Air conditioner

Abstract

The application provides an air conditioner, which comprises an indoor unit and an outdoor unit, the indoor unit comprises an indoor shell provided with an indoor heat exchanger, the outdoor unit comprises an outdoor shell provided with an outdoor heat exchanger, the outdoor shell further comprises a compressor cabin provided with a compressor, the compressor comprises an air inlet and an air outlet, the air inlet is provided with a suction pipe, the air outlet is provided with a discharge pipe, the refrigerant temperature in the discharge pipe is higher than that in the suction pipe, and the air conditioner further comprises an internal circulation fan arranged between the suction pipe and the discharge pipe. In the process of calculating the refrigeration performance coefficient of the air conditioner, when it is determined that the air outlet of the evaporator is not overheated, heat compensation needs to be performed, in the process of heat compensation, the internal circulation fan 79 is started, the airflow in the compressor cabin is internally circulated, the air heated by the refrigerant of the discharge pipe exchanges heat with the refrigerant in the suction pipe, so as to compensate the temperature of the refrigerant in the suction pipe, and when it is determined that the air outlet of the evaporator is overheated, the internal circulation fan is closed.

Description

Technical Field

[0001] This invention relates to the field of household appliance technology, and more particularly to an air conditioner. Background Technology

[0002] Currently, an air conditioner includes an indoor unit and an outdoor unit. The indoor unit includes an indoor heat exchanger, and the outdoor unit includes an outdoor heat exchanger, a compressor, and a throttling device. The indoor heat exchanger, outdoor heat exchanger, compressor, and throttling device together constitute a refrigeration system. Generally speaking, in order to improve the cooling capacity of the system and ensure its normal operation, it is usually necessary to obtain various performance coefficients during the operation of the air conditioner.

[0003] Calculating the online coefficient of performance (COP) of an air conditioner requires obtaining both the compressor power and the heat exchange capacity on the refrigerant side or the air side. However, in actual operation at a user's home, there is no device to simultaneously measure the heat exchange capacity and compressor power, making it impossible to obtain accurate measurement values. This is detrimental to energy-saving operation, performance prediction, or guiding optimization design of the air conditioner.

[0004] In related technologies, the real-time heat exchange and compressor power of an air conditioner under cooling or hot and humid conditions can be calculated by sampling various parameters of the air conditioner, thereby obtaining the air conditioner performance coefficient EER (under cooling conditions) or COP (under heating conditions).

[0005] Because of the latent heat generated during the dehumidification process of an air conditioner, the heat exchange capacity on the air side is usually inaccurate. In this case, the real-time power of the heat exchanger can be obtained by calculating the heat exchange capacity on the refrigerant side. However, when the evaporator outlet is not overheated, since the refrigerant dryness fraction is an unknown quantity slightly less than 1, the enthalpy value cannot be calculated, and therefore the heat exchange capacity on the refrigerant side cannot be obtained, affecting the application scenarios of the air conditioner performance coefficient calculation method.

[0006] In related technologies, the heat exchange of the evaporator and condenser is calculated by fitting the compressor flow rate, as well as the air volume and pressure drop, and then the air conditioning system is monitored online. However, this method still ignores the performance calculation deviation caused by the compressor suction not being overheated or the condenser outlet not being overcooled, which makes it impossible to calculate the coefficient of performance in some scenarios.

[0007] In view of the above, this application is hereby submitted. Summary of the Invention

[0008] This application provides an air conditioner that, when the evaporator outlet is not overheated, uses internal airflow within the compressor compartment for recirculation. The air heated by the refrigerant at the compressor outlet compensates for the temperature of the refrigerant in the suction pipe, thereby heating the evaporator outlet to a certain extent and ensuring heat compensation under non-overheating conditions to meet the usage conditions for online performance calculation.

[0009] Therefore, this application aims to provide an air conditioner, comprising:

[0010] An indoor unit includes an indoor casing, within which an indoor heat exchanger is installed;

[0011] Outdoor unit, which includes outdoor casing;

[0012] The outdoor heat exchanger is located inside the outdoor shell. In heating mode, the outdoor heat exchanger acts as an evaporator and the indoor heat exchanger acts as a condenser. In cooling mode, the outdoor heat exchanger acts as a condenser and the indoor heat exchanger acts as an evaporator.

[0013] The compressor compartment is located inside the outdoor casing;

[0014] The compressor is located in the compressor compartment. The compressor includes an air inlet and an air outlet. The air inlet is equipped with a suction pipe, and the air outlet is equipped with a discharge pipe. The refrigerant temperature in the discharge pipe is higher than the refrigerant temperature in the suction pipe.

[0015] An internal circulation fan is located inside the compressor compartment and between the intake and exhaust pipes to promote airflow circulation and heat exchange within the compressor compartment.

[0016] The first temperature detection device is located at the indoor heat exchanger and is used to detect the temperature of the inner coil.

[0017] The second temperature detection device is located at the air inlet of the compressor and is used to detect the air intake temperature of the compressor.

[0018] A pressure detection device is installed at the air inlet of the compressor to detect the compressor's suction pressure.

[0019] The controller is configured to perform heat compensation when it is determined that the compressor inlet or the evaporator outlet is not overheating during the calculation of the air conditioner's coefficient of performance.

[0020] During the heat compensation process, the internal circulation fan is turned on, and the airflow in the compressor compartment circulates internally. The air heated by the refrigerant in the exhaust pipe exchanges heat with the refrigerant in the intake pipe to compensate for the temperature of the refrigerant in the intake pipe.

[0021] When the compressor suction temperature rises to the corresponding saturation temperature that reaches the compressor suction pressure and / or the difference between the compressor suction temperature and the internal coil temperature exceeds the first preset difference, it is determined that the compressor inlet or the evaporator outlet is overheated and the internal circulation fan is turned off.

[0022] In some embodiments of this application, when the compressor inlet or the evaporator outlet is overheated, the air conditioning coefficient is calculated based on the air conditioning operating conditions.

[0023] When the air conditioner is in cooling mode, the heat exchange on the evaporator side is obtained based on the enthalpy difference between the inlet and outlet of the evaporator and the refrigerant flow rate. Then, the heat exchange on the evaporator side and the operating power of the compressor are logically calculated to obtain the coefficient of performance (EERe).

[0024] When the air conditioner is in heating mode, the heat exchange on the condenser side is obtained based on the heat exchange on the evaporator side and the operating power of the compressor. Then, the heat exchange on the condenser side and the operating power of the compressor are logically calculated to obtain the heating performance coefficient COPe.

[0025] In some embodiments of this application, the intake pipe is defined as the main circuit; the air conditioner also includes:

[0026] The bypass circuit is configured as a branch of the main circuit. The connection points between the bypass circuit and the main circuit are defined as the first connection point and the second connection point. The refrigerant in the main circuit flows into the bypass circuit through the first connection point, and the refrigerant in the bypass circuit then flows back into the main circuit through the second connection point.

[0027] The main circuit valve is located on the main circuit and between the first connection point and the second connection point, and is used to control whether the refrigerant flows through the main circuit.

[0028] A bypass valve is located in the bypass circuit and between the first connection point and the second connection point. It is used to control the flow of refrigerant in the main circuit into the bypass circuit for heat exchange.

[0029] An electronically controlled heat dissipation unit is located on one side of the bypass circuit and is used to exchange heat with the refrigerant in the bypass circuit.

[0030] The controller is configured to open the main circuit valve during air conditioner operation, and if the compressor inlet or evaporator outlet is still not overheated after the internal circulation fan has been running for a period of time, it is determined that heat compensation needs to be increased.

[0031] Open the bypass valve, keeping both the main circuit valve and the bypass valve open at the same time. The refrigerant flows through both the main circuit and the bypass circuit simultaneously, and the refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled heat dissipation unit.

[0032] The heated refrigerant merges with the refrigerant in the main circuit and then flows together into the compressor's air inlet.

[0033] In some embodiments of this application, the controller is configured to determine that if the compressor inlet or evaporator outlet is still not overheated after the main circuit valve and bypass valve have been open for a period of time, heat compensation needs to be strengthened.

[0034] With the bypass valve open and the main circuit valve closed, all the refrigerant flowing through the first connection point flows into the bypass circuit, where it exchanges heat with the electronically controlled heat dissipation unit.

[0035] After being heated, the refrigerant flows back to the main circuit through the second connection point and then into the compressor's air inlet.

[0036] In some embodiments of this application, when the compressor suction temperature does not exceed the saturation temperature corresponding to the compressor suction pressure, the first parameter is defined as a1; otherwise, the first parameter is defined as b1′.

[0037] When the difference between the compressor suction temperature and the internal coil temperature does not reach the first preset temperature difference, the second parameter is defined as a2; otherwise, the second parameter is defined as b2.

[0038] When the compressor frequency does not reach the first preset frequency, the third parameter is defined as a3; otherwise, the third parameter is defined as b3.

[0039] When the current operating time of the air conditioner has not reached the first preset time, the fourth parameter is defined as a4; otherwise, the fourth parameter is defined as b4.

[0040] When the sum of the first, second, third, and fourth parameters is not within the preset parameter range, it is determined that the compressor inlet or the evaporator outlet is not overheating.

[0041] In some embodiments of this application, it also includes:

[0042] The third temperature detection device, located on the outdoor heat exchanger, is used to detect the temperature of the outdoor coil.

[0043] In refrigeration mode, the temperature of the outer coil is defined as the condensing temperature, and the temperature of the inner coil is defined as the evaporating temperature.

[0044] The controller is configured to obtain the compressor's operating power and operating frequency and determine the refrigerant flow rate in the refrigerant circuit accordingly;

[0045] The condensing pressure is determined based on the condensing temperature, and the evaporating pressure is determined based on the evaporating temperature.

[0046] The condenser outlet temperature is calculated based on the condensing temperature, refrigerant flow rate, and operating frequency; the condenser outlet pressure is calculated based on the condensing pressure and refrigerant flow rate.

[0047] The enthalpy value of the condenser outlet is obtained by enthalpy calculation based on the outlet temperature and outlet pressure of the condenser. The outlet enthalpy value of the condenser is defined as the inlet enthalpy value of the evaporator.

[0048] The outlet temperature of the evaporator is calculated based on the evaporation temperature, refrigerant flow rate, and operating frequency; the outlet pressure of the evaporator is calculated based on the evaporation pressure and refrigerant flow rate.

[0049] The enthalpy value of the evaporator outlet is obtained by enthalpy calculation based on the outlet temperature and outlet pressure of the evaporator.

[0050] In some embodiments of this application, it further includes: a fourth temperature detection device, which is located at the outlet of the condenser and is used to detect the outlet temperature of the condenser;

[0051] And / or a fifth temperature detection device, located at the outlet of the evaporator, for detecting the outlet temperature of the evaporator.

[0052] The temperature values ​​detected by the fourth and fifth temperature detection devices are used to replace the corresponding calculated temperature values, and enthalpy calculation is performed.

[0053] This application also provides an air conditioner, including:

[0054] An indoor unit includes an indoor casing, within which an indoor heat exchanger is installed;

[0055] Outdoor unit, which includes outdoor casing;

[0056] The outdoor heat exchanger is located inside the outdoor shell. In heating mode, the outdoor heat exchanger acts as an evaporator and the indoor heat exchanger acts as a condenser. In cooling mode, the outdoor heat exchanger acts as a condenser and the indoor heat exchanger acts as an evaporator.

