Air conditioner

Abstract

The air conditioner comprises an indoor unit and an outdoor unit, the indoor unit comprises an indoor shell internally provided with an indoor heat exchanger, and the outdoor unit comprises an outdoor shell internally provided with an outdoor heat exchanger; a compressor bin internally provided with a compressor is further arranged in the outdoor shell, the compressor comprises an air inlet and an air outlet, the air inlet is provided with an air suction pipe in a matched mode, the air outlet is provided with an exhaust pipe in a matched mode, and the temperature of refrigerants in the exhaust pipe is higher than that of refrigerants in the air suction pipe. In the process of calculating the refrigeration performance coefficient of the air conditioner, when it is judged that an air outlet of an evaporator is not overheated, heat compensation needs to be carried out, in the heat compensation process, an inner circulation fan 79 is started, airflow in a compressor bin is internally circulated, air heated by a refrigerant of an exhaust pipe exchanges heat with a refrigerant in an air suction pipe, and the air outlet of the evaporator is not overheated. The temperature of a refrigerant in the air suction pipe is compensated; and when the air outlet of the evaporator is overheated, the internal circulation fan is closed.

Description

Technical Field

[0001] The present invention relates to the technical field of household appliances, and in particular to an air conditioner. Background Art

[0002] At present, the 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, the outdoor heat exchanger, the compressor and the throttling device together constitute a refrigeration system. Generally speaking, in order to increase the cooling capacity of the system and ensure the normal operation of the system, it is usually necessary to obtain various performance coefficients during the operation of the air conditioner.

[0003] The calculation of the online coefficient of performance of an air conditioner requires the simultaneous acquisition of the compressor power and the heat exchange capacity on the refrigerant side or the air side. However, during the actual operation of the air conditioner in the user's home, there is no device to simultaneously measure the heat exchange capacity and the compressor power. Therefore, accurate measurement values ​​cannot be obtained, which is not conducive to the energy-saving operation, performance prediction or guidance of optimization design of the air conditioner.

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

[0005] Due to the latent heat caused by the air conditioner during the dehumidification process, the heat exchange capacity on the air side is usually inaccurate. At this time, 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 is an unknown quantity slightly less than 1, the enthalpy value cannot be calculated and the heat exchange capacity on the refrigerant side cannot be obtained, which affects the use scenario of the air conditioner performance coefficient calculation method.

[0006] In the related art, the heat exchange of the evaporator and condenser is calculated by fitting the compressor flow, 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 air not being overheated or the condenser outlet not being overcooled, resulting in the inability to calculate the performance coefficient in some scenarios.

[0007] In view of this, this application is filed. Summary of the invention

[0008] The present application provides an air conditioner, which, when the outlet of the evaporator is not overheated, performs internal circulation through the air flow in the compressor compartment, and uses the air heated by the refrigerant at the outlet of the compressor to compensate for the temperature of the refrigerant in the intake pipe, so as to heat the outlet of the evaporator to a certain extent, ensuring heat compensation under non-overheating conditions, so as to meet the use conditions of online performance calculation.

[0009] To this end, the present application is intended to provide an air conditioner, comprising:

[0010] The indoor unit comprises an indoor shell in which an indoor heat exchanger is arranged;

[0011] An outdoor unit, comprising an outdoor housing;

[0012] The outdoor heat exchanger is arranged in the outdoor housing. In the heating condition, the outdoor heat exchanger is an evaporator and the indoor heat exchanger is a condenser. In the cooling condition, the outdoor heat exchanger is a condenser and the indoor heat exchanger is an evaporator.

[0013] A compressor compartment, which is disposed in the outdoor housing;

[0014] A compressor is arranged in the compressor compartment, the compressor comprises an air inlet and an air outlet, the air inlet is provided with an air suction pipe, the air outlet is provided with an exhaust pipe, and the refrigerant temperature in the exhaust pipe is higher than the refrigerant temperature in the air suction pipe;

[0015] An internal circulation fan is arranged in the compressor compartment and between the air intake pipe and the air discharge pipe, and is used to promote air circulation and heat exchange in the compressor compartment;

[0016] A first temperature detection device is provided at the indoor heat exchanger and is used to detect the temperature of the inner coil;

[0017] A second temperature detection device, which is arranged at the air inlet of the compressor and is used to detect the suction temperature of the compressor;

[0018] A pressure detection device, which is arranged at the air inlet of the compressor and is used to detect the suction pressure of the compressor;

[0019] The controller is configured to, during the process of calculating the coefficient of performance of the air conditioner, perform heat compensation when it is determined that the air inlet of the compressor is not overheated or the air outlet of the evaporator is not overheated;

[0020] During the heat compensation process, the internal circulation fan is turned on, the airflow in the compressor compartment is internally circulated, and 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 saturation temperature corresponding to the compressor suction pressure and / or the difference between the compressor suction temperature and the inner coil temperature exceeds a first preset difference, it is determined that the compressor air inlet or the evaporator air outlet is overheated at this time, and the inner circulation fan is turned off.

[0022] In some embodiments of the present application, when the air inlet of the compressor or the air outlet of the evaporator is overheated, the refrigeration performance coefficient of the air conditioner is calculated according to the working condition of the air conditioner;

[0023] When the air conditioner is running in cooling mode, the heat exchange on the evaporator side is obtained according to the enthalpy difference between the inlet and outlet of the evaporator and the refrigerant flow rate, and then the heat exchange on the evaporator side and the operating power of the compressor are logically operated to obtain the refrigeration performance coefficient EERe;

[0024] When the air conditioner is operating 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, and then the heat exchange on the condenser side and the operating power of the compressor are logically operated to obtain the heating performance coefficient COPe.

[0025] In some embodiments of the present application, the air intake pipe is defined as a main circuit; the air conditioner further comprises:

[0026] The bypass circuit is configured as a branch of the main circuit. The connection point between the bypass circuit and the main circuit is 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 flows into the main circuit through the second connection point.

[0027] A main circuit valve, which is arranged on the main circuit and located between the first connection point and the second connection point, and is used to control whether the refrigerant in the main circuit flows through;

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

[0029] An electrically controlled heat dissipation unit is disposed on one side of the bypass circuit and is used for performing heat exchange with the refrigerant in the bypass circuit;

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

[0031] Open the bypass valve, keep the main circuit valve and the bypass valve open at the same time, and the refrigerant flows through the main circuit and the bypass circuit at the same time. The refrigerant flowing through the bypass circuit exchanges heat with the electronically controlled cooling unit;

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

[0033] In some embodiments of the present application, the controller is configured to determine that enhanced heat compensation is required at this time if the air inlet of the compressor or the air outlet of the evaporator is still not overheated after the main circuit valve and the bypass valve are opened together for a period of time;

[0034] Open the bypass valve, close the main circuit valve, and 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 cooling unit.

[0035] The heated refrigerant flows back to the main circuit through the second connection point and then flows into the air inlet of the compressor.

[0036] In some embodiments of the present 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 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;

[0038] When the frequency of 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 running time of the current working condition 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;

[0040] 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 air inlet of the compressor or the air outlet of the evaporator is not overheated at this time.

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

[0042] The third temperature detection device is installed in the outdoor heat exchanger and is used to detect the temperature of the external coil.

[0043] Under refrigeration conditions, the outer coil temperature is defined as the condensing temperature, and the inner coil temperature is defined as the evaporating temperature;

[0044] 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;

[0045] The condensation pressure is determined according to the condensation temperature, and the evaporation pressure is determined according to the evaporation temperature;

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

[0047] The outlet enthalpy value of the condenser is obtained by enthalpy calculation according to the outlet temperature and outlet pressure of the condenser, and 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, and the outlet pressure of the evaporator is calculated based on the evaporation pressure and refrigerant flow rate;

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

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

[0051] and / or a fifth temperature detection device, which is arranged at the air outlet of the evaporator and is used to detect the outlet temperature of the evaporator,

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

[0053] The present application also provides an air conditioner, comprising:

[0054] The indoor unit comprises an indoor shell in which an indoor heat exchanger is arranged;

[0055] An outdoor unit, comprising an outdoor housing;

[0056] The outdoor heat exchanger is arranged in the outdoor housing. In the heating condition, the outdoor heat exchanger is an evaporator and the indoor heat exchanger is a condenser. In the cooling condition, the outdoor heat exchanger is a condenser and the indoor heat exchanger is an evaporator.

