JP5744081B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner having a refrigerant circuit for circulating a refrigerant. In particular, the present invention relates to a compressor deterioration detection technique for an air conditioner.

  In an air conditioner that performs a refrigeration cycle, the compressor itself deteriorates when an operation period elapses for a long time after the apparatus is installed. Due to wear of the compression mechanism portion, refrigerant leakage or the like from the high pressure side to the low pressure side in the compressor occurs, so that the compression efficiency is lowered and the COP (coefficient of performance) of the refrigeration cycle is lowered. Conventionally, there is no way to directly know even if the compressor deteriorates in this way, and it is left without being updated until a situation where it is clearly recognized as abnormal or until the compressor completely fails There were many. Therefore, conventionally, several techniques for detecting the deterioration of the compressor in the refrigerant circuit have been proposed in the refrigeration cycle apparatus having the refrigerant circuit.

  As a conventional technology, in a refrigeration system that performs a vapor compression refrigeration cycle, values such as the polytropic index are calculated based on the compressor intake temperature, compressor intake pressure, compressor discharge temperature, and compressor discharge pressure. In addition, a refrigeration apparatus has been proposed that allows the deterioration of the compressor to be detected by determining the deterioration of the compressor from the change over time of the value, etc., and enables the determination of the update time (see, for example, Patent Document 1). ).

  As another prior art, in a refrigeration apparatus that performs a vapor compression refrigeration cycle, operation is performed with at least the same state value of the refrigerant on the low-pressure side at every predetermined time to obtain a polytropic index or polytropic efficiency, and deterioration of the compressor A refrigeration apparatus that determines the above has been proposed (see, for example, Patent Document 2).

  As another conventional technique, in a compressor, the compression efficiency is calculated from the compressor inlet temperature, the compressor inlet pressure, the compressor outlet temperature, and the compressor outlet pressure, and is obtained from the compression efficiency and the compressor inlet temperature in the rated state. Compressor efficiency is calculated from the corrected efficiency calculated from the inlet guide vane opening at the rated condition and the calculated efficiency is below the efficiency setting value. A monitoring method has been proposed (see, for example, Patent Document 3).

  As another prior art, a gas turbine including a gas turbine compressor diagnosis unit that calculates a compression efficiency based on detection process data related to the gas turbine and performs an abnormality diagnosis of the gas turbine compressor based on a change amount Δη of the compression efficiency An apparatus has been proposed (see, for example, Patent Document 4).

JP 2002-147905 A (summary) JP 2003-214735 A (summary) JP 11-257240 A (summary) JP 2000-257449 A (summary)

  In Patent Document 1 and Patent Document 2, since the polytropic index is a value that does not change as long as the refrigerant state before and after the compression stroke is constant, this value changes and the change exceeds a predetermined range. It is determined that the compressor has deteriorated. However, in such a conventional technique, the determination cannot be made unless the refrigerant state is set to a specific condition by a special operation in which the refrigerant state is made the same to some extent. For this reason, the compressor deterioration determination cannot be performed during the normal operation, and there is a problem that the operation range in which the compressor deterioration determination is possible is limited.

  In Patent Document 3, the compression efficiency of the gas turbine compressor is calculated from the operating state of the gas turbine apparatus, and the compressor is diagnosed using the calculated compression efficiency as an index.

  However, none of Patent Documents 1 to 3 mentions how to determine and set the determination reference value (determination threshold), and is a value that matches the actual condition (actual performance) of the diagnostic target compressor. There is doubt about whether or not. When the determination reference value is not a value that matches the actual situation (actual performance), there has been a problem that the compressor deterioration cannot be accurately determined and erroneous determination occurs.

  In Patent Document 4, the compression efficiency of the gas turbine compressor is calculated from the operating state of the gas turbine apparatus, and the expected amount of change in the compression efficiency time is obtained from the amount of time change in the compression efficiency and the amount of time change in the specific operating state. The abnormality diagnosis of the gas turbine compressor is performed using the expected amount of change in compression efficiency as an index. Thereby, an abnormality diagnosis according to the change in the operating state of the compressor is possible.

  However, the compression efficiency is a value that changes according to the operating condition even if the compressor is not deteriorated. For this reason, even if the time change amount of the compressor efficiency in Patent Document 4 is used for the compressor deterioration determination, the compressor deterioration cannot be accurately determined, and an erroneous determination occurs. Also, in Patent Document 4, there is no room for improvement because no consideration has been given to the actual performance of the compressor to be diagnosed.

  The present invention has been made to solve the above-described problems, and is an air conditioner capable of highly accurately determining deterioration of a compressor using a determination reference value suitable for the actual performance of the compressor in a wide operating range. The purpose is to obtain.

An air conditioner according to the present invention has a compressor, a condenser, a throttling device, and an evaporator that can vary the operation capacity, and is configured to detect the operation state amount of the refrigerant circuit configured to circulate the refrigerant. When the operation state of the refrigerant circuit and the operation state of the refrigerant circuit satisfy a predetermined operation condition during the initial operation of the refrigerant circuit , the discharge refrigerant temperature and the intake refrigerant temperature are determined based on the operation state amount of the operation state amount detection device. A reference value that is a temperature difference between the initial learning unit that creates the actual relationship between the determined reference value and the operating state of the refrigerant circuit , and discharge based on the operating state quantity of the operating state quantity detection device A judgment index calculation unit that calculates the current judgment index , which is a temperature difference between the refrigerant temperature and the intake refrigerant temperature, and a judgment reference value corresponding to the current operation state based on the actual relationship created by the initial learning unit And the reference value setting section Current determination index calculated by the target calculation unit, the determination if the reference value has risen above a predetermined value than, the compressor is determined to have deteriorated, the current determination indicator has not risen above the predetermined value than the determination reference value If not, a deterioration determining unit that determines that the compressor has not deteriorated is provided.

  ADVANTAGE OF THE INVENTION According to this invention, the air conditioning apparatus which can determine a compressor deterioration with high precision using the determination reference value suitable for the actual performance of the compressor in a wide operating range can be obtained.

It is a refrigerant circuit figure of the air harmony device concerning Embodiment 1 of the present invention. It is a control block diagram of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a Mollier diagram (Ph diagram) for demonstrating the compression efficiency used as the determination parameter | index of compressor deterioration in the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a characteristic view of compression efficiency ηc with respect to compression ratio γ in the air-conditioning apparatus according to Embodiment 1 of the present invention. It is a flowchart which shows the flow of the compressor deterioration determination in the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a flowchart which shows the flow of the initial learning mode in the air conditioning apparatus which concerns on Embodiment 1 of this invention. FIG. 7A is an example of a table of compression efficiency reference values ηcm stored in advance in the storage unit, and FIG. 7B is a diagram illustrating an example of a table of corrected compression efficiency reference values ηcm. It is a figure which shows the modification of the table | surface of compression efficiency reference value (eta) cm. It is a flowchart which shows the modification of the flow of the initial learning mode in the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a flowchart which shows the flow of the compressor deterioration determination in the air conditioning apparatus which concerns on this Embodiment 2 of this invention. It is a flowchart which shows the flow of the compressor deterioration determination in the air conditioning apparatus which concerns on this Embodiment 3 of this invention.