[0057] The compressor compartment is located inside the outdoor casing;

[0058] The compressor is located in the compressor compartment. The compressor includes an air inlet and an air outlet. The air inlet is equipped with a suction pipe, and the air outlet is equipped with a discharge pipe. The refrigerant temperature in the discharge pipe is higher than the refrigerant temperature in the suction pipe. The suction pipe is defined as the main circuit.

[0059] A bypass circuit is configured as a branch of the main circuit. The connection points between the bypass circuit and the main circuit are defined as the first connection point and the second connection point. The refrigerant in the main circuit flows into the bypass circuit through the first connection point, and the refrigerant in the bypass circuit then flows into the main circuit through the second connection point. The main circuit valve is located on the main circuit and between the first connection point and the second connection point, and is used to control whether the refrigerant passes through.

[0060] A bypass valve is located in the bypass circuit and between the first connection point and the second connection point. It is used to control the flow of refrigerant in the main circuit into the bypass circuit for heat exchange.

[0061] An electronically controlled heat dissipation unit is located on one side of the bypass circuit and is used to exchange heat with the refrigerant in the bypass circuit.

[0062] The controller is configured to open the main circuit valve during air conditioner operation, and when it is determined that the compressor inlet or the evaporator outlet is not overheated during the calculation of the air conditioner's coefficient of performance, it determines that heat compensation is required and opens the bypass valve, keeping the main circuit valve and the bypass valve open at the same time, so that the refrigerant flows through the main circuit and the bypass circuit at the same time, and the refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled heat dissipation unit.

[0063] The heated refrigerant merges with the refrigerant in the main circuit and flows together into the compressor's air inlet.

[0064] In some embodiments of this application, the controller is configured to close the main circuit valve if the compressor inlet is still not overheated after the main circuit valve and the bypass valve have been open for a period of time. All the refrigerant flowing through the first connection point flows into the bypass circuit, and the refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled heat dissipation unit.

[0065] After being heated, the refrigerant flows back to the main circuit through the second connection point and then into the compressor's air inlet.

[0066] In some embodiments of this application, the electronically controlled heat dissipation unit includes:

[0067] A radiator, comprising at least a heat sink and a heat dissipation base surface disposed on one side of the heat sink;

[0068] The bypass circuit should include at least:

[0069] Internal refrigerant flow path: The internal refrigerant flow path is set as a passage for refrigerant to flow, formed inside the heat dissipation base surface;

[0070] The external refrigerant flow path is connected to the internal refrigerant flow path and the main circuit, and is installed in close contact with the heat dissipation base surface.

[0071] In the above embodiments, the air conditioner includes an indoor unit and an outdoor unit. The indoor unit includes an indoor casing with an indoor heat exchanger inside, and the outdoor unit includes an outdoor casing with an outdoor heat exchanger inside. In heating mode, the outdoor heat exchanger is configured as an evaporator, and the indoor heat exchanger is configured as a condenser. In cooling mode, the outdoor heat exchanger is configured as a condenser, and the indoor heat exchanger is configured as an evaporator. The outdoor casing also includes a compressor compartment with a compressor installed inside. The compressor includes an inlet and an outlet. The inlet is equipped with a suction pipe, and the outlet is equipped with an exhaust pipe. The refrigerant temperature in the exhaust pipe is higher than the refrigerant temperature in the suction pipe. The compressor compartment also includes an internal circulation fan, which is specifically located between the suction pipe and the exhaust pipe to promote airflow circulation and heat exchange within the compressor compartment. The air conditioner also includes an indoor heat exchanger. The controller is configured to, during the calculation of the air conditioning coefficient of performance (COP), perform heat compensation when it is determined that the compressor inlet or the evaporator outlet is not overheated. During the heat compensation process, the internal circulation fan is turned on, and the airflow in the compressor compartment circulates internally. The air heated by the refrigerant in the exhaust pipe exchanges heat with the refrigerant in the suction pipe to compensate for the temperature of the refrigerant in the suction pipe. When the compressor suction temperature rises to the corresponding saturation temperature of the compressor suction pressure and / or the difference between the compressor suction temperature and the internal coil temperature reaches a first preset difference, it is determined that the compressor inlet or the evaporator outlet is overheated, and the internal circulation fan is turned off.

[0072] By turning on the internal circulation fan to circulate the air inside the compressor compartment, the convective heat transfer coefficient between the air temperature inside the compressor compartment and the high-temperature air is increased. This allows the high-temperature air to better heat the intake pipe of the compressor and reuse the heat dissipation of the compressor's exhaust pipe. This causes the intake position of the compressor or the outlet position of the evaporator to overheat, so that the enthalpy value can be calculated using temperature and pressure, and the air conditioning performance coefficient can be calculated online. Attached Figure Description

[0073] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0074] Figure 1 This is a schematic diagram of the structure of an air conditioner provided according to an exemplary embodiment;

[0075] Figure 2 This is a schematic diagram of the system structure of an air conditioner provided according to an exemplary embodiment;

[0076] Figure 3 This is the correspondence between the air conditioning refrigeration / heat pump cycle TS diagram and the refrigeration or heating process in the exemplary embodiments of this application;

[0077] Figure 4 This is a hardware configuration block diagram of an air conditioner proposed according to an exemplary embodiment;

[0078] Figure 5 This is a schematic diagram of the controller provided in this application according to an exemplary embodiment.

[0079] Figure 6 The calculation logic for the coefficient of performance of an air conditioner under cooling conditions, provided according to an exemplary embodiment;

[0080] Figure 7 This is yet another calculation logic for the coefficient of performance of an air conditioner under cooling conditions, provided according to an exemplary embodiment.

[0081] Figure 8 This is a flowchart illustrating the calculation of the coefficient of performance (COP) using the evaporator-side COP and the condenser-side COP through a coefficient compensation operation, provided according to an exemplary embodiment.

[0082] Figure 9 This is a flowchart illustrating how the heating performance coefficient is calculated using the evaporator-side heating performance coefficient and the condenser-side heating performance coefficient through coefficient compensation calculation according to an exemplary embodiment of this application.

[0083] Figure 10 This is a flowchart illustrating the process of determining whether preset performance coefficient calculation conditions are met according to an exemplary embodiment of this application.

[0084] Figure 11 This is another hardware configuration block diagram of an air conditioner proposed according to an exemplary embodiment;

[0085] Figure 12 This is one implementation of calculating performance coefficients in an exemplary embodiment of this application;

[0086] Figure 13 This is another hardware configuration block diagram of an air conditioner proposed according to an exemplary embodiment;

[0087] Figure 14 This is one implementation of calculating performance coefficients in an exemplary embodiment of this application;

[0088] Figure 15 The specific control logic of the air conditioner in the exemplary embodiments provided in this application;

[0089] Figure 16 This is a schematic diagram of the outdoor unit provided in an exemplary embodiment of this application;

[0090] Figure 17 This is a schematic diagram of the structure of the electronically controlled heat dissipation unit provided in an exemplary embodiment of this application. Figure 1 ;

[0091] Figure 18 This is a schematic diagram of the structure of the electronically controlled heat dissipation unit according to an exemplary embodiment of this application. Figure 2 ;

[0092] Figure 19 This is a schematic diagram of the structure of the electronically controlled heat dissipation unit according to an exemplary embodiment of this application. Figure 3 ;

[0093] Figure 20 This is a schematic diagram of the structure of the electronically controlled heat dissipation unit according to an exemplary embodiment of this application. Figure 4 ;

[0094] Figure 21 This is the control logic for heat compensation in the exemplary embodiments of this application;

[0095] Figure 22 This is another control logic for heat compensation in the exemplary embodiments of this application;

[0096] Figure 23 This is another control logic for heat compensation in the exemplary embodiments of this application;

[0097] In the above figures:

[0098] Bus 81; Memory 82; Processor 83; Communication interface 84; Controller 8;

[0099] Throttling device 3; Compressor 4; Condenser 2; Evaporator 1; Indoor unit 7; Outdoor unit 6;

[0100] First temperature detection device 91; Second temperature detection device 92; Third temperature detection device 95;

[0101] Exhaust temperature sensor 93; Fourth temperature detection device 94;

[0102] First pressure detection device 51; Second pressure detection device 52; Third pressure detection device 53;

[0103] Electronically controlled heat dissipation unit 10; radiator 101; heat sink 102; heat dissipation base surface 103;

[0104] External refrigerant flow path 104; internal refrigerant flow path 105′

[0105] Internal circulation fan 7979′; compressor compartment 74; main circuit 75; main circuit valve 76; bypass circuit 77; bypass valve 78′

[0106] Outdoor unit housing 71; First connecting pipe 710'; Second connecting pipe 711; External circulation fan 73'

[0107] Outdoor heat exchanger 72; first connection point 712′, second connection point 713. Detailed Implementation

[0108] The present invention will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0109] In the description of this invention, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0110] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

[0111] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0112] Reference Figure 1 The air conditioner in the picture includes: an indoor unit 7. Taking the indoor wall-mounted unit (shown in the picture) as an example, the indoor wall-mounted unit is usually installed on the indoor wall. Another example is the indoor floor-standing unit (not shown in the picture), which is also a type of indoor unit 7.

[0113] Outdoor unit 6, typically installed outdoors, is used for heat exchange within the indoor environment. Additionally, in Figure 1 In the diagram, outdoor unit 6 is located outdoors on the opposite side of indoor unit 7, separated by a wall, and is represented by a dashed line.

[0114] Reference Figure 2The diagram shows the air conditioner circuit structure, which includes a refrigerant circuit. By circulating the refrigerant in the refrigerant circuit, a vapor compression refrigeration cycle can be performed. Connecting pipes are used to connect the indoor unit 7 and the outdoor unit 6 to form a refrigerant circuit for refrigerant circulation.

[0115] In this application, the air conditioner performs its refrigeration cycle by using a refrigerant circuit consisting of a compressor 4, a condenser 2, a throttling device 3, and an evaporator 1. (See reference...) Figure 3 The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, supplying refrigerant to the conditioned and heat-exchanged air. The compressor 4 establishes the high and low pressure conditions required for refrigerant operation. Through heat exchange with outdoor air, it releases heat from the indoor air to the outdoor air (cooling mode) or absorbs heat from the outdoor air to replenish the indoor air (heating mode).

[0116] Compression process: Compressor 4 compresses the refrigerant gas under high temperature and high pressure and discharges the compressed refrigerant gas. Compressor 4 can be a variable capacity inverter compressor 4 with inverter-based speed control. The refrigerant gas discharged from compressor 4 flows into condenser 2.

[0117] Condensation process: Condenser 2 condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0118] Expansion process: The throttling device 3 causes the high-temperature, high-pressure liquid refrigerant condensed in the condenser 2 to expand into a low-pressure liquid refrigerant.

[0119] Evaporation process: Evaporator 1 evaporates the refrigerant that expands in the throttling device 3, and returns the refrigerant gas at a low temperature and low pressure to compressor 4. Evaporator 1 achieves a cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material to be cooled. Throughout the cycle, the air conditioner regulates the temperature of the indoor space.

[0120] The outdoor unit 6 of the air conditioner refers to the part of the refrigeration cycle that includes the compressor 4 and the outdoor heat exchanger 72. The indoor unit 7 of the air conditioner includes the indoor heat exchanger, and the throttling device 3 can be provided in the indoor unit 7 or the outdoor unit 6.