[0057] A compressor compartment, which is disposed in the outdoor housing;

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

[0059] A bypass circuit is configured as a branch of the main circuit, and the connection point between the bypass circuit and the main circuit is 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 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 passes through;

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

[0061] An electrically controlled heat dissipation unit is disposed on one side of the bypass circuit and is used for performing heat exchange with the refrigerant in the bypass circuit;

[0062] The controller is configured to, during the operation of the air conditioner, open the main circuit valve, and during the calculation of the coefficient of performance of the air conditioner, when it is determined that the air inlet of the compressor is not overheated or the air outlet of the evaporator is not overheated, determine that heat compensation is required at this time, open the bypass valve, keep the main circuit valve and the bypass valve open at the same time, and 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 into the air inlet of the compressor together.

[0064] In some embodiments of the present application, the controller is configured to close the main circuit valve if the air inlet of the compressor is still not overheated after the main circuit valve and the bypass valve are opened for a period of time, so that 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 cooling unit;

[0065] The heated refrigerant flows back to the main circuit through the second connection point and then flows into the air inlet of the compressor.

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

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

[0068] The bypass circuit includes at least:

[0069] An internal refrigerant flow path, the internal refrigerant flow path is configured as a passage formed inside the heat dissipation base surface for the refrigerant to flow;

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

[0071] In the above embodiment, the air conditioner includes an indoor unit and an outdoor unit, the indoor unit includes an indoor shell with an indoor heat exchanger arranged therein, the outdoor unit includes an outdoor shell with an outdoor heat exchanger arranged therein, under heating conditions, the outdoor heat exchanger is configured as an evaporator, and the indoor heat exchanger is a condenser, and under cooling conditions, the outdoor heat exchanger is a condenser, and the indoor heat exchanger is an evaporator; the outdoor shell also includes a compressor compartment with a compressor installed therein, the compressor includes an air inlet and an air outlet, the air inlet is provided with an air intake pipe, and the air outlet is provided with an exhaust pipe, the refrigerant temperature in the exhaust pipe is higher than the refrigerant temperature in the intake pipe, the compressor compartment also includes an internal circulation fan, the internal circulation fan is specifically arranged between the intake pipe and the exhaust pipe, and is used to promote air circulation and heat exchange in the compressor compartment, and the air conditioner also includes an indoor heat exchanger arranged between the intake pipe and the exhaust pipe. A first temperature detection device is provided at the compressor, a second temperature detection device is provided at the air inlet of the compressor, and a pressure detection device is provided at the air inlet of the compressor. The controller is configured to, in the process of calculating the refrigeration performance coefficient of the air conditioner, when it is determined that the air inlet of the compressor is not overheated or the air outlet of the evaporator is not overheated, heat compensation is required. During the heat compensation process, the internal circulation fan is turned on, the air flow in the compressor compartment is internally circulated, and the air heated by the refrigerant in the exhaust pipe is heat exchanged 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 reach the corresponding saturation temperature of the compressor suction pressure and / or the difference between the compressor suction temperature and the inner coil temperature reaches a first preset difference, it is determined that the air inlet of the compressor is overheated or the air outlet of the evaporator is overheated, and the internal circulation fan is turned off.

[0072] By turning on the internal circulation fan to circulate the air in the compressor compartment, the convective heat transfer coefficient between the air temperature in the compressor compartment and the high-temperature air is increased, so that the high-temperature air can better heat the suction pipe at the compressor inlet, and the heat dissipation of the compressor exhaust pipe is reused, so that the suction position of the compressor is overheated or the outlet position of the evaporator is overheated, so that the enthalpy value can be calculated using temperature and pressure, and the online calculation of the air conditioning performance coefficient can be realized. BRIEF DESCRIPTION OF THE DRAWINGS

[0073] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

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

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

[0076] Figure 3 is the correspondence between the TS diagram of the air conditioning refrigeration / heat pump cycle and the refrigeration or heating process according to the exemplary embodiment of the present application;

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

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

[0079] Figure 6 The calculation logic of the coefficient of performance of the air conditioner under the cooling condition is provided according to the exemplary embodiment;

[0080] Figure 7 A further calculation logic for the coefficient of performance of the air conditioner in the cooling condition provided according to the exemplary embodiment;

[0081] Figure 8 A flow chart of calculating a refrigeration performance coefficient by coefficient compensation operation using an evaporator-side refrigeration performance coefficient and a condenser-side refrigeration performance coefficient according to an exemplary embodiment;

[0082] Fig. 9 A flow chart of calculating a heating performance coefficient by coefficient compensation operation using an evaporator-side heating performance coefficient and a condenser-side heating performance coefficient according to an exemplary embodiment of the present application;

[0083] Fig.10 This is a flow chart of determining whether a preset performance coefficient calculation condition is met according to an exemplary embodiment of the present application;

[0084] Fig.11 is another hardware configuration block diagram of an air conditioner according to an exemplary embodiment;

[0085] Fig.12 One of the implementation methods for calculating the performance coefficient in the exemplary embodiment of the present application;

[0086] Fig.13 is another hardware configuration block diagram of an air conditioner according to an exemplary embodiment;

[0087] Fig.14 One of the implementation methods for calculating the performance coefficient in the exemplary embodiment of the present application;

[0088] Fig.15 Provides specific control logic of the air conditioner in an exemplary embodiment for this application;

[0089] Fig.16 A schematic diagram of the structure of an outdoor unit provided in an exemplary embodiment of the present application;

[0090] Fig.17 The structure of the electric control cooling unit provided in the exemplary embodiment of the present application is schematically shown in FIG. Figure 1 ;

[0091] Fig.18 This is a schematic diagram of the structure of the electric control cooling unit according to the exemplary embodiment of the present application. Figure 2 ;

[0092] Fig.19 This is a schematic diagram of the structure of the electric control cooling unit according to the exemplary embodiment of the present application. Figure 3 ;

[0093] Fig. 20 This is a schematic diagram of the structure of the electric control cooling unit according to the exemplary embodiment of the present application. Figure 4 ;

[0094] Fig.21 is the control logic for performing heat compensation according to an exemplary embodiment of the present application;

[0095] Fig. 22 is another control logic for performing heat compensation according to an exemplary embodiment of the present application;

[0096] Fig.23 is another control logic for performing heat compensation according to an exemplary embodiment of the present 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] A first temperature detection device 91; a second temperature detection device 92; a third temperature detection device 95;

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

[0102] A first pressure detection device 51; a second pressure detection device 52; a 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 connection pipe 710' second connection pipe 711; external circulation fan 73'

[0107] Outdoor heat exchanger 72; first connection point 712' and second connection point 713. DETAILED DESCRIPTION

[0108] The present invention is described in detail below by way of exemplary embodiments. However, it should be understood that elements, structures, and features in one embodiment may also be beneficially combined in other embodiments without further description.

[0109] In the description of the present invention, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

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

[0111] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0112] Reference Figure 1 The air conditioner in the embodiment includes: an indoor unit 7, taking an indoor hanging unit (shown in the figure) as an example, the indoor hanging unit is usually installed on an indoor wall surface, etc. For another example, an indoor cabinet unit (not shown in the figure) is also a form of an indoor unit 7 of the indoor unit 7.

[0113] The outdoor unit 6 is usually installed outdoors and is used for heat exchange in the indoor environment. Figure 1 In the figure, since the outdoor unit 6 is located outdoors on the opposite side of the indoor unit 7 across the wall, the outdoor unit 6 is indicated by a dotted line.

[0114] Reference Figure 2, the air conditioner circuit structure is shown in FIG. 1 , which has a refrigerant circuit, and can perform a vapor compression refrigeration cycle by circulating the refrigerant in the refrigerant circuit. The indoor unit 7 and the outdoor unit 6 are connected by connecting pipes to form a refrigerant circuit for circulating the refrigerant.

