2 = 0.4 and Table 1, the controller 500 determines that the fan gear adjustment value required for the outdoor fan 180 is -1. In this case, the controller 500 lowers the first fan gear of the outdoor fan 180 by one gear. If the fan gear of the outdoor fan 180 after adjustment at the first moment is gear 1, the controller 500 can adjust the fan gear to gear 0 at the second moment.

[0184] In some embodiments, when the first indoor unit 201 and the second indoor unit 202 both operate in the heating operation mode, the air conditioner 1000 may further include another preset correspondence table.

[0185] When the first indoor unit 201 operates in the non-cooling and dehumidifying operation mode and the second indoor unit 202 operates in the cooling operation mode, the corresponding relationship between the pressure deviation value ΔPd2 and the fan gear adjustment value is shown in Table 2, which is a preset corresponding relationship table.

[0186] Table 2

[0187] When both the first indoor unit 201 and the second indoor unit 202 are operating in the non-cooling and dehumidifying operation mode, the corresponding relationship between the pressure deviation value ΔPd2 and the fan gear adjustment value is shown in Table 3, which is a preset corresponding relationship table. Table 3

[0188] It should be noted that when the second exhaust pressure value Pd02 of the compressor 110 is equal to the maximum target pressure value at the second moment, or the second exhaust pressure value Pd02 of the compressor 110 is relatively close to the maximum target pressure value at the second moment, for example, when the pressure deviation value ΔPd2 between the second exhaust pressure value Pd02 of the compressor 110 and the maximum target pressure value is less than a certain preset pressure threshold, the controller 500 may determine that the second exhaust pressure value Pd02 of the compressor 110 has reached the maximum target pressure value. The preset threshold may be a preset smaller pressure value.

[0189] FIG27 is a logic flow chart of a control method for an air conditioning system according to some embodiments. As shown in FIG27 , when the first indoor unit 201 operates in the non-cooling and dehumidifying operation mode and the second indoor unit 202 operates in the cooling operation mode, or when both the first indoor unit 201 and the second indoor unit 202 operate in the non-cooling and dehumidifying operation mode, the following steps may be further included after steps S101 to S104:

[0190] Step S201 : Acquire the ambient temperature Ti and the set temperature Ts, and determine a first temperature difference ΔT1 and a temperature difference change rate X.

[0191] The controller 500 obtains the first ambient temperature Ti1 at the first moment and the second ambient temperature Ti2 at the second moment through the first air inlet temperature sensor 51 of the first indoor unit 201, and obtains the set temperature Ts.

[0192] The second moment is the moment after one cycle has passed from the first moment, with a certain detection time as a cycle. Based on this rule, the n+1th moment is the moment after one cycle has passed from the nth moment. The present disclosure does not limit the length of a cycle. For example, a cycle can be 10 seconds.

[0193] The set temperature Ts is a set temperature value input by the user.

[0194] The temperature difference ΔT is the difference between the ambient temperature Ti and the set temperature Ts at any time when any indoor unit 200 is operating. For example, when the first indoor unit 201 is operating at a first time, the first temperature difference ΔT1 = Ti1 - Ts, and when the first indoor unit 201 is operating at a second time, the second temperature difference ΔT2 = Ti2 - Ts.

[0195] The temperature difference change rate X refers to the temperature difference at time n+1 and the temperature difference at time n. The temperature difference change rate X can be determined according to formula 12: X = (Ti(n+1)-Ts) + (Ti(n)-Ts) Formula 12

[0196] Ti(n+1) represents the ambient temperature detected at the (n+1)th moment, and Ti(n) represents the ambient temperature detected at the nth moment. For example, when n=1, the indoor ambient temperature detected by the first air inlet temperature sensor 51 of the first indoor unit 201 at the first moment is Ti1, and the indoor ambient temperature detected by the first air inlet temperature sensor 51 of the first indoor unit 201 at the second moment is Ti2. At this time, the temperature difference change rate X between the second temperature difference ΔT2 when the first indoor unit 201 is operating at the second moment and the first temperature difference ΔT1 when the first indoor unit 201 is operating at the first moment is (Ti2-Ts)+(Ti1-Ts).

[0197] Step S202 , obtaining a second exhaust pressure value Pd02 and determining a relationship between the second exhaust pressure value Pd02 and the first exhaust pressure value Pd01 .

[0198] The controller 500 obtains a second exhaust pressure value Pd02 of the compressor 110 at a second moment through the pressure sensor 60 .

