EP3348939B1 - Refrigeration cycle device - Google Patents

Refrigeration cycle device Download PDF

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Publication number
EP3348939B1
EP3348939B1 EP16843748.1A EP16843748A EP3348939B1 EP 3348939 B1 EP3348939 B1 EP 3348939B1 EP 16843748 A EP16843748 A EP 16843748A EP 3348939 B1 EP3348939 B1 EP 3348939B1
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EP
European Patent Office
Prior art keywords
refrigerant
subcooling
subcooling degree
degree
economizer
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EP16843748.1A
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German (de)
English (en)
French (fr)
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EP3348939A1 (en
EP3348939A4 (en
Inventor
Atsuhiko Yokozeki
Hiroaki Tsuboe
Masaki Uno
Hideyuki Ueda
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Johnson Controls Air Conditioning Inc
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/32—Responding to malfunctions or emergencies
    • F24F11/36—Responding to malfunctions or emergencies to leakage of heat-exchange fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/52—Indication arrangements, e.g. displays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/05—Cost reduction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/24—Low amount of refrigerant in the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the present invention relates to a technology of a refrigeration cycle device.
  • Patent Document 1 discloses, in claims, an air conditioning device (1) which includes a heat source unit (2) having a compressor (21), a heat source-side heat exchanger (23) and a cooling heat source adjusting means (27) capable of adjusting a cooling function of the a cooling heat source for the heat source-side heat exchanger (23), a utilizing unit (4) having a utilization-side heat exchanger (41), an expansion mechanism (33), a refrigerant circuit (10) capable of performing at least a cooling operation for functioning the utilization-side heat exchanger as a condenser for the refrigerant compressed by the compressor and as an evaporator for the refrigerant condensed by the compressor, a mode switching means for switch the utilization-side heat exchanger to a refrigerant quantity determining operation mode to make a degree of superheat of the refrigerant at an outlet of the utilization-side heat exchanger from a normal operation mode for controlling respective devices in the utilizing unit, a detecting means for detecting a subcooling degree of the refriger
  • Patent Document 2 discloses a leakage estimation for a refrigeration system based on the sub-cooling degree downstream from the condenser/sub-cooling unit, based on a threshold evaluation in terms of controller 40, determining the limit value of " ⁇ SC" at which the refrigerant amount is still regarded as normal, see paragraphs [0093-0094].
  • Patent Document 2 also shows a liquid injection valve 22 which is an on/off-valve and which injects into the compressor suction line upstream from the feed reservoir.
  • Patent Document 2 represents the closest prior art to the present invention.
  • the air conditioning device In the air conditioning device disclosed in the PATENT DOCUMENT 1, at first, shifts to a refrigerant determination operation mode for controlling a refrigerant superheating degree at an outlet of the evaporator in cooling operation to have a positive value. Next, the air conditioning device detects the refrigerant subcooling degree at the outlet of the condenser and derives a relative subcooling degree obtained by dividing the degree of subcooling by a value obtained by subtracting outdoor temperature from condensation temperature as a subcooling degree correction value. After that, the air conditioning device performs the refrigerant quantity propriety and impropriety in the refrigerant circuit on the basis of the subcooling degree correction value (relative supercharging value).
  • the air conditioning device according to PATENT DOCUMENT 1, a refrigerant quantity propriety and impropriety determination at a high accuracy without influence of external disturbance such as an outdoor temperature, and external disturbance such as an outdoor temperature, soil of the outdoor heat exchanger.
  • PATENT DOCUMENT 1 disclosed it is possible to increase the determination accuracy by using the subcooling degree corrected by the outdoor temperature and a condensing temperature.
  • the determination accuracy is insufficient for responding to an operation state of the refrigerator, etc. in which the operation condition in the refrigerating cycle has a wider range(extremely varies).
  • the liquid injection valve is arranged to control a liquid level in the compressor feed reservoir, deviating from the configuration of the present invention. With the arrangement of PATENT DOCUMENT 2, no detailed consideration of the opening degree of the liquid injection valve is possible or for leakage estimation.
  • the present invention is developed in consideration of the background describe above and has a problem in that the refrigerant quantity is determined at a high accuracy.
  • the present invention proposes to solve the above problems by a configuration as defined in appended independent claim 1.
  • Fig. 1 is a drawing showing a configuration example of an air conditioning device according to a first embodiment.
  • the airconditioning device 1 is configured including an outdoor unit 10, an indoor unit 20, a controller 100, and a display device 200.
  • the display device 200 can be omitted.
  • the outdoor unit 10 is configured including an outdoor heat exchanger 11 operating as condenser, a receiver (excess refrigerant storage) 13, a subcooling device 16, an outdoor fan 12, a liquid injection valve 17, a compressor 14, an accumulator 15, the gas stop valve 18a, and a liquid stop valve 18b.