[0115] In the present application, the air conditioner performs a refrigeration cycle of the air conditioner by using a refrigerant circuit consisting of a compressor 4, a condenser 2, a throttling device 3 and an evaporator 1. Figure 3 The refrigeration cycle includes a series of processes involving compression, condensation, expansion and evaporation, and supplies refrigerant to the conditioned and heat-exchanged air. The high-pressure and low-pressure states required for the refrigerant to work are established by the compressor 4, and the heat of the indoor air is released to the outdoor air (cooling condition) or the heat absorbed from the outdoor air is supplemented to the indoor air (heating condition) by exchanging heat with the outdoor air.

[0116] Compression process: The compressor 4 compresses the high-temperature and high-pressure refrigerant gas and discharges the compressed refrigerant gas. The compressor 4 may be a variable capacity inverter compressor 4 that performs inverter-based speed control. The refrigerant gas discharged by the compressor 4 flows into the condenser 2.

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

[0118] Expansion process: The throttling device 3 expands the high-temperature and high-pressure liquid-phase refrigerant condensed in the condenser 2 into a low-pressure liquid-phase refrigerant.

[0119] Evaporation process: The evaporator 1 evaporates the refrigerant expanded in the throttling device 3 and returns the refrigerant gas in a low temperature and low pressure state to the compressor 4. The evaporator 1 can achieve a refrigeration effect by utilizing the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. In the whole cycle, the air conditioner can adjust the temperature of the indoor space.

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

[0121] The indoor heat exchanger and the outdoor heat exchanger 72 function as a condenser 2 or an evaporator 1. When the indoor heat exchanger functions as a condenser 2, the air conditioner functions as a heater in a heating mode, and when the indoor heat exchanger functions as an evaporator 1, the air conditioner functions as a cooler in a cooling mode.

[0122] Figure 4 This is a hardware configuration block diagram of an air conditioner according to an exemplary embodiment of the present application. 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. In addition, 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 communicatively connected with the controller 8.

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

[0124] In some implementations of this embodiment, for the second temperature detection device 92, the second temperature detection device 92 is installed at the air inlet of the compressor 4, and is used 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 implementations of this embodiment, for the third temperature detection device 95, the third temperature detection device 95 is installed on the outdoor heat exchanger 72, and is used to detect the external coil temperature of the outdoor unit 6, and send the detected external coil temperature to the controller 8.

[0126] It can be known that, under refrigeration conditions, the third temperature detection device 95 is a condensing temperature detection device, the outer coil temperature is the condensing temperature, the first temperature detection device 91 is an evaporating temperature detection device, and the inner coil temperature is the evaporating temperature; under heating conditions, the third temperature detection device 95 is an evaporating temperature detection device, the outer coil temperature is the evaporating temperature, the first temperature detection device 91 is a condensing temperature detection device, and the inner coil temperature is the condensing temperature.

[0127] In some implementations of this embodiment, the first pressure detection device 5151 is installed at the air inlet of the compressor 4, and 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 in the figure does not constitute a limitation on the air conditioner, and the air conditioner may include more or fewer components than shown in the figure, or combine certain components, or arrange the components differently.

[0129] In some implementations of this embodiment, the controller 8 can be used to control the operation of the compressor 4, the throttling device 3, the fan, etc., so that the air conditioner can operate to achieve various predetermined functions of the air conditioner.

[0130] In some implementations of this embodiment, the controller 8 may obtain the operating current value of the compressor 4 at each moment, and obtain the operating frequency f and the operating power of the compressor 4 according to the operating current value.

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

[0132] In the embodiment shown in the present application, the controller 8 refers to a device that can generate an operation control signal according to an instruction operation code and a timing signal to instruct the air conditioner to execute the control instruction.

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

[0134] The processor 83 may be a central processing unit 83 (CPU), a general processor 83, a network processor 83 (NP), a digital signal processor 83 (DSP), a microprocessor 83, a microcontroller 88, a programmable logic device (PLD), or any combination thereof. The processor 83 may also be any other device having a processing function, such as a circuit, a device, or a software module. The processor 83 may also include multiple CPUs, and the processor 83 may be a single-CPU processor 83 or a multi-CPU processor 83. The processor 83 here may refer to one or more devices, circuits, or processing cores for processing data (such as computer program instructions).

[0135] The memory 82 may be a read-only memory 82 (ROM) or other types of static storage devices that can store static information and instructions, a random access memory 82 (RAM) or other types of dynamic storage devices that can store information and instructions, or an electrically erasable programmable read-only memory 82 (EEPROM), a compact disc read-only memory (CD-ROM) or other optical disc storage, optical disc storage (including compressed optical disc, laser disc, optical disc, digital versatile disc, Blu-ray disc, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium that can be used to carry or store the desired program code in the form of an instruction or data structure and can be accessed by a computer, and the present embodiment of the application does not impose any restrictions on this. The memory 82 may exist independently or be integrated with the processor 83. Among them, the memory 82 may contain a computer program code. The processor 83 is used to execute the computer program code stored in the memory 82, thereby realizing the control method of the multi-split air conditioning system provided in the embodiment of the present application.

[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, a circuit, a transceiver or any device that can achieve communication.

[0137] The bus 81 may be a peripheral component interconnect (PCI) bus 81 or an extended industry standard architecture (EISA) bus 81, etc. The bus 81 may be divided into an address bus 81, a data bus 81, a control bus 81, etc. For ease of representation, Fig.11 Although only one thick line is used in the figure, it does not mean that there is only one bus 81 or only one type of bus 81.

[0138] This application can complete the calculation of the performance coefficient of the air conditioner when the hardware sensor is insufficient.

[0139] In some implementations of this embodiment, the coefficient of performance under refrigeration conditions is first used as an example for explanation.

[0140] This application requires at least the condensing temperature and the evaporating 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 condition of the air conditioner meets the preset performance coefficient calculation condition (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, 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 according to the operating power and operating frequency of the compressor 4;

[0144] Determine the condensation pressure according to the condensation temperature (step S32); determine the evaporation pressure according to the evaporation temperature (step S33);

[0145] After executing steps S31, S32, and S33, execute step S41; calculate the outlet temperature of condenser 2 according to the condensing temperature, refrigerant flow rate, and operating frequency, and execute step S42 to calculate the outlet pressure of condenser 2 according to the condensing pressure and refrigerant flow rate;

[0146] After executing steps S41 and S42, step S51 is executed to obtain the outlet enthalpy value of condenser 2 through enthalpy calculation based on the outlet temperature and outlet pressure of condenser 2; it can be known that the outlet enthalpy value of condenser 2 is defined as the inlet enthalpy value of evaporator 1.

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

[0148] After executing step S43 and step S44, step S52 is executed to obtain the outlet enthalpy value of the evaporator 1 through enthalpy calculation according to the outlet temperature and outlet pressure of the evaporator 1;

[0149] After executing step S52 and step S51, execute step S6 to obtain the heat exchange amount on the evaporator 1 side according to the inlet enthalpy value, outlet enthalpy value and refrigerant flow rate of the evaporator 1, and then execute step S7 to obtain the refrigeration performance coefficient EERe on the evaporator 1 side through performance coefficient calculation according to the heat exchange amount on the evaporator 1 side and the operating frequency of the compressor 4, and use the refrigeration performance coefficient EERe on the evaporator 1 side as the refrigeration performance coefficient EER;

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

[0151] In step S8, if the refrigeration performance coefficient is not less than the preset refrigeration coefficient, step S91 is executed to output and display the calculation result EER, and inform the user that the current air conditioner is in a good operating state;

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

[0153] It should be noted that, for those skilled in the art, it is achievable to calculate the enthalpy value of a certain position using the temperature and pressure of the position, which is a prior art and will not be described in detail in this application.

[0154] If it is determined in step S1 that the current operating condition of the air conditioner does not meet the preset performance coefficient calculation condition, step S3 is executed to prompt that heat compensation is required.

[0155] It should be noted that in step S31, the relationship between the operating power W of the compressor 4 and the operating frequency f to determine the refrigerant flow rate mr in the refrigerant circuit is mr=f1(W, f), wherein f1 is a performance curve function of the compressor 4 or an associated equation fitted according to the performance curve of the compressor 4.

[0156] It is understandable that the model can also be trained using existing operating power, operating frequency and refrigerant flow data, the operating power W and operating frequency f of the compressor 4 are input into the model, and the refrigerant flow is output.