[0199] When it is determined that the second exhaust pressure value Pd02 of the compressor 110 at the second moment is equal to the first exhaust pressure value Pd01 at the first moment, it is considered that the first exhaust pressure value Pd01 of the compressor 110 at the first moment has reached the maximum target pressure value at the first moment, and the maximum target pressure value of the compressor 110 at the second moment is equal to the maximum target pressure value at the first moment. Therefore, the compressor 110 has reached the maximum target pressure value at the second moment at the second moment, and there is no need to perform the next iterative calculation at this time. If they are not equal, continue to step S203.

[0200] Step S203 , obtaining the target pressure change value ΔPd1 , and determining the third target pressure value Pdset1 ( 2 ) and the fourth target pressure value Pdset2 ( 2 ).

[0201] When it is determined that the second exhaust pressure value Pd02 of the compressor 110 at the second moment is not equal to the first exhaust pressure value Pd01 at the first moment, the target pressure change value ΔPd1 is determined based on the temperature difference ΔT1 between the first ambient temperature Ti1 and the set temperature Ts and the temperature difference change rate X.

[0202] The target pressure change value ΔPd1 is the difference between the target pressure value Pdset1 (n+1) of the indoor unit 200 at the (n+1)th time and the target exhaust pressure value Pdset1 (n) at the nth time.

[0203] The relationship between the target pressure change value ΔPd1, Pdset1(n+1), and Pdset1(n) is shown in Formula 13: Pdset1(n+1)=ΔPd1+Pdset1(n) Formula 13

[0204] For example, the target pressure change value ΔPd1 of the first indoor unit 201 is the difference between the first target pressure value Pdset1(1) when the first indoor unit 201 operates at the first moment and the third target pressure value Pdset1(2) when the first indoor unit 201 operates at the second moment.

[0205] Table 4 shows the relationship between the target pressure change value ΔPd1, the temperature difference ΔT, and the temperature difference change rate X.

[0206] As shown in Table 4, ΔPd1 is determined by combining the temperature difference ΔT and the temperature difference change rate X. Based on the target pressure value Pdset(n) of the indoor unit 200 at the nth time and Formula 2, the target value of the exhaust pressure of the indoor unit 200 at the (n+1)th time can be determined.

[0207] For example, when the first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment is 5 MPa, the temperature difference ΔT between the ambient temperature Ti1 detected by the first temperature sensor at the first moment and the set temperature Ts is -4°C. When the temperature difference change rate X is -0.7°C, based on the temperature difference ΔT of -4°C, the temperature difference change rate x of -0.7°C and Table 4, ΔPd1=0.5 MPa is obtained, and the third target pressure value Pdset1(2) at the second moment can be determined to be 5 MPa+0.5 MPa=5.5 MPa.

[0208] For example, when the first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment is 12 MPa, the temperature difference ΔT between the ambient temperature Ti1 detected by the first air inlet temperature sensor 51 at the first moment and the set temperature Ts is 2°C. When the temperature difference change rate X is 0.3°C, based on the temperature difference ΔT of 2°C, the temperature difference change rate X of 0.3°C and Table 4, ΔPd1=-0.2 MPa is obtained, and the third target pressure value Pdset1(2) at the second moment can be determined to be 12 MPa+(-0.2 MPa)=11.8 MPa.

[0209] When the second indoor unit 202 operates in the non-cooling and dehumidification operation mode, the calculation method of the fourth target pressure value Pdset2(2) at the second moment is consistent with the calculation method of the third target pressure value Pdset1(2) when the first indoor unit 201 operates at the second moment, and will not be repeated in this disclosure.

[0210] Step S204 , determining the magnitude of the third target pressure value Pdset1 ( 2 ) and the fourth target pressure value Pdset2 ( 2 ).

[0211] When the first indoor unit 201 operates in the non-cooling and dehumidification operation mode and the second indoor unit 202 operates in the cooling operation mode, the target pressure value Pdset of the second indoor unit 202 does not change. Therefore, the fourth target pressure value Pdset2(2) of the second indoor unit 202 operating at the second moment is equal to the second target pressure value Pdset2(1) at the first moment. At this time, steps S204A1 to S209 are executed.

[0212] Step S204A1 , determining whether the third target pressure value Pdset1 ( 2 ) is greater than the fourth target pressure value Pdset2 ( 2 ).

[0213] The controller 500 determines the magnitude of the third target pressure value Pdset1(2) of the first indoor unit 201 at the second moment and the fourth target pressure value Pdset2(2) of the second indoor unit 202 at the second moment.