Embodiment 1 FIG.
"Equipment configuration"
The structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention is demonstrated based on FIG.1 and FIG.2.

FIG. 1 is a refrigerant circuit diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention.
The air conditioner 100 has a heat source side unit A and a plurality of load side units B1 and B2, and is connected by refrigerant piping. The heat source side unit A includes a compressor 1, a four-way valve 2, and a heat source side heat exchanger 3. The load side units B1 and B2 have load side heat exchangers 5a and 5b and expansion valves 4a and 4b which are throttle devices with variable opening. The compressor 1, the four-way valve 2, the heat source side heat exchanger 3, the expansion valves 4a and 4b, and the load side heat exchangers 5a and 5b form a refrigerant circuit for circulating the refrigerant.

  The heat source side heat exchanger 3 is provided with a heat source side air blower 6 for blowing air. The load side heat exchangers 5a and 5b are also provided with load side air blowers 7a and 7b for similarly blowing air. These blowers are fans that blow air, and are constituted by a centrifugal fan or a multiblade fan that is driven by a DC motor (not shown), and the amount of blown air can be adjusted.

  The compressor 1 is a positive displacement compressor capable of varying an operating capacity (frequency). As a control method for changing the operation capacity, for example, there is a method by driving a motor controlled by an inverter or a method using a slide valve.

  The valves 11a and 11b provided at the piping outlet of the heat source side unit A are constituted by valves that can be opened and closed such as ball valves or on / off valves and operation valves.

  In the first embodiment, a configuration in which there are two load side units (B1, B2) will be described as an example. However, the present invention is not limited to this, and one load side unit or A plurality of three or more may be used. Moreover, even if each capacity | capacitance of several load side units differs from large to small, all may be the same capacity | capacitance.

In addition, the kind of the refrigerant | coolant which circulates through the refrigerant circuit of the air conditioning apparatus 100 in this Embodiment 1 does not have limitation in particular, Arbitrary refrigerant | coolants can be used. For example, in addition to natural refrigerants such as carbon dioxide (CO ₂ ), hydrocarbons, and helium, refrigerants that do not contain chlorine, such as R410A and alternative refrigerants such as R407C and R404A, may be employed.

  In addition, although this Embodiment 1 demonstrates the case where the four-way valve 2 is provided and the refrigerant circuit which can switch heating operation and cooling operation is comprised, this invention is not limited to this. For example, without providing the four-way valve 2, only one of the cooling operation and the heating operation may be performed.

Subsequently, the sensors and the control unit will be described.
The heat source side unit A includes a discharge temperature sensor 41, a suction temperature sensor 42, a heat source side air temperature sensor 40, a discharge pressure sensor 31, and a suction pressure sensor 32 as an operation state quantity detection device. The heat source side unit A further includes, as an operating state quantity detection device, a compressor frequency detecting means (not shown) for detecting the operating capacity (frequency) of the compressor 1 and a compressor input detecting means for detecting the compressor input (see FIG. Not shown).

  The discharge temperature sensor 41 is installed on the discharge side of the compressor 1 and detects the temperature of the refrigerant discharged from the compressor 1. The suction temperature sensor 42 is installed on the suction side of the compressor 1 and detects the temperature of the refrigerant sucked into the compressor 1. The discharge temperature sensor 41 and the suction temperature sensor 42 are provided so as to be in contact with or inserted into the refrigerant pipe, and detect the refrigerant temperature.

  The heat source side air temperature sensor 40 detects the ambient air temperature of the heat source side unit A in which the heat source side heat exchanger 3 is installed (for example, the ambient air temperature outside the room if installed outside the room).

  The discharge pressure sensor 31 is installed on the discharge side of the compressor 1 and detects the pressure of the refrigerant discharged from the compressor 1. The suction pressure sensor 32 is installed on the suction side of the compressor 1 and detects the pressure of the refrigerant sucked into the compressor 1. The condensation temperature CT of the refrigeration cycle can be obtained by converting the pressure detected by the discharge pressure sensor 31 into the saturation temperature, and the refrigeration cycle can be obtained by converting the pressure detected by the suction pressure sensor 32 into the saturation temperature. The evaporation temperature ET can be determined.

  Note that the installation positions of the discharge pressure sensor 31 and the discharge temperature sensor 41 are not limited to the illustrated positions, and may be provided anywhere as long as the section extends from the discharge side of the compressor 1 to the four-way valve 2. It may be done. Further, the installation positions of the suction pressure sensor 32 and the suction temperature sensor 42 are not limited to the illustrated positions, and may be provided anywhere in the section from the four-way valve 2 to the suction side of the compressor 1. It may be done.

  The load-side units B1 and B2 include gas-side temperature sensors 44a and 44b, liquid-side temperature sensors 45a and 45b, and load-side air temperature sensors 43a and 43b as operation state quantity detection devices.

  The gas side temperature sensors 44a and 44b detect the temperature of the refrigerant flowing out from the load side heat exchangers 5a and 5b during the cooling operation.

  The liquid side temperature sensors 45a and 45b detect the temperature of the refrigerant flowing out of the load side heat exchangers 5a and 5b during the heating operation.

  The load-side air temperature sensors 43a and 43b detect the ambient air temperature of the load-side units B1 and B2 where the load-side heat exchangers 5a and 5b are installed (for example, the ambient air temperature inside the room if installed indoors). To do.

FIG. 2 is a control block diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention.
FIG. 2 illustrates a connection configuration of the control unit 30 that performs measurement control of the air-conditioning apparatus 100 according to Embodiment 1 and sensors and actuators connected thereto.

  The control unit 30 is built in, for example, the heat source side unit A, and includes a measurement unit 30a, a calculation unit 30b, a drive unit 30c, a storage unit 30d, and a determination unit 30e. The control unit 30 functionally realizes an initial learning correction unit, a determination index calculation unit, a reference value setting unit, and a deterioration determination unit of the present invention.

  The operation state quantity detected by various sensors (pressure sensor and temperature sensor) is input to the measurement unit 30a, and the pressure and temperature are measured. The measurement unit 30a also measures the operation state quantity such as the operation capacity of the compressor 1 and the compressor input. The operation state quantity measured by the measurement unit 30a is input to the calculation unit 30b.

  The computing unit 30b is based on the operating state quantity measured by the measuring unit 30a and uses, for example, a functional property or a function table (table) stored in the storage unit 30d, for example, a refrigerant physical property value (saturation pressure, saturation temperature, enthalpy, etc.). Is calculated. Moreover, the calculating part 30b performs arithmetic processing, such as calculating the determination parameter | index for performing deterioration determination of the compressor 1, based on the driving | running state amount measured by the measurement part 30a.

  The drive unit 30c drives the compressor 1, the expansion valves 4a and 4b, the heat source side fan 6, the load side fans 7a and 7b, and the like based on the calculation result of the calculation unit 30b.

  As a result of the calculation unit 30b, the storage unit 30d stores a predetermined constant, a function formula or a function table (table) for calculating the physical property value (saturation pressure, saturation temperature) of the refrigerant, and a compression efficiency reference value described later. A table or a function for obtaining is stored. These stored contents in the storage unit 30d can be rewritten as necessary. The storage unit 30d further stores a control program and a program corresponding to a flowchart described later, and the control unit 30 controls the entire air conditioner 100 according to the program in the storage unit 30d.