[0157] Through the above steps, the real-time heat exchange rate and compressor 4 power of the air conditioner under refrigeration conditions can be calculated only according to the evaporating temperature detected by the evaporating temperature detection device and the condensing temperature detected by the condensing temperature detection device, and then the performance coefficient under refrigeration conditions can be obtained. While providing data support for adjusting the working state of the air conditioner, it also reduces the requirements for the hardware of the air conditioner itself, and can meet the performance coefficient calculation of most air conditioners. According to the performance coefficient, the current operating state and energy-saving level of the air conditioner can be judged, which can be used to guide the online monitoring, performance prediction and energy-saving operation guidance of the air conditioner, so as to achieve the purpose of improving the long-term operation characteristics of the air conditioner.

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

[0159] In addition, since latent heat is generated when the air conditioner is in the dehumidification process, the heat exchange capacity on the air side is usually inaccurate, and the real-time power of the heat exchanger can be obtained by the heat exchange capacity on the refrigerant side. The heat exchange capacity on the refrigerant side can adopt the calculation method of the heat exchange capacity of the present application.

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

[0161] In some embodiments, the air conditioner is further provided with an exhaust temperature sensor 93 , which is provided at the air outlet of the compressor 4 and is used to detect the exhaust temperature of the compressor 4 .

[0162] In some implementations of this embodiment, the refrigeration performance coefficient EER can also be calculated by calculating the refrigeration performance coefficient EERc on the condenser 2 side. Figure 7 , the exhaust pressure is estimated according to the condensing pressure and the refrigerant flow rate (step S701), and then the exhaust enthalpy value of the compressor 4 is obtained by enthalpy calculation according to the exhaust temperature and the exhaust pressure (step S702), and the exhaust enthalpy value of the compressor 4 can be defined as the inlet enthalpy value of the condenser 2;

[0163] Then, the heat exchanger on the condenser 2 side is obtained according to the inlet enthalpy value, outlet enthalpy value and refrigerant flow rate of the refrigerant circuit of the condenser 2 (step S703). The heat exchanger on the condenser 2 side is combined with the operating power of the 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 of the refrigeration performance coefficient EER and the preset refrigeration coefficient (step S705).

[0164] Through the above steps, the performance coefficient can be calculated only based on the exhaust temperature detected by the exhaust temperature sensor 93 and the condensing temperature detected by the condensing temperature detection device. While providing data support for adjusting the air-conditioning working state, it also reduces the requirements for the air-conditioning hardware itself, and can meet the performance coefficient calculation of most air conditioners.

[0165] It can be known that when the hardware conditions are insufficient, the refrigeration performance coefficient of the evaporator 1 side or the refrigeration performance coefficient of the condenser 2 side can be used as the refrigeration performance coefficient of the air conditioner under refrigeration conditions. When the hardware conditions are sufficient, a weighted calculation can be performed based on the refrigeration performance parameters on the evaporator 1 side and the refrigeration performance coefficient on the condenser 2 side to obtain the refrigeration performance coefficient EER.

[0166] Specifically, in this embodiment, the coefficient of refrigeration performance EERc on the condenser 2 side and the coefficient of refrigeration performance EERe on the evaporator 1 side can be used to perform coefficient compensation calculation to complete the calculation of the refrigeration performance coefficient EER. Figure 8 , which illustrates a flow chart for calculating the refrigeration performance coefficient by coefficient compensation operation using the refrigeration performance parameters on the evaporator 1 side and the refrigeration performance coefficient on the condenser 2 side.

[0167] Determine the ratio of the absolute value of the difference between the evaporator 1 side refrigeration performance coefficient EERe and the condenser 2 side refrigeration performance coefficient EERc and the condenser 2 side refrigeration performance coefficient EERc Whether the lower limit of the first preset deviation value θ1 is reached (step S801)

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

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

[0170] Through the above settings, the calculation method of EER will be adjusted according to the relationship between the calculated refrigeration performance parameters on the evaporator 1 side and the refrigeration performance coefficient on the condenser 2 side and the preset deviation value, so as to improve the accuracy of the refrigeration performance coefficient.

[0171] In some implementations of this embodiment, the following describes how to calculate the heating performance coefficient in the heating condition. The heating performance coefficient on the condenser 2 side can be used as the heating performance coefficient, and the heating performance coefficient on the evaporator 1 side can be used as the heating performance coefficient alone, or the heating performance coefficient can be obtained by weighting the heating performance parameters on the condenser 2 side and the heating performance coefficient on the evaporator 1 side.

[0172] The following description will be made by taking the heating performance coefficient of the condenser 2 side as the heating performance coefficient as an example.

[0173] First, the heat exchange amount on the condenser 2 side is obtained according to the inlet enthalpy value, outlet enthalpy value and refrigerant flow rate of the condenser 2, and then the heat exchange amount on the condenser 2 side is combined with the operating power of the compressor 4 to obtain the heating performance coefficient COPc on the condenser 2 side through performance coefficient calculation. Here, the heating performance coefficient COPc on the condenser 2 side is used as the heating performance coefficient COP;

[0174] Finally, the working state of each component of the air conditioner can be controlled according to the comparison result of the heating performance coefficient COP and the preset heating coefficient.

[0175] The following description will be made by taking the heating performance coefficient of the evaporator 1 side as the heating performance coefficient as an example.

[0176] Firstly, the heat exchange amount on the evaporator 1 side is obtained according to the inlet enthalpy value, outlet enthalpy value and refrigerant flow rate of the evaporator 1, and then the heat exchange amount on the evaporator 1 side is combined with the operating power of the compressor 4 through performance coefficient calculation to obtain the heating performance coefficient COPe on the evaporator 1 side, and the heating performance coefficient COPe on the evaporator 1 side is used as the heating performance coefficient COP; finally, the operation of each component of the air conditioner is controlled according to the comparison result of the heating performance coefficient COP with the preset heating coefficient.

[0177] Through the above steps, the real-time heat exchange rate and compressor 4 power of the air conditioner under heating conditions can be calculated only according to the evaporating temperature detected by the evaporating temperature detection device and the condensing temperature detected by the condensing temperature detection device, and then the performance coefficient under heating conditions can be obtained. While providing data support for adjusting the working state of the air conditioner, it also reduces the requirements for the hardware of the air conditioner itself, and can meet the performance coefficient calculation of most air conditioners. The current operating state and energy-saving level of the air conditioner can be judged according to the performance coefficient, which can be used to guide the online monitoring, performance prediction and energy-saving operation guidance of the air conditioner, so as to achieve the purpose of improving the long-term operation characteristics of the air conditioner.

[0178] At the same time, the present 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 description will be made by taking the heating performance coefficient obtained by weighted calculation using the heating performance coefficient on the condenser 2 side and the heating performance coefficient on the evaporator 1 side as an example.

[0180] Reference Fig. 9 , a flow chart illustrating the calculation of the heating performance coefficient by coefficient compensation operation using the heating performance coefficient on the evaporator 1 side and the heating performance coefficient on the condenser 2 side.

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

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

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

[0184] Through the above settings, the COP calculation method will be adjusted according to the relationship between the calculated heating performance coefficient on the evaporator 1 side and the heating performance coefficient on the condenser 2 side and the second preset deviation value, so as to improve the accuracy of the heating performance coefficient.

[0185] Reference Fig.10 , illustrating one implementation method of calculating the performance coefficient in this embodiment.

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

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

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

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

[0190] According to the corresponding relationship between the saturation temperature and the saturation pressure corresponding to the refrigerant type, the evaporation pressure p1=f3(T1) and the condensation pressure p2=f5(T2) are determined, and the outlet pressure p3 of the compressor 4 can be approximately equal to p2 (step S115);

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

[0192] According to the corresponding relationship between the evaporation pressure p1, the refrigerant flow rate mr and the outlet pressure P11 of the evaporator 1, p11=f9(p1,mr); according to the corresponding relationship between the condensation pressure p2, the refrigerant flow rate mr and the outlet pressure p22 of the condenser 2, it is estimated that p22=f10(p2,mr) (step S1110);

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

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

[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] It is understandable that, referring to Figure 3 In this application, it is considered that the process in the throttling device 3 is isenthalpic.