[0214] The first target pressure value Pdset1(1) of the first indoor unit 201 at the first moment is greater than the second target pressure value Pdset2(1) of the second indoor unit 202 at the first moment. It can be obtained that the third target pressure value Pdset1(2) of the first indoor unit 201 at the second moment is greater than the second target pressure value Pdset2(1) of the second indoor unit 202 at the first moment. At the second moment, the maximum target pressure value of the first indoor unit 201 and the second indoor unit 202 should be the third target pressure value Pdset1(2).

[0215] Step S205, obtain the maximum target pressure value of the indoor unit 200 at the second moment, that is, the third target pressure value Pdset1(2) of the first indoor unit 201 at the second moment, and adjust the gear position of the outdoor fan 180 based on the third target pressure value Pdset1(2).

[0216] Based on the pressure deviation value ΔPd2 between the third target pressure value Pdset1(2) of the first indoor unit 201 at the second moment and the second exhaust pressure value Pd02 of the compressor 110 at the second moment, the gear position of the outdoor fan 180 is adjusted so that the exhaust pressure value Pd of the compressor 110 is adjusted from the second exhaust pressure value Pd02 to the third target pressure value Pdset1(2).

[0217] The outdoor fan 180 is adjusted according to the pressure deviation value ΔPd2 between the third target pressure value Pdset1(2) of the first indoor unit 201 at the second moment and the second exhaust pressure value Pd02 of the compressor 110 at the second moment and Table 2.

[0218] Step S206, determining whether the exhaust pressure value Pd of the compressor 110 at any moment reaches the maximum target pressure value at that moment, i.e., the third target pressure value Pdset1(2). If not, continue to execute step S205; if reached, execute step S207.

[0219] Step S207, determine the size of the second exhaust pressure value Pd02 of the compressor 110 at this time and the second saturation pressure value Pd2 corresponding to the ambient temperature Ti of the second indoor unit 202, and adjust the opening of the fifth indoor expansion valve 324 according to the second target pressure value Pdset2(1) and the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2.

[0220] When the second exhaust pressure value Pd02 of the compressor 110 is greater than the second saturation pressure value Pd2 corresponding to the ambient temperature of the second indoor unit 202, step S208 is executed; otherwise, step S209 is executed.

[0221] In step S208 , the opening degree of the fifth indoor expansion valve 324 of the second indoor unit 202 is reduced.

[0222] In step S209 , the opening degree of the fifth indoor expansion valve 324 of the second indoor unit 202 is increased.

[0223] In step S210, it is determined whether the exhaust pressure value Pd of the compressor 110 reaches the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2 of the second indoor unit 202, that is, Pd02 = Pd2.

[0224] Step S211, ending the adjustment task.

[0225] It should be noted that when the second target pressure value Pdset2(1) of the second indoor unit 202 is equal to the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2, the controller 500 can determine that the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2 of the second indoor unit 202 reaches the second exhaust pressure value Pd02 of the compressor 110.

[0226] Alternatively, the second discharge pressure value Pd02 of the compressor 110 is relatively close to the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2. For example, when the pressure deviation value ΔPd2 between the second discharge pressure value Pd02 of the compressor 110 and the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2 is less than a preset threshold, the controller 500 may determine that the second saturation pressure value Pd2 corresponding to the second ambient temperature Ti2 of the second indoor unit 202 reaches the second discharge pressure value Pd02 of the compressor 110. The preset threshold may be a preset smaller pressure value.

[0227] It should be noted that when the second indoor unit 202 operates in the cooling operation mode, the fifth electronic expansion valve 324 and the fourth electronic expansion valve 323 both maintain their maximum openings.

[0228] When the first indoor unit 201 operates in cooling mode, the second indoor unit 202 operates in non-cooling and dehumidification mode, and the first target pressure value Pdset1 of the first indoor unit 201 is less than the second target pressure value Pdset2 of the second indoor unit 202, the adjustment process is similar to steps S201 to S211, and the present disclosure will not repeat them here.

[0229] When the first indoor unit 201 and the second indoor unit 202 are both operating in the non-cooling and dehumidification operation mode, and the first target pressure value Pdset1(1) of the first indoor unit 201 operating at the first moment is greater than the second target pressure value Pdset2(1) of the second indoor unit 202 operating at the first moment, run steps S204 to S211.

[0230] When the first indoor unit 201 and the second indoor unit 202 are both operating in the non-cooling and dehumidification operation mode, and the first target pressure value Pdset1(1) of the first indoor unit 201 operating at the first moment is less than the second target pressure value Pdset2(1) of the second indoor unit 202 operating at the first moment, run steps S204A2 to S311.

[0231] Step S204A2 , determining whether the third target pressure value Pdset1 ( 2 ) is smaller than the fourth target pressure value Pdset2 ( 2 ).