  The determination unit 30e performs processing such as comparison and determination based on the result obtained by the calculation unit 30b. The determination unit 30e performs a compressor deterioration determination that determines deterioration of the compressor 1 by determining a threshold value using an operation value calculated from the operation state amount detected by various sensors (pressure sensor and temperature sensor) as a determination index. Do. Details of the compressor deterioration determination will be described again.

  The measurement unit 30a, the calculation unit 30b, the drive unit 30c, and the determination unit 30e are configured by, for example, a microcomputer, and the storage unit 30d is configured by a semiconductor memory or the like.

  Further, the control unit 30 displays and outputs the processing result in the microcomputer by an LED or a monitor or the like, or outputs information to a remote place by a communication means (not shown) such as a telephone line, a LAN line, and a radio. An output unit 30g is connected. The control unit 30 is further connected to an input unit 30f for inputting communication data information from a communication means (not shown) such as an operation input from a remote controller or switches on the board, a telephone line, a LAN line, or wireless. .

  In the configuration example of the present embodiment, the control unit 30 is built in the heat source unit A, but the present invention is not limited to this. By providing a main control unit in the heat source side unit A and a sub control unit having a part of the function of the control unit in the load side units B1 and B2, and performing data communication between the main control unit and the sub control unit It is good also as a structure which performs a cooperation process. In addition, it is good also as a structure which installs the control part which has all the functions in load side unit B1, B2, or the form which separately arranges a control part in these.

《Normal operation mode (cooling operation)》
Next, the cooling operation that is the normal operation mode of the air-conditioning apparatus 100 according to Embodiment 1 will be described with reference to FIG. During the cooling operation, the four-way valve 2 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the heat source side heat exchanger 3, and the suction side of the compressor 1 is the load side heat exchanger 5a, 5b. It is in a connected state.

  The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows into the heat source side heat exchanger 3 that is a condenser through the four-way valve 2. The refrigerant that has flowed into the heat source side heat exchanger 3 is condensed and liquefied by the blowing action of the heat source side fan 6 and becomes a high-pressure and low-temperature refrigerant. The condensed and liquefied high-temperature and low-pressure refrigerant is decompressed by the expansion valves 4a and 4b to become a two-phase refrigerant, and is sent to the load-side heat exchangers 5a and 5b which are evaporators. The refrigerant sent to the load-side heat exchangers 5a and 5b evaporates by the blowing action of the load-side fans 7a and 7b, and becomes a low-pressure gas refrigerant. The low-pressure gas refrigerant is sucked into the compressor 1 through the four-way valve 2.

  Here, the flow rate of the refrigerant flowing through the load side heat exchangers 5a and 5b with the opening degree of the expansion valves 4a and 4b adjusted so that the refrigerant superheat degree at the outlets of the load side heat exchangers 5a and 5b becomes a predetermined value, respectively. Is controlling. For this reason, the low-pressure gas refrigerant evaporated in the load-side heat exchangers 5a and 5b has a predetermined degree of superheat. The refrigerant superheat degree at the outlets of the load side heat exchangers 5a and 5b is a value obtained by subtracting the saturation temperature conversion value (evaporation temperature ET) of the pressure detection value of the suction pressure sensor 32 from the detection value of the gas side temperature sensors 44a and 44b. To detect. As described above, the flow rate refrigerant according to the operation load required in the air-conditioned space in which the load-side units B1 and B2 are installed flows through the load-side heat exchangers 5a and 5b.

《Normal operation mode (heating operation)》
Next, the operation operation of the heating operation that is the normal operation mode of the air-conditioning apparatus 100 according to Embodiment 1 will be described with reference to FIG. During the heating operation, the four-way valve 2 is shown in a broken line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the load side heat exchangers 5a and 5b, and the suction side of the compressor 1 is the heat source side heat exchanger 3 It is in a connected state.

  The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the load-side heat exchangers 5a and 5b, which are condensers, via the four-way valve 2, and is condensed and liquefied by the blowing action of the load-side fans 7a and 7b. It becomes a low-temperature refrigerant. The condensed and liquefied high-temperature and low-pressure refrigerant is decompressed by the expansion valves 4 a and 4 b to become a two-phase refrigerant, and is sent to the heat source side heat exchanger 3. The decompressed two-phase refrigerant evaporates by the blowing action of the heat source side fan 6 in the heat source side heat exchanger 3 which is an evaporator, and becomes a low pressure gas refrigerant. Then, the low-pressure gas refrigerant is sucked into the compressor 1 through the four-way valve 2.

  Here, the expansion valves 4a and 4b adjust the opening degree so that the refrigerant subcooling degree at the outlets of the load side heat exchangers 5a and 5b becomes a predetermined value, respectively, and the refrigerant flowing through the load side heat exchangers 5a and 5b. The flow rate is controlled. For this reason, the liquid refrigerant condensed in the load side heat exchangers 5a and 5b is in a state having a predetermined degree of supercooling. The refrigerant supercooling degree at the outlets of the load side heat exchangers 5a and 5b is a value obtained by subtracting the detection values of the liquid side temperature sensors 45a and 45b from the saturated temperature converted value (condensation temperature CT) of the pressure detection value of the discharge pressure sensor 31. Detect with. As described above, the flow rate refrigerant according to the operation load required in the air-conditioned space in which the load-side units B1 and B2 are installed flows through the load-side heat exchangers 5a and 5b.

《Compression efficiency》
FIG. 3 is a Mollier diagram (Ph diagram) for explaining the compression efficiency that is used as a determination index for compressor deterioration in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.

  In the vapor compression refrigeration cycle, which is the operating principle of the air conditioner 100, when the compressor 1 performs adiabatic compression, the refrigerant undergoes an isentropic change as indicated by the broken line in FIG. After being compressed from point A to point B, it is cooled to point C in the condensation stroke. The refrigerant cooled to the point C is depressurized to the point D in the expansion stroke and is heated to the point A in the evaporation stroke, and circulates in the refrigerant circuit.

  In an actual compressor, heat loss occurs during compression, so adiabatic compression (isentropic change) does not occur in the compression stroke, and the actual compression stroke changes from point A to point B ′ as shown by the solid line in FIG. It becomes. Assuming that the power when the compressor performs adiabatic compression is the theoretical compression power, the actual compression requires a larger power than the theoretical compression power. The ratio of the power given to the refrigerant in the actual compression and the theoretical compression power is called compression efficiency (adiabatic efficiency), and the compression efficiency (adiabatic efficiency) is smaller than 1, generally about 0.6 to 0.7. Become. The compression efficiency can be expressed by the following equation.

here,
ηc: compression efficiency (adiabatic efficiency) [−]
Wth: Theoretical compression power [kW]
Wcomp: Actual compression power [kW]
ΔHad: Theoretical enthalpy difference [kJ / kg]
ΔHcomp: Actual compression enthalpy difference [kJ / kg]

  Thus, the compression efficiency is different from the actual compressor in theory. Therefore, in this Embodiment 1, compression efficiency is correct | amended to the value suitable for an actual compressor, and the value after correction | amendment is used as a threshold value of compressor deterioration determination. Thus, the operation | movement which calculates | requires the determination threshold value suitable for an actual compressor is performed in the below-mentioned initial learning mode.