[0197] The heat exchange amount on the evaporator 1 side is Qe=Δh21×mr, or the heat exchange amount on the condensation side is Qc=Δh32×mr or Qc=Δh21×mr+W (step S118);

[0198] The cooling performance coefficient under the cooling condition or the heating performance coefficient under the heating condition is calculated (step S119).

[0199] In some implementations of this embodiment, in the actual operation of the air conditioner, the target performance coefficient of the air conditioner in different states (including at least a preset cooling coefficient and a preset heating coefficient) can be set. For example, the preset cooling coefficient EER0 under the cooling condition or the preset heating coefficient COP0 under the heating condition is related to the compressor 4 frequency f, the windshield G, the indoor ambient temperature Tinner loop, the outdoor ambient temperature Touter loop, the indoor set temperature Tset, the indoor ambient humidity Inner ring, indoor set humidity One or more related functions of several parameters such as setting, etc., in the actual operation process, determine the influence of each parameter on EER0 or COP0, clarify the largest influencing parameter, 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 the present application, reference Fig.11 , this embodiment is further provided with a fourth temperature detection device 9494 that is in communication connection with the controller 8. The fourth temperature detection device 9494 is installed at the air outlet of the condenser 2, and is used to detect the outlet temperature of the condenser 2, and send the outlet temperature of the condenser 2 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 the enthalpy value is calculated to obtain the performance coefficient of the air conditioner.

[0201] In this embodiment, accurate refrigerant temperature data is measured to determine a more accurate thermal state of the refrigerant at the inlet of the compressor 4 or the outlet of the condenser 2 , and other processes are consistent with Embodiment 1.

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

[0203] Reference Fig.12 , illustrating one implementation method of calculating the performance coefficient in this embodiment.

[0204] Predetermine the functions or formulas of 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 S141); obtain the evaporation temperature T1, the condensation temperature T2, the exhaust temperature T3 of the compressor 4, the outlet temperature T11 of the evaporator 1, and the outlet temperature T22 of the condenser 2 detected by the temperature sensor (step S142); extract the operating power W and the operating frequency f of the compressor 4, and calculate the refrigerant flow mr in the current refrigerant circuit according to the performance curve formula mr=f1(W, f) of the compressor 4 (step S143);

[0205] According to the corresponding relationship between the saturation temperature and the saturation pressure corresponding to the refrigerant type, the evaporation pressure p1=f3(T1) and the condensation pressure p2=f5(T2) are determined, and the outlet pressure p3 of the compressor 4 can be approximately equal to p2 (step S145);

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

[0207] According to the corresponding relationship between the evaporation pressure p1, the refrigerant flow rate mr and the outlet pressure P11 of the evaporator 1, p11 = f9 (p1, mr); according to the corresponding relationship between the condensation pressure p2, the refrigerant flow rate mr and the outlet pressure p22 of the condenser 2, p22 = f10 (p2, mr) is estimated (step S1410);

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

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

[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 can be understood that in this application, it is considered that the process in the throttling device 3 is isenthalpic.

[0212] The heat exchange amount on the evaporator 1 side is Qe=Δh21×mr, or the heat exchange amount on the condensation side is Qc=Δh32×mr or Qc=Δh21×mr+W (step S148);

[0213] The cooling performance coefficient under the cooling condition or the heating performance coefficient under the heating condition is calculated (step S149).

[0214] In some embodiments of the present application, reference Fig.13 This embodiment is also provided with a second pressure detection device 5252 and / or a third pressure detection device 53 which are connected to the controller 8 for storage communication, and are used to detect the pressure value of the set position and send the pressure value to the controller 8.

[0215] In some implementations of this embodiment, the second pressure detection device 5252 is installed at the air outlet of the compressor 4, and 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 implementations of this embodiment, the third pressure detection device 5353 is installed at the air outlet of the condenser 2 , and 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 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 are used to replace the corresponding calculated pressure values, and corresponding operations are performed to obtain the performance coefficient of the air conditioner.

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

[0219] It should be noted that, in this embodiment, the pressure detection device at the inlet of the compressor 4 (also called the outlet of the evaporator 1) or / and the pressure detection device at the outlet of the condenser 2 (also called in front of the throttling device 3) or / and the pressure detection device at the exhaust position of the compressor 4 are added to respectively measure the compressor 4 inlet pressure p11 or / and the condenser 2 outlet pressure p22 or / and the refrigerant exhaust pressure p3. If only one of the above three pressure detection devices is added, for this case, the pressure parameters without sensors can be executed according to the method corresponding to the technical scheme of Example 1. The technical scheme of this embodiment and the control method described in the schemes of Examples 1 and 2 can realize the function of calculating the online performance of the air conditioner, and should also be included in the protection scope of the present invention.

[0220] Reference Fig.14 , describing the workflow for calculating the performance coefficient in this embodiment.

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

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

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

[0224] According to the corresponding relationship between the saturation temperature and the saturation pressure corresponding to the refrigerant type, the condensing pressure p2 = f5 (T2), and the outlet pressure p3 of the compressor 4 can be approximately equal to p2 (step S165);

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

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

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

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

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

[0230] The heat exchange amount on the evaporator 1 side is Qe=Δh21×mr, or the heat exchange amount on the condensation side is Qc=Δh32×mr or Qc=Δh21×mr+W (step S168);

[0231] The cooling performance coefficient under the cooling condition or the heating performance coefficient under the heating condition is calculated (step S169).

[0232] In some implementations of this embodiment, the above method of calculating the performance coefficient needs to satisfy the operating conditions of the air conditioner to meet the preset conditions. The preset conditions include judging whether the operating time of the current working condition of the air conditioner, the suction temperature of the compressor 4, the internal coil temperature and the operating frequency of the compressor 4 meet the corresponding conditions.

[0233] In some embodiments, when the suction temperature of the compressor 4 does not exceed the saturation temperature corresponding to the suction pressure of the 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 the 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 frequency of compressor 4 does not reach the first preset frequency, the third parameter is defined as a3, otherwise, the third parameter is defined as b3; when the running time of the current working condition 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 parameter, the second parameter, the third parameter and the fourth parameter is not within the preset parameter range, it is determined that the air inlet of the compressor 4 or the air outlet of the evaporator 1 is not overheated.

[0237] It should be noted that when the outlet of evaporator 1 is superheated (i.e., refrigerant dryness x=1), the outlet enthalpy value 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 supercooled (i.e., refrigerant dryness=0), the outlet enthalpy value h2 of condenser 2 is a function of the outlet temperature of condenser 2 and the outlet pressure of evaporator 1. It can be known that in the case where the computing power of controller 8 is insufficient or it is inconvenient to obtain the outlet pressure of evaporator 1, the outlet enthalpy value h2 of condenser 2 can also be obtained by using the outlet temperature of condenser 2 and the condensation temperature.

[0238] In the actual operation of the air conditioner, the evaporator 1 outlet may not be overheated (the refrigerant dryness is less than 1) and the condenser 2 outlet may not be overcooled (the refrigerant dryness is greater than 0) under low operating frequency or low load conditions. In addition, the air conditioner may not reach a steady state during the startup phase. These two situations will cause deviations or even distortions in the online performance coefficient calculation.

[0239] Therefore, in order to ensure the accuracy of the entire calculation result, it is necessary to judge the operating status of the air conditioner (including operating time and operating parameters) and then decide whether to calculate the performance coefficient.

[0240] Specifically, when the suction temperature of the compressor 4 does not exceed the saturation temperature corresponding to the suction pressure of the 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 the 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 compressor 4 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 running time of the current working condition 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;

[0244] All the obtained parameters are accumulated to obtain the parameter sum c.

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

[0246] Reference Fig.15 , illustrating the specific control logic of the air conditioner in this embodiment.

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

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

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

[0250] In step S126, if the parameters and are within the preset coefficient condition range, step S127 is executed to calculate the real-time performance coefficient EERe (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); set the first preset deviation value θ1 acceptable under the cooling condition and the second preset deviation value θ2 acceptable under the heating condition respectively (step S128);

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

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

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

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

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

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

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

[0258] In step S1211, if the lower limit of the second preset deviation value θ2 is not reached, step S1216 is executed to set COP=αCOPe+(1-)COPc, where α∈(0,1). Then step 1214 is executed;

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

[0260] In step S122, if the user does not enable the online performance coefficient calculation function, step S121 is continued.