[0232] Step S305, obtain the maximum target pressure value of the indoor unit 200 at the second moment, that is, the fourth target pressure value Pdset2(2) of the second indoor unit 202 at the second moment, and adjust the gear position of the outdoor fan 180 based on the fourth target pressure value Pdset2(2).

[0233] Based on the pressure deviation value ΔPd2 between the fourth target pressure value Pdset2(2) of the second indoor unit 202 at the second moment and the second exhaust pressure value Pd02 of the compressor 110 at the second moment, the gear position of the outdoor fan 180 is adjusted so that the exhaust pressure value Pd of the compressor 110 is adjusted from the second exhaust pressure value Pd02 to the fourth target pressure value Pdset2(2).

[0234] The outdoor fan 180 is adjusted according to the pressure deviation value ΔPd2 between the fourth target pressure value Pdset2(2) of the second indoor unit 202 at the second moment and the second exhaust pressure value Pd02 of the compressor 110 at the second moment and Table 2.

[0235] Step S306, determining whether the exhaust pressure value Pd of the compressor 110 at any moment reaches the maximum target pressure value at that moment, i.e., the fourth target pressure value Pdset2(2). If not, continue to execute step S305; if reached, execute step S307.

[0236] Step S307, determine the size of the second exhaust pressure value Pd02 of the compressor 110 at this time and the first saturation pressure value Pd1 corresponding to the ambient temperature Ti of the first indoor unit 201, and adjust the opening of the second indoor expansion valve 322 according to the first target pressure value Pdset1(1) and the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti1.

[0237] When the second exhaust pressure value Pd02 of the compressor 110 is greater than the first saturation pressure value Pd1 corresponding to the ambient temperature Ti of the first indoor unit 201 , step S308 is executed; otherwise, step S309 is executed.

[0238] Step S308: Reduce the opening degree of the second indoor expansion valve 322 of the first indoor unit 201.

[0239] Step S309: Increase the opening degree of the second indoor expansion valve 322 of the first indoor unit 201.

[0240] In step S310 , it is determined whether the exhaust pressure value Pd of the compressor 110 reaches the first saturation pressure value Pd1 corresponding to the ambient temperature Ti of the first indoor unit 201 , that is, Pd02 = Pd1 .

[0241] Step S311, ending the adjustment task.

[0242] It should be noted that when the first target pressure value Pdset1(1) of the first indoor unit 201 is equal to the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti2, the controller 500 can determine that the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti1 of the first indoor unit 201 reaches the second exhaust pressure value Pd02 of the compressor 110.

[0243] Alternatively, the second exhaust pressure value Pd02 of the compressor 110 is relatively close to the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti2. For example, when the pressure deviation value ΔPd2 between the second exhaust pressure value Pd02 of the compressor 110 and the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti1 is less than a preset threshold, the controller 500 may determine that the first saturation pressure value Pd1 corresponding to the first ambient temperature Ti1 of the first indoor unit 201 reaches the second exhaust pressure value Pd02 of the compressor 110. The preset threshold may be a preset smaller pressure value.

[0244] The technical solutions provided by some embodiments of the present disclosure bring at least the following beneficial effects: the outdoor unit 100 of the air conditioner 1000 assigns an initial windage value to the outdoor fan 180 based on the outdoor ambient temperature and the operating frequency of the compressor 110, thereby obtaining a corresponding first exhaust pressure value Pd01 of the compressor 110. The corresponding indoor ambient temperature Ti is obtained from the inlet air temperature sensor 50. If the ambient temperatures Ti of the two indoor units 200 are different, and the set temperatures Ts of the two temperature-controlled dehumidification indoor units 200 are also different, a target pressure change value is obtained based on the temperature difference between the ambient temperature Ti and the set temperature Ts, and the temperature difference change rate X. This determines the target exhaust pressure value for the next step, ultimately ensuring that the ambient temperature Ti of the indoor units 200 is consistent with the set temperature Ts. This improves the efficiency of the user's settings for the air conditioner 1000 and optimizes the user experience.

[0245] Those skilled in the art should readily appreciate that, in conjunction with the modules and algorithmic steps of the various examples described in the embodiments disclosed in this disclosure, some embodiments of the present disclosure can be implemented in the form of hardware or a combination of hardware and computer software. Whether a function is executed in hardware or in a manner driven by computer software depends on the specific application and design constraints of the technical solution. Professional and technical personnel may use different methods to implement the described functions for each specific application, but such implementation should not be considered to be beyond the scope of the present invention.

