JP4749369B2 - Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same - Google Patents

Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same Download PDF

Info

Publication number
JP4749369B2
JP4749369B2 JP2007090398A JP2007090398A JP4749369B2 JP 4749369 B2 JP4749369 B2 JP 4749369B2 JP 2007090398 A JP2007090398 A JP 2007090398A JP 2007090398 A JP2007090398 A JP 2007090398A JP 4749369 B2 JP4749369 B2 JP 4749369B2
Authority
JP
Japan
Prior art keywords
state quantity
refrigerant
heat pump
pump cycle
abnormality
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2007090398A
Other languages
Japanese (ja)
Other versions
JP2008249234A (en
Inventor
太郎 伊早坂
浩司 山下
祐二 柳原
航祐 田中
Original Assignee
三菱電機ビルテクノサービス株式会社
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機ビルテクノサービス株式会社, 三菱電機株式会社 filed Critical 三菱電機ビルテクノサービス株式会社
Priority to JP2007090398A priority Critical patent/JP4749369B2/en
Publication of JP2008249234A publication Critical patent/JP2008249234A/en
Application granted granted Critical
Publication of JP4749369B2 publication Critical patent/JP4749369B2/en
Application status is Active legal-status Critical
Anticipated expiration legal-status Critical

Links

Images

Description

  The present invention relates to a failure diagnosis device for a refrigeration cycle device that performs failure diagnosis and monitoring of a refrigeration cycle device such as a refrigeration device and an air conditioner, and a refrigeration cycle device equipped with the failure diagnosis device, and in particular, after or after installation of the refrigeration cycle device. The present invention relates to a failure diagnosis apparatus for a refrigeration cycle apparatus that determines whether or not each device, fluid circuit, and the like constituting the refrigeration cycle apparatus are normal, and a refrigeration cycle apparatus equipped with the failure diagnosis apparatus.

  Conventionally, in refrigeration cycle apparatuses such as refrigeration apparatuses and air conditioners, failure diagnosis and monitoring have been performed so that normal operation can be maintained and continued. As such failure diagnosis, control data such as set values of various sensors, abnormal signals, etc. are taken, and further, the maximum and minimum values of pressure, temperature, etc. and daily operation trend data are used to check the operation status in the case of each failure. A state monitoring device for an air conditioner that stores a sequence in a microcomputer and performs failure diagnosis remotely has been proposed (see, for example, Patent Document 1 or Patent Document 2).

  Attempts have also been made to use Mahalanobis distance, which is a multivariate analysis technique, for fault diagnosis. As a failure diagnosis using this Mahalanobis distance, a device monitoring / preventive maintenance system that attempts to find signs of deterioration using various types of sensors has been proposed (see, for example, Patent Document 3). Recently, the refrigerant pressure, refrigerant temperature, etc. in the refrigeration cycle of the air conditioner, or other measurement quantities are detected, and the Mahalanobis distance is calculated from the correlation of these measurement quantity items. There has been proposed a device diagnostic apparatus that determines normality and abnormality of an air conditioner and identifies the cause of the abnormality (see, for example, Patent Document 4).

Japanese Patent No. 3475915 (FIG. 1) Japanese Patent No. 3119046 (FIG. 1) JP 2000-259222 A (FIGS. 3 to 9) Japanese Patent Laying-Open No. 2005-207644 (FIG. 2)

  Like the air conditioner state monitoring device described in Patent Document 1 or Patent Document 2, it takes in control data such as sensor setting values and abnormal signals, and further performs maximum and minimum values such as pressure and temperature, and daily operation. Attempts to diagnose faults in the operating state of each fault using trend data have the problem that although extreme abnormal conditions can be determined, small abnormal conditions cannot be determined, and fault diagnosis cannot be performed with high accuracy. . For example, when a measured value exceeds a preset allowable limit value, an attempt to generate an abnormal signal from the alarm means focuses only on the threshold value of specific operation data and includes the entire refrigeration cycle apparatus. Since it was impossible to capture subtle and complex changes in data, it was impossible to detect the possibility of anomaly when a sign of failure appeared.

  In order to improve the accuracy of fault diagnosis, too much data must be acquired, and judgments that assume various conditions are required. Every time there was a change, the microcomputer had to be changed, which required a great deal of money. Furthermore, since the threshold value used for the determination of the failure diagnosis of the air conditioner is determined by the design value or the test of the specific machine, this determination takes a lot of time and the individual difference of the actual machine cannot be taken into account and is erroneous. The possibility of detection was high.

  Even if the method of multivariate analysis is used as in the equipment monitoring / preventive maintenance system described in Patent Document 3, the determination with respect to the threshold is insufficient, or a large amount of data is necessary for the countermeasure, We were unable to respond quickly to monitoring and maintenance. Also, when finding the Mahalanobis distance in multivariate analysis, if the number of data is not larger than the number of items, a solution cannot be obtained, and even if the number of data is large, there is a strong correlation (multicollinearity) between items. Alternatively, when there is an item of standard deviation = 0, there is a problem that analysis cannot be performed.

  Furthermore, when standardizing from normal measurement data and determining whether there is an abnormality based on the Mahalanobis distance, the direction of change due to aging such as dirt on the heat exchanger or clogging of the piping is determined. Although it is easy to determine the amount of refrigerant in the installation or when it is determined whether the refrigerant charge amount of the existing air conditioner is excessive or insufficient, or when the state at the appropriate time is set as the reference state, the refrigerant is excessively charged. The state of Mahalanobis increases in either state regardless of whether the refrigerant amount is insufficient or not, so it can be determined that the refrigerant amount is not appropriate, but the output result indicates that the refrigerant amount is excessive or insufficient. There was a problem that it was not possible to determine whether it was.

  In the device diagnosis apparatus described in Patent Document 4, a model in which a storage device such as an accumulator or a receiver that stores excess refrigerant is a constituent element of the device diagnosis apparatus is a refrigeration cycle in which only the liquid level of the excess refrigerant in the storage container is lowered when the refrigerant leaks. Since the temperature and pressure of the refrigerant in the tank do not change, there is a problem that refrigerant leakage cannot be detected early from the temperature and pressure information as long as there is excess refrigerant. Further, in order to detect refrigerant leakage, it is necessary to estimate the amount of refrigerant by directly detecting the liquid level of surplus refrigerant with a unique detector such as an ultrasonic sensor, which requires a great deal of cost. was there.

  The present invention has been made to solve the above-described problems, and incorporates a failure diagnosis device for a refrigeration cycle apparatus that enables detection of an early sign of a failure based on the state quantity of the entire refrigeration cycle apparatus, and the like. An object of the present invention is to provide a refrigeration cycle apparatus. The present invention absorbs actual machine individual differences in failure determination, differences due to operation control methods of models, and has a practical refrigeration cycle apparatus failure diagnosis apparatus that can be easily and easily used to set abnormality determination thresholds, etc. An object of the present invention is to provide a refrigeration cycle apparatus.

  The present invention can specify the cause of failure in failure determination even when the number of measurement data is small, or when there is a strong correlation between items of measurement data, even when the standard deviation of the data is 0, with high accuracy. An object of the present invention is to provide a failure diagnosis device for a refrigeration cycle apparatus capable of performing failure diagnosis and obtaining high reliability, and a refrigeration cycle device equipped with the failure diagnosis device. The present invention is a failure diagnosis of a refrigeration cycle apparatus that can determine the state of a refrigeration cycle such as excess or deficiency of refrigerant amount and the like and can obtain high reliability with only information of general temperature detection means and pressure detection means. An object is to provide an apparatus and a refrigeration cycle apparatus equipped with the apparatus.

  An object of the present invention is to provide a failure diagnosis device for a refrigeration cycle device that can be easily applied to an existing refrigeration cycle device, and a refrigeration cycle device equipped with the failure diagnosis device. By using multiple data, the present invention can identify abnormalities such as heat exchange performance degradation due to refrigerant shortage, refrigerant excess, and heat exchanger contamination, and clogging of refrigerant circuit piping, and can detect abnormalities early. In addition, an object of the present invention is to provide a practical refrigeration cycle apparatus failure diagnosis apparatus capable of predicting and the like and a refrigeration cycle apparatus equipped with the failure diagnosis apparatus.

The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention includes a low pressure detection means for detecting a refrigerant pressure at any position in a flow path from the throttle means to the suction side of the compressor, and a throttle means from the discharge side of the compressor. High pressure detection means for detecting the pressure of the refrigerant at any position in the flow path leading to the discharge temperature detection means for detecting the temperature of the refrigerant at any position in the flow path from the compressor to the condenser, and the condenser Liquid temperature detection means for detecting the temperature of the refrigerant at the outlet, and a failure diagnosis device for a refrigeration cycle apparatus that performs failure diagnosis of a heat pump cycle based on a measurement value from each detection means, comprising at least the low-pressure detection means In addition, the measurement values from the high-pressure detection means and the discharge temperature detection means are subjected to a composite variable calculation using multivariate analysis by the T method (Tagchi methods). A calculation unit, a storage unit that stores a state quantity calculated by using the measurement value, the calculation value, or the measurement value and the calculation value as a plurality of variables, and a normal state that stores a state quantity of a normal operation state of the heat pump cycle A state quantity storage unit, an abnormal state quantity storage unit that stores a state quantity of an abnormal operation state of the heat pump cycle, and a state quantity calculated as a plurality of variables from the measured values obtained from the current operation state of the heat pump cycle A comparison unit that compares a current operation state quantity with a state quantity indicating a normal operation state stored in the normal state quantity storage unit and / or a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit And the degree of normality or abnormality of the heat pump cycle, the normality / abnormality determination, or the cause of the abnormality is determined from the state quantity or the change in the state quantity compared by the comparison unit. And a determining unit, the calculating unit, the measured values based on the same error factors, the depending on the state quantity calculation value or abnormal operating conditions, expressed using variables the degree of abnormality of the heat pump cycle, wherein A multivariate analysis is performed .

The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention includes a high-pressure detection means for detecting a refrigerant pressure at any position in a flow path from the discharge side of the compressor to the throttle means, and a flow from the compressor to the condenser. Discharge temperature detection means for detecting the temperature of the refrigerant at any position in the path, and condenser inflow temperature detection means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the condenser, A failure diagnosis apparatus for a refrigeration cycle apparatus that performs failure diagnosis of a heat pump cycle based on a measurement value from a detection means, wherein the measurement values from the high-pressure detection means, the discharge temperature detection means, and the condenser inflow temperature detection means An arithmetic unit that performs a composite variable calculation using multivariate analysis by the T method (Taguch methods), and a combination of the measured value, the calculated value, or the measured value and the calculated value. A storage unit that stores a state quantity calculated as a variable of number, a normal state quantity storage unit that stores a state quantity of a normal operation state of the heat pump cycle, and an abnormal state that stores a state quantity of an abnormal operation state of the heat pump cycle A quantity storage unit, a current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, and a normal operation state stored in the normal state quantity storage unit. A comparison unit that compares the state quantity that is indicated and / or the state quantity that indicates the abnormal operation state stored in the abnormal state quantity storage unit, and the state quantity or the change in the state quantity that is compared in the comparison unit, normal degree or abnormal degree, and a determining section for determining the cause of the normal / abnormal determination or abnormal, the calculation section, the measurement based on the same fault factor , In response to said state quantity calculation value or abnormal operating conditions, indicates the degree of abnormality of the heat pump cycle using a variable, which comprises carrying out the multivariate analysis.

The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention includes a low-pressure detection means for detecting the pressure of refrigerant at any position in the flow path from the throttle means to the suction side of the compressor, and a flow from the compressor to the condenser. Discharge temperature detection means for detecting the temperature of the refrigerant at any position of the path, and evaporator inflow temperature detection means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the evaporator, A failure diagnosis apparatus for a refrigeration cycle apparatus that performs failure diagnosis of a heat pump cycle based on a measurement value from a detection means, wherein the measurement values from the low-pressure detection means, the discharge temperature detection means, and the evaporator inflow temperature detection means are An arithmetic unit that performs a composite variable calculation using multivariate analysis by the T method (Taguch methods), and a combination of the measured value, the calculated value, or the measured value and the calculated value. A storage unit that stores a state quantity calculated as a variable of number, a normal state quantity storage unit that stores a state quantity of a normal operation state of the heat pump cycle, and an abnormal state that stores a state quantity of an abnormal operation state of the heat pump cycle A quantity storage unit, a current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, and a normal operation state stored in the normal state quantity storage unit. A comparison unit that compares the state quantity that is indicated and / or the state quantity that indicates the abnormal operation state stored in the abnormal state quantity storage unit, and the state quantity or the change in the state quantity that is compared in the comparison unit, normal degree or abnormal degree, and a determining section for determining the cause of the normal / abnormal determination or abnormal, the calculation section, the measurement based on the same fault factor , In response to said state quantity calculation value or abnormal operating conditions, indicates the degree of abnormality of the heat pump cycle using a variable, which comprises carrying out the multivariate analysis.

The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention includes a low pressure detection means for detecting a refrigerant pressure at any position in a flow path from the throttle means to the suction side of the compressor, and a throttle means from the discharge side of the compressor. High pressure detection means for detecting the pressure of the refrigerant at any position in the flow path leading to the liquid, and liquid temperature detection means for detecting the temperature of the refrigerant at the outlet of the condenser are provided, and based on the measured values from each detection means A failure diagnosis apparatus for a refrigeration cycle apparatus for performing a failure diagnosis of a heat pump cycle, wherein the measured values from the low-pressure detection means, the high-pressure detection means, and the liquid temperature detection means are subjected to multivariate analysis using a T method (Taguchi methods). And a storage unit for storing a state quantity obtained by calculating the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables. A normal state quantity storage unit that stores a state quantity of a normal operation state of the heat pump cycle, an abnormal state quantity storage unit that stores a state quantity of an abnormal operation state of the heat pump cycle, and a current operation of the heat pump cycle A current operating state quantity that is a state quantity calculated from the measured value obtained from the state as a plurality of variables, a state quantity indicating a normal operating state stored in the normal state quantity storage unit, and / or the abnormal state quantity storage unit A comparison unit that compares the state quantity indicating the abnormal operation state stored in the state, and the normality or degree of abnormality of the heat pump cycle or the normal / abnormal and a determining section for determining the cause of discrimination or abnormal, the calculation section, the measurement value based on the same error factors, response to the state of the operational value or abnormal operating conditions Te represents the degree of abnormality of the heat pump cycle using a variable, which comprises carrying out the multivariate analysis.