[0261] In the above step S124, it is executed sequentially or simultaneously or in accordance with the preset rule sequence to determine whether the suction temperature of compressor 4 exceeds the saturation temperature corresponding to the suction pressure of compressor 4; determine whether the difference between the suction temperature of compressor 4 and the temperature of the inner coil reaches the first preset temperature difference; determine whether the frequency of compressor 4 reaches the first preset frequency; determine whether the operating time of the current working condition of the air conditioner reaches the first preset time; after the judgment, the corresponding result parameters are obtained and then accumulated to obtain the cumulative sum c.

[0262] It should be noted that in the above steps, only the cooling and heating working conditions of the air conditioner are considered. If there are other modes in actual applications, the mode judgment can be added before calculation.

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

[0264] The real-time performance coefficient of the air conditioner is calculated using the above method. However, in actual operation, if the operating parameters of the air conditioner do not meet the preset conditions, that is, the outlet of the evaporator 1 is not overheated or the outlet of the condenser 2 is not overcooled, the refrigerant dryness x at this time is between 0 and 1, and 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 will be impossible to determine the refrigerant inlet and outlet enthalpy values ​​of the evaporator 1 or condenser 2 and the heat exchange amount on the refrigerant side, which will also result in the air conditioner's performance coefficient being unable to be obtained by the above calculation method.

[0266] In order to solve the above problem, in some implementations of the present embodiment, a heat compensation method is proposed to ensure that the suction position of the compressor 4 is overheated, which is used to calculate the online performance coefficient of the air conditioner through correction through the technical solution in the present application when the evaporator 1 is not overheated.

[0267] It should be noted that in the actual operation of the air conditioner, there is excess waste heat such as in the compressor compartment 74 and the electronically controlled cooling unit 10, but there is usually no excess cooling capacity that can be recycled, so this application only provides a correction method for the condition where the evaporator 1 is not overheated. Therefore, since there is no cooling capacity compensation method for the condenser 2 outlet not being overcooled, the calculation of the heat exchange Qc of the condenser 2 under the heating condition needs to be calculated using the formula Qc=Qe+W, and then the COP is calculated using formula (2).

[0268] The following is an explanation of the principle of non-overheating compensation in this application.

[0269] Reference Figure 3 , the evaporation process of evaporator 1 is from point D to point A3, wherein the refrigerant in the heat exchange section from point D to point A2 (excluding A2) is in a gas-liquid two-phase state, and the enthalpy value in this process is a ternary function of the refrigerant dryness, temperature and pressure, wherein the pressure and / or temperature can be obtained by corresponding pressure and / or temperature sensors, while the refrigerant dryness cannot be directly measured or calculated by conventional sensors, so the refrigerant at the outlet of evaporator 1 must be made to reach a saturated (A2) or superheated steam state (point A2 (excluding A2) to A3), the refrigerant dryness in this state is 1, and the enthalpy value is a binary function of temperature and pressure, in order to perform the effective heat exchange in evaporator 1 according to the following calculation method.

[0270] Qe=Δhe·G=(h1-h2')·mr

[0271] In addition, for the compressor 4, it is necessary to require that the outlet of the evaporator 1, that is, the inlet of the condenser 2, is a single-phase refrigerant vapor, otherwise it is easy to cause liquid hammer phenomenon in the compressor 4, affecting the service life or operating performance of the compressor 4. Therefore, considering the safety of air-conditioning operation and the availability of the performance calculation method, the outlet of the evaporator 1 must be changed to the overheating state A3 by effective means, at least to the saturation state A2, and cannot be the non-overheating state A1.

[0272] In order to superheat the outlet of the evaporator 1 , it is proposed to perform heat compensation at this location or at the air inlet of the compressor 4 .

[0273] Reference Fig.16The outdoor unit 6 is connected to the throttling device 3, 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, and the outdoor unit 6 includes an outdoor shell 71, and a compressor compartment 74 is defined in the outdoor shell 71.

[0274] The outdoor housing 71 is provided with 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 bracket, etc. The main function is to drive the outdoor air to circulate externally and realize heat exchange between the air and the outdoor heat exchanger 72.

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

[0276] Among them, refrigerant flows inside the intake pipe, the compressor 4, the exhaust pipe, and the throttling device 3. Due to the principle of refrigeration cycle, the temperature of the refrigerant in the exhaust pipe is higher than the temperature of the refrigerant in the intake pipe.

[0277] In order to improve the working efficiency of the internal circulation fan 79 , the internal circulation fan 79 is arranged between the intake pipe and the exhaust pipe to accelerate the air flow in the compressor compartment 74 , thereby promoting air circulation and heat exchange in the compressor compartment 74 .

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

[0279] During the heat compensation process, the internal circulation fan 79 is turned on, the airflow in the compressor compartment 74 is internally circulated, and the air heated by the refrigerant in the exhaust pipe exchanges heat with the refrigerant in the intake pipe to compensate for the refrigerant temperature 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 performance coefficient can be calculated normally, the internal circulation fan 79 is turned off, and the fan internal circulation compensation is stopped.

[0281] Through the above steps,

[0282] In some embodiments, when the air inlet of the compressor 4 or the air outlet of the evaporator 1 is overheated, the refrigeration performance coefficient of the air conditioner is calculated according to the working condition of the air conditioner;

[0283] When the air conditioner is running in cooling mode, the heat exchange amount on the evaporator 1 side is obtained according to the enthalpy difference between the inlet and outlet of the evaporator 1 and the refrigerant flow rate, and then the heat exchange amount on the evaporator 1 side and the operating power of the compressor 4 are logically operated to obtain the refrigeration performance coefficient EERe;

[0284] When the air conditioner operates in heating mode, first, the heat exchange on the condenser 2 side is obtained according to the heat exchange on the evaporator 1 side under the cooling condition and the operating power of the compressor 4, and then the heat exchange on the condenser 2 side and the operating power of the compressor 4 are logically operated to obtain the heating performance coefficient COPe.

[0285] In some embodiments, the outdoor housing 71 also includes an electrically controlled cooling unit 10, and the suction pipe of the air inlet of the compressor 4 is defined as the main circuit 75, and a branch of the main circuit 75 - a bypass circuit 77 is set, and the connection point between the main circuit 75 and the bypass circuit 77 is defined as a first connection point 712 and a second connection point 713. After the refrigerant in the main circuit 75 flows out of the evaporator 1, it flows into the bypass circuit 77 through the first connection point 712, and the refrigerant in the bypass circuit 77 will flow into the main circuit 75 again through the second connection point 713.

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

[0287] The bypass valve 78 is also included, which is arranged on the bypass circuit 77 and located 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 arranged on the side of the bypass circuit 77 close to the first connection point 712, shortening the distance between the bypass valve 78 and the first connection point 712 to reduce the loss of the refrigerant.

[0288] The above-mentioned electronically controlled heat dissipation unit 10 is arranged at one side of the bypass circuit 77 , and the electronically controlled heat dissipation unit 10 is used for performing heat exchange with the refrigerant in the bypass circuit 77 .

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

[0290] At the same time, the controller 8 is also configured to determine that it is necessary to increase heat compensation 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;

[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 cooling unit 10, and 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 implementations of this embodiment, the controller 8 is configured to determine that the heat compensation needs to be strengthened if the air inlet of the compressor 4 is still not overheated after the main circuit valve 76 and the bypass valve 78 are opened together for a period of time;

[0293] Open the bypass valve 78 and close the main circuit valve 76. The refrigerant flowing through the first connection point 712 will all flow into the bypass circuit 77. The refrigerant flowing through the bypass circuit 77 will exchange heat with the electronically controlled cooling unit 10. The heated refrigerant will flow back to the main circuit 75 through the second connection point 713 and then flow into the air inlet of the compressor 4.