[0121] The indoor heat exchanger and the outdoor heat exchanger 72 are used as either condenser 2 or evaporator 1. When the indoor heat exchanger is used as condenser 2, the air conditioner is used as a heater in heating mode; when the indoor heat exchanger is used as evaporator 1, the air conditioner is used as a cooler in cooling mode.

[0122] Figure 4 This is a hardware configuration block diagram of an air conditioner according to an exemplary embodiment of this application. (Refer to...) Figure 4The air conditioner also includes one or more of the following: a first temperature detection device 91, a second temperature detection device 92, a third temperature detection device 95, a fourth temperature detection device 94, a first pressure detection device 51, and a controller 8. Furthermore, the first temperature detection device 91, the second temperature detection device 92, the third temperature detection device 95, the fourth temperature detection device 94, the fifth temperature detection device, and the first pressure detection device 51 are all connected to the controller 8.

[0123] In some embodiments of this example, the first temperature detection device 91 is installed at the indoor heat exchanger to detect the temperature of the inner coil of the indoor unit 7 and send the detected inner coil temperature to the controller 8.

[0124] In some embodiments of this example, the second temperature detection device 92 is installed at the air inlet of the compressor 4 to detect the suction temperature of the compressor 4 and send the suction temperature of the compressor 4 to the controller 8. It should be noted that in some scenarios, the suction temperature of the compressor 4 is defined as the exhaust temperature of the evaporator 1.

[0125] In some embodiments of this example, the third temperature detection device 95 is installed on the outdoor heat exchanger 72 to detect the temperature of the outdoor unit 6's external coil and send the detected external coil temperature to the controller 8.

[0126] It can be seen that, under cooling conditions, the third temperature detection device 95 is a condensing temperature detection device, and the external coil temperature is the condensing temperature; the first temperature detection device 91 is an evaporating temperature detection device, and the internal coil temperature is the evaporating temperature. Under heating conditions, the third temperature detection device 95 is an evaporating temperature detection device, and the external coil temperature is the evaporating temperature; the first temperature detection device 91 is a condensing temperature detection device, and the internal coil temperature is the condensing temperature.

[0127] In some embodiments of this example, a first pressure detection device 5151 is installed at the air inlet of the compressor 4. The first pressure detection device 5151 is used to detect the air inlet pressure of the compressor 4 and send it to the controller 8. The air inlet pressure of the compressor 4 is defined as the air outlet pressure of the evaporator 1.

[0128] Those skilled in the art will understand that Figure 4 The hardware structure shown does not constitute a limitation on the air conditioner. The air conditioner may include more or fewer components than shown, or combine certain components, or have different component arrangements.

[0129] In some embodiments of this example, the controller 8 can be used to operate the compressor 4, the throttling device 3, the fan, etc., so that the air conditioner can perform various predetermined functions.

[0130] In some embodiments of this example, the controller 8 can obtain the operating current value of the compressor 4 at each moment, and obtain the operating frequency f and operating power of the compressor 4 based on the operating current value.

[0131] It is known that the operating frequency f of compressor 4 can be calculated from the operating current value or by detecting the speed of compressor 4. The operating power of compressor 4 can also be detected by a power meter installed in the circuit system of compressor 4.

[0132] In the embodiments shown in this application, controller 8 refers to a device that can generate operation control signals according to instruction operation codes and timing signals to instruct the air conditioner to execute control commands.

[0133] This application embodiment also provides a hardware structure diagram of the controller 8, such as... Figure 5 As shown, the controller 8 includes a processor 83, and optionally, a memory 82 and a communication interface 84 connected to the processor 83. The processor 83, memory 82, and communication interface 84 are connected via a bus 81.

[0134] Processor 83 can be a central processing unit (CPU), a general-purpose processor (NP), a network processor (NP), a digital signal processor (DSP), a microprocessor (MCU), a microcontroller (MCU), a programmable logic device (PLD), or any combination thereof. Processor 83 can also be any other device with processing capabilities, such as a circuit, device, or software module. Processor 83 can also include multiple CPUs, and processor 83 can be a single-core (single-CPU) processor 83 or a multi-core (multi-CPU) processor 83. Here, processor 83 can refer to one or more devices, circuits, or processing cores used for processing data (e.g., computer program instructions).

[0135] The memory 82 can be a read-only memory (ROM) or other type of static storage device capable of storing static information and instructions, a random access memory (RAM) or other type of dynamic storage device capable of storing 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 universal optical discs, Blu-ray discs, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium capable of carrying or storing desired program code in the form of instructions or data structures and accessible by a computer. This application embodiment does not impose any limitations on this. The memory 82 can exist independently or be integrated with the processor 83. The memory 82 may contain computer program code. The processor 83 is used to execute the computer program code stored in the memory 82, thereby implementing the control method for the multi-split air conditioning system provided in this application embodiment.

[0136] The communication interface 84 can be used to communicate with other devices or communication networks (such as Ethernet, radio access network (RAN), wireless local area networks (WLAN), etc.). The communication interface 84 can be a module, circuit, transceiver, or any device capable of communication.

[0137] Bus 81 can be a Peripheral Component Interconnect (PCI) bus 81 or an Extended Industry Standard Architecture (EISA) bus 81, etc. Bus 81 can be divided into address bus 81, data bus 81, control bus 81, etc. For ease of representation, Figure 11 The bus is represented by only one thick line, but this does not mean that there is only one bus 81 or one type of bus 81.

[0138] This application enables the calculation of the coefficient of performance (COP) of an air conditioner even when hardware sensors are insufficient.

[0139] In some embodiments of this example, the coefficient of performance under refrigeration conditions will be used as an example for explanation.

[0140] This application requires at least the condensation temperature and evaporation temperature to obtain the necessary amount of data for calculating the coefficient of performance.

[0141] Reference Figure 6 The controller 8 is configured to: in the cooling condition, first determine whether the current operating conditions of the air conditioner meet the preset performance coefficient calculation conditions (step S1);

[0142] If it is determined in step S1 that the current operating conditions of the air conditioner meet the preset performance coefficient calculation conditions, then step S2 is executed to obtain the operating power, operating frequency, condensing temperature and evaporating temperature of the compressor 4.

[0143] Then, step S31 is executed to determine the refrigerant flow rate in the refrigerant circuit based on the operating power and operating frequency of compressor 4.

[0144] The condensation pressure is determined based on the condensation temperature (step S32); the evaporation pressure is determined based on the evaporation temperature (step S33);

[0145] After completing steps S31, S32, and S33, proceed to step S41; calculate the outlet temperature of condenser 2 based on the condensing temperature, refrigerant flow rate, and operating frequency, and proceed to step S42; calculate the outlet pressure of condenser 2 based on the condensing pressure and refrigerant flow rate.

[0146] After executing steps S41 and S42, execute step S51. Calculate the outlet enthalpy of condenser 2 based on its outlet temperature and pressure. It can be seen that the outlet enthalpy of condenser 2 is defined as the inlet enthalpy of evaporator 1.

[0147] After completing steps S31, S32, and S33, proceed to step S43 to calculate the outlet temperature of evaporator 1 based on the evaporation temperature, refrigerant flow rate, and operating frequency. In step S44, calculate the outlet pressure of evaporator 1 based on the evaporation pressure and refrigerant flow rate.

[0148] After completing steps S43 and S44, step S52 is executed, and the outlet enthalpy of evaporator 1 is obtained by enthalpy calculation based on the outlet temperature and outlet pressure of evaporator 1.

[0149] After completing steps S52 and S51, step S6 is executed. The heat exchange of evaporator 1 is obtained based on the inlet enthalpy, outlet enthalpy, and refrigerant flow rate of evaporator 1. Then, step S7 is executed. The refrigeration performance coefficient EERe of evaporator 1 is obtained by calculation based on the heat exchange of evaporator 1 and the operating frequency of compressor 4. The refrigeration performance coefficient EERe of evaporator 1 is used as the refrigeration performance coefficient EER.

[0150] Determine whether the coefficient of performance (EER) is less than the preset coefficient of performance (step S8)

[0151] In step S8, if the coefficient of performance (COP) is not less than the preset COP, then step S91 is executed, the calculation result EER is output and displayed, and the user is informed that the air conditioner is currently in a good operating state.

[0152] In step S8, if the cooling performance coefficient is less than the preset cooling performance coefficient, then step S92 is executed to prompt the user that the current air conditioner is not operating in the optimal state, and to adjust the working state of each component of the air conditioner according to the settings.

[0153] It should be noted that it is possible for those skilled in the art to calculate the enthalpy value at a certain location using the temperature and pressure at that location, which is existing technology and will not be elaborated upon in this application.

[0154] If it is determined in step S1 that the current operating conditions of the air conditioner do not meet the preset performance coefficient calculation conditions, then step S3 is executed, prompting that heat compensation is required.

[0155] It should be noted that in step S31, the relationship between the operating power W and the operating frequency f of compressor 4 and the refrigerant flow rate mr in the refrigerant circuit is mr = f1(W, f), where f1 is a function of the performance curve of compressor 4 or a correlation fitted based on the performance curve of compressor 4.

[0156] Understandably, the existing operating power, operating frequency, and refrigerant flow data can also be used to train the model. The operating power W and operating frequency f of compressor 4 can be input into the model, and the refrigerant flow can be output.

[0157] Through the above steps, the real-time heat exchange and compressor power of the air conditioner under cooling conditions can be calculated solely based on the evaporation temperature detected by the evaporation temperature detection device and the condensation temperature detected by the condensation temperature detection device. This allows for the calculation of the coefficient of performance (COP) under cooling conditions. While providing data support for adjusting the air conditioner's operating status, it also reduces the hardware requirements of the air conditioner itself. It can meet the COP calculation needs of the vast majority of air conditioners. Based on the COP, the current operating status and energy-saving level of the air conditioner can be determined, which can be used to guide the online monitoring, performance prediction, and energy-saving operation of the air conditioner, thereby improving the long-term operating characteristics of the air conditioner.

[0158] Meanwhile, this application can be carried out without the aid of an enthalpy difference laboratory, which also reduces the difficulty of calculating performance parameters.

[0159] Furthermore, since latent heat is generated during the dehumidification process of an air conditioner, the heat exchange capacity on the air side is usually inaccurate. The real-time power of the heat exchanger can be obtained through the heat exchange capacity on the refrigerant side. The heat exchange capacity on the refrigerant side can be calculated using the heat exchange calculation method described in this application.

[0160] Latent heat refers to the heat absorbed or released by a substance when it changes from one phase to another under isothermal and isobaric conditions. This is one of the characteristics of a substance when it transforms between solid, liquid, and gas phases, as well as between different solid phases.

[0161] In some embodiments, the air conditioner is also equipped with an exhaust temperature sensor 93, which is located at the outlet of the compressor 4 to detect the exhaust temperature of the compressor 4.

[0162] In some embodiments of this example, the coefficient of performance (EER) can also be calculated by calculating the coefficient of performance (EERc) on the condenser side 2. Specifically, refer to... Figure 7 The discharge pressure is estimated based on the condensing pressure and refrigerant flow rate (step S701). Then, the discharge enthalpy of compressor 4 is obtained by enthalpy calculation based on discharge temperature and discharge pressure (step S702). The discharge enthalpy of compressor 4 can be defined as the inlet enthalpy of condenser 2.