  Moreover, the change of each refrigerating cycle when a long time (for example, several years) passes since installation and when a compressor deteriorates can also be demonstrated with FIG. That is, at the initial stage of installation, the refrigerant is compressed from the point A to the point B in the compression stroke, and then cooled to the point C in the condensation stroke. The refrigerant cooled to the point C is depressurized to the point D in the expansion stroke and is heated to the point A in the evaporation stroke, and circulates in the refrigerant circuit.

  However, if the compressor deteriorates after a long period of time (for example, several years) after installation, even if the suction side refrigerant state (point A) of the compressor is the same, the curve of the compression stroke changes and the discharge side refrigerant state changes. The point B moves to the point B ′. In this case, the enthalpy difference in the compressor corresponding to the compressor input increases from the beginning of installation, and the compression efficiency decreases. In other words, the discharge refrigerant pressure Pd and the suction refrigerant pressure Ps are the same in the movement from the point A to the point B and the movement from the point A to the point B ′, that is, the compression ratio (= discharge refrigerant pressure / (Suction refrigerant pressure) is the same, but changes in the enthalpy difference result in different compression efficiencies.

  Further, the compression efficiency takes different values depending on the refrigeration cycle state, that is, the operating state of the air conditioner 100. For example, the compression efficiency ηc with respect to the compression ratio γ has characteristics as shown in FIG. 4. When the compression ratio γ changes, the compression efficiency ηc also changes. For this reason, when the deterioration determination of the compressor 1 is performed, it is necessary to compare the compression efficiency ηc at the time of installation when the compression ratio γ is the same with the current compression efficiency ηc. And the determination accuracy can be improved by setting the compression efficiency ηc at the same compression ratio γ at the time of installation to a value that matches the actual performance of the compressor 1 as described above.

  Here, the compression efficiency ηc has been described as a function using the compression ratio γ as a variable, but may be a function using other operating state quantities as variables. That is, the compression ratio = discharge pressure / suction pressure, and the compression ratio changes even if one or both of the discharge pressure and the suction pressure are changed. Further, since the discharge pressure has a one-to-one correspondence with the condensation temperature CT, which is the saturation temperature, and the evaporation temperature ET, which is the saturation temperature, the discharge pressure has the same meaning. Further, since the compression ratio changes even if the compressor frequency is changed, there is interlocking. Therefore, the compression efficiency η may be a function having the discharge pressure, the suction pressure, the condensation temperature CT, and the evaporation temperature ET as variables.

<Compressor deterioration judgment method>
A compressor deterioration determination method in the air-conditioning apparatus 100 according to Embodiment 1 will be described. When the compressor 1 deteriorates after a certain period of time has elapsed since the installation of the air conditioner 100, the actual compression power increases with respect to the theoretical compression power, and the compression efficiency ηc decreases. In the first embodiment, the compression efficiency (compression efficiency reference value ηcm) calculated from the operation state at the initial stage of installation is compared with the compression efficiency ηc calculated from the operation state when a predetermined period has elapsed since installation. 1 degradation is determined.

  Hereinafter, the compressor deterioration determination mode, which is a characteristic part of the first embodiment, will be described. Note that the operation of the refrigerant circuit portion in the compressor deterioration determination mode will be described as all cooling operations.

《Compressor deterioration judgment mode》
FIG. 5 is a flowchart showing a flow of compressor deterioration determination in the air-conditioning apparatus according to Embodiment 1 of the present invention. Hereinafter, a specific operation of the compressor deterioration determination will be described based on the flowchart of FIG.

  After starting the compressor deterioration determination flow, the control unit 30 determines whether or not initial learning for storing the initial state of the compression efficiency ηc of the air conditioner 100 is performed (step S1). When it is determined that the initial learning has been completed (step S1; YES), the control unit 30 proceeds to the next step as it is. When it is determined that the initial learning has not been completed (step S1; NO), the control unit 30 operates the initial learning mode (step S2), and proceeds to the next step after the initial learning mode ends. The initial learning mode is a determination criterion value for determining the deterioration of the compressor suitable for the actual performance of the compressor 1 depending on the occasion when the deterioration determination of the compressor is performed (the criterion of the determination index for determining whether or not the compressor 1 has deteriorated). This is an operation for obtaining information for dynamically setting (value) (corresponding to the “real relationship” of the present invention, specifically a table or a function), and is performed at the initial installation of the air conditioner 100. Specific operations in the initial learning mode will be described later.

  Next, a normal operation mode that is a normal operation in the air conditioner 100 is activated (step S3). After the normal operation mode is activated, the operation state quantity of the air conditioner 100 is detected by the measurement unit 30a (step S4). After detecting the operating state quantity, the calculation unit 30b calculates the compression efficiency ηc, which is a determination index, using the detected operating state quantity and the physical property value of the refrigerant (step S5). The compression efficiency ηc can be calculated by the following formula.

here,
ηv: volumetric efficiency [−]
Vst: Stroke volume [cc]
F: Compressor frequency [Hz]
W: Compressor input [kW]
ρs: Refrigerant density [kg / m ³ ]
Hdad: Theoretical discharge enthalpy [kJ / kg]
Hs: Inhalation enthalpy [kJ / kg]

  The volume efficiency ηv uses a constant such as 0.9 as a general value. Since the stroke volume Vst is determined by the compressor specification, the specification value of the diagnosis target compressor 1 is used. These values are stored in advance in the storage unit 30d, and the calculation unit 30b refers to the values stored in the storage unit 30d and uses them for calculation.

  The compressor frequency F and the compressor input W are detected as operating state quantities by the measuring unit 30a. The suction refrigerant density ρs, the theoretical discharge enthalpy Hdad, and the suction enthalpy Hs are obtained from the operating state quantity and the refrigerant physical properties. The suction refrigerant density ρs is obtained from the suction refrigerant pressure Ps, the suction refrigerant temperature Ts, and the refrigerant physical property value. The theoretical discharge enthalpy Hdad is obtained from the discharge refrigerant pressure Pd, the intake refrigerant pressure Ps, the intake refrigerant temperature Ts, and the refrigerant physical property value. The suction enthalpy Hs is obtained from the suction refrigerant pressure Ps, the suction refrigerant temperature Ts, and the refrigerant property value. Each operating state quantity uses a detection value detected by the measuring unit 30a, and a refrigerant physical property value is used with reference to a refrigerant physical function stored in the storage unit 30d in advance.

  The expression for obtaining the compression efficiency ηc may be the following expression.

here,
Hd: Discharge enthalpy [kJ / kg]

  The discharge enthalpy Hd is obtained from the detected value of the discharge refrigerant pressure Pd and the discharge refrigerant temperature Td and the refrigerant physical property value.