The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention includes a low pressure detection means for detecting a refrigerant pressure at any position in a flow path from the throttle means to the suction side of the compressor, and a throttle means from the discharge side of the compressor. High pressure detection means for detecting the pressure of the refrigerant at any position in the flow path leading to the discharge temperature detection means for detecting the temperature of the refrigerant at any position in the flow path from the compressor to the condenser, and the condenser Liquid temperature detecting means for detecting the temperature of the refrigerant at the outlet, condenser inflow temperature detecting means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the condenser, and the refrigerant and heat flowing inside the evaporator And an evaporator inflow temperature detecting means for measuring the inflow temperature of the fluid to be exchanged, and a failure diagnosing device for a refrigeration cycle apparatus for diagnosing a heat pump cycle failure based on a measured value from each detecting means A is, the low-pressure detecting means, said high pressure detecting means, the discharge temperature detecting means, the liquid temperature detecting means, the condenser inlet temperature detecting means and the evaporator measurements from inlet temperature detecting means T method (Taguchi a calculation unit that performs a complex variable calculation using multivariate analysis according to methods), a storage unit that stores a state quantity obtained by calculating the measurement value, the calculation value, or the measurement value and the calculation value as a plurality of variables; Obtained from a normal state quantity storage unit that stores a state quantity of a normal operation state of the heat pump cycle, an abnormal state quantity storage unit that stores a state quantity of an abnormal operation state of the heat pump cycle, and a current operation state of the heat pump cycle The current operation state quantity that is a state quantity calculated by using the measured values as a plurality of variables, and the normal operation state stored in the normal state quantity storage unit A comparison unit comparing the state quantity and / or the state quantity indicating the abnormal operation state stored in the abnormal state quantity storage unit, and the normality of the heat pump cycle from the change in the state quantity or the state quantity compared in the comparison unit Or a degree of abnormality, a normality / abnormality determination, or a determination unit for determining the cause of the abnormality, and the arithmetic unit is the measurement value based on the same abnormal factor, the calculated value, or the state quantity of the abnormal operation state Accordingly, the degree of abnormality of the heat pump cycle is expressed using a variable, the multivariate analysis is performed, and the determination unit determines that the abnormality of the heat pump cycle is due to a lack of refrigerant sealed in the heat pump cycle. Or due to excessively filled refrigerant, dirt or damage on the surface of the condenser, clogging of the filter, the condenser or the condenser Due to deterioration or failure of the blower provided in the vicinity, dirt or damage on the surface of the evaporator, clogging of the filter, deterioration or failure of the blower provided in the vicinity of the evaporator or the evaporator Or due to clogging or failure of the throttling means, clogging of a strainer to remove dust etc. inside the circulating refrigerant or moisture drier of the refrigerant, breakage, breakage or clogging of the pipe The presence or absence of abnormality is judged based on at least one of them.

  The failure diagnosis apparatus for a refrigeration cycle apparatus according to the present invention diagnoses an operation state from a general measurement amount of the refrigeration cycle apparatus, and an initial diagnosis at the time of installation or trial operation of the refrigeration cycle apparatus by simple and reliable diagnosis. Alternatively, it is possible to detect an abnormality of an existing apparatus after installation or to make an early prediction of an abnormality time. Moreover, the failure diagnosis device for a refrigeration cycle device according to the present invention is highly accurate and practical even when the measurement data is small, and can specify the cause of failure.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a conceptual diagram showing an overall concept of a failure diagnosis apparatus 100 according to an embodiment of the present invention. Based on FIG. 1, the overall concept of the failure diagnosis apparatus 100 will be described. The failure diagnosis apparatus 100 performs failure diagnosis and monitoring of the refrigeration cycle apparatus 1 such as a refrigeration apparatus, an air conditioner (for example, a room air conditioner or a packaged air conditioner), a refrigerator, a humidifier, a humidity control apparatus, and a heat pump water heater. Is. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The failure diagnosis apparatus 100 detects data of at least the operating state of the refrigeration cycle apparatus 1 and performs data transmission / reception between the microcomputer 2 and a microcomputer 2 that includes a device for calculating, storing, and transmitting / receiving data to / from the outside. And a computer 5 which is a remote monitoring means having a display and calculation function. The microcomputer 2 is provided in the refrigeration cycle apparatus 1, and the computer 5 is provided in the remote monitoring room 4. The microcomputer 2 and the computer 5 are communicated with each other by a communication means 3 such as a telephone line, a LAN line, and wireless. Here, the case where the computer 5 is installed in the remote monitoring room 4 for performing centralized management such as remote monitoring and control of the refrigeration cycle apparatus 1 is shown as an example.

  In FIG. 1, an abnormality has occurred in the refrigeration cycle apparatus 1 in a display device 6 such as a liquid crystal display that displays the state of the refrigeration cycle apparatus 1, an input device 7 such as a touch panel and buttons, and the refrigeration cycle apparatus 1. A case is shown as an example in which an alarm device 6 configured with an alarm lamp or the like is provided. The display device 6 may be provided with a touch panel, and the input device 7 and the display device 6 may be configured together. Moreover, you may comprise the alerting | reporting apparatus 8 so that alert sounds, such as a voice message and a buzzer, can be alert | reported besides an alert lamp. This notification device 8 may also be configured together with the display device 6.

  The refrigeration cycle apparatus 1 is an air conditioner installed in a building, a refrigerator installed in a large store such as a supermarket, an air conditioning system, a refrigeration / air conditioner in a small store, an air conditioner in each household of an apartment house, etc. Good. That is, any device equipped with a refrigeration cycle may be used. In addition, the computer 5 installed in the remote monitoring room 4 may monitor the plurality of facilities or may monitor individual facilities. Further, the remote monitoring room 4 may be installed in each house such as a detached house, and the microcomputer 2 may be connected to a monitoring computer or a monitoring device there.

  In FIG. 1, the display device 6, the input device 7, and the notification device 8 are shown as an example in which they are built in the refrigeration cycle apparatus 1, but the present invention is not limited to this, and all or Some of these may be installed outside the refrigeration cycle apparatus 1, or a configuration in which some or all of these may not be installed. When all or part of the display device 6, the input device 7, and the notification device 8 are not installed, some alternative means, for example, a computer or the like connected to the remote point by the communication means 3 may be installed.

  FIG. 2 is a schematic configuration diagram showing configurations of the refrigeration cycle apparatus 1 and the microcomputer 2. Based on FIG. 2, the configuration of the refrigeration cycle apparatus 1 and the internal configuration of the microcomputer 2 will be described in detail. First, the refrigeration cycle apparatus 1 will be described. The refrigeration cycle apparatus 1 includes a compressor 11, a four-way valve 12 as a flow path switching valve, an outdoor heat exchanger 13, a throttling means 15a and a throttling means 15b, an indoor heat exchanger 17a and an indoor heat exchanger 17b. The heat pump cycle in which the accumulator 20 is sequentially connected by the connecting pipe 16 and the connecting pipe 19 is mounted. That is, the refrigerant is circulated through the heat pump cycle, so that the refrigeration cycle apparatus 1 can perform a cooling operation and a heating operation.

  The compressor 11 sucks the refrigerant and compresses the refrigerant to be in a high temperature / high pressure state. For example, the compressor 11 may be of a type in which the rotation speed is controlled by an inverter and the capacity is controlled. The four-way valve 12 switches the refrigerant flow between the cooling operation and the heating operation. The outdoor heat exchanger 13 functions as a high-pressure side heat exchanger (condenser) during cooling operation and as a low-pressure side heat exchanger (evaporator) during heating operation. Near the outdoor heat exchanger 13 is a fluid supply device composed of a centrifugal fan or a multiblade fan driven by a DC motor (not shown) for supplying air to the outdoor heat exchanger 13. An outdoor blower 14 is provided. That is, the outdoor heat exchanger 13 exchanges heat between the air supplied from the outdoor blower 14 and the refrigerant, and evaporates or condenses the refrigerant.

  The throttling means 15a and the throttling means 15b function as a pressure reducing valve or an expansion valve, and decompress the refrigerant to expand it. The throttling means 15a and the throttling means 15b may be configured by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve. The indoor heat exchanger 17a and the indoor heat exchanger 17b function as a low-pressure side heat exchanger (evaporator) during cooling operation and as a high-pressure side heat exchanger (condenser) during heating operation. In the vicinity of the indoor heat exchanger 17a and the indoor heat exchanger 17b, a centrifugal fan driven by a DC motor (not shown) for supplying air to the indoor heat exchanger 17a and the indoor heat exchanger 17b, An indoor fan 18a and an indoor fan 18b, which are fluid supply devices including a multiblade fan, are provided.

  That is, the indoor heat exchanger 17a and the indoor heat exchanger 17b perform heat exchange between the refrigerant and the air, and evaporate or condense the refrigerant. The accumulator 20 stores excess refrigerant. In addition, this accumulator 20 should just be a container which can store an excessive refrigerant | coolant, and is not specifically limited. The connection pipe 16 and the connection pipe 19 are refrigerant pipes for conducting a liquid or gas state refrigerant circulating in the heat pump refrigeration cycle.

  Further, the refrigeration cycle apparatus 1 includes a compressor discharge temperature detecting means 201, a high pressure detecting means 202, an outdoor heat exchanger liquid temperature detecting means 203, an indoor heat exchanger liquid temperature detecting means 204a, and an indoor heat exchanger liquid. A temperature detecting means 204b, a low pressure detecting means 205, an indoor heat exchanger gas temperature detecting means 206a and an indoor heat exchanger gas temperature detecting means 206b are provided. The compressor discharge temperature detection means 201 is installed in the discharge side pipe connected to the compressor 11 and has a function of detecting the temperature of the refrigerant discharged from the compressor 11. The high pressure detection means 202 is installed in the discharge side pipe connected to the compressor 11 and has a function of detecting the high pressure of the refrigerant discharged from the compressor 11.

  The outdoor heat exchanger liquid temperature detecting means 203 is installed in the outlet side pipe of the outdoor heat exchanger 13 (the pipe on the outlet side of the refrigerant flowing into the outdoor heat exchanger 13 during heating operation) and flows out of the outdoor heat exchanger 13. It has a function of detecting the temperature of the liquid refrigerant. The indoor heat exchanger liquid temperature detection means 204a and the indoor heat exchanger liquid temperature detection means 204b are installed in a pipe between the indoor heat exchanger 17a and the indoor heat exchanger 17b, and the expansion means 15a and the expansion means 15b. It has a function of detecting the temperature of the liquid refrigerant flowing into the indoor heat exchanger 17a and the indoor heat exchanger 17b. The low pressure detecting means 205 is installed in the suction side pipe connected to the compressor 11 and has a function of detecting the low pressure of the refrigerant sucked into the compressor 11.

  The indoor heat exchanger gas temperature detection means 106a and the indoor heat exchanger gas temperature detection means 206b are connected to the outlet side pipes of the indoor heat exchanger 17a and the indoor heat exchanger 17b (the indoor heat exchanger 17a and the indoor heat exchanger during the heating operation). 17b) and has a function of detecting the temperature of the gas refrigerant flowing out of the indoor heat exchanger 17a and the indoor heat exchanger 17b. Various types of information acquired by these various types of detection means are sent to the measurement unit 101 described later. In addition, these various detection means are not specifically limited, What is necessary is just to comprise with a temperature sensor and a pressure sensor.

  Next, the internal configuration of the microcomputer 2 will be described. As shown in FIG. 2, the microcomputer 2 includes a measurement unit 101 that detects a refrigerant state from acquired information of various detection units, and a calculation unit that performs various complex variable calculation processes based on the detection result of the measurement unit 101. 102, a storage unit 104 for storing various data such as a calculation result, a normal value or an abnormal state reference value, a device type name, a control specification value, etc., a calculation result from the calculation unit 102, and a storage content of the storage unit 104 Are compared with each other, the determination unit 106 that makes a determination based on the comparison result of the comparison unit 105, and the overall control of the refrigeration cycle apparatus 1, the compressor 11, the four-way valve 12, the outdoor blower 14, A control unit 103 that controls the indoor fan 18a, the indoor fan 18b, the throttle means 15a, the throttle means 15b, and the like is incorporated.

  Among them, the calculation unit 102 (including functions as a condenser inflow temperature detection unit and an evaporator inflow temperature detection unit) and a storage unit 104 (a normal state amount storage unit, an abnormal state amount storage unit, and device specification information storage) And the comparison unit 105 constitutes the calculation comparison unit 108. The control unit 103 receives information from the operation comparison unit 108 that performs operation comparison processing based on the measurement results of each detection means such as temperature and pressure, and operation input information from a remote controller (not shown) or switches on the input device 7. Or based on the result of the communication data information from the communication means 3, the drive frequency of the compressor 11 and the switching of the four-way valve 12, the rotational speed of the outdoor blower 14, the rotational speed of the indoor blower 18a, the rotational speed of the indoor blower 18b, the throttle The opening degree of the means 15a, the opening degree of the throttle means 15b, and the like are controlled so as to be within a desired control target range.

  The refrigeration cycle apparatus 1 has a notification unit for notifying the determination result from the determination unit 106 to the notification device 8 that displays on an LED (light emitting diode), a remote monitor, etc., or notifies by a voice message or a buzzer. 107 is provided. Moreover, the memory | storage part 104 should just be what can memorize | store various data, for example, should comprise a semiconductor memory etc., for example. Furthermore, the microcomputer 2 may be provided on the indoor unit side or on the outdoor unit side.

  In this embodiment, the case where two indoor heat exchangers and two throttle means are mounted on the refrigeration cycle apparatus 1 is shown as an example, but the present invention is not limited to this. A stand may be mounted, or three or more may be mounted. The outdoor heat exchanger 13 is accommodated in an outdoor unit or the like, and is installed outdoors such as a machine room or a rooftop. The indoor heat exchanger 17a and the indoor heat exchanger 17b are accommodated in an indoor unit or the like, and a showcase or the like. It is supposed to be installed in. Furthermore, in the outdoor heat exchanger 13 of the refrigeration cycle apparatus 1, air has been described as an example of the heat absorption target of the refrigerant, but the present invention is not limited to this. For example, water, a refrigerant, brine, or the like may be the endothermic object. When the heat absorption target is other than air, a fluid supply device such as a pump is preferably provided in the vicinity of the outdoor heat exchanger 13 instead of the outdoor blower 14.

  In the description of FIG. 1 and FIG. 2, a heat pump cycle in which refrigerant is circulated to perform air conditioning such as heating and cooling, refrigeration and freezing in a refrigerator and a freezer warehouse, various sensors for detecting the operating state of the heat pump cycle, calculation, and the like An example in which the microcomputer 2 and the substrates necessary for the control are stored in the refrigeration cycle apparatus 1, the operating state is measured, calculated, and compared up to a judgment is made in the refrigeration cycle apparatus 1. Although described, the present invention is not limited to this. For example, in the refrigeration cycle apparatus 1, the measurement may be performed up to the measurement by various sensors, and the calculation after the calculation may be performed by the computer 5 in the remote monitoring room 4.