[0163] Then, based on the inlet enthalpy, outlet enthalpy, and refrigerant flow rate of the refrigerant circuit of condenser 2, the heat exchanger on the condenser 2 side is obtained (step S703). The heat exchanger on the condenser 2 side is combined with the operating power of compressor 4 to obtain the refrigeration performance coefficient EERc on the condenser 2 side through performance coefficient calculation (step S704). The refrigeration performance coefficient EERc on the condenser 2 side is used as the refrigeration performance coefficient EER, and the operation of each component of the air conditioner is controlled according to the comparison result between the refrigeration performance coefficient EER and the preset refrigeration coefficient (step S705).

[0164] Through the above steps, the coefficient of performance can be calculated based solely on the exhaust temperature detected by the exhaust temperature sensor 93 and the condensing temperature detected by the condensing temperature detection device. This provides data support for adjusting the air conditioner's operating status and reduces the hardware requirements of the air conditioner itself, thus satisfying the coefficient of performance calculation for the vast majority of air conditioners.

[0165] It is known that when hardware conditions are insufficient, the cooling performance coefficient of the air conditioner under cooling conditions can be obtained by relying solely on the cooling performance coefficient of the evaporator 1 side or the cooling performance coefficient of the condenser 2 side. When hardware conditions are sufficient, the cooling performance coefficient EER can be obtained by weighted calculation based on the cooling performance parameters of the evaporator 1 side and the cooling performance coefficient of the condenser 2 side.

[0166] Specifically, in this embodiment, the coefficient of performance (COP) EERc on the condenser 2 side and the COPEERe on the evaporator 1 side can be used for coefficient compensation calculation to complete the calculation of the COP EER. (Refer to...) Figure 8 This is a flowchart illustrating the calculation of the coefficient of performance (COP) using the refrigeration performance parameters on the evaporator 1 side and the refrigeration performance coefficient on the condenser 2 side through coefficient compensation calculation.

[0167] Determine the ratio of the absolute value of the difference between the coefficient of performance (COP) of evaporator 1 (EERe) and the coefficient of performance (COP) of condenser 2 (EERc) to the COP of condenser 2 (EERc). Has the lower limit of the first preset deviation value θ1 been reached (step S801)?

[0168] In step S801, if the lower limit of the first preset deviation value θ1 is reached, then step S802 is executed, and the coefficient of performance EER is set to the coefficient of performance EERc of the condenser 2 side.

[0169] In step S801, if the lower limit of the first preset deviation value θ1 is not reached, then step S803 is executed, and EER = αEERe + (1-α)EERc is set, where α∈(0,1).

[0170] By using the above settings, the calculation method of EER will be adjusted based on the relationship between the calculated evaporator 1 side refrigeration performance parameters and the condenser 2 side refrigeration performance coefficient and the value below the preset deviation, which can improve the accuracy of the refrigeration performance coefficient.

[0171] In some embodiments of this example, the following describes the calculation of the coefficient of performance (COP) under heating conditions. The COP can be calculated by taking the COP of the condenser 2 side as the COP, taking the COP of the evaporator 1 side as the COP alone, or by weighting the COP of the COP of the condenser 2 side and the COP of the evaporator 1 side.

[0172] The following explanation uses the heating performance coefficient of the condenser side 2 as an example.

[0173] First, the heat exchange rate of condenser 2 is obtained based on the inlet enthalpy, outlet enthalpy, and refrigerant flow rate of condenser 2. Then, the heat exchange rate of condenser 2 is combined with the operating power of compressor 4 and the coefficient of performance is calculated to obtain the heating performance coefficient COPc of condenser 2. Here, the heating performance coefficient COPc of condenser 2 is taken as the heating performance coefficient COP.

[0174] Finally, the operating status of each component of the air conditioner can be controlled based on the comparison between the coefficient of performance (COP) and the preset coefficient of performance (COP).

[0175] The following explanation uses the heating performance coefficient of evaporator 1 as an example.

[0176] First, the heat exchange rate of evaporator 1 is obtained based on the inlet enthalpy, outlet enthalpy, and refrigerant flow rate of evaporator 1. Then, the heat exchange rate of evaporator 1 is combined with the operating power of compressor 4 and the coefficient of performance is calculated to obtain the heating performance coefficient COPe of evaporator 1. The heating performance coefficient COPe of evaporator 1 is used as the heating performance coefficient COP. Finally, the operation of each component of the air conditioner is controlled based on the comparison result between the heating performance coefficient COP and the preset heating coefficient.

[0177] Through the above steps, the real-time heat exchange and compressor power of the air conditioner under heating conditions can be calculated solely based on the evaporation temperature detected by the evaporation temperature detection device and the condensation temperature detected by the condensation temperature detection device. This allows for the calculation of the coefficient of performance (COP) under heating conditions. While providing data support for adjusting the air conditioner's operating status, this method also reduces the hardware requirements of the air conditioner itself. It can meet the COP calculation needs of the vast majority of air conditioners. Based on the COP, the current operating status and energy-saving level of the air conditioner can be determined, which can be used to guide online monitoring, performance prediction, and energy-saving operation guidance, thereby improving the long-term operating characteristics of the air conditioner.

[0178] Meanwhile, this application can be carried out without the aid of an enthalpy difference laboratory, which also reduces the difficulty of calculating performance parameters.

[0179] The following explanation uses the heating performance coefficient obtained by weighting the heating performance coefficients of the condenser side 2 and the evaporator side 1 as an example.

[0180] Reference Figure 9 This is a flowchart illustrating the calculation of the coefficient of performance (COP) using the COP of the evaporator 1 side and the COP of the condenser 2 side through coefficient compensation calculation.

[0181] Determine the ratio of the absolute value of the difference between the coefficient of performance (COPc) of evaporator 1 and the coefficient of performance (COPc) of condenser 2 to the coefficient of performance (COPc) of condenser 2. Whether the lower limit of the second preset deviation value θ2 has been reached (step S901);

[0182] In step S801, if the lower limit of the second preset deviation value θ2 is reached, then step S902 is executed, and the heating performance coefficient COP is set to COPc of the condenser 2 side.

[0183] In step S801, if the lower limit of the second preset deviation value θ2 is not reached, then step S903 is executed, and COP=αCOPe+(1-α)COPc is set, where α∈(0,1).

[0184] By using the above settings, the calculation method of COP will be adjusted according to the relationship between the calculated heating performance coefficient of evaporator 1 and the heating performance coefficient of condenser 2 and the value below the second preset deviation value, which can improve the accuracy of the heating performance coefficient.

[0185] Reference Figure 10 This illustrates one implementation method for calculating performance coefficients in this embodiment.

[0186] Predetermine the functions or formulas f1, f2, f3, f4, f5, f6, f7, f8, f9, and f10, and write them into the controller 8 corresponding to the indoor unit 7 or the outdoor unit 6 (step S111);

[0187] Obtain the evaporation temperature T1, condensation temperature T2, and discharge temperature T3 of compressor 4 detected by the temperature sensor (step S112);

[0188] Extract the operating power W and operating frequency f of compressor 4, and calculate the refrigerant flow rate mr in the current refrigerant circuit according to the compressor 4 performance curve formula mr=f1(W,f) (step S113);

[0189] Extract the evaporation temperature T1, refrigerant flow rate mr, and operating frequency f, and calculate the outlet temperature T11 of evaporator 1 according to the formula T11=f2(T1,mr,f); extract the condensation temperature T2, refrigerant flow rate mr, and operating frequency f, and calculate the outlet temperature T22 of condenser 2 according to the formula T22=f4(T2,mr,f) (step S114);

[0190] Based on the correspondence between the saturation temperature and saturation pressure corresponding to the refrigerant type, the evaporation pressure p1 = f3(T1) and the condensation pressure p2 = f5(T2) are determined. The outlet pressure p3 of the compressor 4 can be approximated to p2 (step S115).

[0191] It should be noted that P3 and P2 can be approximated because the pressure drop of condenser 2 is smaller. It is also known that the exhaust pressure can be estimated using the condensing pressure and refrigerant flow rate.

[0192] Based on the correspondence between evaporation pressure p1, refrigerant flow rate mr and outlet pressure P11 of evaporator 1, p11 = f9(p1, mr); based on the correspondence between condensation pressure p2, refrigerant flow rate mr and outlet pressure p22 of condenser 2, estimate p22 = f10(p2, mr) (step S1110).

[0193] Calculate the outlet enthalpy h1 = f6(T11, p11, 1) of evaporator 1, the outlet enthalpy h3 = f7(T3, P3, 1) of compressor 4, and the outlet enthalpy h2 = f8(T22, P22, 0) of condenser 2 (step S116).

[0194] It should be noted that the above steps are performed on the premise that the refrigerant dryness at the outlet of evaporator 1 and compressor 4 is 1, and the refrigerant dryness at the outlet of condenser 2 is 0.

[0195] Calculate the enthalpy difference Δh21 = h2 - hi on the evaporator 1 side and / or the enthalpy difference Δh32 = h3 - h2 on the condenser 2 side (step S117);

[0196] Understandably, referring to Figure 3 In this application, the process within the throttling device 3 is considered to be an isenthalpic process.

[0197] The heat exchange on the evaporator side is Qe = Δh21 × mr, or the heat exchange on the condenser side is Qc = Δh32 × mr or Qc = Δh21 × mr + W (step S118);

[0198] Calculate the coefficient of performance (COP) under cooling conditions or the coefficient of performance (COP) under heating conditions (step S119).

[0199] In some embodiments of this example, during the actual operation of the air conditioner, target performance coefficients (including at least preset cooling coefficients and preset heating coefficients) can be set for the air conditioner under different states. For example, the preset cooling coefficient EER0 under cooling conditions or the preset heating coefficient COP0 under heating conditions is related to the compressor frequency f, fan speed G, indoor ambient temperature T inner ring, outdoor ambient temperature T outer ring, indoor set temperature T set, and indoor ambient humidity. Inner ring, indoor set humidity Set one or more related functions among several parameters, and in actual operation, determine the influence relationship of each parameter on EER0 or COP0, identify the parameter with the greatest influence, and ask the user whether to perform energy-saving operation management of the air conditioner and start the corresponding control method.

[0200] In some embodiments of this application, reference is made to Figure 11 This embodiment also includes a fourth temperature detection device 9494 that is communicatively connected to the controller 8. The fourth temperature detection device 9494 is installed at the outlet of the condenser 2 and is used to detect the outlet temperature of the condenser 2 and send this temperature to the controller 8. The suction temperature of the compressor 4 is defined as the outlet temperature of the evaporator 1. The temperature values ​​detected by the fourth temperature detection device 9494 and the second temperature detection device 9295 are used to replace the corresponding calculated temperature values, and enthalpy is calculated to obtain the coefficient of performance (COP) of the air conditioner.

[0201] In this embodiment, precise refrigerant temperature data is measured to determine the more accurate thermodynamic state of the refrigerant at the inlet of compressor 4 or the outlet of condenser 2. Other procedures are the same as in embodiment 1.

[0202] It should be noted that the temperature sensor added in this embodiment at the outlet of condenser 2 (also known as before the throttling device 3) measures the outlet temperature T22 of condenser 2. If only one of the temperature sensors at the inlet of compressor 4 or the outlet of condenser 2 (also known as before the throttling device 3) is provided, the corresponding method can be applied to the temperature parameter without a sensor. The control method described in this embodiment and other embodiments can realize the function of online performance calculation of air conditioning and should also be included within the protection scope of this invention.

[0203] Reference Figure 12 This illustrates one implementation method for calculating performance coefficients in this embodiment.