  Next, the control unit 30 sets a compression efficiency reference value ηcm corresponding to the current compression ratio γ (step S6). In step S6, the control unit 30 first calculates the current compression ratio γ from the detected value of the discharge pressure sensor 31 and the detected value of the suction pressure sensor 32 among the operation state quantities detected in step S4. Then, the table acquired in the initial learning mode is referred to from the storage unit 30d, the table is referred to based on the current compression ratio, and the compression efficiency reference value ηcm is set. The table is, for example, a table in which a compression efficiency reference value ηcm is set for each compression ratio γ, as shown in FIG. If the current compression ratio γ is not in the table, the compression efficiency reference value ηcm may be set by performing a complementary operation such as linear interpolation, for example.

  Next, the determination unit 30e compares the compression efficiency ηc calculated in step S5 with the compression efficiency reference value ηcm set in step S6, and determines whether or not the compressor 1 of the air conditioner 100 has deteriorated. (Step S7). The determination unit 30e determines that the compressor 1 has deteriorated if ηc <ηcm (step S7; YES), and outputs a “compressor deterioration abnormality” signal from the output unit 30g (step S8). Then, the compressor deterioration determination mode is terminated. If ηc and ηcm are equal or close to each other, the determination unit 30e determines that the compressor 1 has not deteriorated (step S7; NO), and ends the compressor deterioration determination mode as it is.

  By the way, since the compression efficiency reference value ηcm set in step S6 is a value obtained based on the table acquired in the initial learning mode, the compression ratio γ at the initial stage of installation is the compression efficiency at the same compression ratio γ as at present. The compression efficiency reference value matches the actual performance of the compressor 1. By performing the compressor deterioration determination using the compression efficiency reference value ηcm, it is possible to perform a determination that matches the actual performance of the compressor 1 and to perform a highly accurate determination.

  In addition, the calculation method of compression efficiency (eta) c is not limited to the method of calculating by said Formula (1)-(3), The calculation method by another means may be sufficient.

  The determination threshold value for determining the compressor deterioration is not limited to the compression efficiency reference value ηcm itself calculated in the initial learning mode, but is a value lower than the compression efficiency reference value ηcm by a predetermined ratio, for example, the compression efficiency reference value ηcm. May also be set to a value 3% lower. That is, when the compression efficiency ηc decreases by 3% or more with respect to the compression efficiency reference value ηcm, it may be determined that the compressor 1 has deteriorated. By setting the determination threshold with a certain range in this way, the calculated compression efficiency can be calculated from factors other than the deterioration of the compressor (for example, the influence of external factors such as outside air temperature and outside wind at the outdoor unit installation location). It is possible to avoid misjudgment due to being estimated too low.

  Further, in the flowchart of FIG. 5, if it is determined once that the compressor 1 has deteriorated, a signal indicating “abnormal compressor deterioration” is output. For example, the deterioration determination is repeated a plurality of times, and the number of determinations is a predetermined number of times. When the above is reached, a signal indicating “abnormality of compressor deterioration” may be output. By doing so, it is possible to avoid abnormal reporting due to erroneous determination, and to realize highly accurate compressor deterioration determination.

《Initial learning mode》
FIG. 6 is a flowchart showing the flow of the initial learning mode in the air-conditioning apparatus according to Embodiment 1 of the present invention. Hereinafter, a specific operation in the initial learning mode will be described based on the flowchart of FIG.
During initial operation at the initial stage of installation, when the remote control or the switches on the board are operated by the installer or the like and the start of the initial learning mode is instructed, the control unit 30 receives the operation input via the input unit 30f, A screen for inputting initial learning conditions is displayed on, for example, a remote control screen. Here, the initial learning condition may be any operation condition, but a plurality of condition numbers are set.

  The initial learning condition is composed of the evaporation temperature ET and the condensation temperature CT. For example, two or more operating conditions with different compression ratios γ are input as the initial learning condition. Specifically, for example, ET = 2 ° C., CT = 45 ° C. operating conditions, ET = 2 ° C., CT = 48 ° C. operating conditions, ET = 5 ° C., CT = 45 ° C. operating conditions, ET = Operation conditions such as 5 ° C. and CT = 48 ° C. are input. Here, the following description will be given on the assumption that four operating conditions are designated as initial learning conditions.

  When the initial learning condition is input based on the screen for inputting the initial learning condition (step S21), the control unit 30 operates as follows. First, the first operation condition among the plurality of operation conditions input as the initial learning condition is set as the control target values ETm and CTm (step S22).

  Subsequently, the control unit 30 controls the actuator (the compressor 1 and the heat source side fan 6) so that the operation state satisfies the control target value (Step S23 to Step S26). This will be specifically described below.

  The control unit 30 controls the capacity (frequency) of the compressor 1 so that the evaporation temperature ET obtained by converting the pressure detected by the suction pressure sensor 32 into the saturation temperature becomes the target value ETm. That is, the control unit 30 compares the evaporation temperature ET with the target value ETm (step S23), and maintains the capacity of the compressor 1 as it is when the evaporation temperature ET is equal to or close to the target value ETm. (Step S23; YES), the process proceeds to the next step.

  On the other hand, when the evaporating temperature ET is significantly higher than the target value ETm (ET> ETm), the control unit 30 increases the capacity of the compressor 1 and the evaporating temperature ET is lower than the target value ETm. (ET <ETm), the capacity of the compressor 1 is reduced (step S23; NO, step S24).

  In addition, the control unit 30 controls the rotation speed of the heat source side fan 6 so that the condensation temperature CT obtained by converting the pressure detected by the discharge pressure sensor 31 into a saturation temperature becomes a preset target value CTm. That is, the control unit 30 compares the condensation temperature CT with the target value CTm (step S25). If the condensation temperature CT is equal to or close to the target value CTm, the rotation speed of the heat source side fan 6, that is, The fan air volume is maintained as it is (step S25; YES), and the process proceeds to the next step.

  On the other hand, when the condensation temperature CT is higher than the target value CTm (CT> CTm), the control unit 30 increases the rotational speed of the heat source side fan 6 to increase the air volume, and the condensation temperature CT becomes the target value CTm. If it is lower than that (CT <CTm), the rotational speed of the heat source side fan 6 is decreased and the air volume is decreased (step S25; NO, step S26). The load-side fans 7a and 7b are operated at a predetermined rotation speed here, but the rotation speeds of the load-side fans 7a and 7b may also be controlled.

  Thereafter, the control unit 30 determines whether or not the evaporation temperature ET and the condensation temperature CT have reached the target values ETm and CTm (step S27). If any one of the evaporation temperature ET and the condensation temperature CT has not reached the target value (step S27; NO), the process returns to step S23. If both the evaporation temperature ET and the condensation temperature CT are at the target values (step S27; YES), the process proceeds to the next step.

  Next, the operation state quantity of the air conditioner 100 is detected by the measurement unit 30a (step S28), and the calculation unit 30b uses the operation state quantity detected by the measurement unit 30a to obtain the compression efficiency ηc as an initial determination index. Calculate (step S29). The calculation method of the compression efficiency ηc here uses the same method as in the compressor deterioration determination mode described above (step S5).

  The calculation unit 30b compares the compression efficiency ηc obtained from the operating state quantity and the physical property value of the refrigerant with the compression efficiency reference value ηcm obtained from the table of the compression efficiency reference values ηcm stored in advance in the storage unit 30d, and calculates ηc And ηcm are discriminated (step S30).