Here, the operation of the refrigeration cycle apparatus 1 will be described.
First, the operation of the cooling operation will be described. A refrigerant is sealed in a refrigerant circuit constituting the heat pump cycle of the refrigeration cycle apparatus 1. This refrigerant is heated to a high temperature and a high pressure by the compressor 11, discharged from the compressor 11, and flows into the outdoor heat exchanger 13 through the four-way switching valve 12. The refrigerant flowing into the outdoor heat exchanger 13 exchanges heat with the air supplied from the outdoor blower 14 and is condensed and liquefied. That is, the refrigerant dissipates heat and changes its state to liquid. The condensed and liquefied refrigerant flows through the connecting pipe 16 and flows into the throttle means 15a and the throttle means 15b.

  The refrigerant flowing into the throttling means 15a and the throttling means 15b is decompressed and expanded, and changes its state to a low-temperature / low-pressure gas-liquid two-phase refrigerant of liquid and gas. This gas-liquid two-phase refrigerant flows into the indoor heat exchanger 17a and the indoor heat exchanger 17b, and exchanges heat with the air supplied from the indoor blower 18a and the indoor blower 18b to evaporate. That is, it absorbs heat from the air (cools the air) and changes its state to gas. The evaporated gas refrigerant flows out of the indoor heat exchanger 17a and the indoor heat exchanger 17b, flows through the connection pipe 19, and is sucked into the compressor 11 again via the four-way valve 12 and the accumulator 20.

  At this time, the condensation temperature at the time of condensation in the outdoor heat exchanger 13 is calculated by converting the pressure of the high-pressure detection means 202 into a saturation temperature. Further, the degree of supercooling of the outdoor heat exchanger 13 is calculated by subtracting the value of the outdoor heat exchanger liquid temperature detecting means 203 from the condensation temperature. Further, the evaporation temperature is calculated by converting the pressure of the low-pressure detection means 205 into a saturation temperature. The condensing temperature may be calculated by adding a temperature detecting means to a portion where the refrigerant changes in two phases in the flow path from the four-way valve 12 to the throttling means 15a and the throttling means 15b. The temperature may be calculated by adding temperature detecting means to the portion where the refrigerant changes in two phases in the flow path from the throttle means 15b to the indoor heat exchanger 17a and the indoor heat exchanger 17b.

  Next, the heating operation will be described. During the heating operation, the refrigerant flow path is switched by the four-way valve 12. The refrigerant sealed in the heat pump cycle is made high temperature and high pressure by the compressor 11, discharged from the compressor 11, and flows into the indoor heat exchanger 17a and the indoor heat exchanger 17b via the four-way switching valve 12. . The refrigerant that has flowed into the indoor heat exchanger 17a and the indoor heat exchanger 17b exchanges heat with the air supplied from the indoor blower 18a and the indoor blower 18b to be condensed and liquefied. The refrigerant dissipates heat (warms the air) and changes its state to a liquid. The condensed and liquefied refrigerant flows through the connecting pipe 16 and flows into the throttle means 15a and the throttle means 15b.

  The refrigerant flowing into the throttling means 15a and the throttling means 15b is decompressed and expanded, and changes its state to a low-temperature / low-pressure gas-liquid two-phase refrigerant of liquid and gas. This gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 13 and evaporates and gasifies by heat exchanger with the air supplied from the outdoor blower 14. That is, heat is absorbed from the air, and the state changes to gas. The evaporated gas refrigerant flows out of the outdoor heat exchanger 13, flows through the connection pipe 192, passes through the four-way valve 12 and the accumulator 14, and is sucked into the compressor 11 again.

  At this time, the condensation temperature at the time of condensation of the indoor heat exchanger 17a and the indoor heat exchanger 17b is calculated by converting the pressure of the high-pressure detection means 202 into a saturation temperature. The degree of supercooling of the indoor heat exchanger 17a and the indoor heat exchanger 17b is calculated by subtracting the values of the indoor heat exchanger liquid temperature detecting means 204a and the indoor heat exchanger liquid temperature detecting means 204b from the condensation temperature. . Further, the evaporation temperature is calculated by converting the pressure of the low-pressure detection means 205 into a saturation temperature. The condensing temperature may be calculated by adding a temperature detecting means to a portion where the refrigerant changes in two phases in the flow path from the four-way valve 12 to the throttling means 15a and the throttling means 15b. The temperature may be calculated by adding temperature detection means to the portion where the refrigerant changes in two phases in the flow path from the expansion means 15b to the outdoor heat exchanger 13.

The refrigerant used for the refrigeration cycle apparatus 1 will be described.
Examples of the refrigerant that can be used in the heat pump cycle of the refrigeration cycle apparatus 1 include a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, and a single refrigerant. Non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant. Since this non-azeotropic refrigerant mixture is a mixture of refrigerants having different boiling points, it has a characteristic that the composition ratio of the liquid-phase refrigerant and the gas-phase refrigerant is different. The pseudo azeotropic refrigerant mixture includes R410A (R32 / R125) and R404A (R125 / R143a / R134a) which are HFC refrigerants. This pseudo azeotrope refrigerant has the same characteristic as that of the non-azeotrope refrigerant and has an operating pressure of about 1.6 times that of R22.

  The single refrigerant includes R22, which is an HCFC (hydrochlorofluorocarbon) refrigerant, R134a, which is an HFC refrigerant, and the like. Since this single refrigerant is not a mixture, it has the property of being easy to handle. In addition, carbon dioxide, propane, isobutane, ammonia, helium, etc., which are natural refrigerants, can also be used. R22 represents chlorodifluoromethane, R32 represents difluoromethane, R125 represents pentafluoroethane, R134a represents 1,1,1,2-tetrafluoroethane, and R143a represents 1,1,1-trifluoroethane. ing. Therefore, it is good to use the refrigerant | coolant according to the use and the objective of the refrigerating cycle apparatus 1. FIG.

  Note that the failure diagnosis determination executed by the failure diagnosis apparatus 100 according to the present embodiment is not limited to the case where the refrigeration cycle apparatus 1 is a new product, and may be applied to the existing refrigeration cycle apparatus 1. it can. In the case where the refrigeration cycle apparatus 1 is already installed, failure diagnosis determination can be executed by adding various missing detection means as a retrofit. That is, the failure diagnosis determination can be performed by selecting the deficient detection means according to the state of the various detection means installed in the refrigeration cycle apparatus 1 and adding as appropriate later.

  In this embodiment, as shown in FIG. 2, the measurement unit 101, the calculation unit 102, the control unit 103, the storage unit 104, the comparison unit 105, the determination unit 106, and the notification unit 107 are configured by using each set of means as a substrate. Although the system incorporated in the microcomputer 2 provided in the refrigeration cycle apparatus 1 has been described as an example, the present invention is not limited to this. For example, the computing unit 102, the control unit 103, the storage unit 104, the comparison unit 105, the determination unit 106, and the notification unit 107 are assigned to the computer 5 provided in the remote monitoring room 4. You may make it the system which performs.

  Moreover, the function of each means may be shared by both the microcomputer 2 provided in the refrigeration cycle apparatus 1 and the computer 5 provided in the remote monitoring room 4, or may coexist. For example, the microcomputer 2 and the computer 5 are provided with a storage unit 105 having different storage capacities, the microcomputer 2 is provided with a storage unit 105 having a small storage capacity, and the computer 5 is provided with a storage unit 105 having a large storage capacity. May be rewritten with the corresponding data of the computer 5. This is an effective method when it is desired to use different data depending on the season and the installation state of the refrigeration cycle apparatus 1.

  Further, all the means may be provided either in the microcomputer 2 of the refrigeration cycle apparatus 1 or in the computer 5 of the remote monitoring room 4. That is, each means only needs to be able to execute each function without limiting the installation location of each means. Note that the case where the computer 5 is provided in the remote monitoring room 4 is described as an example because it is convenient for centralized monitoring of a plurality of devices, but the present invention is not limited to this. For example, when a specific device is targeted, a mobile device such as a mobile device may be used so that a service person can always perform fault diagnosis or monitoring while moving. Or you may enable it to monitor.

Here, the operation of failure diagnosis and abnormality determination of the refrigeration cycle apparatus 1 will be described.
Data detected by each detection means of the refrigeration cycle apparatus 1 is a measured amount of pressure and temperature at each part of the refrigerant flowing through the refrigerant circuit necessary for grasping the operation state of the heat pump cycle. This data is collected by the measurement unit 101. These various detection means are usually easy to use when they are arranged in the refrigeration cycle apparatus 1, but if they are insufficient, they may be externally attached later if necessary. .

  The data collected by the measurement unit 101 can be calculated and calculated as a state quantity representing the characteristics of each data. For example, a composite variable is calculated by the calculation unit 102, and a plurality of measured values of each detecting means are used as composite variables, or a characteristic calculated value is obtained from a measured quantity, and the calculated values are used together with the measured values as composite variables. Is stored in the storage unit 104, the value during normal operation stored in advance in the storage unit 104 is compared with the current measured value or the calculated value corresponding thereto, and the refrigeration cycle apparatus 1 is based on the comparison result. It is possible to determine whether the state is normal or abnormal.

  The pressure may be measured using pressure detection means such as a pressure converter that converts the refrigerant pressure into an electrical signal, and the temperature may be measured using temperature detection means such as a thermistor or a thermocouple. In addition, about the measurement position of a pressure and temperature, it is good to determine according to the structure of the object refrigeration cycle apparatus 1, and an operating characteristic. Moreover, you may comprise so that the driving | running state of the refrigerating-cycle apparatus 1 can be grasped | ascertained more correctly by enabling the change of a measurement position and the expansion of a measurement position. The measurement of the state quantity is performed at a certain interval, for example, a minute unit such as one minute, a time unit interval, and the like, and the information is transmitted to the measurement unit 101.

  Next, a method for combining the measured data into a composite variable, and a method for detecting an abnormality in a system such as the compressor 11 and the system such as the refrigeration cycle apparatus 1 using the composite variable will be described. As an example of a method for processing a plurality of measurement quantities, a generally known T method (Taguchi methods) can be mentioned. The T method is, for example, “Objective functions and basic functions (6) Comprehensive prediction based on the T method” published by the Quality Engineering Society in 2005. Quality Engineering vol. 13 (3) p. 309-314, which is a technique used in the field of multivariate analysis, and calculates a pattern difference for an object outside the unit space that does not belong to the unit space represented by the normal data group. Thus, the signal output value is predicted or estimated.

  Hereinafter, a case where failure diagnosis of the refrigeration cycle apparatus 1 is performed using the T method will be described. Except for the final stage that clearly appears on the surface such as breakage and insulation short circuit, excess and shortage of refrigerant, product deterioration, failure, etc. It is complicated. This is because data is a combination of complicated factors. Therefore, a complicated structure may be simplified by grasping these in a plural rather than a unified manner, and a technique called multivariate analysis is adopted. However, simply using the multivariate analysis cannot determine the excess or deficiency of the refrigerant, for example. In this embodiment, a practical fault diagnosis technique can be obtained between the variables.

  First, the total number of items of each measurement data representing the operation state of the refrigeration cycle apparatus 1 is set to k, each measurement amount or state amount is assigned to a variable x, and k operation state amounts x1 to xk are defined. Next, a total of one or more operation data numbers n of x1 to xk are collected in a normal operation state as a reference, for example, in an operation in which the refrigerant of the refrigeration cycle apparatus 1 is properly sealed. The average of the output values of the state quantities of the composite variables represented by the collected normal state data is M0 = 0 (abnormality level 0%), and the average value for each item (number of items k) of the normal state data is X10, x20,..., Xk0, respectively.

  On the other hand, a state in which an abnormal state is clearly occurring, for example, a refrigerant is insufficient, a state in which cooling capacity or heating capacity is not ensured, or dirt on the outdoor heat exchanger 13 is severe, and the operation is intermittent. Each output value of the operation data (operation data number n) such as the state is M1, M2,..., Mn = 1 (abnormality degree 100%). The value obtained by subtracting the average value x10, x20, ..., xk0 of each item in the normal state from the value of each item x1, x2, ..., xk in the abnormal operation state (x11, x12, ..., x1k), ..., (Xn1, xn2,..., Xnk).

  M1, M2,..., Mn are obtained by subtracting the average M0 of the output values in the abnormal operation state from the output value Mx in the abnormal operation state (in this case, since M0 = 0, M1, M2,..., Mn No change in value). This is called normalization. FIG. 3 shows the relationship between the normalized output value and the measured data item value. Next, the proportionality constant β (corresponding to the difference between the average value of the normalized data and the abnormal condition) and the SN ratio η (the dispersion of the output value and the error variance) are proportional to the output value of the abnormal data. The larger the ratio and the larger the value, the stronger the index against noise such as disturbance). For example, β1 and SN ratio η1 of the first item x1 are obtained from the following equations (1) to (7). This is the same calculation as x1 for all items x2,..., Xk.

Here, r is defined as an effective divisor, and is represented by Expression (2).

The SN ratio η is
If Sβ ≦ Ve,
If Sβ> Ve,
It is expressed.

Here, Ve is defined as the variation of the Sβ proportional term in equation (4), is represented by equation (5), is defined as error variance, and is represented by equation (6). . ST in equation (6) is defined as total variation and is represented by equation (7).

From the above, the estimated value of M representing the degree of abnormality by each item xi (i = 1, 2,..., K) of the data measured from the current operating state of the refrigeration cycle apparatus 1 is the normal data of each item. The difference is expressed by Expression (8) as a composite variable obtained by taking a weighted average of the SN ratio η. By using this M value, the degree of abnormality of the refrigeration cycle apparatus 1 can be estimated.

  FIG. 4 is an explanatory diagram for explaining the concept of the degree of abnormality M represented by normal data in a normal state and abnormal data in an abnormal state for each item. Based on FIG. 4, the concept of the degree of abnormality M represented by normal data in the normal state and abnormal data in the abnormal state will be described. As shown in FIG. 4, when the current operation data approaches the data at the time of abnormality, the numerical value increases, and the abnormality degree M (degree of departure from normal) increases. Further, since the equation (8) representing the degree of abnormality M is output as a value having a positive or negative value, for example, if the degree of abnormality M in the abnormality data at the time of refrigerant shortage is set to 1, the refrigerant is in relation to the appropriate amount of refrigerant enclosed. When the abnormality degree M is calculated using the operation data of the excessively filled refrigeration cycle, it is possible to determine that the refrigerant is excessive because the value of M is output as a negative value.

  The conventional method of determining normality / abnormality by obtaining the Mahalanobis distance has the following four constraints and features in the analysis. (1) The number of samples must be greater than the number of items. (2) There must be no strong correlation (multicollinearity) between items. (3) There must be no standard deviation = 0 in the unit space. (4) Output only + sign. However, in this embodiment, as apparent from the derivation process of Equation (8), it is not necessary to consider the above-mentioned constraint conditions, so that there is no problem in computational load and data extraction method, and the degree of abnormality Since the value of M has a sign of ±, there is a feature that an abnormal state can be more accurately discriminated in the characteristic in the traveling direction.