  • the indoor unit 20 is configured including an indoor heat exchanger 21 operating as an evaporator, an indoor fan 22, and an indoor expansion valve (decompressor) 23.
  • the outdoor unit 10 and the indoor unit 20 are connected with pipes 30 and 31 through which refrigerant flow.
  • the outdoor unit 10 is connected to the pipe 31 through a gas stop valve 18a and the pipe 30 through a liquid stop valve 18b.
  • the airconditioning device 1 makes a refrigerating cycle with a compressor 14, the outdoor heat exchanger 11, the receiver 13, the subcooling device 16, a liquid injection valve 17, the indoor heat exchanger 21, and the expansion valve 23.
  • the controller 100 controls the outdoor unit 10 by starting and stopping the outdoor fan 12 in the outdoor unit 10, adjusting an open degree of the liquid injection valve 17, adjusting a rotation speed Fr of the compressor 14 in the outdoor unit 10. Further, the controller 100 controls the indoor unit 20 by, in the indoor unit 20, starting and stopping the indoor fan 22, adjusting an open degree of the expansion valve 23, etc. Further, control lines for these controls are omitted in Fig. 1 .
  • the refrigerant (gas, gaseous state) compressed by the compressor 14 flows into the outdoor heat exchanger 11 as a condenser where the refrigerant is condensed as a result of cooing by heat exchange with the outdoor air blown by the outdoor fan 12.
  • the refrigerant (liquid) condensed by the outdoor heat exchanger 11 passes through the receiver 13 while an excess refrigerant is stored in the receiver 13 and subcooled by the subcooling device 16, and then introduced into the indoor unit 20 flowing through the pipe 30.
  • a part of the refrigerant after passing through the subcooling device 16 (first passage) is adjusted by the liquid injection valve 17 to have a predetermined flow rate and injected to an intermediate section of the compressing chamber of the compressor 14. This controls a discharging temperature Td of the compressor 14 to an appropriate value.
  • the refrigerant (gas and liquid two phase state or liquid) flowing into the indoor heat exchanger 21 vaporizes (evaporates) by heat exchange with indoor air blown by the indoor fan 22. During this, the refrigerant (liquid) which is evaporated in the indoor heat exchanger 21 removes heat of evaporation from the indoor air, which cools the indoor air.
  • the refrigerant (gas, gaseous state) which is evaporated in the indoor heat exchanger 21 is introduced into the outdoor unit 10, flowing through the pipe 31 and flows into an accumulator 15.
  • the accumulator 15 functions as a buffer tank for storing the refrigerant (liquid) when the liquid refrigerant transiently excessively flowing thereinto, which prevents the compressor 14 from compressing the liquid. Accordingly the accumulator 15 adjusts dryness of the refrigerant, so that the refrigerant having an appropriate dryness flows into the compressor 14, which prevents liquid-compression, etc, so that reliability is secured.
  • the outdoor unit 10 includes a discharging temperature sensor 10ta for measuring a temperature (discharging temperature Td) of the refrigerant discharged by the compressor 14, the discharging pressure sensor 10pa for measuring a pressure (discharging pressure Pd) of the refrigerant on an outlet side of the compressor 14 and an inlet pressure sensor 10pb for measuring a pressure (an inlet pressure Ps) of the refrigerant on an inlet side of the compressor 14.
  • the outdoor unit 10 includes a temperature sensor 10tb for measuring a condensation temperature Tc of the refrigerant at the outdoor heat exchanger 11 and a temperature sensor 10tc for measuring an outlet temperature Tsc of the subcooling device 16. Further, the outdoor unit 10 includes a temperature sensor 10td for measuring a outlet temperature Ts of the gas stop valve 18a (an inlet temperature of the accumulator 15). Further, the outdoor unit 10 includes a temperature sensor 10te for measuring a temperature of the refrigerant at an outlet of a condenser (the outdoor heat exchanger 11) and an outdoor air temperature sensor 10tf for measuring an outdoor temperature. Further, the outdoor unit 10 includes a temperature sensor 10tg installed to the pipe at the gas and liquid two phase state part of the outdoor heat exchanger 11 for measuring a temperature at a gas and liquid two phase state part.
  • the indoor unit 20 includes a temperature sensor 20ta for measuring an evaporation temperature Te of the refrigerant at the indoor heat exchanger 21. Further, the indoor unit 20 includes a temperature sensor 20tb for measuring an inlet temperature of the indoor heat exchanger 21 and a temperature sensor 20tc for measuring an outlet temperature of the indoor heat exchanger 21.