[0204] Predetermine the functions or formulas f1, f2, f3, f4, f5, f6, f7, f8, f9, and f10, and write them into the controller 8 corresponding to the indoor unit 7 or outdoor unit 6 (step S141); obtain the evaporation temperature T1, condensation temperature T2, compressor 4 exhaust temperature T3, evaporator 1 outlet temperature T11, and condenser 2 outlet temperature T22 detected by the temperature sensor (step S142); extract the operating power W and operating frequency f of compressor 4, and calculate the refrigerant flow rate mr in the current refrigerant circuit according to the compressor 4 performance curve formula mr = f1(W, f) (step S143);

[0205] Based on the correspondence between the saturation temperature and saturation pressure corresponding to the refrigerant type, the evaporation pressure p1 = f3(T1) and the condensation pressure p2 = f5(T2) are determined. The outlet pressure p3 of the compressor 4 can be approximated to p2 (step S145).

[0206] It should be noted that P3 and P2 can be approximated because the pressure drop of condenser 2 is smaller. It is also known that the exhaust pressure can be estimated using the condensing pressure and refrigerant flow rate.

[0207] Based on the correspondence between evaporation pressure p1, refrigerant flow rate mr and outlet pressure P11 of evaporator 1, p11 = f9(p1, mr); based on the correspondence between condensation pressure p2, refrigerant flow rate mr and outlet pressure p22 of condenser 2, estimate p22 = f10(p2, mr) (step S1410).

[0208] Calculate the outlet enthalpy h1 = f6(T11, p11, 1) of evaporator 1, the outlet enthalpy h3 = f7(T3, P3, 1) of compressor 4, and the outlet enthalpy h2 = f8(T22, P22, 0) of condenser 2 (step S146).

[0209] It should be noted that the above steps are performed on the premise that the refrigerant dryness at the outlet of evaporator 1 and compressor 4 is 1, and the refrigerant dryness at the outlet of condenser 2 is 0.

[0210] Calculate the enthalpy difference Δh21 = h2 - h1 on the evaporator 1 side and / or the enthalpy difference Δh32 = h3 - h2 on the condenser 2 side (step S147);

[0211] It is understood that in this application, the process within the throttling device 3 is considered to be an isenthalpic process.

[0212] The heat exchange on the evaporator side is Qe = Δh21 × mr, or the heat exchange on the condenser side is Qc = Δh32 × mr or Qc = Δh21 × mr + W (step S148);

[0213] Calculate the coefficient of performance (COP) under cooling or heating conditions (step S149).

[0214] In some embodiments of this application, reference is made to Figure 13 This embodiment also includes a second pressure detection device 5252 and / or a third pressure detection device 53 that are connected to the controller 8 for storage and communication, for detecting the pressure value at the set position and sending the pressure value to the controller 8.

[0215] In some embodiments of this example, the second pressure detection device 5252 is installed at the outlet of the compressor 4. The second pressure detection device 5252 is used to detect the outlet pressure of the compressor 4 and send it to the controller 8. The outlet pressure of the compressor 4 is defined as the inlet pressure of the condenser 2.

[0216] In some embodiments of this example, the third pressure detection device 5353 is installed at the outlet of the condenser 2. The third pressure detection device 5353 is used to detect the outlet pressure of the condenser 2 and send it to the controller 8.

[0217] The corresponding calculated pressure values ​​are replaced by the outlet pressure of the evaporator 1 detected by the first pressure detection device 5151, the inlet pressure of the condenser 2 detected by the second pressure detection device 5252, and the outlet pressure of the condenser 2 detected by the third pressure detection device 5353, and corresponding calculations are performed to obtain the performance coefficient of the air conditioner.

[0218] In this embodiment, accurate refrigerant pressure data is measured to determine the more precise thermodynamic state of the refrigerant at the inlet of compressor 4 or the outlet of condenser 2, while other processes remain unchanged.

[0219] It should be noted that this embodiment adds a pressure detection device at the inlet of compressor 4 (also known as the outlet of evaporator 1) or / and a pressure detection device at the outlet of condenser 2 (also known as before throttling device 3) or / and a pressure detection device at the discharge position of compressor 4 to measure the inlet pressure p11 of compressor 4 or / and the outlet pressure p22 of condenser 2 or / and the refrigerant discharge pressure p3, respectively. If only one of the above three pressure detection devices is added, in this case, the pressure parameters without sensors can be handled according to the method corresponding to the technical solution of embodiment 1. The technical solution of this embodiment and the control method described in embodiments 1 and 2 can realize the function of online performance calculation of air conditioner, and should also be included within the protection scope of this invention.

[0220] Reference Figure 14 This section explains the workflow for calculating performance coefficients in this embodiment.

[0221] Predetermine the functions or formulas f1, f2, f3, f4, f5, f6, f7, f8, f9, and f10, and write them into the controller 8 corresponding to the indoor unit 7 or outdoor unit 6 (step S161).

[0222] Obtain the evaporation temperature T1, condensation temperature T2, discharge temperature T3 of compressor 4, outlet temperature T11 of evaporator 1, outlet temperature T22 of condenser 2, outlet pressure p11 of evaporator 1 and outlet pressure p22 of condenser 2 detected by the temperature sensor (step S162).

[0223] Extract the operating power W and operating frequency f of compressor 4, and calculate the refrigerant flow rate mr in the current refrigerant circuit according to the compressor 4 performance curve formula mr=f1(W,f) (step S163);

[0224] Based on the correspondence between the saturation temperature and saturation pressure corresponding to the refrigerant type, the condensing pressure p2 = f5(T2), so the outlet pressure p3 of compressor 4 can be approximated to p2 (step S165).

[0225] It should be noted that P3 and P2 can be approximated because the pressure drop of condenser 2 is smaller. It is also known that the exhaust pressure can be estimated using the condensing pressure and refrigerant flow rate.

[0226] Calculate the outlet enthalpy h1 = f6(T11, p11, 1) of evaporator 1, the outlet enthalpy h3 = f7(T3, P3, 1) of compressor 4, and the outlet enthalpy h2 = f8(T22, P22, 0) of condenser 2 (step S166).

[0227] It should be noted that the above steps are performed on the premise that the refrigerant dryness at the outlet of evaporator 1 and compressor 4 is 1, and the refrigerant dryness at the outlet of condenser 2 is 0.

[0228] Calculate the enthalpy difference Δh21 = h2 - h1 on the evaporator 1 side and / or the enthalpy difference Δh32 = h3 - h2 on the condenser 2 side (step S167);

[0229] It is understood that in this application, the process within the throttling device 3 is considered to be an isenthalpic process.

[0230] The heat exchange on the evaporator side is Qe = Δh21 × mr, or the heat exchange on the condenser side is Qc = Δh32 × mr or Qc = Δh21 × mr + W (step S168);

[0231] Calculate the coefficient of performance (COP) under cooling or heating conditions (step S169).

[0232] In some embodiments of this example, the above-described method for calculating the performance coefficient requires that the air conditioner's operating conditions meet preset conditions before it can be performed. These preset conditions include determining whether the air conditioner's current operating time, the compressor 4's suction temperature, the internal coil temperature, and the compressor 4's operating frequency meet corresponding conditions.

[0233] In some implementations, when the suction temperature of compressor 4 does not exceed the saturation temperature corresponding to the suction pressure of compressor 4, the first parameter is defined as a1; otherwise, the first parameter is defined as b1.

[0234] When the difference between the suction temperature of compressor 4 and the temperature of the inner coil does not reach the first preset temperature difference, the second parameter is defined as a2; otherwise, the second parameter is defined as b2.

[0235] When the compressor's 4-frequency frequency does not reach the first preset frequency, the third parameter is defined as a3; otherwise, the third parameter is defined as b3. When the current operating time of the air conditioner does not reach the first preset time, the fourth parameter is defined as a4; otherwise, the fourth parameter is defined as b4.

[0236] When the sum of the first, second, third, and fourth parameters is not within the preset parameter range, it is determined that the air inlet of compressor 4 or the air outlet of evaporator 1 is not overheating.

[0237] It should be noted that when the outlet of evaporator 1 is superheated (i.e., refrigerant dryness x = 1), the outlet enthalpy h1 of evaporator 1 is a function of the outlet temperature and outlet pressure of evaporator 1 (or the inlet temperature and inlet pressure of compressor 4); when the outlet of condenser 2 is subcooled (i.e., refrigerant dryness = 0), the outlet enthalpy h2 of condenser 2 is a function of the outlet temperature of condenser 2 and the outlet pressure of evaporator 1. It can be understood that even when the controller 8 has insufficient processing power or when it is inconvenient to obtain the outlet pressure of evaporator 1, the outlet enthalpy h2 of condenser 2 can be obtained using the outlet temperature and condensation temperature of condenser 2.

[0238] In actual operation of air conditioners, under low operating frequency or low load conditions, the evaporator 1 outlet may not be overheated (refrigerant dryness fraction less than 1) and the condenser 2 outlet may not be overcooled (refrigerant dryness fraction greater than 0). Also, during the start-up phase of the air conditioner, the air conditioner may not have reached a steady state. Both of these situations can cause deviations or even distortions in the online performance coefficient calculation.

[0239] Therefore, in order to ensure the accuracy of the overall calculation results, it is necessary to judge the operating status of the air conditioner (including operating time and operating parameters) before deciding whether to perform performance coefficient calculation.

[0240] Specifically, when the suction temperature of compressor 4 does not exceed the saturation temperature corresponding to the suction pressure of compressor 4, the first parameter is defined as a1; otherwise, the first parameter is defined as b1′.

[0241] When the difference between the suction temperature of compressor 4 and the temperature of the inner coil does not reach the first preset temperature difference, the second parameter is defined as a2; otherwise, the second parameter is defined as b2.

[0242] When the frequency of the compressor's 4-frequency unit does not reach the first preset frequency, the third parameter is defined as a3; otherwise, the third parameter is defined as b3.

[0243] When the current operating time of the air conditioner has not reached the first preset time, the fourth parameter is defined as a4; otherwise, the fourth parameter is defined as b4.

[0244] Sum all the obtained parameters to get the parameter and c.

[0245] Determine whether the parameters and c are within the preset coefficient condition range [c_down, c_up]. If the parameters are within the preset coefficient condition range, calculate the performance coefficient; otherwise, prompt the user that heat compensation is required.

[0246] Reference Figure 15 This section explains the specific control logic of the air conditioner in this embodiment.

[0247] After the air conditioner is turned on, record the running time of the air conditioner (step S121);

[0248] Determine whether the user has enabled the online performance coefficient calculation function (step S122);

[0249] In step S122, if the user enables the online performance coefficient calculation function, then step S124 is executed to enter the preset conditions and obtain the parameters; then step S126 is executed to determine whether the parameters are within the preset coefficient condition range [c_down,c_up].

[0250] In step S126, if the parameters are within the range of preset coefficient conditions, then step S127 is executed to calculate the real-time performance coefficients EEEre (evaporator 1 side cooling performance coefficient), EERc (condenser 2 side cooling performance coefficient) or COPe (evaporator 1 side heating performance coefficient), COPc (evaporator 1 side cooling performance coefficient); and respectively set the first preset deviation value θ1 acceptable under cooling conditions and the second preset deviation value θ2 acceptable under heating conditions (step S128);

[0251] Determine whether the current operating condition is cooling condition (step S129);

[0252] In step S129, if the current operating condition is determined to be a cooling condition, then step S1210 is executed to determine the ratio of the absolute value of the difference between the coefficient of performance (COP) ERe on the evaporator 1 side and the COP EERc on the condenser 2 side to the COP EERc on the condenser 2 side. Whether the lower limit of the first preset deviation value θ1 has been reached;

[0253] In step S1210, if the lower limit of the first preset deviation value θ1 is reached, then step S1212 is executed, and the coefficient of performance EER is set to the coefficient of performance EERc of the condenser 2 side.