  FIG. 5 is an explanatory diagram for explaining the concept of the abnormality determination method using the T method. Based on FIG. 5, the concept of the abnormality determination method using the T method will be described based on the relationship between the output value (abnormality degree M) and the appearance rate thereof. In FIG. 5, the horizontal axis represents the output value (abnormality M), and the vertical axis represents the appearance rate. As shown in FIG. 5, the failure state of the refrigeration cycle apparatus 1 can be confirmed by determining the positional relationship between the current value and the abnormal data group and the normal data group. It is.

  Next, diagnosis of refrigerant leakage will be described based on FIG. 2 including the operation of the refrigeration cycle apparatus 1 and a method for estimating an abnormality. First, the amount of refrigerant in the refrigerant circuit of the refrigeration cycle apparatus 1 will be described. In the refrigeration cycle apparatus 1, in order for the heat pump cycle to exhibit predetermined performance, an amount of refrigerant suitable for the internal volume of the heat pump cycle is required. Therefore, if the number of indoor heat exchangers, the internal volume, and the length of the piping are different, the amount of refrigerant required for the entire heat pump cycle will also be different. Therefore, the refrigerant of the refrigeration cycle apparatus 1 can be installed locally. After installation, it is filled according to the pipe length and the number of connected indoor heat exchangers.

  Further, the amount of refrigerant required in the heat pump cycle varies depending on the operation mode of the heat pump cycle. As shown in FIG. 2, when there are throttle means (throttle means 15a and throttle means 15b) on the indoor unit side, the connection pipe 16 is a liquid refrigerant cooled and liquefied by the outdoor heat exchanger 13 during cooling operation. On the other hand, during the heating operation, the connection pipe 16 is filled with the two-phase refrigerant after passing through the throttle means 15a and the throttle means 15b, so that excess refrigerant is generated by reducing the density of the refrigerant that fills the connection pipe 16. Will do. In order to eliminate the difference in the required amount of refrigerant due to the difference in the operation mode, an accumulator 20 is provided for accumulating surplus refrigerant generated during the heating operation.

  Furthermore, in order to ensure the necessary cooling capacity during the cooling operation, the refrigerant is sealed in an amount that can ensure a certain degree of supercooling so that the refrigerant condensed in the outdoor heat exchanger 13 functioning as a condenser becomes liquid. Will be. However, there is a case where refrigerant leaks from which the refrigerant escapes from the heat pump cycle due to a change over time such as a construction failure at the initial stage of installation or loosening of a connection portion between the pipe and the valve due to vibration. When such a refrigerant leak occurs, the refrigerant in the heat pump cycle gradually decreases, and the degree of supercooling after passing through the outdoor heat exchanger 13 cannot be secured, and the throttle means 15a and the throttle means 15b are in a two-phase state. It will flow in, the heat pump cycle will become unstable, and it will eventually fall into an uncooled state.

  FIG. 6 is a Mollier diagram (PH diagram) showing the refrigerant state during the cooling operation. In FIG. 6, the broken line represents the characteristic of the state in which the refrigerant is properly contained (normal state), and the solid line represents the characteristic of the state (abnormal state) when the refrigerant leaks from the appropriate amount of refrigerant. In FIG. 6, the vertical axis represents absolute pressure (P) and the horizontal axis represents specific enthalpy (H). Based on FIG. 6, the characteristics of the normal state and the characteristics of the abnormal state during the cooling operation will be described.

  In FIG. 6, the portion surrounded by the saturated liquid line and the saturated vapor line indicates that the refrigerant is in a gas-liquid two-phase state, and the left side of the saturated liquid line indicates that the refrigerant is in a liquefied state. On the right side, the refrigerant is in a gasified state. As shown in FIG. 6, in the abnormal state, the subcooling degree SC of the liquid part (difference between the condensation temperature and the outdoor heat exchanger 13 outlet temperature) is reduced by reducing the refrigerant as compared with the normal state. The evaporating temperature Te decreases due to a decrease and the internal pressure in the heat pump cycle decreases, and accordingly, the discharge temperature Td at the outlet of the compressor 11 becomes high.

  Further, during the cooling operation, the expansion means 15a and the expansion means 15b set the refrigerant in the indoor heat exchanger 17a and the indoor heat exchanger 17b to a two-phase state with a high heat transfer coefficient. Therefore, the superheat degree SH (the difference between the outlet temperature of the indoor heat exchanger 17a and the indoor heat exchanger 17b and the evaporating temperature) at the outlet of the indoor heat exchanger 17a and the indoor heat exchanger 17b, that is, the evaporator outlet, is controlled to be constant and does not change. . Furthermore, the condensation temperature Tc decreases the proportion of the liquid phase having a poor heat transfer coefficient of the entire outdoor heat exchanger 13 as the refrigerant amount decreases, so that the heat transfer performance is improved and the condenser intake air temperature (outside air Temperature) and the condensing temperature Tc are slightly reduced and the condensing temperature Tc is lowered. However, if the condenser intake air temperature is the same, the state of the heat pump cycle is almost unchanged.

  On the other hand, the phenomenon at the time of refrigerant leakage differs during heating operation. During the heating operation, when the refrigerant leaks and the refrigerant in the heat pump cycle gradually decreases, the surplus refrigerant is secured in the accumulator 20, so the liquid level of the surplus refrigerant only decreases, and the state of the heat pump cycle is Since it does not change, the heating capacity can be secured. However, when refrigerant leakage further progresses, the refrigerant in the accumulator 20 runs out and the state of the heat pump cycle changes.

  FIG. 7 is a Mollier diagram (PH diagram) showing a refrigerant state during cooling operation. In FIG. 7, the broken line represents the characteristic of the state in which the refrigerant is properly contained (normal state), and the solid line represents the characteristic of the state (abnormal state) when the refrigerant leaks from the appropriate amount of refrigerant. In FIG. 7, the vertical axis represents absolute pressure (P) and the horizontal axis represents specific enthalpy (H). Based on this FIG. 7, the characteristic of the normal state in the heating operation and the characteristic of the abnormal state will be described.

  As shown in FIG. 7, in the abnormal state, even when the refrigerant is reduced as compared with the normal state, the expansion means 15a and the expansion means 15b are connected to the indoor heat exchanger 17a and the indoor heat exchanger 17b. In order to change the state of the refrigerant into a two-phase state having a high heat transfer coefficient, the supercooling degree SC is controlled because the supercooling degree SC at the indoor heat exchanger 17a and the indoor heat exchanger 17b, that is, the condenser outlet is controlled to be constant. do not do. However, when the internal pressure in the heat pump cycle decreases, the evaporation temperature Te decreases, and the degree of superheat SH at the outlet of the outdoor heat exchanger 13 increases. Along with this, there is a feature that the discharge temperature Td at the outlet of the compressor 11 becomes high.

  Since the degree of supercooling SC is controlled to be constant, the condensation temperature Tc is almost the same as the state of the heat pump cycle if the intake air temperatures (indoor temperatures) of the indoor heat exchanger 17a and the indoor heat exchanger 17b are the same. It is a level that does not change. Thus, when the refrigerant decreases, the evaporation temperature Te decreases and the compression ratio increases, so the input to the compressor 11 increases, resulting in inefficient operation, and the discharge temperature at the outlet of the compressor 11 is high. Therefore, a great load is also applied to the compressor 11.

  However, since the refrigerant leaks from a minute pipe gap, the refrigerant leakage proceeds at a very slow speed. That is, the refrigerant leakage often proceeds with a slow leak. If a slow leak has occurred, the refrigerant will gradually escape over several weeks or months. For this reason, there is almost no refrigerant ejection sound, and the change in the heat pump cycle due to the decrease in the refrigerant is small in daily change, so it is very difficult to detect. Refrigerant leakage is also one of the most common claims on the market.

  Therefore, it is very significant to take measures to detect and refill the refrigerant before falling into the uncooled and unwarmed state. As described above, during the heating operation, as long as surplus refrigerant exists, the liquid level only drops when the refrigerant leaks, and depending on the configuration of the equipment, if the refrigerant does not leak more than half of the initial enclosed refrigerant amount, the heat pump cycle There is a problem that it is difficult to find because it does not change. However, even during heating operation, early detection of refrigerant leaks is important from the standpoint of global environmental protection, which is prevention of global warming due to refrigerant leaks, and safety, such as detection of leaks of combustible refrigerants.

  In the heat pump cycle, the heat exchange amount in the outdoor heat exchanger 13 is different when the outside air temperature is different. Moreover, the ambient air temperature of the indoor heat exchanger 17a and the indoor heat exchanger 17b is always controlled by the opening degree of the expansion means 15a and the expansion means 15b. Further, the compressor 11 is subjected to capacity control or ON / OFF control so that the heat pump cycle operates normally. Since the heat pump cycle is formed by circulating refrigerant in the piping, high or low pressure, supercooling degree (difference between condensing temperature and condenser outlet liquid temperature), superheating degree (evaporator outlet) due to changes in operating conditions Each state quantity of the heat pump cycle, such as the difference between the gas temperature and the evaporation temperature, changes.

  Therefore, for example, even if only a change in the degree of supercooling of the heat pump cycle is measured, it cannot be specified whether the change in the degree of supercooling is due to refrigerant leakage or a change in the operating state of the heat pump cycle. . However, since the change factors other than the refrigerant leakage are generated in the normal operation of the refrigeration cycle apparatus 1, a plurality of state quantities including the degree of supercooling of the heat pump cycle are measured in the normal operation state where the refrigerant leakage does not occur. If the plurality of state quantities can be treated as a single state quantity, the refrigerant leak can be specified when the refrigerant leak occurs because the state quantity deviates from the normal value. . As described above, as a method of capturing a plurality of state quantities as one state quantity, there is a method using multivariate analysis of the T method already described.

  As a result of investigations, it was found that the characteristic quantities of refrigerant leakage were low pressure, discharge temperature, and degree of supercooling when it was used to detect refrigerant leakage during cooling of a heat pump cycle. The feature amount is a state amount that changes when the phenomenon occurs. Here, the average values of the feature values (number of items 3) of the normal data of the heat pump cycle are x10, x20, and x30, respectively, and the average of the output values of the state variables of the composite variables represented by the collected normal data Is M0 = 0 (degree of abnormality 0%).

  On the other hand, M1, M2,..., Mn = 1 (output values of operation data (operation data number n) in a state where an abnormal state is apparently generated, for example, the refrigerant is insufficient and the cooling capacity is not ensured). (Abnormality degree 100%). The value obtained by subtracting the average value x10, x20, x30 of each item during normal operation from the value of each item x1, x2, x3 in the abnormal operation state (x11, x12, x13), (xn1, xn2, xn3) ). M1, M2,..., Mn are obtained by subtracting the average M0 of the output values in the abnormal operation state from the output value Mx in the abnormal operation state (in this case, since M0 = 0, M1, M2,..., Mn No change in value).

  Thus, the data is normalized, and the proportionality constant β and the SN ratio η of the proportional expression with respect to the output value of the abnormal data are obtained for each item by the above formulas (1) to (7). Next, the feature amount is measured every moment, and an estimated value of M representing the degree of abnormality is obtained by each item x1, x2, x3 of the data measured from the current operating state of the heat pump cycle by the above equation (8). As a result, the abnormality degree M of the refrigerant leakage from the refrigerant circuit of the heat pump cycle can be estimated.

  FIG. 8 is an explanatory diagram for explaining the relationship between the degree of abnormality and extracted data. In FIG. 8, in the same model refrigeration cycle apparatus 1 installed in the same building, the refrigerant amount is 100% of the normal refrigerant amount (a) and 60% refrigerant leakage. In the abnormal state simulating ((b) shown in the figure), the number of extracted data and the calculation result of the output value M of the degree of abnormality are shown for the operation data for three days in summer by the above method. In FIG. 8, the horizontal axis indicates the number of extracted data, and the vertical axis indicates the degree of abnormality.

  FIG. 8 shows that the degree of abnormality is high when the amount of refrigerant is small, that is, in an abnormal state simulating 60% refrigerant leakage ((b) shown in the figure). That is, a predetermined abnormality determination threshold value (solid line shown in the figure) is set, and abnormality determination (whether refrigerant is leaking) is performed based on whether or not the abnormality determination threshold value is exceeded. Note that the abnormality determination threshold is 50% in the figure, but a plurality of abnormality determination thresholds may be set. Further, the display and output method of the notification device 8 may be changed depending on the degree of abnormality.

  FIG. 9 is an explanatory diagram for explaining the transition of the degree of abnormality from the normal state over time. Based on FIG. 9, the transition of the degree of abnormality from the normal state over time when the refrigerant leakage abnormality due to the slow leak occurs will be described. In FIG. 9, the horizontal axis represents time, and the vertical axis represents the degree of abnormality. As shown in FIG. 9, it can be seen that the degree of abnormality is small in the normal state, and gradually increases to a larger value as time elapses as the refrigerant leakage increases.

  Therefore, it is possible to estimate the time until failure from the relationship between the increasing tendency of the abnormality degree and the failure threshold. And it becomes possible to prevent the fall of the cooling capacity of the refrigerating-cycle apparatus 1 or the fall of a heating capacity by performing an exact maintenance before the estimated failure time. For example, if it takes one month from the initial normal state until the degree of abnormality reaches half of the threshold value, it can be predicted that it will take another month before the degree of abnormality reaches the threshold value and falls into a failure state.

  Further, as described above, the estimated value of M of the degree of abnormality represented by the equation (8) has a sign of ±, so it is possible to determine whether the refrigerant is excessive or insufficient. In other words, if the output value M of the degree of abnormality in the abnormal state of refrigerant leakage is 1, it will be close to 0 if the amount of refrigerant is appropriate, and will be negative if the refrigerant is excessively charged as a heat pump cycle. Since the value is output, it is also possible to determine the possibility of the liquid back operation to the compressor 11 that occurs when the refrigerant is excessively sealed.

  In addition, when the existing connection pipe is used for replacing only the outdoor heat of the existing refrigeration cycle apparatus 1 or adding an indoor unit, the length of the connection pipe and the capacity of the existing indoor unit are unknown. Although it was impossible to determine the required amount of refrigerant, normal operation data was stored in advance, the characteristic amount related to refrigerant leakage was measured every moment in the refrigerant charging process, and the value of the degree of abnormality M was calculated However, when the value of the degree of abnormality M approaches 0, if the charging of the refrigerant is stopped, an appropriate amount of the necessary refrigerant can be charged, so that the workability of the refrigeration cycle apparatus 1 is improved.