  • the controller 100 calculates a subcooling degree at an outlet of the subcooling device 16 and determines a quantity of the refrigerant in the refrigerating cycle by comparing the subcooling degree with a determination threshold calculated by a method which will be described later on the basis of the information acquired from various sensors, i.e., the discharging temperature sensor 10ta, the temperature sensor 10tb, the temperature sensor 10tc,the temperature sensor 10td, the temperature sensor 10te,the outdoor air temperature sensor 10tf,the temperature sensor 10tg, a temperature sensor 10pa,the inlet pressure sensor 10pb, a temperature sensor temperature sensor 20ta,a temperature sensor 20tb, and the temperature sensor 20tc, the liquid injection valve 17, the indoor expansion valve 23, etc.
  • the determination of the quantity of the refrigerant will be described later.
  • the controller 100 displays the determination result of the quantity of the refrigerant on the display device 200, etc.
  • Fig. 2 is a block diagram of a configuration example of the controller according to the first embodiment.
  • the controller 100 includes a memory 110, a CPU (Central Processing Unit) 120, a storing device 130 such as a HD (Hard Disk), and a communication device 140.
  • a memory 110 a central processing Unit 120
  • a storing device 130 such as a HD (Hard Disk)
  • a communication device 140 a communication device 140.
  • a program is loaded in the memory 110 and executed by the CPU 120, so that a processing section 111, an operation information acquiring section 112, an operation state determining section 113, a subcooling degree calculating section 114 (an appropriate subcooling degree estimation section, determination threshold calculating section), a refrigerant quantity determination section (determining process section) 115, and the an outputting section 116 are embodied.
  • the operation information acquiring section 112 acquires information from the discharging temperature sensor 10ta, the temperature sensor 10tb, the temperature sensor 10tc, the temperature sensor 10td, the temperature sensor 10te, the outdoor air temperature sensor 10tf, the temperature sensor 10tg, a temperature sensor 10pa, the inlet pressure sensor 10pb, a temperature sensor temperature sensor 20ta, a temperature sensor 20tb, and the temperature sensor 20tc,etc.in Fig. 1 and information of the open degrees of the liquid injection valve 17 and the indoor expansion valve 23.
  • the operation state determining section 113 determines whether a state of the airconditioning device 1 is in a state suitable for a refrigerant leakage state or not.
  • the subcooling degree calculating section 114 calculates a determination threshold described later and an actual measurement subcooling degree at an outlet of the subcooling device 16.
  • the refrigerant quantity determination section 115 determines whether the quantity of the refrigerant is appropriate on the basis of the determination threshold calculated by the subcooling degree calculating section 114 and the actual measurement subcooling degree.
  • the outputting section 116 outputs information indicating that the quantity of the refrigerant is improper when the quantity of the refrigerant is improper (erroneous) on the basis of the refrigerant quantity determination section 115.
  • Fig. 3 is a Mollier chart (P-h chart) of the air conditioning device according to the first embodiment. Occasionally, Fig. 1 is referred.
  • the refrigerant (gas, or a gaseous state) in a state 301 is compressed by the compressor 14, so that a temperature (specific enthalpy) and a pressure of the refrigerant increase and the state shifts to a state 302 at an intermediate pressure point of the compressor 14.
  • the refrigerant in a state 307 having a low specific enthalpy is injected from the liquid injection valve 17, so that the refrigerant shifts to a state 303.
  • the refrigerant is brought into a state 304 because the refrigerant in the state 303 is compressed by the compressor 14 to a high pressure Pd.
  • the refrigerant is introduced into the outdoor heat exchanger 11 operating as a condenser during a cooling operation, so that the refrigerant is cooled by the outdoor air blown by the outdoor fan 12 and condensed and the state shift to a state 305 (liquid) and the liquid is introduced into the receiver 13. Since the receiver 13 is kept in a saturated state because there is a liquid level in the receiver 13, the refrigerant is discharged from a bottom part thereof and introduced into the subcooling device 16 and brought into a state 306 which is a subcooled state by the outdoor air blown by the outdoor fan 12.
  • a part (broken line) of the refrigerant in the state 306 is decompressed to the state 307 by the liquid injection valve 17. Only a predetermined quantity of the refrigerant in the state 307 is injected to the intermediate pressure of the compressor 14 becoming the state 303 to perform the control of the discharging temperature Td.
  • a liquid refrigerant is sent through the pipe 30 to the indoor unit 20 where the liquid refrigerant is decompressed by the indoor expansion valve 23.
  • the refrigerant becomes in the state indicated by a point 308, i.e., in the gas and liquid two phase state at a low temperature and is introduced into the indoor heat exchanger 21.
  • heat exchange is performed between the refrigerant and the room air blown by the indoor fan 22, so that the refrigerant evaporates and becomes a gaseous refrigerant, which provides a cooling function for the room air.