[0254] In step S1210, if the lower limit of the first preset deviation value θ1 is not reached, then step S1213 is executed, and EER=αEERe+(1-α)EERc is set, where α∈(0,1).

[0255] Then execute step S1214 to output and display the calculation result EER or COP;

[0256] In step S129, if it is determined that the current operating condition is not a cooling condition, then step S1211 is executed to determine the ratio of the absolute value of the difference between the heating performance coefficient COPc of evaporator 1 and the heating performance coefficient COPc of condenser 2 to the heating performance coefficient COPc of condenser 2. Whether the lower limit of the second preset deviation value θ2 has been reached;

[0257] In step S1211, if the lower limit of the second preset deviation value θ2 is reached, then step S1215 is executed, and the heating performance coefficient COP is set to COPc of the condenser 2 side.

[0258] In step S1211, if the lower limit of the second preset deviation value θ2 is not reached, then step S1216 is executed, letting COP = αCOPe + (1-)COPc, where α∈(0,1). Then step S1214 is executed;

[0259] In step S126, if the parameters are not within the preset coefficient range, then step S125 is executed to perform heat compensation.

[0260] If the user has not enabled the online performance coefficient calculation function in step S122, then proceed to step S121.

[0261] In the above steps S124, the following steps are executed sequentially, simultaneously, or according to a preset rule: determining whether the suction temperature of compressor 4 exceeds the saturation temperature corresponding to the suction pressure of compressor 4; determining whether the difference between the suction temperature of compressor 4 and the temperature of the inner coil reaches the first preset temperature difference; determining whether the frequency of compressor 4 reaches the first preset frequency; determining whether the current operating time of the air conditioner reaches the first preset time; and after the judgment, the corresponding result parameters are obtained and then accumulated to obtain the sum c.

[0262] It should be noted that the above steps only consider the air conditioner's cooling and heating modes. If other modes exist in actual applications, mode judgment can be added before calculation.

[0263] It should be noted that the calculation logic for the inlet enthalpy of condenser 2, the outlet enthalpy of condenser 2, the inlet enthalpy of evaporator 1, and the outlet enthalpy of evaporator 1 under heating conditions is the same as that under cooling conditions, and will not be repeated here.

[0264] The real-time performance coefficient of the air conditioner can be calculated using the above method. However, in actual calculations, if the operating parameters of the air conditioner do not meet the preset conditions, such as the outlet of evaporator 1 not being overheated or the outlet of condenser 2 not being overcooled, the refrigerant dryness x will be between 0 and 1. The determination of the enthalpy value requires three variables: temperature, pressure, and refrigerant dryness.

[0265] Since the dryness of the refrigerant cannot be directly measured by the sensor, it is impossible to determine the enthalpy values ​​of the refrigerant inlet and outlet of the evaporator 1 or the heat exchange on the refrigerant side. Consequently, the coefficient of performance of the air conditioner cannot be obtained through the above calculation method.

[0266] To address the aforementioned issues, in some embodiments of this invention, a heat compensation method is proposed to ensure that the suction position of the compressor 4 does not overheat. This method is used to correct the overheating of the air conditioner by means of the technical solution in this application, so that the online performance coefficient of the air conditioner can be calculated.

[0267] It should be noted that during actual operation, air conditioners generate excess waste heat, such as in the compressor compartment 74 and the electronically controlled heat dissipation unit 10, but usually there is no excess cooling capacity that can be recovered and utilized. Therefore, this application only provides a correction method for the evaporator 1 under non-overheating conditions. Therefore, since there is no method to compensate for the cooling capacity of the condenser 2 outlet that is not undercooled, the calculation of the heat exchange capacity Qc of the condenser 2 under heating conditions needs to be obtained using the formula Qc=Qe+W, and then the COP is calculated using formula (2).

[0268] The following is a description of the principle of non-overheat compensation in this application.

[0269] Reference Figure 3 The evaporation process of evaporator 1 extends from point D to point A3. During the heat exchange section from point D to point A2 (excluding A2), the refrigerant is in a gas-liquid two-phase state. The enthalpy in this process is a ternary function of refrigerant dryness, temperature, and pressure. Pressure and / or temperature can be obtained through corresponding pressure and / or temperature sensors, but refrigerant dryness cannot be directly measured or calculated using conventional sensors. Therefore, the refrigerant at the outlet of evaporator 1 must reach saturation (A2) or a superheated vapor state (point A2 (excluding A2) to A3). In this state, the refrigerant dryness is 1, and the enthalpy is a binary function of temperature and pressure. Only then can the effective heat exchange within evaporator 1 be calculated according to the following method.

[0270] Qe=Δhe·G=(h1-h2')·mr

[0271] Furthermore, for compressor 4, the outlet of evaporator 1, which is also the inlet of condenser 2, must be single-phase refrigerant vapor; otherwise, liquid slugging may occur in compressor 4, affecting its service life or operating performance. Therefore, considering both the safety of air conditioning operation and the usability of performance calculation methods, it is necessary to use effective means to make the outlet of evaporator 1 a superheated state A3, or at least a saturated state A2, and not a non-superheated state A1.

[0272] To prevent overheating at the outlet of evaporator 1, heat compensation was proposed for that location or the inlet of compressor 4.

[0273] Reference Figure 16The outdoor unit 6 is connected to the throttling device 3, and the throttling device 3 is connected to the indoor unit 7 through the second connecting pipe 711. The compressor 4 and the indoor unit 7 are connected through the first connecting pipe 710. The outdoor unit 6 includes an outdoor housing 71, and a compressor compartment 74 is defined within the outdoor housing 71.

[0274] The outdoor housing 71 houses an outdoor heat exchanger 72, an outdoor fan assembly, and various sensors for detecting outdoor parameters. The outdoor fan assembly includes an external circulation fan 73 and a support bracket. Its main function is to drive the outdoor air to circulate externally, achieving heat exchange between the air and the outdoor heat exchanger 72.

[0275] The compressor compartment 74 contains a compressor 4, an internal circulation fan 79, a controller 8, a throttling device 3, an intake pipe located at the intake port of the compressor 4, an exhaust pipe located at the outlet port of the compressor 4, a temperature sensor, and a pressure detection device. The compressor compartment 74 is configured as a closed space to protect the controller 8, the compressor 4, the throttling device 3, etc. from damage and interference from the external environment.

[0276] The intake pipe, compressor 4, exhaust pipe, and throttling device 3 all contain refrigerant. Due to the refrigeration cycle principle, the refrigerant temperature in the exhaust pipe is higher than that in the intake pipe.

[0277] To improve the working efficiency of the internal circulation fan 79, the internal circulation fan 79 is placed between the intake pipe and the exhaust pipe to accelerate the airflow in the compressor compartment 74, thereby promoting airflow circulation and heat exchange within the compressor compartment 74.

[0278] In some embodiments of this application, a heat compensation method using a fan internal circulation method is proposed. Specifically, the controller 8 is configured to perform heat compensation when it is determined that the outlet of the evaporator 1 or the inlet of the compressor 4 is not overheated during the calculation of the cooling performance coefficient of the air conditioner.

[0279] During the heat compensation process, the internal circulation fan 79 is turned on, and the airflow in the compressor compartment 74 circulates internally. The air heated by the refrigerant in the exhaust pipe exchanges heat with the refrigerant in the intake pipe to compensate for the temperature of the refrigerant in the intake pipe.

[0280] When the suction temperature of compressor 4 rises to the saturation temperature corresponding to the suction pressure of compressor 4 and / or the difference between the suction temperature of compressor 4 and the temperature of the inner coil exceeds the first preset difference, it is determined that the air inlet of compressor 4 or the air outlet of evaporator 1 is overheated. At this time, the coefficient of performance can be calculated normally, the internal circulation fan 79 is turned off, and the internal circulation compensation of the fan is stopped.

[0281] Through the above steps

[0282] In some implementations, when the air inlet of compressor 4 or the air outlet of evaporator 1 is overheated, the coefficient of performance (COP) of the air conditioner is calculated based on the operating conditions of the air conditioner.

[0283] When the air conditioner is in cooling mode, the heat exchange of the evaporator 1 side is obtained based on the enthalpy difference between the inlet and outlet of the evaporator 1 and the refrigerant flow rate. Then, the heat exchange of the evaporator 1 side and the operating power of the compressor 4 are logically calculated to obtain the coefficient of performance (EERe).

[0284] When the air conditioner is in heating mode, the heat exchange on the evaporator 1 side is first determined based on the heat exchange on the evaporator 1 side and the operating power of the compressor 4. Then, the heat exchange on the condenser 2 side is obtained by performing logical calculations on the heat exchange on the condenser 2 side and the operating power of the compressor 4 to obtain the heating performance coefficient COPe.

[0285] In some embodiments, the outdoor housing 71 also includes an electronically controlled heat dissipation unit 10. The intake pipe of the compressor 4 is defined as the main circuit 75, and a branch circuit 77 of the main circuit 75 is provided. The connection point between the main circuit 75 and the bypass circuit 77 is defined as the first connection point 712 and the second connection point 713. The refrigerant in the main circuit 75 flows out of the evaporator 1 and flows into the bypass circuit 77 through the first connection point 712. The refrigerant in the bypass circuit 77 will flow back into the main circuit 75 through the second connection point 713.

[0286] It also includes a main circuit valve 76, which is installed on the main circuit 75 and located between the first connection point 712 and the second connection point 713. It is used to control whether the refrigerant flows through a portion of the main circuit 75, where the portion of the main circuit 75 is between the first connection point 712 and the second connection point 713 on the main circuit 75.

[0287] It also includes a bypass valve 78, which is located on the bypass circuit 77 and between the first connection point 712 and the second connection point 713, and is used to control whether the refrigerant in the main circuit 75 flows into the bypass circuit 77 for heat exchange. Specifically, the bypass valve 78 is located on the side of the bypass circuit 77 closer to the first connection point 712, shortening the distance between the bypass valve 78 and the first connection point 712 to reduce refrigerant loss.

[0288] The aforementioned electronically controlled heat dissipation unit 10 is disposed on one side of the bypass circuit 77, and the electronically controlled heat dissipation unit 10 is used to exchange heat with the refrigerant in the bypass circuit 77.

[0289] In some implementations, the controller 8 is configured to open the main circuit valve 76 when the air conditioner is in normal operating condition, so that the refrigerant in the refrigeration system can normally enter the air inlet of the compressor 4 from the evaporator 1.

[0290] Meanwhile, the controller 8 is also configured to determine that when the air inlet of the compressor 4 is still not overheated after the internal circulation fan 79 has been working for a period of time, it is necessary to increase heat compensation.

[0291] Specifically, the bypass valve 78 is opened, and the main circuit valve 76 and the bypass valve 78 are kept open at the same time, so that the refrigerant flowing out of the evaporator 1 flows through the main circuit 75 and the bypass circuit 77 at the same time. The refrigerant flowing through the bypass circuit 77 exchanges heat with the electronically controlled heat dissipation unit 10. The heated refrigerant flows through the second connection point 713 and merges with the refrigerant in the main circuit 75, and then flows into the air inlet of the compressor 4.