  Here, the case where the refrigerant leakage is estimated by three measurement amounts or state quantities of the low pressure of the heat pump cycle, the discharge temperature, and the degree of supercooling has been described as an example, but the present invention is not limited to this. For example, the evaporation temperature (evaporator saturation temperature) may be used instead of the low pressure. Further, the abnormality degree M may be obtained using more state quantities than the three state quantities. Thus, the detection accuracy of the refrigerant leak occurring in the refrigeration cycle apparatus 1 is improved by using more state quantities.

  Furthermore, although the outdoor heat exchanger liquid temperature detection means 203 demonstrated to the example the case where it installed in the exit piping of the outdoor heat exchanger 13, it is not limited to this, The connection piping 16 which is liquid piping is used. If it installs in any place, if it installs in any place, the same effect can be produced. However, when the degree of supercooling at the position where the outdoor heat exchanger liquid temperature detecting means 203 is installed is as large as possible, the refrigerant leakage detection accuracy is higher, so that it is closer to the high pressure side and the throttle means 15a and the throttle means 15b. More preferably, it is installed at the position.

  Moreover, although the operation data of each item assumed in the normal operation of the heat pump cycle is stored in the storage unit 104 in advance as the normal operation data described above, this is not limited to one, and is detected. In order to improve accuracy, multiple normal operation data may be retained according to the outside air temperature, and the normal data may be changed according to the measured outside air temperature. You may make it changeable according to the information of the number of indoor units in operation, and a control target. The same applies to abnormal operation data.

  Furthermore, in this embodiment, when abnormal operation data is set, the output values M1, M2,..., Mn = 1 of each abnormal data are all set to 100% abnormalities. Even if the operation data is acquired and the output value M of the abnormal data is changed, for example, M1 = 0.5, M2 = 0.8,. Good. Thus, the detection accuracy of the refrigerant leak is improved when the output value M is changed according to the degree of abnormality.

  Further, even in a normal state in which the refrigerant amount is properly sealed when the device is installed, the actual initial charged refrigerant amount varies somewhat depending on the construction situation even in the same device. Therefore, when it is determined that the normal state, normal data stored in the storage unit 104 can be changed and corrected again to absorb variations due to individual device differences. For example, if the measured value is smaller than the average value of the supercooling degree of the operation data when the degree of supercooling, which is the feature quantity of refrigerant leakage, is normal, the measured value is used as the normal operation data. It can be realized by replacing it with the average value of the degree of supercooling.

  Here, the case of the cooling operation has been described as an example, but the same applies to the case of the heating operation. The refrigerant flowing out of the accumulator 20 is a saturated gas refrigerant. However, when the surplus refrigerant decreases due to refrigerant leakage, the refrigerant gas flows out of the accumulator 20. Then, since the temperature measured by the compressor discharge temperature detecting means 201 becomes high, the refrigerant leaks by performing the same processing as above with the high pressure or condensation temperature, the low pressure or evaporation temperature, and the compressor discharge temperature as the feature quantities. Can be determined.

  However, in this case, since the heat pump cycle does not change as long as the surplus refrigerant exists, the throttling means 15a and the throttling means 15b are arranged so that the surplus refrigerant in the accumulator 20 is eliminated only when the abnormal state is determined in the heating operation. If the operation of storing the excess refrigerant in the indoor heat exchanger 17a and the indoor heat exchanger 17b is performed so that the refrigerant becomes a gas refrigerant at the outlet of the outdoor heat exchanger 13, the change when the refrigerant decreases is Similar to the change of the heat pump cycle in operation, the degree of supercooling SC decreases, the evaporation temperature Te decreases, the compressor discharge temperature increases, and the refrigerant leakage can be estimated from the temperature and pressure information.

  As described above, the failure diagnosis apparatus 100 can detect the refrigerant leak at an early stage by providing a special operation mode for determining the refrigerant leak and periodically performing the operation. This special operation mode can be executed by forcibly controlling the heat pump cycle by the control unit 103 by a signal from a remote from the input device 7 or a signal such as a dip switch. In order to determine that all of the surplus refrigerant is gas refrigerant, a suction temperature detecting means is provided in the suction pipe of the compressor 11 from the outlet of the accumulator 20, and the degree of superheat (measured value of the suction temperature and the low pressure detecting means 205) is provided. It is possible to determine that the gas is surely determined by determining whether the difference in the saturated gas temperature obtained by (1) is positive, so that the detection accuracy is improved.

Further, the suction temperature may be obtained from the high pressure, the low pressure, and the compressor discharge temperature of the compressor 11 from the following equation (9), assuming that the compression process in the compressor 11 is a polytropic change.
Here, Ts represents the suction temperature [K], Td represents the discharge temperature [K], Ps represents the low pressure [MPa] of the compressor suction, Pd represents the high pressure [Pd] of the compressor discharge, and n represents the polytropic index. .

  FIG. 10 is a schematic configuration diagram showing configurations of the refrigeration cycle apparatus 1a and the microcomputer 2. The configuration of the refrigeration cycle apparatus 1a will be described in detail based on FIG. Here, the description will focus on the differences between the refrigeration cycle apparatus 1a and the refrigeration cycle apparatus 1, and the same parts as those in the refrigeration cycle apparatus 1 will be denoted by the same reference numerals and description thereof will be omitted. This refrigeration cycle apparatus 1a differs from the configuration of the refrigeration cycle apparatus 1 in that a receiver 21 and a throttle means 22 (lower stage side) are provided instead of the accumulator 20. The same can be said for the refrigeration cycle apparatus 1 having such a configuration as described above.

  In the case of the refrigeration cycle apparatus 1a, excess refrigerant is stored in the receiver 21, and when the excess refrigerant is in the receiver 21, the refrigerant flowing out from the receiver 21 is saturated liquid refrigerant, but there is little excess refrigerant due to refrigerant leakage. Then, the two-phase refrigerant flows out from the receiver 21. Then, since the temperature of the compressor discharge temperature detection means 201 becomes high, the refrigerant leakage can be determined by performing the same processing as described above with the high pressure or the condensation temperature, the low pressure or the evaporation temperature, and the discharge temperature as the feature quantities. .

  Further, in order to eliminate excess refrigerant, that is, during the cooling operation, the opening area of the expansion means 22 is made smaller than the total opening area of the expansion means 15a and the expansion means 15b, and during the heating operation, the total of the expansion means 15a and the expansion means 15b. The opening area is controlled to be smaller than the opening area of the diaphragm means 22. By doing so, the outlet refrigerant of the receiver 21 is in a two-phase state, and the extra refrigerant in the receiver 21 is moved into a condenser (outdoor heat exchanger or indoor heat exchanger) and stored in a special operation. This makes it possible to estimate changes in refrigerant leakage from temperature and pressure information, and to determine refrigerant leakage at an early stage.

  In a refrigeration cycle apparatus without an accumulator 20 or a receiver 21, such as a room air conditioner or a chilling unit, excess refrigerant accumulates in the condenser, but when an abnormality occurs, the change behavior of the state quantity of the heat pump cycle can be predicted by simple calculation. Therefore, the refrigerant leakage can be determined by the same method. In other words, usually excess refrigerant accumulates in a part of the condenser, but when refrigerant leakage occurs, the amount of refrigerant accumulated in the condenser (outdoor heat exchanger or indoor heat exchanger) decreases, and the condenser Since the area contributing to heat transfer increases, the degree of supercooling SC decreases. Therefore, the leakage of the refrigerant can be determined by performing the same processing as described above using the discharge temperature, the low pressure or the evaporation temperature, and the degree of supercooling as the feature amount.

  In addition, here, refrigerant leakage has been described as an example of an abnormality in the heat pump cycle, but the present invention is not limited to this. For other abnormalities, the behavior of the heat pump cycle when the abnormality occurs can be predicted by simple calculation. Can be identified. The term “abnormality” here is described as a concept including not only a failure of the device but also a change with time such as deterioration of the device. That is, any abnormality can be detected as long as the operating state of the refrigeration cycle apparatus 1a changes.

  For example, the surface of the outdoor heat exchanger 13, the indoor heat exchanger 17 a, and the indoor heat exchanger 17 b that are subjected to heat exchange is contaminated or damaged, the outdoor fan 14, the indoor fan 18 a, the indoor fan 18 b is deteriorated or broken, and the refrigerant circulates. It is possible to detect and discriminate clogging of a strainer that removes dust and the like in the interior of the inside and a dryer for preventing moisture in the refrigerant, breakage, breakage, clogging, and the like of the pipe with the same configuration and method. The method will be described below. First, after determining abnormality in the outdoor heat exchanger 13 and the outdoor blower 14, the determination of abnormality in the indoor heat exchanger 17a, the indoor heat exchanger 17b, the indoor blower 18a, and the indoor blower 18b will be described.

  FIG. 11 is an explanatory diagram for explaining a method of determining abnormality in the outdoor heat exchanger 13 and the outdoor blower 14 during the cooling operation. Based on FIG. 11, a method for determining dirt or breakage of the outdoor heat exchanger 13 and abnormality of the outdoor fan 14 will be described. In FIG. 11, the horizontal axis indicates the position of the outdoor heat exchanger 13, and the vertical axis indicates the temperature of the outdoor heat exchanger 13 and the condenser intake air temperature (outside air temperature Tao). Further, broken line arrows indicate the characteristics of the normal state, and solid line arrows indicate the characteristics of the abnormal state.

  That is, in FIG. 11, the outdoor heat exchanger 13 is not contaminated during the cooling operation, and the outdoor fan 14 outputs a desired air volume, which is in a normal state (normal state), and the outdoor heat exchanger 13 is aged over time. The outdoor heat exchanger 13 functioning as a condenser due to the contamination or the failure of the outdoor blower 14 represents the characteristics of the function deterioration (abnormal state) as the heat exchanger. The heat exchange amount Q [W] in the outdoor heat exchanger 13 can be expressed by the following formula (10).

Here, Ao is the heat transfer area [m2] of the outdoor heat exchanger 13, Kto is the heat passage rate [W / m2K] based on the temperature difference, and ΔT is the temperature difference between the temperature of the outdoor heat exchanger and the air temperature [° C. ] Respectively.

  When the outdoor heat exchanger 13 is damaged due to deterioration over time, or when the outdoor heat exchanger 13 is soiled or the outdoor blower 14 is broken, the value of the heat transfer area Ao or the heat transfer rate Kto decreases. In order to process the same air conditioning load, the temperature difference ΔT becomes large. Therefore, as shown in FIG. 11, the refrigerant temperature Td and the condensation temperature Tc at the inlet of the outdoor heat exchanger 13 increase as compared with the normal time, and the temperature difference from the outdoor air temperature Tao increases. Since the temperature of the outdoor heat exchanger 13 is almost dominant in the two-phase region, if the temperature difference dTc between the condensation temperature Tc and the outside air temperature Tao is ΔT, the condensation temperature Tc and the discharge temperatures Td and ΔT are the outdoor heat. It can be selected as an item of the characteristic amount when the exchanger is dirty or the outdoor blower 14 is out of order.

  The normal ΔT is stored at the time of initial operation, the abnormal state is assumed to be a state where the value of Ao × Kto is reduced to 50% of the normal value, and the abnormal ΔT is set to twice the normal ΔT value. If the abnormality data is created with the degree of abnormality at this time as 100%, it is possible to detect the contamination of the outdoor heat exchanger 13 and the failure of the outdoor blower 14 by the above method. Here, the condensing temperature Tc, the discharge temperature Td, and ΔT have been described as the characteristic amount of the performance deterioration of the outdoor heat exchanger 13 during cooling, but the characteristic amount is not limited to this, and the degree of supercooling SC or Any index may be used as long as it represents the characteristics of the heat exchange performance of the outdoor unit such as the temperature efficiency of the refrigerant in the liquid phase part obtained by dividing the degree of supercooling SC by ΔT.

  FIG. 12 is an explanatory diagram for explaining a method for determining abnormality in the outdoor heat exchanger 13 and the outdoor blower 14 during the heating operation. Based on FIG. 12, a method of determining whether the outdoor heat exchanger 13 is dirty or damaged, or the outdoor fan 14 is abnormal will be described. In FIG. 12, the horizontal axis indicates the position of the outdoor heat exchanger 13 and the vertical axis indicates the temperature of the outdoor heat exchanger 13 and the evaporator intake air temperature (outside air temperature Tao), as in FIG. Further, broken line arrows indicate the characteristics of the normal state, and solid line arrows indicate the characteristics of the abnormal state.

  That is, in FIG. 12, the outdoor heat exchanger 13 is not contaminated during heating operation, and the outdoor fan 14 outputs a desired air volume. The characteristics of the normal state (normal state) and the deterioration of the outdoor heat exchanger 13 over time. The outdoor heat exchanger 13 functioning as an evaporator due to the contamination or the failure of the outdoor blower 14 represents the characteristic of the function deterioration (abnormal state) as the heat exchanger. The heat exchange amount Q [W] in the outdoor heat exchanger 13 can be expressed by the following formula (11).

Here, Ao is the heat transfer area [m 2] of the outdoor heat exchanger 13, Kho is the heat transfer rate [W / (m 2 · J / kg)] based on the enthalpy difference, and ΔH is a refrigerant flowing through the outdoor heat exchanger 13. It represents the enthalpy difference [J / kg] between the air at the temperature and the intake air.

  When the outdoor heat exchanger 13 is damaged due to deterioration over time, or when the outdoor heat exchanger 13 is soiled or the outdoor blower 14 is broken, the value of the heat transfer area Ao or the heat transfer rate Kho decreases. In order to process the same air conditioning load, the enthalpy difference ΔH becomes large. Accordingly, as shown in FIG. 12, the evaporation temperature Te at the inlet of the outdoor heat exchanger 13 is lowered with respect to the normal time, and the temperature difference from the outside air temperature Tao is increased. Further, the discharge temperature Td of the compressor increases as the evaporation temperature Te decreases.

  The enthalpy difference ΔH is approximately proportional to the temperature difference between the air and the outdoor heat exchanger 13 if the relative humidity is equal. Therefore, the temperature of the outdoor heat exchanger 13 is almost dominated by the two-phase region. Since the temperature difference between the temperature Te and the outside air temperature Tao is dTe, the evaporating temperature Te, the discharge temperature Td, and dTe can be selected as items of the feature quantity when the outdoor heat exchanger 13 becomes dirty or the outdoor blower 14 fails. is there. The normal dTe is stored at the time of initial operation, the abnormal state is assumed to be a state where the value of Ao × Kho is reduced to 50% of the normal time, and the dTe at the time of the abnormal is set to a value twice the normal dTe. If the abnormality data is created with the abnormality degree at this time being 100%, it is possible to detect the contamination of the outdoor heat exchanger 13 or the failure of the outdoor blower 14 by the above method.