  • the gaseous refrigerant evaporating in the indoor heat exchanger 21 is brought into the state 301 and returned to the outdoor unit 10 through the pipe 31 on a gaseous side where the refrigerant is returned to the compressor 14 through the accumulator 15, which forms a sequential refrigerating cycle.
  • the receiver 13 when the receiver 13 is in an excess state of the refrigerant, the receiver 13 is fully filled with subcooled refrigerant therein, and a state of an outlet of the outdoor heat exchanger 11 as a condenser, located upstream from the receiver 13, shifts to a subcooled state. In this state, the inside of the outdoor heat exchanger 11 is filled with the liquid refrigerant, so that a condensation pressure increases by a subcooled degree.
  • the liquid level decreases in the receiver 13 down to a lower end.
  • the outlet of the condenser is brought into the gas and liquid two phase state, so that the point indicated with a state 305 in Fig. 3 is inside the saturated line, and the specific enthalpy increases.
  • a difference in the specific enthalpies in the evaporator is made smaller (the state 308 to the state 301), which results in decrease in the cooling performance and the performance coefficient.
  • the quantity of the refrigerant when the quantity of the refrigerant is appropriate because the receiver 13 is in a state that there is a liquid level in the receiver 13, this contributes to a high efficient cooling operation. Further, in other words, if it is possible to determine whether the refrigerant in the receiver 13 changes to an under quantity side from progress of operation, it becomes possible to determine whether the refrigerant leaks. This contributes to prevention of global warming due to the leakage of the refrigerant and fire accidents due to a slightly flammable refrigerant. This provides a useful function.
  • a quantity of the refrigerant in the entire refrigeration cycle is called a refrigerant quantity and a quantity of the refrigerant flowing per a unit interval is called a refrigerant circulation quantity (mass flow rate).
  • Fig. 4 is a characteristic diagram showing a refrigerant circulation quantity Gr and subcooling degrees at respective parts.
  • a refrigerant circulation quantity Gr in Fig. 4 indicates a refrigerant circulating from a discharging side of the compressor 14, via the outdoor heat exchanger 11, the receiver 13, and the subcooling device 16.
  • a point indicated with “ ⁇ " represents a subcooling degree (the state 304 in Fig. 3 ) at an outlet of the condenser (the outdoor heat exchanger 11); a point indicated with " ⁇ ” is a subcooling degree (the state 306 in Fig. 3 ) at the outlet of the subcooling device 16.
  • “ ⁇ " in Fig. 4 will be described later.
  • the points shown in Fig. 4 indicate the state in which there is a liquid level in the receiver 13, i.e., the operation state at an appropriate refrigerant quantity, i.e., various states in which operation state such as the evaporation temperature Te, the outdoor air temperature, an outdoor fan rotation speed, a compressor rotation speed, etc vary. More specifically, in the state that there is an excess refrigerant in the receiver 13, various states are shown in ranges of the evaporation temperature Te from -40 to 0°C, the compressor rotation speed from 40 to 85 rps, the outdoor air temperature from 16 to 36°C, and the outdoor fan rotation speed from 60 to 100%.
  • the subcooling degree (" ⁇ ") at the outlet of the condenser has a small value not greater than 2 [K]
  • an accuracy of the detecting means is considered to be insufficient.
  • the subcooling degree is calculated from a difference between an outlet temperature of the condenser (outdoor heat exchanger 11) and the condensation temperature Tc. Accordingly, detection errors of two sensors, i.e., the temperature sensor 10te for measuring an outlet temperature of the condenser and the temperature sensor 10tb for measuring the condensation temperature Tc are added, so that it is difficult to determine whether the refrigerant is excessive and insufficient at a temperature not greater than 2 [K].
  • the subcooling degree of " ⁇ " at the outlet of the subcooling device 16 indicates a subcooling degree of downstream of the receiver 13, where the refrigerant passes there while the subcooling degree is in a substantially saturation state. Accordingly, this indicates the subcooling degree having values from 5 to 10 [K], and the inventor found that the values are usable and appropriate for determining whether the quantity of the refrigerant is excessive or insufficient though there may be a detection error in the temperature sensor 10tc.
  • A1 and A2 are values acquired from the line 401 in Fig. 4 . More specifically, A1 and A2 are values acquired as a result of fitting the subcooling degree at the outlet of the subcooling device 16 with respect to the refrigerant circulation quantity. Particularly, A2 is an appropriate subcooling degree when the refrigerant circulation quantity is a rated circulation quantity. Gr is a refrigerant circulation quantity.
  • the values of A1 and A2 are variable in accordance with simulation conditions. However, it is desirable that A1 have a value in a range from 5 to 7.