[0246] FIG28 is a block diagram of the hardware configuration of a controller for an air conditioning system according to some embodiments. As shown in FIG28 , the controller 500 includes a processor 1001 and, in some embodiments, further includes a memory 1002 and a communication interface 1003 connected to the processor 1001. The processor 1001, the memory 1002, and the communication interface 1003 are connected via a bus 1004.

[0247] The processor 1001 may be a central processing unit (CPU), a general-purpose processor, a network processor (NP), a digital signal processor (DSP), a microprocessor, a microcontroller, a programmable logic device (PLD), or any combination thereof. The processor 1001 may also be any other device having a processing function, such as a circuit, a device, or a software module. The processor 1001 may also include multiple CPUs, and the processor 1001 may be a single-core (single-CPU) processor or a multi-core (multi-CPU) processor. The processor here may refer to one or more devices, circuits, or processing cores for processing data (such as computer program instructions).

[0248] The memory 1002 may be a read-only memory (ROM) or other types of static storage devices that can store static information and instructions, a random access memory (RAM) or other types of dynamic storage devices that can store information and instructions, or an electrically erasable programmable read-only memory (EEPROM), a compact disc read-only memory (CD-ROM) or other optical disc storage, optical disc storage (including compressed optical discs, laser discs, optical discs, digital versatile discs, Blu-ray discs, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium that can be used to carry or store desired program codes in the form of instructions or data structures and can be accessed by a computer, and the present embodiment of the application does not impose any restrictions on this. The memory 1002 may exist independently or be integrated with the processor 1001. Among them, the memory 1002 may contain computer program code. The processor 1001 is used to execute the computer program code stored in the memory 1002, thereby implementing a control method for an air-conditioning system provided in an embodiment of the present application.

[0249] The communication interface 1003 can be used to communicate with other devices or communication networks (such as Ethernet, radio access network (RAN), wireless local area network (WLAN), etc.) The communication interface 1003 can be a module, circuit, transceiver or any device capable of achieving communication.

[0250] Bus 1004 may be a Peripheral Component Interconnect (PCI) bus or an Extended Industry Standard Architecture (EISA) bus. Bus 1004 may be classified as an address bus, a data bus, a control bus, etc. For ease of illustration, FIG28 shows only one thick line, but this does not mean that there is only one bus or only one type of bus.

[0251] Some embodiments of the present disclosure further provide a computer-readable storage medium, which includes computer-executable instructions. When the computer-executable instructions are executed on a computer, the computer executes a method for controlling an air conditioner as provided in the above embodiments.

[0252] Some embodiments of the present disclosure also provide a computer program product, which can be directly loaded into a memory and contains software code. After being loaded and executed by a computer, the computer program product can implement a control method for an air conditioner 1000 provided in the above embodiment.

[0253] Those skilled in the art will understand that the scope of the present invention is not limited to the above specific embodiments, and that certain elements of the embodiments may be modified and replaced without departing from the spirit of the present invention. The scope of the present invention is limited by the appended claims.

Claims

1. An indoor unit, comprising: A housing, the housing comprising an upper cover plate and a bottom plate arranged opposite to each other, and a first side plate connected to the upper cover plate and the bottom plate; An air outlet is provided on the first side panel; an indoor heat exchanger, the indoor heat exchanger being located inside the casing, the indoor heat exchanger extending in a direction parallel to the extending direction of the air outlet and having a length shorter than the length of the air outlet, the first end of the indoor heat exchanger being located on the same side as the first end of the air outlet, the second end of the indoor heat exchanger being located on the same side as the second end of the air outlet, and a clearance space being provided between the first end of the indoor heat exchanger and the first end of the air outlet; A shielding component is connected to the first end of the indoor heat exchanger and the first end of the air outlet to shield the avoidance space.

2. The indoor unit according to claim 1, wherein: The shielding component includes: a first shielding portion, the first shielding portion being parallel to the air outlet and fixedly connected to the first side panel; A second shielding portion is connected to the first shielding portion, and the second shielding portion is perpendicular to the air outlet, and the second shielding portion is fixedly connected to the first end of the indoor heat exchanger.

3. The indoor unit according to claim 2, further comprising: A water receiving tray is provided inside the housing and is located on a side of the indoor heat exchanger close to the bottom plate; wherein the water receiving tray includes: Water tray bottom plate; a first water receiving tray side plate connected to the water receiving tray bottom plate, wherein the first water receiving tray side plate is parallel to and adjacent to the first side plate; The first shielding portion includes: a main body of the shielding portion; A first supporting portion is provided at one end of the shielding portion body close to the upper cover plate and abuts against a surface of the upper cover plate close to the bottom plate; a second supporting portion, provided at one end of the shielding portion body close to the bottom plate, and abutting against a surface of the first water receiving tray side plate close to the upper cover plate; The second shielding portion includes: a third supporting portion, abutting against a surface of the upper cover plate close to the bottom plate; The fourth supporting portion abuts against a surface of the bottom plate of the water receiving tray close to the upper cover plate.