  Here, the evaporating temperature Te, the discharge temperature Td, and dTe have been described as the characteristic amounts of dirt in the outdoor heat exchanger 13 during heating. However, the characteristic amounts are not limited thereto, and the discharge temperature Td and the condensation temperature are not limited thereto. Since the difference in Tc and the like increase as the heat exchange performance of the outdoor heat exchanger 13 decreases, it may be added as an index that represents the characteristics of the heat exchange performance of the outdoor unit. Moreover, although it demonstrated that it was necessary to measure the intake air temperature (outside air temperature Tao) of the outdoor heat exchanger 13, when the refrigeration cycle apparatus 1a has stopped equipment, such as thermo OFF, The value of the temperature sensor attached to the outdoor heat exchanger 13 or the outdoor unit may be substituted as the outside air temperature is equal, or the outside air temperature of the weather data may be received.

  FIG. 13 is an explanatory diagram for explaining a method of determining an abnormality in the indoor heat exchanger 17a, the indoor heat exchanger 17b, the indoor blower 18a, and the indoor blower 18b during the cooling operation. Based on FIG. 13, a description will be given of a method for determining whether the indoor heat exchanger 17a or the indoor heat exchanger 17b is dirty or damaged, or the abnormality of the indoor blower 18a or the indoor blower 18b or the outdoor blower 14. In FIG. 13, the horizontal axis indicates the position of the indoor heat exchanger 17a and the indoor heat exchanger 17b, and the vertical axis indicates the temperature of the indoor heat exchanger 17a and the indoor heat exchanger 17b, and the evaporator intake air temperature (room temperature Tai). Respectively. Further, broken line arrows indicate the characteristics of the normal state, and solid line arrows indicate the characteristics of the abnormal state.

  That is, in FIG. 13, during the cooling operation, the indoor heat exchanger 17a and the indoor heat exchanger 17b are not contaminated, and the indoor fan 18a and the indoor fan 18b output a desired air volume (normal state). The indoor heat exchanger 17a and the indoor heat exchanger 17b functioning as an evaporator due to aging deterioration and dirt of the indoor heat exchanger 17a and the indoor heat exchanger 17b or a failure of the indoor fan 18a and the indoor fan 18b are used as heat exchangers. It represents the characteristics of the state of functional deterioration (abnormal state). The heat exchange amount Q [W] in the indoor heat exchanger 17a and the indoor heat exchanger 17b can be expressed by the following equation (12).

Here, Ai is the heat transfer area [m2] of the indoor heat exchanger 17a and the indoor heat exchanger 17b, Khi is the heat transfer rate [W / (m2 · J / kg)] based on the enthalpy difference, and ΔH is the indoor heat exchange. Represents the enthalpy difference [J / kg] between the temperature of the heat exchanger 17a and the indoor heat exchanger 17b and the air temperature.

  When the indoor heat exchanger 17a or the indoor heat exchanger 17b is damaged due to deterioration over time, or when the indoor heat exchanger 17a or the indoor heat exchanger 17b is dirty, a filter installed at the inlet of the indoor unit When clogged, the value of the heat transfer area Ai or the heat transfer rate Khi is reduced when the indoor fan 18a or the indoor fan 18b is broken, so that the temperature difference ΔH is large to handle the same air conditioning load. Will be. Therefore, as shown in FIG. 13, the evaporation temperature Te at the inlet of the heat exchanger is lowered with respect to the normal time, and the temperature difference from the indoor temperature Tai is increased.

  Further, the discharge temperature Td of the compressor 11 increases as the evaporation temperature Te decreases. The evaporator outlet temperature Teo has a constant temperature difference between Teo and Te because the superheat degree SH at the outlet of the indoor heat exchanger 17a and the indoor heat exchanger 17b is controlled by the throttle means 15a and the throttle means 15b. . If the relative humidity is equal, the enthalpy difference ΔH is almost proportional to the temperature difference between the intake air and the heat exchanger. Therefore, the temperature of the indoor heat exchanger 17a and the indoor heat exchanger 17b is almost dominated by the two-phase region. Therefore, the temperature difference between the evaporation temperature Te and the room temperature Tai is dTe, and the evaporation temperature Te, the discharge temperatures Td and dTe are used as dirt in the indoor heat exchanger 17a and the indoor heat exchanger 17b, the indoor fan 18a and the indoor fan. It can be selected as an item of the feature amount at the time of failure 18b.

  The normal dTe is stored in the initial operation, the abnormal state is assumed to be a state where the value of Ai × Khi has been reduced to 50% of the normal value, and the dTe value in the abnormal state is set to a value twice the normal dTe value. If the abnormality data is created with the degree of abnormality at this time as 100%, the contamination of the indoor heat exchanger 17a and the indoor heat exchanger 17b and the failure of the indoor fan 18a and the indoor fan 18b can be detected by the above method. Is possible. Here, the evaporating temperature Te, the discharge temperature Td, and dTe have been described as the characteristic amount of the performance deterioration of the indoor heat exchanger 17a and the indoor heat exchanger 17b during cooling, but the characteristic amount is not limited thereto. In addition, the difference between the discharge temperature Td and the condensation temperature Tc also increases with a decrease in the heat exchange performance of the indoor heat exchanger 17a and the indoor heat exchanger 17b, so that it is added as an index that represents the characteristics of the heat exchange performance of the indoor unit. Also good.

  In addition, it is assumed that the relative humidity of the intake air of the indoor heat exchanger 17a and the indoor heat exchanger 17b is equal to the relative humidity at the heat exchanger temperature, but the intake of the indoor heat exchanger 17a and the indoor heat exchanger 17b A sensor for measuring the relative humidity of the air is provided, the relative humidity is measured, the enthalpy of the air is obtained, and the relative humidity of the indoor heat exchanger 17a and the indoor heat exchanger 17b is assumed to be a wet surface and 100% humidity. If the enthalpy difference ΔH is obtained, the detection accuracy can be further improved.

  FIG. 14 is an explanatory diagram for explaining a method for determining an abnormality in the indoor heat exchanger 17a, the indoor heat exchanger 17b, the indoor blower 18a, and the indoor blower 18b during the heating operation. Based on FIG. 14, a description will be given of a method for determining whether the indoor heat exchanger 17a or the indoor heat exchanger 17b is dirty or damaged, or the abnormality of the indoor blower 18a or the indoor blower 18b or the outdoor blower 14. In FIG. 12, as in FIG. 11, the horizontal axis indicates the position of the indoor heat exchanger 17a or the indoor heat exchanger 17b, and the vertical axis indicates the temperature of the indoor heat exchanger 17a or the indoor heat exchanger 17b, the evaporator intake air temperature. (Outside air temperature Tai) is shown. Further, broken line arrows indicate the characteristics of the normal state, and solid line arrows indicate the characteristics of the abnormal state.

  That is, in FIG. 12, the indoor heat exchanger 17a and the indoor heat exchanger 17b are not contaminated during the heating operation, and the indoor fan 18a and the indoor fan 18b output a desired air volume (normal state). The indoor heat exchanger 17a and the indoor heat exchanger 17b functioning as a condenser due to aging deterioration and dirt of the indoor heat exchanger 17a and the indoor heat exchanger 17b or failure of the indoor blower 18a and the indoor blower 18b are used as heat exchangers. It represents the characteristics of the state of functional deterioration (abnormal state). The heat exchange amount Q [W] in the indoor heat exchanger 17a and the indoor heat exchanger 17b can be expressed by the following equation (13).

Here, Ai is the heat transfer area [m2] of the indoor heat exchanger 17a and the indoor heat exchanger 17b, Kti is the heat transfer rate [W / m2 K] based on the temperature difference, and ΔT is the indoor heat exchanger 17a and the indoor heat. The temperature difference [° C.] between the temperature of the exchanger 17b and the air temperature is shown.

  When the indoor heat exchanger 17a or the indoor heat exchanger 17b is damaged due to deterioration over time, or when the indoor heat exchanger 17a or the indoor heat exchanger 17b is dirty, a filter installed at the inlet of the indoor unit When clogged, the value of the heat transfer area Ai or the heat transfer rate Kti decreases when the indoor blower 18a or the indoor blower 18b fails, so that the temperature difference ΔT is large to handle the same air conditioning load. Will be. Therefore, as shown in FIG. 14, the refrigerant temperature Tci and the condensation temperature Tc at the inlet of the heat exchanger increase with respect to the normal time, and the temperature difference from the outside air temperature Tao increases.

  Since the temperature of the indoor heat exchanger 17a and the indoor heat exchanger 17b is almost dominant in the two-phase region, if the temperature difference dTc between the condensation temperature Tc and the outside air temperature Tao is ΔT, the condensation temperature Tc, the condenser The inlet temperatures Tci and ΔT can be selected as items of the feature amount when the indoor heat exchanger 17a or the indoor heat exchanger 17b is dirty or when the indoor fan 18a or the indoor fan 18b is out of order. The normal ΔT is stored at the time of initial operation, and the abnormal state is assumed to be a state where the value of Ai × Kti has been reduced to 50% of the normal value, and the abnormal ΔT is set to twice the normal ΔT value. If the abnormality data is created with the degree of abnormality at this time as 100%, the contamination of the indoor heat exchanger 17a and the indoor heat exchanger 17b and the failure of the indoor fan 18a and the indoor fan 18b can be detected by the above method. Is possible.

  Here, the condensing temperature Tc, the condenser inlet temperature Tci, and ΔT have been described as the characteristic amount of the performance deterioration of the indoor heat exchanger 17a and the indoor heat exchanger 17b during heating, but the characteristic amount is limited to this. Rather, an index that represents the heat exchange performance characteristics of the indoor unit, such as the temperature efficiency of the refrigerant in the liquid phase part obtained by dividing the supercooling degree SC or the supercooling degree SC by ΔT, is used as a feature amount for abnormality detection. May be.

Next, abnormalities such as clogging of a strainer for removing dust etc. in the inside of the circulating refrigerant and a drier for preventing moisture of the refrigerant, breakage or breakage of piping, clogging or failure of the throttling means 15a or throttling means 15b are determined. The method is described. The following formula (14) expresses the relationship between the mass flow rate of the fluid and the differential pressure before and after that by a dimensionless index called Cv value.

  Here, M is the flow rate [gal / min], G is the specific gravity, and ΔP is the differential pressure [psi] before and after the valve. The Cv value is “the flow rate of water at a temperature of 60 ° F. (about 15.5 ° C.) flowing through the valve when the pressure difference is 1 lb / in 2 [6.895 kPa] at a specific opening of the valve. / Min (1 US gal = 3.785 L) (numerical value (no dimension)) ”. In general, when a valve is selected, a Cv value is obtained from a fluid specification, and compared with a Cv value indicated by a valve manufacturer. One. If the fluid flow rate M, specific gravity G, and differential pressure ΔP are obtained from the equation (14), the Cv value can be obtained.

  Here, the specific gravity G can be obtained from the temperature of the refrigerant flowing into the throttling means 15a and the throttling means 15b and the condensation side pressure because the density can be calculated if the refrigerant flowing through the circuit of the heat pump cycle is determined. Value. The flow rate M can be estimated from the amount of displacement of the compressor 11, the frequency, and the refrigerant density sucked by the compressor 11. The front-rear differential pressure ΔP can also be calculated by converting the pressure detection means or the value of the saturation temperature into a pressure. Therefore, it is possible to obtain the Cv value from the operation state of the heat pump cycle. In this way, the Cv value obtained from the operating state of the heat pump cycle is hereinafter referred to as Cvcyc.

  Referring to the refrigerant circuit of FIG. 2, there are a plurality of throttle means (throttle means 15a and throttle means 15b), but the combined Cv value when the throttle means 15a and the throttle means 15b are in parallel is given by It turns out that it becomes the total value of each Cv value. FIG. 15 shows the relationship between the opening degree of the throttle means 15a and the throttle means 15b and the Cv value. It can be seen that the larger the opening of the throttling means 15a and the throttling means 15b, the larger the Cv value. Normally, the throttle means 15a and the throttle means 15b change the opening degree to control the superheat degree SH at the outlet of the evaporator during cooling and to control the degree of supercooling SC at the outlet of the condenser during heating. The Cv value can be obtained if the indicated opening degree of the throttle means 15a and the throttle means 15b is known. Therefore, the combined Cv value obtained from the indicated opening is hereinafter referred to as Cvx.

  If the heat pump cycle is normal and there is no place where pressure loss occurs anywhere on the circuit, the pressure Pd measured by the high pressure detection means 202 before and after the compressor 11 and the pressure Ps measured by the low pressure detection means 205 Cvcyc can be obtained from the operating state of the heat pump cycle from the flow rate M estimated from the operating capacity of the compressor 11 and the specific gravity G of the refrigerant flowing through the circuit of the heat pump cycle, where the differential pressure is ΔP. It becomes equal to Cvx which is a synthetic Cv value obtained from the indicated opening degree of 15a and the throttle means 15b.

  However, if the strainer that removes dust in the refrigerant circuit of the heat pump cycle is clogged, the refrigerant moisture is clogged with the dryer, the pipe is broken, or the throttle means 15a or the throttle means 15b is clogged, the flow rate is increased by that amount. Since it is necessary, the opening degree of the throttle means 15a and the throttle means 15b is increased, and the value of Cvx is increased. Further, since Cvcyc obtained from the differential pressure between the high pressure Pd and the low pressure Ps before and after the compressor 11 is the same, the relationship Cvcyc <Cvx is established, and the relationship between the two diverges. It is possible to determine that clogging has occurred.

  On the other hand, when the opening degree is kept open due to a failure of the throttle means 15a or the throttle means 15b and the throttle cannot be reduced to the indicated opening degree, the relationship Cvcyc <Cvx is established. It can be determined that this is a failure. Therefore, for example, the difference between the high pressure Pd, the low pressure Ps, and Cvcyc and Cvx is used as the characteristic amount of the clogging of the components of the refrigerant circuit of the heat pump cycle. Is set to a predetermined value, the degree of abnormality at that time is set to 100%, and analysis is performed by the method described above, so that when the pipe is clogged, the degree of abnormality approaches + 100%, and the throttling means 15a and throttling means 15b When the predetermined opening degree cannot be reduced due to a failure, the error approaches -100%, so that various abnormalities can be determined.

  Here, the method for determining the clogging of the entire refrigerant circuit of the heat pump cycle has been described. However, as shown in FIG. 2, the indoor unit holding the indoor heat exchanger 17a is stopped and the throttle means 15a is fully closed. In the state in which the indoor unit that holds the indoor heat exchanger 17b is operating, the refrigerant flows only in the throttle means 15b, so that the piping circuit of the circuit other than the pipe passing through the throttle means 15a is clogged. Can be determined. Of course, the same applies to the reverse case, and the clogged portion can be specified. Further, if this operation is forcibly performed, each indoor unit is rotated and operated, and the circuit of each indoor unit is diagnosed, it becomes possible to determine the circuit clogging at an earlier stage.