[0294] Through the above steps, the electronically controlled heat dissipation compensation method is divided into a basic heat compensation method and an enhanced heat compensation method. In the basic heat compensation method, when heat compensation is required, the controller 8 sends out a cooling signal to open the bypass valve 78, and keeps the main circuit valve 76 and the bypass valve 78 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 being further heated, the refrigerant 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, so that all the refrigerant flows into the bypass circuit 77 to absorb the heat of the electronically controlled cooling unit 10. At this time, since the refrigerant flowing into the bypass circuit 77 increases, the convection heat transfer coefficient in the tube is enhanced, so the effective heat absorption from the electronically controlled cooling unit 10 increases, which can ensure the superheated state of the outlet of the evaporator 1.

[0296] In some implementations of this embodiment, refer to Figure 17-20 The electronically controlled heat dissipation unit 10 includes a heat sink 101 , and the heat sink 101 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 inner refrigerant flow path 105 and an outer refrigerant flow path 104. The inner refrigerant flow path 105 is configured as a passage for the circulation of the refrigerant formed inside the heat dissipation base surface 103. The outer refrigerant flow path 104 is connected to the inner refrigerant flow path 105 and the main circuit 75, and the outer refrigerant flow path 104 is installed in close contact with the heat dissipation base surface 103 to facilitate the circulation of the refrigerant in the inner refrigerant flow path 105 and the outer refrigerant flow path 104.

[0298] Specifically, the external refrigerant flow path 104 can be set to two sections, namely the first external refrigerant flow path 104 and the second external refrigerant flow path 104, which are respectively arranged at the two 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 of the evaporator 1 enters the first external refrigerant flow path 104 and then enters the internal refrigerant flow path 105, and then passes through the second external refrigerant flow path 104 and merges into the main circuit 75.

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

[0300] In some embodiments, the external refrigerant flow path 104 can be a copper tube, and the radiator 101 can be an aluminum radiator 101. In the technical solution of the present 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 and the copper tube are welded at the inlet and outlet. Although this method increases the heat dissipation risk of the refrigerant at the inlet and outlet, it enhances the heat transfer efficiency inside the radiator 101.

[0301] Compared with the related art in which the surface of the aluminum radiator 101 is processed into a shape that can be embedded in the copper tube and then the two are tightly combined, the problem of the copper tube wall blocking the heat dissipation base surface 103 and the refrigerant, resulting in large heat transfer resistance and poor heat exchange performance, is solved.

[0302] Reference Fig.21 , explaining the control logic of 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 air temperature T11 and the inner disk temperature T1 is less than the first preset temperature difference (step S2022)

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

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

[0308] In step S2021, if yes, then execute step S2025, the first parameter is a1, if no, then execute step S2026, the first parameter is 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 execute step S2029, the third parameter is a3, if no, then execute step S20210, the third parameter is b3;

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

[0312] The first parameter, the second parameter, the third parameter and the fourth parameter are summed, and recorded 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, step S206 is executed to perform performance parameter calculation normally;

[0315] In step S204, if c is not within the preset parameter range, step S205 is executed to determine that the outlet of the evaporator 1 is not overheated at this time and heat compensation is required;

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

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

[0318] In step S208, if the corresponding preset time is reached, step S209 is executed to calculate C again and determine whether it meets the preset parameter range;

[0319] In step S209, if c satisfies the preset parameter range, 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, 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 reaches the corresponding preset time (step S212);

[0322] In step S212, if the corresponding preset time is reached, 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, 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, step S214 is executed to close the main circuit valve 76;

[0324] Determine whether the working time of the current state reaches the corresponding preset time (step S215);

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

[0326] In step S216, if c meets the preset parameter range, step S210 is executed;

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

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

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

[0330] Through the above settings, the fan internal circulation valve is first used for heat compensation. When the preset conditions are not met, the electronically controlled heat dissipation compensation is turned on to minimize the intervention in the refrigeration system and avoid the opening of the heat compensation device affecting the fluctuation of the indoor temperature.

[0331] In some embodiments of the present application, only the electronically controlled heat dissipation compensation method is used, and the controller 8 is configured to perform heat compensation when it is determined that the air outlet of the evaporator 1 is not overheated or the air inlet of the compressor 4 is not overheated during the calculation of the refrigeration 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 cooling unit 10, and 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 implementations of this embodiment, the controller 8 is configured to determine that the heat compensation needs to be strengthened if the air inlet of the compressor 4 is still not overheated after the main circuit valve 76 and the bypass valve 78 are opened together for a period of time;

[0334] Open the bypass valve 78 and close the main circuit valve 76. The refrigerant flowing through the first connection point 712 will all flow into the bypass circuit 77. The refrigerant flowing through the bypass circuit 77 will exchange heat with the electronically controlled cooling unit 10. The heated refrigerant will flow back to the main circuit 75 through the second connection point 713 and then flow into the air inlet of the compressor 4.

[0335] By adjusting the working states of the main circuit valve 76 and the bypass valve 78, the flow direction of the refrigerant is controlled to determine whether heat compensation is performed on the refrigerant so that the outlet of the evaporator 1 is overheated.

[0336] Reference Fig. 22 , illustrating another control logic of 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 air temperature T11 and the inner disk temperature T1 is less than the first preset temperature difference (step S3022)

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

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

[0342] In step S3021, if yes, then execute step S3025, the first parameter is a1, if no, then execute step S3026, 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 execute step S3029, the third parameter is a3, if no, then execute step S30210, the third parameter is b3;

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

[0346] The first parameter, the second parameter, the third parameter and the fourth parameter are summed, and recorded 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, step S306 is executed to perform performance parameter calculation normally;

[0349] In step S304, if c is not within the preset parameter range, step S305 is executed to determine that the outlet of the evaporator 1 is not overheated at this time and heat compensation is required;

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

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

[0352] In step S312, if the corresponding preset time is reached, 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, 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, step S314 is executed to close the main circuit valve 76;

[0354] Determine whether the working time of the current state reaches the corresponding preset time (step S5);

[0355] In step S315, if the corresponding preset time is reached, 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, step S317 is executed to prompt the user that performance calculation cannot be performed at present;

[0356] In step S316, if c meets the preset parameter range, step S310 is executed;

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

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

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

[0360] Reference Fig.23 , illustrating another control logic of 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 air temperature T11 and the inner disk temperature T1 is less than the first preset temperature difference (step S4022)

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

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

[0366] In step S4021, if yes, then execute step S4025, the first parameter is a1, if no, then execute step S4026, 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 execute step S4029, the third parameter is a3, if no, then execute step S40210, 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] The first parameter, the second parameter, the third parameter and the fourth parameter are summed, and recorded 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, step S406 is executed to perform performance parameter calculation normally;

[0373] In step S404, if c is not within the preset parameter range, step S405 is executed to determine that the outlet of the evaporator 1 is not overheated at this time and heat compensation is required;

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

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

[0376] In step S408, if the corresponding preset time is reached, step S409 is executed to calculate C again and determine whether it meets the preset parameter range;

[0377] In step S409, if c satisfies the preset parameter range, 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, step S411 is executed to prompt the user that performance calculation cannot be performed at present;

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

[0380] It should be noted that the fan circulation method and the electric control heat dissipation method in this application can be used alone or in combination, and the enabling conditions of each method can be selected by designing the control logic as needed. Also, considering that the heat compensation that can be provided by the fan and the electric control heat dissipation element 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 additionally considered, and the online performance coefficient before and after compensation is assumed to be approximately equal.

[0381] The present application proposes an air conditioner. When the outlet of the evaporator 1 is not overheated, a heat compensation device is provided to heat the outlet of the evaporator 1 to a certain extent, so as to ensure that heat compensation is performed under the condition of not being overheated, so as to meet the applicable conditions of the online performance calculation method.

[0382] At the same time, the present application can obtain the online operation performance technology of the air conditioner by calculating the enthalpy difference on the refrigerant side, the refrigerant flow rate and the power of compressor 4 without the help of an enthalpy difference laboratory, so as to provide energy-saving operation and optimized design of the air conditioner.