  • A3 0.6 is an example, and the value of A3 is not limited to 0.6 as long as the value of A3 is suitable value for refrigerant leakage determination.
  • Grp a 1 ⁇ Fr + a 2 b 1 ⁇ Ps + b 2 c 1 ⁇ MV + c 2
  • Grp represents an estimated value [kg/h] of the refrigerant circulation quantity
  • Fr represents compressor rotation speed [rps]
  • Ps represents an inlet pressure Ps [MPa] of the compressor 14
  • MV is an opening degree of the liquid injection valve 17.
  • a1, a2, b1, b2, c1, c2 are coefficients respectively acquired by experiments, simulation, etc.
  • Fig. 5 is a graphic chart showing a relation between an estimated value of the refrigerant circulation quantity acquired by Eq. (3) and measurement values of the refrigerant circulation quantity.
  • an axis of abscissa represents the measured refrigerant circulation quantity Gr and an axis of ordinates represents the refrigerant circulation quantity estimation value Grp of the estimated values.
  • a solid line 501 is a line representing that the measured refrigerant circulation quantity Gr agrees with a estimated refrigerant circulation quantity value Grp.
  • a broken line 502 is a line representing that the estimated refrigerant circulation quantity value Grp has a deviation of +5% to the measured refrigerant circulation quantity Gr.
  • a broken line 503 is a line representing that the estimated refrigerant circulation quantity value Grp has a deviation of -5% to the measured refrigerant circulation quantity Gr.
  • plotted points " ⁇ " are made by plotting the estimated refrigerant circulation quantity values Grp calculated using Eq. (2) in the condition when the measured refrigerant circulation quantities Gr are acquired.
  • the estimated refrigerant circulation quantity values Grp (an axis of ordinates) have accuracy not greater than ⁇ 5% with respect to the measured refrigerant circulation quantities Gr (axis of abscissa). Accordingly, it can be considered that the subcooling degree at the outlet of the subcooling device 16 calculated by substituting the estimated refrigerant circulation quantity value Grp estimated using Eq. (3) for the refrigerant circulation quantity Gr in Eq. (1), is substantially accurate. Accordingly, it is supposed that the determination threshold calculated in accordance with Eq. (2) using the estimated refrigerant circulation quantity value Grp of the refrigerant circulation quantity is likely useful.
  • Fig. 6 is a flow chart showing a flow of refrigerant leakage determination process according to the first embodiment. Occasionally, Figs. 1 and 2 are referred.
  • the process shown in Fig. 6 can be performed in a general operation without transition to a special mode such as a refrigerant determination mode in which the subcooling degree is increased for determination, etc.
  • the operation information acquiring section 112 acquires information (regarding operation states) of respective components in the air conditioning device 1 (operation state information)(S101).
  • the operation state information includes information outputted by the various types of sensors (10ta, 10tb, 10tc, 10td, 10te, 10tf, 10tg, 10pa, 10pb, 20ta, 20tb, 20tc, etc., an opening degree information of a valve acquired from the liquid injection valve 17 and the indoor expansion valve 23, the compressor rotation speed Fr, etc. acquired from the compressor 14.
  • the operation state determining section 113 determines whether it is in such a state that the refrigerant leakage determination is possible on the basis of the operation state information (S102).
  • the inlet pressure Ps acquired from the inlet pressure sensor 10pb is appropriate or not, whether an inlet superheat degree SH in the compressor 14 acquired from the outlet temperature Ts of the gas stop valve 18a measured by the temperature sensor 10td is appropriate or not (for example, the suction superheat degree SH is not smaller than 5K and the outlet temperature Ts of the gas stop valve 18a measured by the temperature sensor 10td is not greater than 20°C), whether the outdoor temperature measured by the outdoor air temperature sensor 10tf is appropriate or not (for example, the outdoor temperature is 0 to 35°C), whether a compressor rotation speed Fr is appropriate or not (for example, not smaller than 50% of the rated rotation speed), etc.
  • the operation state determining section 113 determines in a step S102 whether a value related to the operation state is in a state capable of determining the refrigerant state. Further, an inlet temperature of the compressor 14 can be used in place of the outlet temperature Ts of the gas stop valve 18a.
  • the operation state determining section 113 can determine that the determination of the refrigerant leakage when the refrigerant circulation quantity Gr (or the estimated value Grp of the refrigerant circulation quantity) is within a predetermined range (for example, between 150kg/h to 550kg/h). This prevents performing determination of the refrigerant leakage when the operation state is extremely different from the general operation condition.
  • the processing section 111 returns the processing to a step S101.
  • the operation state determining section 113 determines whether a predetermined period has elapsed (for example, about fifteen minutes) (a step S103).