  Here, the compression efficiency reference value ηcm is obtained as follows. The computing unit 30b obtains the compression efficiency reference value ηcm based on the table of compression efficiency reference values ηcm stored in advance in the storage unit 30d and the operating state quantity detected in step S28.

FIG. 7A is an example of a table of compression efficiency reference values ηcm stored in advance in the storage unit.
In the table, a plurality of compression ratios (calculated operating state quantities) γ and compression efficiency reference values ηcm are set in association with each other. Here, the compression efficiency reference values ηcm1 for each of the compression ratios γ1, γ2, γ3, and γ4. , Ηcm2, ηcm3, and ηcm4 are set. The compression efficiency reference value ηcm in the table is obtained in advance by performing a simulation or the like based on the compressor performance characteristics of the target model, and corresponds to the standard reference value of the present invention.

  The calculation unit 30b obtains the current compression ratio γ by dividing the discharge refrigerant pressure detected by the discharge pressure sensor 31 by the suction refrigerant pressure detected by the suction pressure sensor 32, and refer to FIG. To obtain the compression efficiency reference value ηcm. For example, if the current compression ratio γ is γ1, the compression efficiency reference value ηcm is obtained as ηcm1.

  As described above, when it is determined that the compression efficiency ηc obtained from the operation state quantity and the refrigerant property value is different from the compression efficiency reference value ηcm (step S30; YES), the calculation unit 30b determines the compression efficiency ηc. It correct | amends as new compression efficiency reference value (eta) cm (step S31), and progresses to the following step. Further, when the calculation unit 30b determines that the compression efficiency ηc and the compression efficiency reference value ηcm are not deviated (step S30; NO), the calculation unit 30b proceeds to the next step as it is.

  Here, the determination as to whether or not the compression efficiency ηc and the compression efficiency reference value ηcm are different is performed as follows, for example. That is, when the difference between the compression efficiency ηc and the compression efficiency reference value ηcm is greater than or equal to a preset ratio, for example, when it is 3% or more of the compression efficiency reference value ηcm, it is determined that there is a divergence and is less than 3% It is determined that there is no divergence.

  In the next step, it is determined whether or not all the operations under the respective initial operating conditions are completed (step S32). Here, since the operation of the second operating condition has not been completed yet (step S32; NO), the process returns to step S22 and the same operation is performed under the second operating condition. When the operation under all four operating conditions is completed, and the compression efficiency reference value corresponding to each operating condition is appropriately corrected and the initial learning is completed (step S32; YES), the control unit 30 performs the initial learning mode. Exit.

  FIG. 7B is an example of a table after correction of the compression efficiency reference value ηcm. In the example of FIG. 7B, the compression efficiency reference value ηcm of the compression ratios γ1 and γ2 is corrected from ηcm1 and ηcm2 to ηcm6 and ηcm7.

  In the initial learning mode, the refrigerant circuit is actually operated at the initial stage of installation to correct the compression efficiency reference value ηcm. Therefore, the compression efficiency reference value ηcm suitable for the actual performance of the compressor 1 can be obtained.

<Effect>
In the first embodiment, during the initial operation, the determination reference value (compression efficiency reference value ηcm) is based on the operation state amount and the physical property value of the refrigerant circuit when the operation conditions of the refrigerant circuit are changed while satisfying the respective operation conditions. An initial learning mode for correcting the table is performed. As a result, a determination reference value that matches the actual performance of the compressor 1 can be obtained. Then, at the time of compressor deterioration determination, a determination reference value is dynamically set based on the current operating state quantity from the corrected determination reference value table to determine a reduction in compression efficiency. That is, since the compressor deterioration determination can be performed using the compression efficiency reference value ηcm suitable for the actual performance of the compressor 1 as a threshold value, the highly accurate compressor deterioration determination can be realized.

  In addition, in the case of a method for performing compressor deterioration determination using one determination reference value, it is necessary to perform compressor deterioration determination after aligning the current operation state with the same operation state as when the determination reference value is set. There is. However, in the first embodiment, a plurality of determination reference values that can correspond to each of a plurality of operation conditions, in other words, a plurality of determination reference values that can correspond to a wide range of operation conditions, are acquired, and the compressor deterioration determination is performed. Sometimes, since the determination reference value corresponding to the current operation state (compression ratio γ in the above example) is dynamically set, the compressor deterioration determination can be performed during normal operation according to the air conditioning load. That is, it is possible to perform highly accurate compressor deterioration determination over a wide operation range without requiring special operation for making a specific refrigerant state at the time of compressor deterioration determination. That is, it is possible to determine the compressor deterioration while maintaining energy saving and comfort during normal operation of the air conditioner 100.

  In addition, since the air conditioner 100 according to the first embodiment issues a notification when it is determined that the compressor 1 is deteriorated abnormally, it is easy for the user or maintenance contractor to grasp the compressor deterioration state.

  In the above description, the initial learning condition is input from the input unit 30f from the outside in step S21 of FIG. 6, but the initial learning condition may be stored in advance in the storage unit 30d. Here, the evaporation temperature ET and the condensation temperature CT are input as operating conditions. However, the pressure values of the high pressure and the low pressure may be input, or the compression ratio γ is input. Of course it is good.

  Here, the table of the compression efficiency reference value ηcm is a format for obtaining the compression efficiency reference value ηcm based on the compression ratio γ, but the condensation temperature CT is the saturation temperature of the discharge refrigerant pressure, the suction refrigerant pressure, and the discharge refrigerant pressure. Alternatively, the compression efficiency reference value ηcm may be obtained based on the operating state quantity such as the evaporation temperature ET, which is the saturation temperature of the suction refrigerant pressure, and the compressor capacity (frequency). For example, as shown in FIG. 8, it is good also as a form which calculates | requires compression efficiency reference value (eta) cm according to the combination of condensation temperature CT and evaporation temperature ET.

  In the first embodiment, the table of the compression efficiency reference value ηcm is corrected. In short, the relationship between the compressor ratio γ and the compression efficiency reference value ηcm is stored in the storage unit 30d in advance, and the relationship It is sufficient to create an actual relationship that reflects actual performance by correcting. Therefore, for example, instead of the table, a function of the compression efficiency reference value ηcm using the compression ratio γ as a variable may be stored in the storage unit 30d in advance, and the function may be corrected. Since the compression ratio γ and the compression efficiency reference value ηcm have a relationship as shown in FIG. 4, a plurality of combinations of the compression ratio γ and the compression efficiency reference value ηcm can be acquired and mathematically expressed by polynomial approximation. Since the approximate expression is represented by a variable (in this case, a compression ratio) and a coefficient (constant), the function may be corrected by changing the coefficient.

  In the first embodiment, a table is created in advance by simulation or the like, and a table reflecting actual performance is created by correcting the table. A table (actual relationship) reflecting the performance may be created. The processing flow in this case is shown in FIG. In FIG. 9, step S33 is provided instead of step S30 and step S31 of FIG. The other steps are the same as in FIG. In the processing flow of FIG. 9, as shown in step S33, an actual relationship between the compression efficiency ηc obtained in step S29 and the operating state (here, the compression ratio) is created.