  FIG. 16 is a flowchart showing a flow of abnormality determination processing performed by the failure diagnosis apparatus 100. Based on FIG. 16, a processing procedure for determining various abnormal causes of the refrigeration cycle apparatus 1 will be described with respect to the contents described above. First, it is determined whether or not initial learning is necessary based on the number of days elapsed since the refrigeration cycle apparatus 1 is installed, the learning state, and the like (step S101). The initial learning refers to the high pressure and the low pressure due to the different lengths of the connection pipe 16 and the connection pipe 19 with respect to the normal operation data and the abnormal operation data stored in advance as the normal operation state of the refrigeration cycle apparatus 1. Normal in equipment re-installed to absorb data differences due to differences in loss, installation conditions such as the number of connected indoor heat exchangers 17a and 17b, and differences in individual differences in equipment, etc. Operation data and abnormal operation are acquired.

  If the initial learning operation has not been performed, the initial learning operation is performed (step S101; YES). This is executed only when the normal operation is determined from the normal operation data and abnormal operation data stored in advance (step S102). If it is a normal operation state (step S102; YES), normal data is measured and learned from the normal operation state (step S103). The normal data is data of items necessary for determining each abnormality described above, and is the temperature, pressure, control target value, or a value obtained by calculating them in the heat pump cycle.

  Next, the state at the time of occurrence of each abnormality is estimated, normal state data is forcibly processed into one or more items, and abnormal data at the time of abnormal operation is learned (step S104). For example, considering the refrigerant leakage of the refrigeration cycle apparatus 1, when the refrigerant leaks, the supercooling degree becomes a liquid phase due to the lack of refrigerant, so the supercooling degree is forcibly reduced. You should study. Moreover, about what can reproduce an abnormal state with a real machine, forced abnormal operation may be actually performed and abnormal operation data may be learned. The initial learning is completed when the above processing is performed and sufficient data is prepared to constitute each normal state or abnormal state.

  When there is no need for initial learning, calculation is performed in actual operation, that is, from the state quantity of the current operation state (step S101; NO). First, each data is measured every moment (step S105), the data is normalized (step S106), and an abnormality degree M value for each abnormality cause is calculated (step S107). Then, the degree of abnormality is compared, the presence / absence of the abnormality, the cause of the abnormality are determined, and the output of displaying the cause of the abnormality is performed (step S108). Only when the above-described abnormality determination is performed, the detection accuracy of the determination can be improved by setting the above-described special operation mode for abnormality determination or fixing the fan rotation speed of the outdoor fan 14, the indoor fan 18a, or the indoor fan 18b. Improve and judge early.

  As described above, it is possible to absorb differences between individual devices such as the refrigeration cycle apparatus 1 and the refrigeration cycle apparatus 1a, differences due to the operation control method of the model, and to easily set a threshold value for abnormality determination and the number of measurement data Even when there are few or there is a strong correlation between items of measurement data, or when the standard deviation of data is 0, the cause of failure in failure determination can be specified. Further, by using the state quantities of a plurality of data of the heat pump cycle, refrigerant leakage, heat exchanger (outdoor blower 13, indoor heat exchanger 17a, indoor heat exchanger 17b) contamination, refrigerant circuit pipe clogging, etc. It is possible to detect each abnormality and to detect the abnormality at an early stage. In addition to failure diagnosis and monitoring, it is possible to predict the occurrence of an abnormality.

It is a conceptual diagram which shows the whole concept of the failure diagnosis apparatus which concerns on embodiment. It is a schematic block diagram which shows the structure of a refrigerating-cycle apparatus and a microcomputer. It is a figure which shows the relationship between the output value after normalization, and the item value of measurement data. It is explanatory drawing for demonstrating the view of the abnormality degree M represented by the normal data of the normal state of each item, and the abnormal data of an abnormal state. It is explanatory drawing for demonstrating the concept of the abnormality determination method using T method. It is a Mollier diagram (PH diagram) showing a refrigerant state at the time of cooling operation. It is a Mollier diagram (PH diagram) showing a refrigerant state at the time of cooling operation. It is explanatory drawing for demonstrating the relationship between an abnormality degree and extraction data. It is explanatory drawing for demonstrating the transition by the time passage of the abnormality degree from a normal state. It is a schematic block diagram which shows the structure of a refrigerating-cycle apparatus and a microcomputer. It is explanatory drawing for demonstrating the determination method of abnormality in the outdoor heat exchanger and the outdoor air blower at the time of air_conditionaing | cooling operation. It is explanatory drawing for demonstrating the determination method of abnormality in the outdoor heat exchanger and the outdoor air blower at the time of heating operation. It is explanatory drawing for demonstrating the determination method of the abnormality in an indoor heat exchanger at the time of air_conditionaing | cooling operation or an indoor air blower. It is explanatory drawing for demonstrating the determination method of the abnormality of an indoor heat exchanger at the time of heating operation, or an indoor air blower. The relationship between the opening degree of a throttle means and Cv value is shown. It is a flowchart which shows the flow of the abnormality determination process which a failure diagnosis apparatus performs.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Refrigeration cycle apparatus, 1a Refrigeration cycle apparatus, 2 Microcomputer, 3 Communication means, 4 Remote monitoring room, 5 Computer, 6 Display apparatus, 7 Input apparatus, 8 Notification apparatus, 11 Compressor, 12 Four-way valve, 13 Outdoor heat exchanger , 14 outdoor blower, 15a throttle means, 15b throttle means, 16 connection piping, 17a indoor heat exchanger, 17b indoor heat exchanger, 18 indoor blower, 18b indoor blower, 19 connection piping, 20 accumulator, 21 receiver, 22 throttle means , 100 Fault diagnosis device, 101 measurement unit, 102 calculation unit, 103 control unit, 104 storage unit, 105 comparison unit, 106 judgment unit, 107 notification unit, 201 compressor discharge temperature detection unit, 202 high pressure detection unit, 203 outdoor heat Exchanger liquid temperature detection means, 204a Indoor heat exchanger liquid temperature detection means, 204b Indoor heat exchanger liquid temperature detection means, 205 Low pressure detection means, 206a Indoor heat exchanger gas temperature detection means, 206b Indoor heat exchanger gas temperature detection means.

Claims (26)

  1. Low pressure detection means for detecting the pressure of the refrigerant at any position in the flow path from the throttle means to the suction side of the compressor, and the pressure of the refrigerant at any position in the flow path from the discharge side of the compressor to the throttle means High pressure detection means for detecting the refrigerant, discharge temperature detection means for detecting the temperature of the refrigerant at any position in the flow path from the compressor to the condenser, and liquid temperature detection means for detecting the temperature of the refrigerant at the outlet of the condenser, A failure diagnosis device for a refrigeration cycle device that performs failure diagnosis of a heat pump cycle based on a measurement value from each detection means,
    A calculation unit that performs a composite variable calculation using multivariate analysis by at least the low-pressure detection unit, the high-pressure detection unit, and the discharge temperature detection unit using a T method (Taguch methods) ;
    A storage unit that stores a state quantity calculated by using the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables;
    A normal state quantity storage unit for storing a state quantity of a normal operation state of the heat pump cycle;
    An abnormal state quantity storage unit for storing a state quantity of an abnormal operation state of the heat pump cycle;
    A current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, a state quantity indicating a normal operation state stored in the normal state quantity storage unit, and / or Or a comparison unit that compares a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit;
    A determination unit for determining a normal degree or an abnormality degree of the heat pump cycle, a normal / abnormal determination, or a cause of the abnormality from the state quantity or the change in the state quantity compared by the comparison unit;
    The computing unit is
    The degree of abnormality of the heat pump cycle is represented using a variable according to the measured value, the calculated value, or the state quantity of the abnormal operation state based on the same abnormality factor, and the multivariate analysis is performed. Failure diagnosis device for refrigeration cycle equipment.
  2. The suction temperature of the compressor is estimated from measurement values measured by the high pressure detection means, the low pressure detection means, and the discharge temperature detection means, and from the measurement value of the low pressure detection means and the estimated suction temperature It is estimated whether the refrigerant | coolant suck | inhaled by the said compressor is a gas refrigerant. The failure diagnosis apparatus of the refrigerating-cycle apparatus of Claim 1 characterized by the above-mentioned.
  3. The determination unit
    The failure diagnosis device for a refrigeration cycle apparatus according to claim 1 or 2, wherein normality / abnormality is determined based on whether the refrigerant sealed in the heat pump cycle is insufficient or excessive.
  4. The determination unit
    When comparing the current operation state quantity and the state quantity indicating the normal operation state or the state quantity indicating the abnormal operation state,
    The refrigerant leakage amount which is the calculated state quantity of the current operation or a calculated value corresponding thereto is compared with the preset refrigerant quantity in the heat pump cycle, the allowable refrigerant leakage quantity or the corresponding state quantity. The time to reach the limit refrigerant amount that can maintain the cooling capacity or heating capacity of the heat pump cycle is predicted from the comparison result. The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 1 to 3.
  5. High pressure detection means for detecting the pressure of the refrigerant at any position in the flow path from the discharge side of the compressor to the throttle means, and the temperature of the refrigerant at any position in the flow path from the compressor to the condenser Discharge temperature detection means and condenser inflow temperature detection means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the condenser are provided, and a failure of the heat pump cycle based on the measured value from each detection means A failure diagnosis device for a refrigeration cycle device that performs diagnosis,
    A calculation unit for performing a complex variable calculation using a multivariate analysis by a T method (Tagchi methods) on the measurement values from the high-pressure detection unit, the discharge temperature detection unit, and the condenser inflow temperature detection unit;
    A storage unit that stores a state quantity calculated by using the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables;
    A normal state quantity storage unit for storing a state quantity of a normal operation state of the heat pump cycle;
    An abnormal state quantity storage unit for storing a state quantity of an abnormal operation state of the heat pump cycle;
    A current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, a state quantity indicating a normal operation state stored in the normal state quantity storage unit, and / or Or a comparison unit that compares a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit;
    A determination unit for determining a normal degree or an abnormality degree of the heat pump cycle, a normal / abnormal determination, or a cause of the abnormality from the state quantity or the change in the state quantity compared by the comparison unit;
    The computing unit is
    The degree of abnormality of the heat pump cycle is represented using a variable according to the measured value, the calculated value, or the state quantity of the abnormal operation state based on the same abnormality factor, and the multivariate analysis is performed. Failure diagnosis device for refrigeration cycle equipment.
  6. Low pressure detecting means for detecting the pressure of the refrigerant at any position in the flow path from the throttle means to the suction side of the compressor, and detecting the temperature of the refrigerant at any position in the flow path from the compressor to the condenser Discharge temperature detection means and evaporator inflow temperature detection means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the evaporator, and a failure of the heat pump cycle based on the measured value from each detection means A failure diagnosis device for a refrigeration cycle device that performs diagnosis,
    A calculation unit for performing a composite variable calculation using a multivariate analysis based on a T method (Taguch methods) for measurement values from the low-pressure detection unit, the discharge temperature detection unit, and the evaporator inflow temperature detection unit;
    A storage unit that stores a state quantity calculated by using the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables;
    A normal state quantity storage unit for storing a state quantity of a normal operation state of the heat pump cycle;
    An abnormal state quantity storage unit for storing a state quantity of an abnormal operation state of the heat pump cycle;
    A current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, a state quantity indicating a normal operation state stored in the normal state quantity storage unit, and / or Or a comparison unit that compares a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit;
    A determination unit for determining a normal degree or an abnormality degree of the heat pump cycle, a normal / abnormal determination, or a cause of the abnormality from the state quantity or the change in the state quantity compared by the comparison unit;
    The computing unit is
    The degree of abnormality of the heat pump cycle is represented using a variable according to the measured value, the calculated value, or the state quantity of the abnormal operation state based on the same abnormality factor, and the multivariate analysis is performed. Failure diagnosis device for refrigeration cycle equipment.
  7. The determination of normality / abnormality executed by the determination unit is as follows:
    The surface of the condenser or the evaporator is soiled or damaged, the filter is clogged, the blower provided near the condenser or the evaporator is deteriorated, or malfunctioned. A failure diagnosis apparatus for a refrigeration cycle apparatus according to 5 or 6.
  8. The determination unit
    When comparing the current operation state quantity and the state quantity indicating the normal operation state or the state quantity indicating the abnormal operation state,
    The heat exchange performance of the condenser or the evaporator, which is the calculated state quantity of the current operation, or the calculated value corresponding thereto, and the allowable heat exchange performance of the condenser set in advance or the state quantity corresponding thereto. The time when the cooling capacity or the heating capacity of the heat pump cycle can be maintained is predicted from the comparison result. The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 5 to 7.
  9. The condenser inflow temperature detection means or the evaporator inflow temperature detection means,
    The fluid inflow temperature is calculated by estimating from the measured value measured by the condensation temperature detection means or the evaporation temperature detection means when the heat pump cycle is stopped. The failure diagnosis apparatus for the refrigeration cycle apparatus according to 1.
  10. Low pressure detection means for detecting the pressure of the refrigerant at any position in the flow path from the throttle means to the suction side of the compressor, and the pressure of the refrigerant at any position in the flow path from the discharge side of the compressor to the throttle means Fault diagnosis of a refrigeration cycle apparatus that is provided with a high-pressure detection means that detects the temperature of the refrigerant and a liquid temperature detection means that detects the temperature of the refrigerant at the outlet of the condenser and that performs a fault diagnosis of the heat pump cycle based on the measurement value from each detection means A device,
    An arithmetic unit for performing a composite variable operation using a multivariate analysis by a T method (Tagchi methods) for the measurement values from the low pressure detection unit, the high pressure detection unit, and the liquid temperature detection unit;
    A storage unit that stores a state quantity calculated by using the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables;
    A normal state quantity storage unit for storing a state quantity of a normal operation state of the heat pump cycle;
    An abnormal state quantity storage unit for storing a state quantity of an abnormal operation state of the heat pump cycle;
    A current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, a state quantity indicating a normal operation state stored in the normal state quantity storage unit, and / or Or a comparison unit that compares a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit;
    A determination unit for determining a normal degree or an abnormality degree of the heat pump cycle, a normal / abnormal determination, or a cause of the abnormality from the state quantity or the change in the state quantity compared by the comparison unit;
    The computing unit is
    The degree of abnormality of the heat pump cycle is represented using a variable according to the measured value, the calculated value, or the state quantity of the abnormal operation state based on the same abnormality factor, and the multivariate analysis is performed. Failure diagnosis device for refrigeration cycle equipment.
  11. The determination of normality / abnormality executed by the determination unit is as follows:
    Any one of clogging or failure of the throttling means, clogging of a strainer for removing dust etc. in the circulation of the refrigerant or a dryer for preventing moisture of the refrigerant, breakage, breakage, clogging or clogging of the pipe The failure diagnosis apparatus for a refrigeration cycle apparatus according to claim 10, wherein:
  12. When comparing the current operation state quantity and the state quantity indicating the normal operation state or the state quantity indicating the abnormal operation state,
    A comparison is made between the flow resistance of the heat pump cycle, which is the calculated state quantity of the current operation, or a calculated value corresponding thereto, and the preset flow resistance of the heat pump cycle, or a state quantity corresponding thereto. The time when the cooling capacity or the heating capacity of the heat pump cycle can be maintained is predicted from the result. The failure diagnosis apparatus for a refrigeration cycle apparatus according to claim 10 or 11, wherein:
  13. Low pressure detection means for detecting the pressure of the refrigerant at any position in the flow path from the throttle means to the suction side of the compressor, and the pressure of the refrigerant at any position in the flow path from the discharge side of the compressor to the throttle means High pressure detection means for detecting the refrigerant, discharge temperature detection means for detecting the temperature of the refrigerant at any position in the flow path from the compressor to the condenser, and liquid temperature detection means for detecting the temperature of the refrigerant at the outlet of the condenser, A condenser inflow temperature detecting means for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the condenser; and an inflow of the evaporator for measuring the inflow temperature of the fluid that exchanges heat with the refrigerant flowing inside the evaporator A fault diagnosis device for a refrigeration cycle apparatus that is provided with temperature detection means and performs fault diagnosis of a heat pump cycle based on a measurement value from each detection means,
    The measured values from the low-pressure detection means, the high-pressure detection means, the discharge temperature detection means, the liquid temperature detection means, the condenser inflow temperature detection means, and the evaporator inflow temperature detection means are measured by the T method (Tagu methods) . An arithmetic unit that performs complex variable arithmetic using variable analysis;
    A storage unit that stores a state quantity calculated by using the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables;
    A normal state quantity storage unit for storing a state quantity of a normal operation state of the heat pump cycle;
    An abnormal state quantity storage unit for storing a state quantity of an abnormal operation state of the heat pump cycle;
    A current operation state quantity that is a state quantity calculated by using the measured values obtained from the current operation state of the heat pump cycle as a plurality of variables, a state quantity indicating a normal operation state stored in the normal state quantity storage unit, and / or Or a comparison unit that compares a state quantity indicating an abnormal operation state stored in the abnormal state quantity storage unit;
    A determination unit for determining a normal degree or an abnormality degree of the heat pump cycle, a normal / abnormal determination, or a cause of the abnormality from the state quantity or the change in the state quantity compared by the comparison unit;
    The computing unit is
    According to the measured value based on the same abnormality factor, the calculated value or the state quantity of the abnormal operation state, the degree of abnormality of the heat pump cycle is represented using a variable, and the multivariate analysis is performed.
    The determination unit
    Whether the abnormality of the heat pump cycle is due to a lack of refrigerant sealed in the heat pump cycle, or due to excessive sealing of the refrigerant,
    Is it due to dirt or damage on the surface of the condenser, clogging of the filter, deterioration or failure of the condenser or the blower provided in the vicinity of the condenser,
    Due to dirt or damage on the surface of the evaporator, clogging of the filter, deterioration or failure of the blower provided in the vicinity of the evaporator or the evaporator,
    At least one of clogging or failure of the throttling means, clogging of a strainer for removing dust or the like in the circulation of the refrigerant or a dryer for preventing moisture of the refrigerant, breakage, breakage or clogging of the pipe A failure diagnosis apparatus for a refrigeration cycle apparatus, wherein the presence or absence of an abnormality is determined based on the above.
  14. An evaporation temperature obtained by converting the refrigerant pressure detected by the low-pressure detection means into a saturation temperature;
    The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 1 to 13, wherein a condensation temperature obtained by converting the refrigerant pressure detected by the high-pressure detection means into a saturation temperature is used as a measurement value.
  15. A receiver for controlling the opening degree of the throttle means and the low stage side throttle means, a receiver between the condenser and the throttle means, a low stage side throttle means between the condenser and the receiver, respectively. Provided,
    When determining the abnormality of the heat pump cycle in the determination unit,
    The controller is
    By controlling the opening area of the throttling means to be smaller than the opening area of the lower stage throttling means, the outlet refrigerant of the receiver is in a two-phase state, and the excess refrigerant in the receiver is condensed. The special operation mode to move in a container is performed. The failure diagnosis apparatus of the refrigerating-cycle apparatus in any one of Claims 1-14 characterized by the above-mentioned.
  16. An accumulator is provided between the evaporator and the compressor, and a control unit for controlling the opening of the throttle means is provided.
    When determining the abnormality of the heat pump cycle in the determination unit,
    The controller is
    A special operation mode is executed in which the refrigerant flowing into the accumulator is made into a gas refrigerant, and the opening degree of the throttle means is controlled so as to move the surplus refrigerant in the accumulator into the condenser. The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 14 to 14.
  17. Fluid delivery means for supplying a fluid to be heat exchanged with the refrigerant of the condenser or the evaporator to the condenser or the evaporator;
    When determining the abnormality of the heat pump cycle in the determination unit,
    The controller is
    The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 1 to 16, wherein a special operation mode for setting a delivery amount of the fluid delivery means to a predetermined value is executed.
  18. The controller is
    The failure diagnosis apparatus for a refrigeration cycle apparatus according to claim 16 or 17, wherein the special operation mode is periodically executed.
  19. The controller is
    The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 16 to 18, wherein the special operation mode is executed based on an instruction from the outside.
  20. A device specification information storage unit that stores product specifications or control information of each device of the heat pump cycle,
    The determination unit
    The heat pump cycle by changing or correcting the measured value stored in the storage unit, the calculated value, or the state quantity calculated using the measured value and the calculated value as a plurality of variables according to the device specification information The fault diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 1 to 19, wherein the normality degree or the degree of abnormality, the normality / abnormality determination, or the cause of the abnormality is determined.
  21. When the determination unit determines that the heat pump cycle is operating normally,
    The failure diagnosis of the refrigeration cycle apparatus according to any one of claims 1 to 20, wherein a state quantity obtained by calculating the measured value, the calculated value, or the measured value and the calculated value as a plurality of variables is learned. apparatus.
  22. The determination unit
    Normal operation is performed by forcibly converting at least one of the measured value or the calculated value obtained from the measured value into another value and calculating from a plurality of variables including the converted value. The threshold value which distinguishes a state and an abnormal driving | running state is set. The failure diagnosis apparatus of the refrigerating-cycle apparatus in any one of Claims 1-21 characterized by the above-mentioned.
  23. The determination unit
    Combining as a plurality of variables, calculating an associated set, determining the degree of normality or abnormality of the heat pump cycle based on the calculated value, determining normality / abnormality or the cause of the abnormality, and the heat pump cycle The failure diagnosis device for a refrigeration cycle apparatus according to any one of claims 1 to 22, wherein a limit time when the stable operation cannot be continued is predicted.
  24. Providing communication means for communicating data information;
    The failure diagnosis apparatus for a refrigeration cycle apparatus according to any one of claims 1 to 23, wherein remote monitoring is possible via the communication means.
  25. The estimated time that each device is expected to fail is estimated from the calculated value measured and calculated during normal operation and the elapsed operation time of the heat pump cycle with respect to the calculated value measured and calculated from the current operating state. The information is transmitted to the outside via the communication means. The failure diagnosis apparatus for a refrigeration cycle apparatus according to claim 24, wherein:
  26. A compressor, a condenser, a throttle means, and an evaporator are sequentially connected by a refrigerant pipe, and a heat pump cycle is provided.
    A refrigeration cycle apparatus comprising the refrigeration cycle apparatus failure diagnosis apparatus according to any one of claims 1 to 25.
JP2007090398A 2007-03-30 2007-03-30 Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same Active JP4749369B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007090398A JP4749369B2 (en) 2007-03-30 2007-03-30 Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007090398A JP4749369B2 (en) 2007-03-30 2007-03-30 Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same