4. The indoor unit according to claim 3, wherein: The first support portion and the third support portion are both in contact with the surface of the upper cover plate close to the bottom plate, the second support portion is in contact with the surface of the first water receiving tray side plate close to the upper cover plate, and the fourth support portion is in contact with the surface of the water receiving tray bottom plate close to the upper cover plate.

5. The indoor unit according to claim 4, wherein: The upper cover plate comprises: Upper cover body; an upper cover plate foam layer located on a side of the upper cover plate body close to the bottom plate, the upper cover plate foam layer comprising a straight portion parallel to the bottom plate and an inclined portion inclined toward the bottom plate relative to the straight portion, the inclined portion being located on the side where the air outlet is located; The first support portion has an inclination angle adapted to the inclined portion, and the first support portion is adapted to fit the inclined portion; the third support portion includes a first support sub-portion adapted to fit the straight portion and a second support sub-portion adapted to fit the inclined portion. The indoor unit according to claim 5, wherein: The upper cover foam layer further includes a positioning portion, which is arranged on the inclined portion and faces the bottom plate. The side is protruding, and one side of the first supporting portion abuts against the positioning portion.

7. The indoor unit according to claim 3, wherein: The first shielding portion further includes an inserting portion connected to the second supporting portion. A gap is provided between the first water receiving tray side plate and the first side plate, and the inserting portion is inserted in the gap.

8. The indoor unit according to claim 1, wherein: The first shielding part also includes a connecting part, which is arranged on a side of the shielding part body away from the second shielding part, and the connecting part is folded toward the outside of the casing relative to the shielding part body. The connecting part has a first connecting part and a second connecting part, and the second connecting part is in contact with the first side panel and is fixedly connected to the first side panel.

9. The indoor unit according to claim 2, wherein: The second shielding portion is in contact with the first end surface of the heat exchanger, and includes a through portion for avoiding a pipe connected to the indoor heat exchanger.

10. An air conditioner, The indoor unit comprises the indoor unit according to any one of claims 1 to 9.

11. An air conditioner comprising: Indoor unit, including: a first indoor heat exchanger; a second indoor heat exchanger, communicating with the first indoor heat exchanger; a first blowing device, configured to blow air toward the first indoor heat exchanger; an outdoor unit connected to the indoor unit via a circulation pipeline; A controller is electrically connected to both the indoor unit and the outdoor unit and is configured to: In a heating operation mode, controlling the first indoor heat exchanger and the second indoor heat exchanger to function as condensers, and controlling the rotation speed of the first blowing device to a first preset value; In the non-cooling and dehumidifying operation mode, the first indoor heat exchanger is controlled as a condenser, the second indoor heat exchanger is controlled as an evaporator, and the speed of the first blowing device is controlled to a second preset value, which is greater than the first preset value.

12. The air conditioner according to claim 11, wherein The indoor unit further includes: a first electronic expansion valve, communicating with the first indoor heat exchanger and the second indoor heat exchanger; a second electronic expansion valve, communicating with the second indoor heat exchanger and the outdoor unit; The outdoor unit comprises: a compressor assembly having an outlet and an inlet; a first refrigerant flow direction switching device comprising: a first port communicating with the first indoor heat exchanger, a second port communicating with the inlet, a third port communicating with the outlet, and a fourth port; The third electronic expansion valve; a first outdoor heat exchanger, connected to the second electronic expansion valve through the third electronic expansion valve; The second refrigerant flow direction switching device includes: a fifth port communicating with the inlet, a sixth port communicating with the first outdoor heat exchanger, a seventh port communicating with the outlet, and an eighth port communicating with the fourth port.

13. The air conditioner according to claim 12, wherein The controller is further configured to: In the heating operation mode and the non-cooling dehumidification operation mode, the first port is controlled to be in communication with the third port, and the fifth port is controlled to be in communication with the sixth port.

14. The air conditioner according to claim 13, wherein The outdoor unit further includes: a second blowing device, configured to blow air toward the first outdoor heat exchanger; The controller is further configured to: In the cooling operation mode, the first port is controlled to be connected to the second port, the sixth port is controlled to be connected to the seventh port, and the speed of the second blowing device is controlled to be a third preset value; In the cooling and dehumidification operation mode, the first port is controlled to be connected to the second port, the sixth port is controlled to be connected to the seventh port, and the rotation speed of the second blowing device is controlled to a fourth preset value, which is smaller than the third preset value.