  Here, the initial learning mode in FIG. 6 (hereinafter referred to as initial learning mode 1) is compared with the initial learning mode in FIG. 9 (initial learning mode 2). FIG. 9 is a flowchart showing a modified example (initial learning mode 2) of the flow in the initial learning mode in the air-conditioning apparatus according to Embodiment 1 of the present invention. In the initial learning mode 2, unlike the initial learning mode 1, an actual relationship is created from scratch. For this reason, in order to create a highly accurate actual relationship in the initial learning mode 2, a sufficient number of operating conditions of the initial learning conditions need to be specified. On the other hand, in the initial learning mode 1, since the actual relationship is obtained by correcting the relationship obtained by simulation in advance, a highly accurate actual relationship can be obtained even if the number of operating conditions is small. For this reason, in the initial learning mode 1, the initial learning mode can be finished earlier and the normal operation can be started than when the initial learning mode 2 is performed.

  In the initial learning mode 2, a plurality of operating conditions are required as described above. However, depending on the operating conditions, it may be difficult to achieve an operating state that satisfies the operating conditions. For example, there are driving conditions that are difficult to achieve in winter, even if they are easy in summer. For this reason, in the summer season, only the driving conditions corresponding to the summer season are realized, that is, data for creating an actual relationship is reduced. On the other hand, in the initial learning mode 1, it is possible to determine the deterioration of the compressor 1 in a wide operation range by creating a relationship in advance so as to be compatible with a wide operation range.

  In the first embodiment, the driving situation is positively changed so as to sequentially satisfy each of the plurality of driving conditions during the initial driving, but the present invention is not limited to this. For example, at the time of operation of the air conditioner, a target temperature is normally set and the operation is performed so as to be the target temperature. During such operation, the evaporating temperature and the condensing temperature fluctuate according to the indoor temperature environment and the like. For this reason, for example, when the evaporation temperature is set as an operation condition and the operation of the air conditioner 100 is started in the initial operation, the evaporation temperature of the refrigerant circuit becomes the evaporation temperature specified as the operation condition. The condensation temperature may be acquired and the compressor efficiency may be calculated in the same manner as described above.

  Further, the variable of the function of the compression efficiency reference value ηcm is not limited to the compression ratio γ, and as in the case of the table, the discharge refrigerant pressure, the suction refrigerant pressure, the condensation temperature CT that is the saturation temperature of the discharge refrigerant pressure, the suction It is good also as evaporation temperature ET which is the saturation temperature of refrigerant pressure, compressor capacity (frequency), etc.

  The determination index for compressor deterioration is not limited to the absolute value of the compression efficiency ηc calculated from the operating state quantity, and a compression efficiency state estimated value that can estimate the state of the compression efficiency ηc may be used. As the estimated value of the compression efficiency state, calculated values using the discharge refrigerant temperature Td, the intake refrigerant temperature Ts, the discharge refrigerant pressure Pd, and the intake refrigerant pressure Ps of the compressor 1 are used. For example, the discharge refrigerant temperature Td and the intake refrigerant temperature A temperature difference ΔT (= Td−Ts) with respect to Ts can be used.

  Thus, instead of the compression efficiency ηc, it is possible to determine the compression efficiency decrease using the compression efficiency state estimated value that can estimate the state of the compression efficiency ηc as a determination index. When the compression efficiency state estimated value is used as a substitute for the compression efficiency ηc, the compression efficiency state estimated value is replaced with the compression efficiency state estimated value by replacing the compression efficiency portion in the compressor deterioration determination method of the first embodiment. By determining that the compression efficiency ηc is decreasing when the value is higher than the value, it is possible to determine the compressor deterioration.

  For example, when the compression efficiency state estimated value is the temperature difference ΔT between the discharge refrigerant temperature Td and the suction refrigerant temperature Ts, a table in which a reference value ΔTm of the temperature difference for each compression ratio γ is set in advance is stored. Store in 30d. In the initial learning mode, instead of calculating the compression efficiency ηc in step S29 after the processing in steps S21 to S28, the detection value of the suction temperature sensor 42 is subtracted from the detection value of the discharge temperature sensor 41. A temperature difference ΔT between the temperature Td and the suction refrigerant temperature Ts is obtained.

  Then, the calculation unit 30b obtains the current compression ratio γ by dividing the discharge refrigerant pressure detected by the discharge pressure sensor 31 by the suction refrigerant pressure detected by the suction pressure sensor 32, and is stored in advance in the storage unit 30d. The reference value ΔTm of the temperature difference is obtained by referring to the table of the reference value ΔTm of the temperature difference. Then, the calculation unit 30b determines whether the temperature difference ΔT and the temperature difference reference value ΔTm deviate from each other. If there is a difference, the calculation unit 30b corrects the temperature difference ΔT as a new temperature difference reference value ΔTm and deviates. If not, the same processing is performed under the following operating conditions. This is performed under all operating conditions, and the temperature difference reference value ΔTm is corrected.

  When the compressor deterioration is determined, the temperature difference ΔT between the discharge refrigerant temperature Td and the intake refrigerant temperature Ts is calculated by subtracting the detection value of the intake temperature sensor 42 from the detection value of the discharge temperature sensor 41. Further, the temperature difference standard value ΔTm is set with reference to the table based on the current compression ratio γ, and the calculated temperature difference ΔT is compared with the temperature difference standard value ΔTm. When the calculated temperature difference ΔT rises by a predetermined value or more from the temperature difference reference value ΔTm, it is determined that the compressor 1 has deteriorated, and the calculated temperature difference ΔT is a predetermined value or more than the temperature difference reference value ΔTm. If it is not increased, it may be determined that the compressor 1 has not deteriorated.

  In addition, although the operation of the refrigerant circuit portion in the compressor deterioration determination mode in the present embodiment has been described as the cooling operation, the operation of the refrigerant circuit portion may be the heating operation. In the case of heating operation, the relationship between the evaporation temperature ET and the condensation temperature CT in the initial learning mode operation shown in FIG. 6 is reversed. That is, the condensation temperature CT is controlled to the target value by changing the compressor capacity, and the evaporation temperature ET is controlled to the target value by changing the heat source side fan air volume. In this way, by changing the control target, the same determination operation as in cooling can be performed during heating operation.

Embodiment 2. FIG.
The second embodiment is partially different from the first embodiment in the process of determining the compressor deterioration in the air conditioner 100, and the configuration of the air conditioner 100 is the same as that of FIG.

  FIG. 10 is a flowchart showing a flow of compressor deterioration determination in the air-conditioning apparatus according to Embodiment 2 of the present invention. Hereinafter, based on FIG. 10, an operation that is a characteristic part of the air-conditioning apparatus 100 according to Embodiment 2 will be described. In the second embodiment, the difference from the first embodiment will be mainly described. Steps S41 to S46 and Steps S48 to S49 in FIG. 10 are the same as Steps S1 to S6 and Steps S7 to S8 in FIG.

《Compressor deterioration judgment mode》
In step S47, the determination unit 30e determines whether or not the compressor capacity (frequency) detected by the measurement unit 30a is greater than or equal to a predetermined value. If the compressor capacity is equal to or greater than the predetermined value (step S47; YES), the process proceeds to the next step and proceeds to the compressor deterioration determination. For example, 80% of the maximum frequency in use is set as the predetermined value. Here, the size of the compressor capacity is determined, but the size of the compression ratio γ may be determined instead of the compressor capacity. When the compression ratio γ is used, the compressor deterioration is determined within the range of the compression ratio condition such that the compressor capacity becomes a predetermined value or more.