[0292] In some embodiments of this example, the controller 8 is configured to determine that if the intake port of the compressor 4 is still not overheated after the main circuit valve 76 and the bypass valve 78 have been open for a period of time, it is necessary to strengthen heat compensation at this time.

[0293] Open the bypass valve 78 and close the main circuit valve 76. All the refrigerant flowing through the first connection point 712 flows into the bypass circuit 77. The refrigerant flowing through the bypass circuit 77 exchanges heat with the electronically controlled heat dissipation unit 10. After being heated, the refrigerant flows back to the main circuit 75 through the second connection point 713 and then flows into the air inlet of the compressor 4.

[0294] Through the above steps, the electronically controlled heat dissipation compensation method is divided into the basic heat compensation method and the enhanced heat compensation method. In the basic heat compensation method, when heat compensation is required, the controller 8 sends out cooling and opens the bypass valve 78. Main circuit valve 76 and bypass valve 78 are kept open at the same time. When the refrigerant flows through the main circuit 75 and the bypass circuit 77 at the same time, the refrigerant flowing through the bypass circuit 77 can absorb the heat of the electronically controlled heat dissipation unit 10. After the refrigerant is further heated, it merges with the refrigerant in the main circuit 75 and then flows into the air inlet of the compressor 4.

[0295] In the enhanced heat compensation method, when heat compensation is required, the controller 8 issues a command to first open the bypass valve 78 and then close the main circuit valve 76, allowing all refrigerant to flow into the bypass circuit 77 to absorb the heat from the electronically controlled heat dissipation unit 10. At this time, due to the increased refrigerant flow into the bypass circuit 77, the convective heat transfer coefficient inside the pipe is enhanced, thus increasing the effective heat absorption from the electronically controlled heat dissipation unit 10, which can ensure the superheated state of the evaporator 1 outlet.

[0296] In some implementations of this embodiment, reference is made to Figure 17-20 The electronically controlled heat dissipation unit 10 includes a heat sink 101, which further includes at least a heat sink 102 and a heat dissipation base surface 103 disposed on one side of the heat sink 102.

[0297] The bypass circuit 77 includes at least an internal refrigerant flow path 105 and an external refrigerant flow path 104. The internal refrigerant flow path 105 is configured as a passage for refrigerant to flow through the heat dissipation base 103. The external refrigerant flow path 104 is connected to the internal refrigerant flow path 105 and the main circuit 75, and the external refrigerant flow path 104 is fitted to the heat dissipation base 103 to facilitate the flow of refrigerant in the internal refrigerant flow path 105 and the external refrigerant flow path 104.

[0298] Specifically, the external refrigerant flow path 104 can be configured into two sections, namely a first external refrigerant flow path 104 and a second external refrigerant flow path 104, which are respectively located at both ends of the internal refrigerant flow path 105. The side of the first external refrigerant flow path 104 away from the internal refrigerant flow path 105 is connected to the first connection point 712, and the side of the second external refrigerant flow path 104 away from the internal refrigerant flow path 105 is connected to the second connection point 713. The refrigerant flowing out from the evaporator 1 enters the first external refrigerant flow path 104 and then enters the internal refrigerant flow path 105, and then flows through the second external refrigerant flow path 104 to merge into the main circuit 75.

[0299] It should be noted that since the external refrigerant flow path 104 and the heat dissipation base 103 are made of completely separate materials, it is necessary to ensure that the external refrigerant flow path 104 and the heat dissipation base 103 are tightly connected during installation to avoid refrigerant leakage.

[0300] In some embodiments, the external refrigerant flow path 104 can be a copper pipe, and the radiator 101 can be an aluminum radiator 101. In the technical solution of this application, the internal refrigerant flow path 105 is a refrigerant flow path processed inside the heat dissipation base 103. For example, the refrigerant flow path is processed inside the aluminum radiator 101, and then the heat dissipation base 103 is welded to the copper pipe at the inlet and outlet. Although this method increases the risk of refrigerant heat dissipation at the inlet and outlet, it enhances the heat transfer efficiency inside the radiator 101.

[0301] Compared to related technologies that process the surface of the aluminum radiator 101 into a shape that can be embedded with copper tubes and then tightly combine the two, this method solves the problem of the copper tube wall blocking the heat dissipation base 103 and the refrigerant, resulting in high thermal resistance and poor heat exchange performance.

[0302] Reference Figure 21 This explains the control logic for heat compensation in this application.

[0303] The user executes the air conditioner online performance calculation function (step S201);

[0304] Determine whether the suction temperature T11 is less than or equal to the refrigerant saturation temperature corresponding to the evaporation pressure p1 (step S2021);

[0305] Determine whether the difference between the intake temperature T11 and the inner plate temperature T1 is less than the first preset temperature difference (step S2022)

[0306] Determine whether the frequency f of compressor 4 is lower than the first preset frequency f1 (step S2023);

[0307] Determine whether the power-on time or current operating time is less than the first preset time (step S2024);

[0308] In step S2021, if yes, then step S2025 is executed, with the first parameter being a1; if no, then step S2026 is executed, with the first parameter being b1.

[0309] In step S2022, if yes, then step S2027 is executed, and the second parameter is a2; if no, then step S2028 is executed, and the second parameter is b2.

[0310] In step S2023, if yes, then proceed to step S2029, where the third parameter is a3; if no, then proceed to step S20210, where the third parameter is b3.

[0311] In step S2024, if yes, then step S20211 is executed, and the fourth parameter is a4; if no, then step S20212 is executed, and the fourth parameter is b4.

[0312] Sum the first, second, third, and fourth parameters and denote the sum as c (step S203);

[0313] Determine whether c is within the preset parameter range [c_down, c_up] (step S204);

[0314] In step S204, if c is within the preset parameter range, then step S206 is executed to perform the performance parameter calculation normally.

[0315] In step S204, if c is not within the preset parameter range, then step S205 is executed, and it is determined that the outlet of evaporator 1 is not overheated and heat compensation is required.

[0316] Turn on the internal circulation fan 79 (step S207);

[0317] Determine whether the internal circulation fan 79 has been turned on for the corresponding preset time (step S208);

[0318] In step S208, if the corresponding preset time is reached, then step S209 is executed to recalculate C and determine whether the preset parameter range is met.

[0319] In step S209, if c meets the preset parameter range, then step S210 is executed to calculate the performance coefficient according to the working conditions.

[0320] In step S209, if c does not meet the preset parameter range, then step S211 is executed to open the bypass valve 78 and keep the main circuit valve 76 and the bypass valve 78 open.

[0321] Determine whether the working time of the main circuit valve 76 and the bypass valve 78 has reached the corresponding preset time (step S212);

[0322] In step S212, if the corresponding preset time is reached, then step S213 is executed to calculate c and determine whether it meets the preset parameter range; in step S213, if c meets the preset parameter range, then step S210 is executed to calculate the performance coefficient according to the working conditions.

[0323] In step S213, if c does not meet the preset parameter range, then step S214 is executed to close the main circuit valve 76.

[0324] Determine whether the current working time has reached the corresponding preset time (step S215);

[0325] In step S215, if the corresponding preset time is reached, then step S216 is executed to calculate c and determine whether it meets the preset parameter range; if in step S216, c does not meet the preset parameter range, then step S217 is executed to prompt the user that performance calculation cannot be performed at present.

[0326] If c satisfies the preset parameter range in step S216, then step S210 is executed.

[0327] In step S215, if the corresponding preset time has not been reached, then step S215 is executed.

[0328] In step S212, if the corresponding preset time has not been reached, then step S212 is executed.

[0329] In step S208, if the corresponding preset time has not been reached, then step S208 is executed.

[0330] With the above settings, heat compensation is first performed using the fan internal circulation valve. When the preset conditions are not met, the electronically controlled heat dissipation compensation device is activated to minimize interference with the refrigeration system and avoid the activation of the heat compensation device from affecting indoor temperature fluctuations.

[0331] In some embodiments of this application, the controller 8 is configured to perform heat compensation when it is determined that the outlet of the evaporator 1 or the inlet of the compressor 4 is not overheated during the calculation of the cooling performance coefficient of the air conditioner.

[0332] During the heat compensation process, the bypass valve 78 is opened, and the main circuit valve 76 and the bypass valve 78 are kept open at the same time, so that the refrigerant flowing out of the evaporator 1 flows through the main circuit 75 and the bypass circuit 77 at the same time. The refrigerant flowing through the bypass circuit 77 exchanges heat with the electronically controlled heat dissipation unit 10. The heated refrigerant flows through the second connection point 713 and merges with the refrigerant in the main circuit 75, and then flows into the air inlet of the compressor 4.

[0333] In some embodiments of this example, the controller 8 is configured to determine that if the intake port of the compressor 4 is still not overheated after the main circuit valve 76 and the bypass valve 78 have been open for a period of time, it is necessary to strengthen heat compensation at this time.

[0334] Open the bypass valve 78 and close the main circuit valve 76. All the refrigerant flowing through the first connection point 712 flows into the bypass circuit 77. The refrigerant flowing through the bypass circuit 77 exchanges heat with the electronically controlled heat dissipation unit 10. After being heated, the refrigerant flows back to the main circuit 75 through the second connection point 713 and then flows into the air inlet of the compressor 4.

[0335] By adjusting the operating status of the main circuit valve 76 and the bypass valve 78, the flow direction of the refrigerant is controlled, thereby determining whether to perform heat compensation on the refrigerant so that the outlet of the evaporator 1 is overheated.

[0336] Reference Figure 22 This explains another control logic for heat compensation in this application.

[0337] The user executes the air conditioner online performance calculation function (step S301);

[0338] Determine whether the suction temperature T11 is less than or equal to the refrigerant saturation temperature corresponding to the evaporation pressure p1 (step S3021);

[0339] Determine whether the difference between the intake temperature T11 and the inner plate temperature T1 is less than the first preset temperature difference (step S3022)

[0340] Determine whether the frequency f of compressor 4 is lower than the first preset frequency f1 (step S3023);

[0341] Determine whether the power-on time or current operating time is less than the first preset time (step S3024);

[0342] In step S3021, if yes, then step S3025 is executed, and the first parameter is a1; if no, then step S3026 is executed, and the first parameter is b1.

[0343] In step S3022, if yes, then step S3027 is executed, and the second parameter is a2; if no, then step S3028 is executed, and the second parameter is b2.

[0344] In step S3023, if yes, then step S3029 is executed, and the third parameter is a3; if no, then step S30210 is executed, and the third parameter is b3.

[0345] In step S3024, if yes, then step S30211 is executed, and the fourth parameter is a4; if no, then step S30212 is executed, and the fourth parameter is b4.

[0346] Sum the first, second, third, and fourth parameters and denote the sum as c (step S303);

[0347] Determine whether c is within the preset parameter range [c_down, c_up] (step S304);

[0348] In step S304, if c is within the preset parameter range, then step S306 is executed to perform the performance parameter calculation normally.

[0349] In step S304, if c is not within the preset parameter range, then step S305 is executed, determining that the outlet of evaporator 1 is not overheating and heat compensation is required.

[0350] Execute step S311, open bypass valve 78, and keep main circuit valve 76 and bypass valve 78 open.

[0351] Determine whether the working time of the main circuit valve 76 and the bypass valve 78 has reached the corresponding preset time (step S312);

[0352] In step S312, if the corresponding preset time is reached, then step S313 is executed to calculate c and determine whether it meets the preset parameter range; in step S313, if c meets the preset parameter range, then step S310 is executed to calculate the performance coefficient according to the working conditions.