15. The air conditioner according to claim 12, wherein The indoor unit further includes: a third indoor heat exchanger, a fourth electronic expansion valve, a fourth indoor heat exchanger and a fifth electronic expansion valve, wherein the third indoor heat exchanger, the fourth electronic expansion valve, the fourth indoor heat exchanger and the fifth electronic expansion valve are connected in series in sequence; The third indoor heat exchanger is in communication with the first port, and the fifth electronic expansion valve is in communication with the third electronic expansion valve.

16. The air conditioner according to claim 13, further comprising: A solenoid valve is connected to the second electronic expansion valve and the inlet.

17. The air conditioner according to claim 16, wherein The controller is further configured to: In the non-cooling and dehumidifying operation mode, the third electronic expansion valve is controlled to be closed, and the solenoid valve is controlled to be opened.

18. The air conditioner according to claim 14, wherein The outdoor unit further includes: a second outdoor heat exchanger and a sixth electronic expansion valve, wherein the second outdoor heat exchanger is connected to the second electronic expansion valve through the sixth electronic expansion valve; a third blowing device, configured to blow air toward the second outdoor heat exchanger; The third refrigerant flow direction switching device includes: a ninth port communicating with the inlet, a tenth port communicating with the second outdoor heat exchanger, an eleventh port communicating with the outlet, and a twelfth port communicating with the sixth port.

19. The air conditioner according to claim 18, wherein The controller is further configured to: In the heating operation mode and the non-cooling dehumidification operation mode, controlling the ninth port to be connected to the tenth port; In the cooling operation mode and the cooling and dehumidifying operation mode, the tenth port is controlled to communicate with the eleventh port.

20. The air conditioner according to any one of claims 11 to 19, wherein: The first refrigerant flow direction switching device and the second refrigerant flow direction switching device both include: a four-way valve.

21. An air conditioner, comprising: Outdoor fan; Multiple indoor units; compressor; A pressure sensor, used to detect the exhaust pressure value of the compressor; A controller, connected to the pressure sensor, is configured to: obtaining a first exhaust pressure value of the compressor at a first moment through the pressure sensor; determining a maximum target pressure value from a first target pressure value and a second target pressure value, wherein the first target pressure value is a target exhaust pressure value of the compressor when a first indoor unit among the plurality of indoor units operates in a first mode, and the second target pressure value is a target exhaust pressure value of the compressor when a second indoor unit among the plurality of indoor units operates in a second mode; calculating a pressure deviation between the maximum target pressure value and the first exhaust pressure value; Based on the pressure deviation value, the gear position of the outdoor fan is adjusted so that the exhaust pressure value of the compressor reaches the maximum target pressure value.

22. The air conditioner according to claim 21, wherein The first mode is a non-cooling and dehumidifying operation mode, and the second mode is a cooling operation mode; or, The first mode and the second mode are both non-cooling and dehumidification operation modes.

23. The air conditioner according to claim 22, wherein When the first mode is a non-cooling and dehumidifying operation mode and the second mode is a cooling operation mode, the first indoor heat exchanger of the first indoor unit works as a condenser, the second indoor heat exchanger of the first indoor unit works as an evaporator, and the third indoor heat exchanger and the fourth indoor heat exchanger of the second indoor unit both work as evaporators.

24. The air conditioner according to claim 23, further comprising: a first inlet air temperature sensor, configured to detect the ambient temperature of the first indoor unit; The controller is further configured to: obtaining, by means of the first air inlet temperature sensor, a first ambient temperature at a first moment and a second ambient temperature at a second moment; The first target pressure value is adjusted according to a second temperature difference between the second ambient temperature and the preset temperature of the first indoor unit and a temperature difference change rate of the first indoor unit at a second moment; wherein the temperature difference change rate is a change value between the second temperature difference and the first temperature difference, and the first temperature difference is a temperature difference between the first ambient temperature and the preset temperature of the first indoor unit.