[0383] The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. An air conditioner, characterized in that: include: The indoor unit comprises an indoor shell, wherein an indoor heat exchanger is arranged in the indoor shell; An outdoor unit, comprising an outdoor housing; An outdoor heat exchanger is arranged in the outdoor housing. In heating conditions, the outdoor heat exchanger is an evaporator and the indoor heat exchanger is a condenser. In cooling conditions, the outdoor heat exchanger is a condenser and the indoor heat exchanger is an evaporator. A compressor compartment, which is disposed in the outdoor housing; A compressor is arranged in the compressor compartment, the compressor comprises an air inlet and an air outlet, the air inlet is provided with an air intake pipe, the air outlet is provided with an air discharge pipe, and the refrigerant temperature in the air discharge pipe is higher than the refrigerant temperature in the air intake pipe; An internal circulation fan, which is arranged in the compressor compartment and between the air intake pipe and the air exhaust pipe, and is used to promote air circulation and heat exchange in the compressor compartment; A first temperature detection device, which is arranged at the indoor heat exchanger and is used to detect the temperature of the inner coil; A second temperature detection device, which is arranged at the air inlet of the compressor and is used to detect the suction temperature of the compressor; A pressure detection device, which is arranged at the air inlet of the compressor and is used to detect the suction pressure of the compressor; The controller is configured to, during the process of calculating the coefficient of performance of the air conditioner, perform heat compensation when it is determined that the air inlet of the compressor is not overheated or the air outlet of the evaporator is not overheated; During the heat compensation process, the internal circulation fan is turned on, the airflow in the compressor compartment is internally circulated, and 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 saturation temperature corresponding to the compressor suction pressure and / or the difference between the compressor suction temperature and the inner coil temperature exceeds a first preset difference, it is determined that the air inlet of the compressor or the air outlet of the evaporator is overheated at this time, and the inner circulation fan is turned off.

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, calculating the refrigeration performance coefficient of the air conditioner according to the working condition of the air conditioner; When the air conditioner is operating in a cooling mode, the heat exchange amount on the evaporator side is obtained according to the enthalpy difference between the inlet and outlet of the evaporator and the refrigerant flow rate, and then the heat exchange amount on the evaporator side and the operating power of the compressor are logically operated to obtain the refrigeration performance coefficient EERe; When the air conditioner operates in a heating condition, the heat exchange amount on the condenser side is obtained according to the heat exchange amount on the evaporator side and the operating power of the compressor, and then the heat exchange amount on the condenser side and the operating power of the compressor are logically operated to obtain the heating performance coefficient COPe.

3. The air conditioner according to claim 1, characterized in that: The air intake pipe is defined as a main loop, and the air conditioner further comprises: A bypass circuit is configured as a branch of the main circuit, wherein the connection point between the bypass circuit and the main circuit is 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, which 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 part of the main circuit; a bypass valve, which is provided in the bypass circuit and is located between the first connection point and the second connection point, and is used to control the refrigerant in the main circuit to flow into the bypass circuit for heat exchange; An electrically controlled heat dissipation unit, which is disposed on one side of the bypass circuit, and is used for performing heat exchange with the refrigerant in the bypass circuit; The controller is configured to, during the operation of the air conditioner, open the main circuit valve, and when the air inlet of the compressor or the air outlet of the evaporator is still not overheated after the internal circulation fan has been operating for a period of time, determine that heat compensation needs to be increased at this time; Open the bypass valve, keep the main circuit valve and the bypass valve open at the same time, and the refrigerant flows through the main circuit and the bypass circuit at the same time, and the refrigerant flowing through the bypass circuit performs heat exchange with the electronically controlled cooling unit; The heated refrigerant merges with the refrigerant in the main circuit and then flows into the air inlet of the compressor together.

4. The air conditioner according to claim 3, characterized in that: The controller is configured to determine that heat compensation needs to be strengthened if the air inlet of the compressor or the air outlet of the evaporator is still not overheated after the main circuit valve and the bypass valve are opened together for a period of time; The bypass valve is opened, and the main circuit valve is closed, so that all the refrigerant flowing through the first connection point flows into the bypass circuit, and the refrigerant flowing through the bypass circuit performs heat exchange with the electronically controlled cooling unit; The heated refrigerant flows back to the main circuit through the second connection point and then flows into the air inlet of the compressor.

5. The air conditioner according to any one of claims 1 to 4, 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 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 running time of the current working condition 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; 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 air inlet of the compressor or the air outlet of the evaporator is not overheated at this time.

6. The air conditioner according to claim 2, characterized in that: Also includes: A third temperature detection device, which is provided on the outdoor heat exchanger and is used to detect the temperature of the outer coil; Under refrigeration conditions, the outer coil temperature is defined as the condensing temperature, and the inner coil temperature 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; Determine the condensation pressure according to the condensation temperature, and determine the evaporation pressure according to the evaporation temperature; The outlet temperature of the condenser is calculated according to the condensing temperature, the refrigerant flow rate and the operating frequency, and the outlet pressure of the condenser is calculated according to the condensing pressure and the refrigerant flow rate; The outlet enthalpy value of the condenser is obtained by performing enthalpy calculation according to the outlet temperature and outlet pressure of the condenser, and the outlet enthalpy value of the condenser is defined as the inlet enthalpy value of the evaporator; The outlet temperature of the evaporator is calculated according to the evaporation temperature, the refrigerant flow rate and the operating frequency, and the outlet pressure of the evaporator is calculated according to the evaporation pressure and the refrigerant flow rate; The outlet enthalpy value of the evaporator is obtained by enthalpy calculation according to the outlet temperature and outlet pressure of the evaporator.

7. The air conditioner according to claim 6, characterized in that: Also includes: It also includes a fourth temperature detection device, which is arranged at the air 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.

8. An air conditioner, characterized in that: include: The indoor unit comprises an indoor shell, wherein an indoor heat exchanger is arranged in the indoor shell; An outdoor unit, comprising an outdoor housing; An outdoor heat exchanger is arranged in the outdoor housing. In heating conditions, the outdoor heat exchanger is an evaporator and the indoor heat exchanger is a condenser. In cooling conditions, the outdoor heat exchanger is a condenser and the indoor heat exchanger is an evaporator. A compressor compartment, which is disposed in the outdoor housing; A compressor is arranged in the compressor compartment, the compressor comprises an air inlet and an air outlet, the air inlet is provided with an air intake pipe, the air outlet is provided with an air discharge pipe, the refrigerant temperature in the air discharge pipe is higher than the refrigerant temperature in the air intake pipe, and the air intake pipe is defined as a main circuit; A bypass circuit is configured as a branch of the main circuit, wherein the connection point between the bypass circuit and the main circuit is 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, which 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 passes through; a bypass valve, which is provided in the bypass circuit and is located between the first connection point and the second connection point, and is used to control the refrigerant in the main circuit to flow into the bypass circuit for heat exchange; An electrically controlled heat dissipation unit, which is disposed on one side of the bypass circuit, and is used for performing heat exchange with the refrigerant in the bypass circuit; The controller is configured to, during the operation of the air conditioner, open the main circuit valve, and during the calculation of the coefficient of performance of the air conditioner, when it is determined that the air inlet of the compressor is not overheated or the air outlet of the evaporator is not overheated, determine that heat compensation is required at this time, open the bypass valve, keep the main circuit valve and the bypass valve open at the same time, and 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 cooling unit; The heated refrigerant merges with the refrigerant in the main circuit and flows into the air inlet of the compressor together.

9. The air conditioner according to claim 7, characterized in that: The controller is configured to close the main circuit valve if the air inlet of the compressor is still not overheated after the main circuit valve and the bypass valve are opened for a period of time, so that all the refrigerant flowing through the first connection point flows into the bypass circuit, and the refrigerant flowing through the bypass circuit performs heat exchange with the electronically controlled cooling unit; The heated refrigerant flows back to the main circuit through the second connection point and then flows into the air inlet of the compressor.

10. The air conditioner according to claim 7 or 8, characterized in that: The electrically controlled heat dissipation unit comprises: A heat sink, the heat sink comprising at least a heat sink and a heat dissipation base surface provided on one side of the heat sink; The bypass circuit at least comprises: An internal refrigerant flow path, wherein the internal refrigerant flow path is provided as a passage formed inside the heat dissipation base surface for the refrigerant to flow; The outer refrigerant flow path is connected with the inner refrigerant flow path and the main circuit, and the outer refrigerant flow path is mounted in contact with the heat dissipation base surface.

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