Publications (2)

Publication Number Publication Date
JP2008249234A JP2008249234A (en) 2008-10-16
JP4749369B2 true JP4749369B2 (en) 2011-08-17

Family

ID=39974391

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007090398A Active JP4749369B2 (en) 2007-03-30 2007-03-30 Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same

Country Status (1)

Country Link
JP (1) JP4749369B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101595437B1 (en) * 2013-08-19 2016-02-26 스미도모쥬기가이고교 가부시키가이샤 Cooling system and method for monitoring cooling system

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010127568A (en) * 2008-11-28 2010-06-10 Mitsubishi Electric Corp Abnormality detection device and refrigerating cycle device including the same
JP5289109B2 (en) * 2009-03-09 2013-09-11 三菱電機株式会社 Air conditioner
JP4958936B2 (en) 2009-04-13 2012-06-20 三菱電機株式会社 Air conditioning system diagnostic device
JP5036790B2 (en) * 2009-11-16 2012-09-26 三菱電機株式会社 Air conditioner
JP5102320B2 (en) * 2010-02-04 2012-12-19 株式会社トーエネック Abnormality detection device for total heat exchanger and peripheral equipment in air conditioning system
JPWO2011099058A1 (en) * 2010-02-10 2013-06-13 三菱電機株式会社 Air conditioner
JP2011191023A (en) * 2010-03-16 2011-09-29 Panasonic Corp Air conditioner
JP5147889B2 (en) * 2010-04-12 2013-02-20 三菱電機株式会社 Air conditioner
JP5351097B2 (en) * 2010-06-18 2013-11-27 株式会社日立製作所 Refrigerant circulation device
US9739513B2 (en) 2010-06-23 2017-08-22 Mitsubishi Electric Corporation Air conditioning apparatus
JP5676966B2 (en) * 2010-08-10 2015-02-25 株式会社日立製作所 Cooling system
JP5525965B2 (en) * 2010-08-25 2014-06-18 日立アプライアンス株式会社 Refrigeration cycle equipment
US9541319B2 (en) 2011-01-20 2017-01-10 Mitsubishi Electric Corporation Air-conditioning apparatus
WO2012101673A1 (en) * 2011-01-26 2012-08-02 三菱電機株式会社 Air conditioner device
JP5642227B2 (en) * 2013-04-25 2014-12-17 三菱電機株式会社 Air conditioner and air conditioner monitoring system
JP5505540B2 (en) * 2013-04-30 2014-05-28 ダイキン工業株式会社 Air conditioner
WO2015046066A1 (en) * 2013-09-27 2015-04-02 東芝キヤリア株式会社 Freeze cycling device
JP6290687B2 (en) * 2014-03-31 2018-03-07 株式会社Nttファシリティーズ Air Conditioning System
JP6387276B2 (en) * 2014-09-24 2018-09-05 東芝キヤリア株式会社 Refrigeration cycle equipment
JP6362992B2 (en) 2014-10-20 2018-07-25 三菱日立パワーシステムズ株式会社 Heat exchanger monitoring device and heat exchanger monitoring method
JP2016084969A (en) * 2014-10-24 2016-05-19 三菱重工業株式会社 Control device of air conditioning system, air conditioning system, and abnormality determination method of air conditioning system
WO2016129027A1 (en) * 2015-02-09 2016-08-18 三菱電機株式会社 Air conditioning device
WO2017163294A1 (en) * 2016-03-22 2017-09-28 三菱電機株式会社 Refrigerant shortage prediction apparatus, refrigerant shortage prediction method, and program
WO2017212606A1 (en) * 2016-06-09 2017-12-14 三菱電機株式会社 Refrigeration cycle apparatus
CN107490129A (en) * 2017-08-02 2017-12-19 青岛海尔空调电子有限公司 A kind of method and device of equipment control
WO2019082331A1 (en) * 2017-10-26 2019-05-02 三菱電機株式会社 Refrigeration air-conditioning device and control device
WO2019146035A1 (en) * 2018-01-25 2019-08-01 三菱電機株式会社 State analysis system and state analysis device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2997487B2 (en) * 1989-12-13 2000-01-11 株式会社日立製作所 Refrigerant quantity display method in the refrigeration apparatus and refrigeration systems
JPH09113077A (en) * 1995-10-16 1997-05-02 Matsushita Refrig Co Ltd Air conditioner
JP4396286B2 (en) * 2004-01-21 2010-01-13 三菱電機株式会社 Device diagnostic device and device monitoring system
WO2006090451A1 (en) * 2005-02-24 2006-08-31 Mitsubishi Denki Kabushiki Kaisha Air conditioning system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101595437B1 (en) * 2013-08-19 2016-02-26 스미도모쥬기가이고교 가부시키가이샤 Cooling system and method for monitoring cooling system
US10047977B2 (en) 2013-08-19 2018-08-14 Sumitomo Heavy Industries, Ltd. Monitoring method and cooling system

Also Published As

Publication number Publication date
JP2008249234A (en) 2008-10-16

Similar Documents

Publication Publication Date Title
US9424519B1 (en) Cost-effective remote monitoring, diagnostic and system health prediction system and method for vapor compression and heat pump units based on compressor discharge line temperature sampling
US10352602B2 (en) Portable method and apparatus for monitoring refrigerant-cycle systems
US10558229B2 (en) Method and apparatus for monitoring refrigeration-cycle systems
US10113763B2 (en) Refrigeration cycle apparatus
US7494536B2 (en) Method for detecting a fault in an HVAC system
TWI302978B (en) System and method for detecting decreased performance in a refrigeration system
EP1852664B1 (en) Air conditioning system
JP6091506B2 (en) Refrigeration air conditioner, refrigerant leak detection device, and refrigerant leak detection method
JP5196452B2 (en) Transcritical refrigerant vapor compression system with charge control
JP5247833B2 (en) Air conditioner
EP1876403B1 (en) Air conditioner coolant amount judgment system
JP4486133B2 (en) Cooling device for communication device and cooling control method thereof
EP1497597B1 (en) Method for detecting changes in a first flux of a heat or cold transport medium in a refrigeration system
ES2704830T3 (en) Air conditioner
EP1706684B1 (en) Diagnosing a loss of refrigerant charge in a refrigerant system
Breuker et al. Common faults and their impacts for rooftop air conditioners
CN1120970C (en) Refrigerating system, heat pump system and detecting method for leakage of refrigerating agent of said system
US9803902B2 (en) System for refrigerant charge verification using two condenser coil temperatures
US6658373B2 (en) Apparatus and method for detecting faults and providing diagnostics in vapor compression cycle equipment
US20150219370A1 (en) Heat pump apparatus
AU2006324541B2 (en) Air conditioner
JP4975052B2 (en) Refrigeration cycle equipment
US6868678B2 (en) Non-intrusive refrigerant charge indicator
Li et al. Decoupling features and virtual sensors for diagnosis of faults in vapor compression air conditioners
CN103154625B (en) Freezing cycle device

Legal Events

Date Code Title Description
A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20091228

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100601

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100716

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20101116

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20101222

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20110510

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20110517

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140527

Year of fee payment: 3

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250