25. The air conditioner according to claim 22, further comprising: a first inlet air temperature sensor, configured to detect the ambient temperature of the first indoor unit; a second air inlet temperature sensor, configured to detect the ambient temperature of the second indoor unit; a second electronic expansion valve, configured to adjust the flow of refrigerant in the pipeline between the first indoor unit and the outdoor unit; a fifth electronic expansion valve, configured to adjust a refrigerant flow rate in a pipeline between the second indoor unit and the outdoor unit; The controller is further configured to: When both the first mode and the second mode are non-cooling dehumidification operation modes, a second exhaust pressure value of the compressor at a second moment is obtained through the pressure sensor, a second ambient temperature of the first indoor unit at the second moment is obtained through the first inlet air temperature sensor, and a fourth ambient temperature of the second indoor unit at the second moment is obtained through the second inlet air temperature sensor; the second moment is a moment after the first moment; When the second exhaust pressure value reaches the maximum target pressure value, if the first target pressure value is greater than or equal to the second target pressure value, adjusting the opening of the fifth electronic expansion valve according to the second target pressure value and the saturation pressure value at the fourth ambient temperature so that the saturation pressure value at the ambient temperature of the second indoor unit reaches the exhaust pressure value of the compressor; or If the first target pressure value is less than the second target pressure value, the opening of the second electronic expansion valve is adjusted according to the first target pressure value and the saturation pressure value at the second ambient temperature so that the saturation pressure value at the ambient temperature of the first indoor unit reaches the exhaust pressure value of the compressor.

26. A method for controlling an air conditioner, wherein: The air conditioner comprises: Outdoor fan; Multiple indoor units; compressor; A pressure sensor, used to detect the exhaust pressure value of the compressor; a controller connected to the pressure sensor; The method comprises: The controller obtains a first exhaust pressure value of the compressor at a first moment through the pressure sensor; The controller determines a maximum target pressure value from a first target pressure value and a second target pressure value, wherein the first target pressure value is a target exhaust pressure value of the compressor when a first indoor unit among the plurality of indoor units operates in a first mode, and the second target pressure value is a target exhaust pressure value of the compressor when a second indoor unit among the plurality of indoor units operates in a second mode; The controller calculates a pressure deviation value between the maximum target pressure value and the first exhaust pressure value; The controller adjusts the gear position of the outdoor fan based on the pressure deviation value so that the exhaust pressure value of the compressor reaches the maximum target pressure value.

27. The method according to claim 26, wherein The first mode is a non-cooling and dehumidifying operation mode, and the second mode is a cooling operation mode; or, The first mode and the second mode are both non-cooling and dehumidification operation modes.

28. The method according to claim 27, wherein When the first mode is a non-cooling and dehumidifying operation mode and the second mode is a cooling operation mode, the first indoor heat exchanger of the first indoor unit works as a condenser, the second indoor heat exchanger of the first indoor unit works as an evaporator, and the third indoor heat exchanger and the fourth indoor heat exchanger of the second indoor unit both work as evaporators.

29. The method according to claim 28, wherein The air conditioner further comprises a first air inlet temperature sensor for detecting the ambient temperature of the first indoor unit; The method further comprises: The controller obtains a first ambient temperature at a first moment and a second ambient temperature at a second moment through the first air inlet temperature sensor; The controller adjusts the first target pressure value according to a second temperature difference between the second ambient temperature and the preset temperature of the first indoor unit and a temperature difference change rate of the first indoor unit at a second moment; wherein the temperature difference change rate is a change value between the second temperature difference and the first temperature difference, and the first temperature difference is a temperature difference between the first ambient temperature and the preset temperature of the first indoor unit.

30. The method of claim 27, wherein: The air conditioner further comprises: a first inlet air temperature sensor, configured to detect the ambient temperature of the first indoor unit; a second air inlet temperature sensor, configured to detect the ambient temperature of the second indoor unit; a second electronic expansion valve, configured to adjust the flow of refrigerant in the pipeline between the first indoor unit and the outdoor unit; a fifth electronic expansion valve, configured to adjust a refrigerant flow rate in a pipeline between the second indoor unit and the outdoor unit; The method further comprises: When both the first mode and the second mode are non-cooling and dehumidification operation modes, the controller obtains a second exhaust pressure value of the compressor at a second moment through the pressure sensor, obtains a second ambient temperature of the first indoor unit at the second moment through the first inlet air temperature sensor, and obtains a fourth ambient temperature of the second indoor unit at the second moment through the second inlet air temperature sensor; the second moment is a moment after the first moment; When the second exhaust pressure value reaches the maximum target pressure value, if the first target pressure value is greater than or equal to the second target pressure value, the controller adjusts the opening of the fifth electronic expansion valve according to the second target pressure value and the saturation pressure value at the fourth ambient temperature, so that the saturation pressure value at the ambient temperature of the second indoor unit reaches the exhaust pressure value of the compressor; or If the first target pressure value is less than the second target pressure value, the controller adjusts the opening of the second electronic expansion valve according to the first target pressure value and the saturation pressure value at the second ambient temperature so that the saturation pressure value at the ambient temperature of the first indoor unit reaches the exhaust pressure value of the compressor.

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