  • the determination is made based on the operation state information whether the refrigerant leakage determination is possible every hour.
  • the operation state determining section 113 stores information regarding the operation state of the airconditioning device 1 for a predetermined period and determines whether the refrigerant leakage determination is possible on the basis of the stored information regarding the operation state.
  • the processing section 111 returns the processing to the step S101.
  • the subcooling degree calculating section 114 calculates the determination threshold Sclth using Eqs. (1) to (3) (S111).
  • the subcooling degree calculating section 114 calculates a measured subcooling degree Sc1 at the outlet of the subcooling device 16 (S112).
  • the subcooling degree calculating section 114 calculates the condensation temperature Tc from the discharging pressure Pd detected by the discharging pressure sensor 10pa on the basis of the characteristic information of the refrigerant physical property previously stored in the storing device 130.
  • the subcooling degree calculating section 114 calculates the measured subcooling degree Sc1 at the outlet of the subcooling device 16 by Eq. (4) providing a difference between the outlet temperature Tsc of the subcooling device 16 acquired by the temperature sensor 10tc installed at the outlet of the subcooling device 16 and the condensation temperature Tc.
  • Sc 1 Tc ⁇ Tsc
  • a pipe temperature at a gas and liquid two phase state portion of the outdoor heat exchanger 11 is measured by the temperature sensor 10tg or the temperature sensor 10te at the outlet of the condenser at the condenser (the outdoor heat exchanger 11), and the temperature is usable as the condensation temperature Tc to calculate the measured subcooling degree Sc1 at the outlet of the subcooling device 16 similarly.
  • the temperature measured by the temperature sensor 10te at the outlet of the condenser (the outdoor heat exchanger 11)
  • the temperature on a side of boiling point can be measured correctly, though composition changes occurs in the refrigerant. Accordingly, the subcooling degree at the subcooling device 16 can be accurately calculated.
  • the refrigerant quantity determining section 115 determines whether the refrigerant leakage (a quantity of the refrigerant is insufficient) occurs by determining whether the measured subcooling degree Sc1 at the outlet of the subcooling device 16 calculated in a step S112 is equal to or smaller than the determination threshold Sclth or not (S113).
  • the processing section returns the processing to the step S101.
  • the refrigerant quantity determining section 115 determines whether a predetermined period has elapsed (S114). In other words, the refrigerant quantity determining section 115 determines whether a state in which the measured subcooling degree Sc1 is smaller than the Sclth continues for a long time or not.
  • step S114 when the predetermined period has not elapsed (NO in S114), the processing section 111 returns the processing to the step S112. Further, when the predetermined period has not elapsed, the processing section 111 can return the processing also to the step S111.
  • the refrigerant quantity determining section 115 determines that the refrigerant leakage occurs (the quantity of the refrigerant is insufficient) (S121). As described above, determination that the leakage occurs (the refrigerant quantity is insufficient) is made after the predetermined period has elapsed in the state in which the measured subcooling degree Sc1 at the outlet of the subcooling device 16 is smaller than the determination threshold Sc1th. This prevents determination made in response to detection of temporary noise, etc.
  • the outputting section 116 sends a refrigerant leakage determination flag to the display device 200, an alarming device, a concentrated monitoring device (not shown), etc. (S122).
  • the display device 200 makes an alarming indication such as "Refrigerant leakage may occur", etc.
  • the above-description is for the control method of determining whether refrigerant leakage occurs.
  • a countermeasure changes and depends on the kind or use of the airconditioning device 1.
  • a cooling subject of the airconditioning device 1 is a food, a drink, or the like, decrease in quality due to stop of operation becomes a problem.
  • the operation of the airconditioning device 1 is not immediately stopped, but makes an emergency communication with a service center, etc. (not shown) to prompt to send a service man to that place. This provides a quick countermeasure.
  • the controller 100 stops the operation of the airconditioning device 1 and ensure safety with the highest priority such as making an alarm for the surrounding, shutting off shut-off valves, and driving a ventilation device.
  • the controller 100 prevents the refrigerant from leaking to a room by shutting off the indoor expansion valve 23, the gas stop valve 18a, the liquid stop valve 18b, etc. in addition to stopping the operation of the airconditioning device 1.
  • an appropriate subcooling degree Sc1s is calculated using Eq. (1).
  • the embodiments are not limited to this, and it is possible to hold as a map a relation between the refrigerant circulation quantity in Fig. 5 and the subcooling degree of the refrigerant at the outlet of the subcooling device 16 and calculate the appropriate subcooling degree Sc1s on the basis of the map.
  • the map may be made through simulation and made on the basis of the measured values.