<Effect>
According to the second embodiment, the same effects as those of the first embodiment can be obtained, and the following effects can be obtained by performing the compressor deterioration determination only on the condition that the compressor capacity becomes high. . That is, for example, it is possible to estimate a more accurate compression efficiency ηc by suppressing fluctuations in sensor measurement values such as the discharge refrigerant temperature Td due to external factors such as outside air conditions (outside temperature, outside wind, etc.), and high accuracy. Compressor deterioration judgment can be realized.

Embodiment 3 FIG.
The third embodiment is partly different in processing at the time of compressor deterioration determination in the air conditioner 100, and the configuration of the air conditioner 100 is the same as that of FIG.

  FIG. 11 is a flowchart showing a flow of compressor deterioration determination in the air-conditioning apparatus according to Embodiment 3 of the present invention. Hereinafter, based on FIG. 11, an operation that is a characteristic part of the air-conditioning apparatus 100 according to Embodiment 3 will be described. In the third embodiment, the difference from the first embodiment will be mainly described. Steps S61 to S66 and Steps S69 to S70 in FIG. 11 are the same as Steps S1 to S6 and Steps S7 to S8 in FIG.

《Compressor deterioration judgment mode》
In step S67, the control unit 30 detects the compressor integrated operation time t, which is the integrated operation time from the start of compressor operation after the initial installation, by the measurement unit 30a. Thereafter, the determination unit 30e determines whether or not the compressor integrated operation time t has exceeded a predetermined time that is predicted to start the deterioration of the compressor 1 (step S68). If the compressor integrated operation time t is equal to or longer than the predetermined time (step S68; YES), the process proceeds to the next step to determine the compressor deterioration. If the compressor integrated operation time t is less than the predetermined time (step S68; NO), the compressor deterioration determination mode is terminated as it is.

  Here, the condition for entering the compressor deterioration determination has been described as a case where the compressor integrated operation time t has passed a predetermined time or more, but may be as follows. That is, instead of the compressor integrated operation time t, the number of start / stop times from the start of compressor operation is used, and if the compressor start / stop number is equal to or greater than the predetermined number of times that the compressor starts to deteriorate, the compressor deterioration determination If it is less than the predetermined number of times, the compressor deterioration determination mode may be terminated as it is.

<Effect>
According to the third embodiment, the same effects as in the first embodiment can be obtained, and the following effects can be obtained. That is, by determining the compressor deterioration determination in consideration of the accumulated operation time or the number of start / stop times of the compressor 1, it is possible to more accurately determine a reduction in compression efficiency due to deterioration over time, and to determine a highly accurate compressor deterioration determination. Can be realized.

《Cooling device modification》
The features of the present invention have been described in each embodiment. For example, the refrigerant flow path configuration (piping connection), the configuration of refrigerant circuit elements such as a compressor, a heat exchanger, and an expansion valve, etc. The present invention is not limited to the contents described in the embodiments, and can be appropriately changed within the scope of the technology of the present invention.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 Four way valve, 3 Heat source side heat exchanger, 4a, 4b Expansion valve, 5a, 5b Load side heat exchanger, 6 Heat source side fan (heat source side air blower), 7a, 7b Load side fan (load side) Blower), 11a, 11b valve, 30 control unit, 30a measurement unit, 30b calculation unit, 30c drive unit, 30d storage unit, 30e determination unit, 30f input unit, 30g output unit, 31 discharge pressure sensor, 32 suction pressure sensor , 40 Heat source side air temperature sensor, 41 Discharge temperature sensor, 42 Suction temperature sensor, 43a, 43b Load side air temperature sensor, 44a, 44b Gas side temperature sensor, 45a, 45b Liquid side temperature sensor, 100 Air conditioner, A Heat source Side unit, B1, B2 Load side unit.

Claims (9)

A refrigerant circuit having a compressor, a condenser, a throttling device, and an evaporator capable of varying the operation capacity, and configured to circulate the refrigerant;
An operation state amount detection device for detecting an operation state amount of the refrigerant circuit;
During the initial operation of the refrigerant circuit, every time the operation state of the refrigerant circuit satisfies a predetermined operation condition , the temperature difference between the discharge refrigerant temperature and the intake refrigerant temperature is calculated based on the operation state quantity of the operation state quantity detection device. An initial learning unit that obtains a certain criterion value and creates an actual relationship between the obtained criterion value and the operating state of the refrigerant circuit;
A determination index calculation unit that calculates a current determination index , which is a temperature difference between the discharge refrigerant temperature and the intake refrigerant temperature , based on the operation state quantity of the operation state quantity detection device;
A reference value setting unit that sets a determination reference value corresponding to the current operating state based on the actual relationship created by the initial learning unit;
When the current determination index calculated by the determination index calculation unit is higher than the determination reference value by a predetermined value or more, it is determined that the compressor has deteriorated, and the current determination index is lower than the determination reference value. An air conditioner comprising: a deterioration determination unit that determines that the compressor has not deteriorated unless the pressure is increased by a predetermined value or more . A storage unit that stores in advance a relationship between the operation state of the refrigerant circuit and a standard reference value that is a standard determination reference value in the operation state;
The initial learning unit obtains a determination reference value based on the operation state quantity of the operation state quantity detection device every time the operation state of the refrigerant circuit satisfies the predetermined operation condition during the initial operation of the refrigerant circuit, The air conditioner according to claim 1, wherein the actual relationship is created by correcting the relationship stored in advance in the storage unit based on the determined determination reference value. The air conditioner according to claim 1 or 2 , wherein the actual relationship is a relationship between a compression ratio in the compressor and the determination reference value. The operating conditions are:
Air conditioning apparatus according to claim 1 or claim 2, wherein it is a compression ratio in the compressor. The correction in the initial learning unit is:
When the standard reference value is compared with the determination index obtained based on the operation state quantity of the operation state quantity detection device and the physical property value of the refrigerant, and they are different from each other by a preset ratio or more The air conditioner according to any one of claims 2 to 4, which is dependent on claim 2 and claim 2 . The deterioration determination unit
Compressor capacity, claims 1 and performs compressor deterioration determination when the said operation state quantity detecting predetermined value capable of suppressing fluctuation of the operation state quantity of devices or due to external factors 5 The air conditioning apparatus according to any one of the above. The deterioration determination unit
Compressor deterioration determination is performed when a compressor integrated operation time, which is an integrated operation time from the start of compressor operation after initial installation, exceeds a predetermined time that is expected to start deterioration of the compressor. The air conditioning apparatus according to any one of claims 1 to 5 . The deterioration determination unit
2. The compressor deterioration determination is performed when the number of compressor start / stop times from the start of compressor operation after initial installation is equal to or greater than a predetermined number of times when deterioration of the compressor is predicted to start. The air conditioning apparatus according to any one of claims 5 to 6. The deterioration determination unit
The compressor is more than the number determined predetermined and is degraded, according to any one of claims 1 to 8, characterized in that the alarm degradation abnormality of the compressor when the repeated Air conditioner.

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