[0353] In step S313, if c does not meet the preset parameter range, then step S314 is executed to close the main circuit valve 76.

[0354] Determine whether the current working time has reached the corresponding preset time (step S5);

[0355] In step S315, if the corresponding preset time is reached, then step S316 is executed to calculate c and determine whether it meets the preset parameter range; in step S316, if c does not meet the preset parameter range, then step S317 is executed to prompt the user that performance calculation cannot be performed at present.

[0356] If c satisfies the preset parameter range in step S316, then step S310 is executed.

[0357] In step S315, if the corresponding preset time has not been reached, then step S315 is executed.

[0358] In step S312, if the corresponding preset time has not been reached, then step S312 is executed.

[0359] Of course, it is known that air conditioners can also use the fan internal circulation method for heat compensation.

[0360] Reference Figure 23 This explains another control logic for heat compensation in this application.

[0361] The user executes the air conditioner online performance calculation function (step S401);

[0362] Determine whether the suction temperature T11 is less than or equal to the refrigerant saturation temperature corresponding to the evaporation pressure p1 (step S4021);

[0363] Determine whether the difference between the intake temperature T11 and the inner plate temperature T1 is less than the first preset temperature difference (step S4022)

[0364] Determine whether the frequency f of compressor 4 is lower than the first preset frequency f1 (step S4023);

[0365] Determine whether the power-on time or current operating time is less than the first preset time (step S4024);

[0366] In step S4021, if yes, then step S4025 is executed, and the first parameter is a1; if no, then step S4026 is executed, and the first parameter is b1.

[0367] In step S4022, if yes, then step S4027 is executed, and the second parameter is a2; if no, then step S4028 is executed, and the second parameter is b2.

[0368] In step S4023, if yes, then step S4029 is executed, and the third parameter is a3; if no, then step S40210 is executed, and the third parameter is b3.

[0369] In step S4024, if yes, then step S40211 is executed, and the fourth parameter is a4; if no, then step S40212 is executed, and the fourth parameter is b4.

[0370] Sum the first parameter, the second parameter, the third parameter and the fourth parameter, and denote the sum as c (step S403);

[0371] Determine whether c is within the preset parameter range [c_down, c_up] (step S404);

[0372] In step S404, if c is within the preset parameter range, then step S406 is executed to perform the performance parameter calculation normally.

[0373] In step S404, if c is not within the preset parameter range, then step S405 is executed, determining that the outlet of evaporator 1 is not overheating and heat compensation is required.

[0374] Turn on the internal circulation fan 79 (step S407);

[0375] Determine whether the internal circulation fan 79 has been turned on for the corresponding preset time (step S408);

[0376] In step S408, if the corresponding preset time is reached, then step S409 is executed to recalculate C and determine whether the preset parameter range is met.

[0377] In step S409, if c meets the preset parameter range, then step S410 is executed to calculate the performance coefficient according to the working conditions.

[0378] In step S409, if c does not meet the preset parameter range, then step S411 is executed, prompting the user that performance calculation cannot be performed at present;

[0379] In step S408, if the corresponding preset time has not been reached, then step S408 is executed.

[0380] It should be noted that the fan circulation method and the electronically controlled heat dissipation method in this application can be used individually or in combination. The activation conditions of each method can be selected according to the control logic designed as needed. Furthermore, considering that the heat compensation provided by the fan and electronically controlled heat dissipation components is limited and will not have a significant impact on the overall online performance coefficient calculation process, the impact of heat compensation on the calculation deviation of the performance coefficient is not considered separately, and it is assumed that the online performance coefficient before and after compensation is approximately equal.

[0381] This application proposes an air conditioner that, when the outlet of evaporator 1 is not overheated, can heat the outlet of evaporator 1 to a certain extent by setting a heat compensation device, ensuring heat compensation under non-overheating conditions, so as to meet the applicable conditions of online performance calculation method.

[0382] Meanwhile, this application can obtain the online operating performance technology of air conditioners without relying on an enthalpy difference laboratory by calculating the enthalpy difference, refrigerant flow rate and compressor power on the refrigerant side, thus enabling energy-saving operation and optimized design of air conditioners.

[0383] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. An air conditioner, characterized in that, include: An indoor unit includes an indoor casing, within which an indoor heat exchanger is disposed; Outdoor unit, which includes outdoor casing; An outdoor heat exchanger is located inside the outdoor casing. In heating mode, the outdoor heat exchanger is an evaporator and the indoor heat exchanger is a condenser. In cooling mode, the outdoor heat exchanger is a condenser and the indoor heat exchanger is an evaporator. The compressor compartment is located inside the outdoor casing; A compressor is located inside the compressor compartment. The compressor includes an air inlet and an air outlet. The air inlet is equipped with an air suction pipe, and the air outlet is equipped with an air discharge pipe. The refrigerant temperature in the discharge pipe is higher than the refrigerant temperature in the air suction pipe. An internal circulation fan is located inside the compressor compartment and between the intake pipe and the exhaust pipe, and is used to promote airflow circulation and heat exchange within the compressor compartment. The first temperature detection device is located at the indoor heat exchanger and is used to detect the temperature of the inner coil. The second temperature detection device is located at the air inlet of the compressor and is used to detect the compressor's suction temperature. A pressure detection device is installed at the air inlet of the compressor to detect the compressor's suction pressure. The controller is configured to perform heat compensation when it is determined that the compressor inlet or the evaporator outlet is not overheated during the calculation of the air conditioner's coefficient of performance. During the heat compensation process, the internal circulation fan is turned on, and the airflow in the compressor compartment circulates internally. The air heated by the refrigerant in the exhaust pipe exchanges heat with the refrigerant in the intake pipe to compensate for the temperature of the refrigerant in the intake pipe. When the compressor suction temperature rises to the corresponding saturation temperature of the compressor suction pressure and / or the difference between the compressor suction temperature and the internal coil temperature exceeds a first preset difference, it is determined that the compressor inlet or the evaporator outlet is overheated and the internal circulation fan is turned off. The air intake pipe is defined as the main circuit, and the air conditioner further includes: A bypass circuit is configured as a branch of the main circuit. The connection points between the bypass circuit and the main circuit are defined as a first connection point and a second connection point. The refrigerant in the main circuit flows into the bypass circuit through the first connection point, and the refrigerant in the bypass circuit then flows into the main circuit through the second connection point. A main circuit valve is provided on the main circuit and located between the first connection point and the second connection point, and is used to control whether the refrigerant flows through a portion of the main circuit; A bypass valve is provided in the bypass circuit and located between the first connection point and the second connection point, for controlling the refrigerant in the main circuit to flow into the bypass circuit for heat exchange; An electronically controlled heat dissipation unit is located on one side of the bypass circuit, and the electronically controlled heat dissipation unit is used to exchange heat with the refrigerant in the bypass circuit; The controller is configured to open the main circuit valve during air conditioner operation, and if the compressor inlet or evaporator outlet is still not overheated after the internal circulation fan has been working for a period of time, it is determined that heat compensation needs to be increased. Open the bypass valve, keeping the main circuit valve and the bypass valve open at the same time. The refrigerant flows through both the main circuit and the bypass circuit simultaneously. The refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled heat dissipation unit. The heated refrigerant merges with the refrigerant in the main circuit and then flows together into the compressor's air inlet.

2. The air conditioner according to claim 1, characterized in that, When the air inlet of the compressor or the air outlet of the evaporator is overheated, the cooling performance coefficient of the air conditioner is calculated according to the operating conditions of the air conditioner. When the air conditioner is in cooling mode, the heat exchange on the evaporator side is obtained based on the enthalpy difference between the inlet and outlet of the evaporator and the refrigerant flow rate. Then, the heat exchange on the evaporator side and the operating power of the compressor are logically calculated to obtain the coefficient of performance (EERe). When the air conditioner is operating in heating mode, the condenser-side heat exchange is obtained based on the evaporator-side heat exchange and the compressor's operating power. Then, the heating performance coefficient COPe is obtained by performing logical operations on the condenser-side heat exchange and the compressor's operating power.

3. The air conditioner according to claim 2, characterized in that, The controller is configured to determine that if the compressor inlet or evaporator outlet is still not overheated after the main circuit valve and the bypass valve have been open for a period of time, heat compensation needs to be strengthened. Open the bypass valve and close the main circuit valve. All the refrigerant flowing through the first connection point flows into the bypass circuit. The refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled heat dissipation unit. After being heated, the refrigerant flows back to the main circuit through the second connection point and then flows into the compressor's air inlet.

4. The air conditioner according to any one of claims 1-3, characterized in that, When the compressor suction temperature does not exceed the saturation temperature corresponding to the compressor suction pressure, the first parameter is defined as a1; otherwise, the first parameter is defined as b1. When the difference between the compressor suction temperature and the inner coil temperature does not reach the first preset temperature difference, the second parameter is defined as a2; otherwise, the second parameter is defined as b2. When the frequency of the compressor does not reach the first preset frequency, the third parameter is defined as a3; otherwise, the third parameter is defined as b3. When the current operating time of the air conditioner has not reached the first preset time, the fourth parameter is defined as a4; otherwise, the fourth parameter is defined as b4. When the sum of the first parameter, the second parameter, the third parameter, and the fourth parameter is not within the preset parameter range, it is determined that the compressor inlet or the evaporator outlet is not overheating.

5. The air conditioner according to claim 2, characterized in that, Also includes: A third temperature detection device is installed in the outdoor heat exchanger and is used to detect the temperature of the outdoor coil. Under refrigeration conditions, the temperature of the outer coil is defined as the condensing temperature, and the temperature of the inner coil is defined as the evaporating temperature. The controller is configured to obtain the operating power and operating frequency of the compressor and determine the refrigerant flow rate in the refrigerant circuit accordingly. The condensation pressure is determined based on the condensation temperature, and the evaporation pressure is determined based on the evaporation temperature. The outlet temperature of the condenser is calculated based on the condensing temperature, refrigerant flow rate, and operating frequency; the outlet pressure of the condenser is calculated based on the condensing pressure and refrigerant flow rate. The outlet enthalpy of the condenser is obtained by enthalpy calculation based on the outlet temperature and outlet pressure of the condenser, and the outlet enthalpy of the condenser is defined as the inlet enthalpy of the evaporator. The outlet temperature of the evaporator is calculated based on the evaporation temperature, refrigerant flow rate, and operating frequency; the outlet pressure of the evaporator is calculated based on the evaporation pressure and refrigerant flow rate. The outlet enthalpy of the evaporator is obtained by enthalpy calculation based on the outlet temperature and outlet pressure of the evaporator.

6. The air conditioner according to claim 5, characterized in that, Also includes: It also includes a fourth temperature detection device, which is located at the outlet of the condenser and is used to detect the outlet temperature of the condenser; The temperature values ​​detected by the fourth temperature detection device and the second temperature detection device are used to replace the corresponding calculated temperature values, and enthalpy calculation is performed.

7. The air conditioner according to claim 6, characterized in that, The electronically controlled heat dissipation unit includes: A radiator, the radiator comprising at least a heat sink and a heat dissipation base surface disposed on one side of the heat sink; The bypass circuit includes at least: An internal refrigerant flow path is configured as a passageway for refrigerant flow formed inside the heat dissipation base surface. An external refrigerant flow path is connected to the internal refrigerant flow path and the main circuit, and the external refrigerant flow path is fitted to the heat dissipation base surface.

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