  • the controller 100 of the airconditioning device 1 calculates the appropriate subcooling degree at the outlet of the subcooling device 16 on the basis of the refrigerant circulation quantity.
  • the controller 100 calculates the determination threshold on the basis of the appropriate subcooling degree
  • the controller 100 makes determination of the quantity of the refrigerant, more specifically, makes the determination of whether the quantity of the refrigerant is insufficient due to the leakage of the refrigerant by comparing the measured subcooling degree with the determination threshold. According to this operation, the quantity of the refrigerant can be determined at a high accuracy without increase in the subcooling degree.
  • the relation between the refrigerant circulation quantity of the refrigerant and the subcooling degree at the outlet of the subcooling device 16 is stable though the operation state such as the evaporation temperature Te, the outdoor temperature, an outdoor fan rotation speed, a compressor rotation speed changes in various manner. Accordingly, the airconditioning device 1 of the present embodiment can determine the quantity of the refrigerant stable even though various operation states (disturbance, error factor) occur. In other words, the airconditioning device 1 according to the present embodiment can increase authenticity and accuracy in determination of the quantity of the refrigerant.
  • the determination of the quantity of the refrigerant has been made in only in a special mode by fixing the operation state to increase the subcooling degree.
  • the refrigerant quantity determination can be made also in the general operation. This eliminates, in the airconditioning device 1 according to the present embodiment, influence on the cooling temperature on a side of the load, which enables to make determination of the quantity of the refrigerant generally, more specifically, determination of insufficiency of the quantity of the refrigerant (leakage of the refrigerant) can be made.
  • the airconditioning device 1 since it is possible to make determination of the insufficiency of the quantity of the refrigerant in a high accuracy (leakage of the refrigerant) even in various operation states, which enables a rapid countermeasure when the quantity of the refrigerant is insufficient (occurrence of leakage), so that labor saving in inspection, cost reduction, a efficient countermeasure against.
  • the airconditioning device 1 includes the receiver 13 upstream from the subcooling device 16. As described above, the receiver 13 is provided, which stables the subcooling degree at the outlet of the subcooling device 16, so that accuracy of determining the quantity of the refrigerant can be increased.
  • the airconditioning device 1 determines that insufficiency in the quantity of the refrigerant (leakage of the refrigerant) occurs when a state that the actual subcooling degree is smaller than the determination threshold continues for the predetermined period. This can prevent an erroneous determination that the quantity of the refrigerant is insufficient when the measured subcooling degree temporary decreases due to noise etc.
  • the airconditioning device 1 according to the present embodiment calculates the appropriate subcooling degree on the basis of Eq. (1). This can make, in the airconditioning device 1 according to the present embodiment, a memory region necessary for calculating the appropriate subcooling degree.
  • the airconditioning device 1 calculates the determination threshold on the basis of Eq. (2). This can make, in the airconditioning device 1 according to the present embodiment, a memory region necessary for calculating the determination threshold small.
  • the airconditioning device 1 estimates a refrigerant circulation quantity using Eq. (3). This can realize the airconditioning device 1 according to the present embodiment from view point of cost of calculating the refrigerant circulation quantity.
  • the airconditioning device 1 performs calculation, etc. of the appropriate subcooling degree when operation state information is in a state in which determination of the refrigerant state is possible. This can improve the determination accuracy of the refrigerant state.
  • Grc is a rated refrigerant circulation quantity [kg/h].
  • the rated refrigerant circulation quantity is, for example, a refrigerant circulation quantity when the compressor operates at the maximum rotation speed at an evaporating temperature of -10°C.
  • For Fo / Foc
  • Fo is a current rotation speed [rpm] of the outdoor fan 12.
  • Foc is a rated outdoor fan rotation speed [rpm] of the outdoor fan 12.
  • the rated fan rotation speed is, for example, a maximum rotation speed of the outdoor fan 12.
  • Fig. 7 is a characteristic diagram indicating a relation between the refrigerant circulation quantity and the subcooling degree at the outlet of the subcooling device while the outdoor fan rotation speed is changed in the various manners.
  • Fig. 7 indicates the subcooling degree Sc1 on the axis of ordinates and the refrigerant circulation quantity Gr on the axis of abscissa under conditions of various outdoor rotation speeds. Further, in Fig. 7 , a point indicated with “ ⁇ ” indicates a refrigerant leakage rate of 0%. Further, a point indicated with “ ⁇ ” indicates a refrigerant leakage rate of 10%. Still further, a point indicated with " ⁇ ” indicates a refrigerant leakage rate of 15%.
  • Fig. 4 shows the case in which the outdoor fan rotation speed is a standard rotation speed.
  • Fig. 7 shows the relation between the refrigerant circulation quantity and the subcooling degree in various rotation speeds of the outdoor fan 12 in a save energy mode, a standard mode, a low noise mode, etc.
  • a line 601 is a regression line of " ⁇ "
  • a line 602 is a regression line of " ⁇ ”
  • a line 603 is a regression line of " ⁇ ”.
  • the line 601 is also a line indicating the appropriate subcooling degree.
  • the leakage rate has a reference (0%) when a liquid level of the receiver 13 is at the lower end to remove influence of the operation state on the load side and variation in the necessary quantity of the refrigerant due to outdoor temperature. More specifically, the leakage rate of the refrigerant is calculated from a critical state before a state at the inlet of the subcooling device 16 becomes the gas and liquid two phase state.
  • Fig. 7 does not show a line indicating the determination threshold
  • the determination threshold can be calculated only by calculation in accordance with Eq. (2) described above.
  • the measured subcooling degree Sc1 when the above-described index Grr/For is used in place of the refrigerant circulation quantity is shown in the chart in Fig. 8 .
  • Fig. 8 is a characteristic chart showing a relation between a value (Grr/For) acquired by dividing a refrigerant circulation ratio Grr by an outdoor fan rotation speed ratio For and the subcooling degree at the outlet of the subcooling device, while the outdoor fan rotation speed is changed variously.
  • the value acquired by dividing a refrigerant circulation ratio Grr by the outdoor fan rotation speed ratio For (Grr/For) is calculated by, for example, the step S112 in Fig. 6 .
  • the subcooling degree SC1 is represented by the axis of ordinates under various conditions, and the value (Grr/For) which is acquired by dividing the refrigerant circulation quantity ratio Grr by the outdoor fan rotation speed ratio For is shown by the axis of abscissa.
  • the points indicated with " ⁇ ” indicate that the refrigerant leakage rate is 0%. Further, the points indicated with “ ⁇ ” indicate that the refrigerant leakage rate is 10%. Further, the points indicated with “ ⁇ ” indicate that the refrigerant leakage rate is 15%.
  • a line 611 in Fig. 8 is a regression line of the points of " ⁇ "
  • a line 612 is a regression line of the points of " ⁇ ”
  • a line 613 is a regression line of the points of " ⁇ ”.
  • the line 611 is also a line indicating the appropriate subcooling degree.
  • a appropriate subcooling degree Sc3 indicated by the line 611 is represented by the Eq. (11) below.
  • Sc 3 A 4 ⁇ Grr / For + A 5
  • A4 and A5 are values acquired as a result of fitting of points " ⁇ " at the refrigerant leakage rate of 0%, and variable in accordance with specifications of the outdoor heat exchanger 11, the outdoor fan 12, the indoor heat exchanger 21, the indoor fan 22, etc.
  • a line 701 indicating the determination threshold is a line of a determination threshold Sc3th, which is represented by Eq. (12) below.
  • Sc 3 th Sc 3 ⁇ A 6
  • A6 is a decrease rate of the subcooling degree when refrigerant leakage occurs.
  • a chart in which the axis of ordinates of Fig. 8 is changed to the subcooling degree efficiency is shown in Fig. 9 .
  • Fig. 9 is a characteristic chart showing a relation between the value obtained by dividing the refrigerant circulation ratio Grr by the outdoor fan rotation speed ratio For (Grr/For) and the subcooling degree efficiency in the case where the outdoor fan rotation speed is change variously.
  • the subcooling degree efficiency is a value obtained by dividing the subcooling degree Sc1 at the outlet of the subcooling device 16 by a difference between the condensation temperature and the outdoor temperature.
  • a subcooling degree efficiency SCef is represented by the axis of ordinates and Grr/For is represented by the axis of abscissa.
  • the points indicated by “ ⁇ ” indicate that the refrigerant leakage rate is 0%. Further, the points indicated by “ ⁇ ” indicate that the refrigerant leakage rate is 10%. The points indicated by “ ⁇ ” indicate that the refrigerant leakage rate is 15%.
  • a line 621 is a regression line of " ⁇ "
  • a line 622 is a regression line of " ⁇ ”
  • a line 623 is a regression line of " ⁇ ”. Further, the line 621 is also a line representing the appropriate subcooling degree.
  • A7 and A8 are values obtained as a result of fitting of points " ⁇ " at the refrigerant leakage rate of 0%, and variable in accordance with specifications of the outdoor heat exchanger 11, the outdoor fan 12, the indoor heat exchanger 21, the indoor fan 22, etc.
  • A9 is a decrease rate of the subcooling degree when there is refrigerant leakage.
  • the chart in Fig. 9 also provides easy distinction among the leakage rates of 0%, 10%, and 15%.
  • Eqs. (11), (12), (21), and (22) provides calculation of the appropriate subcooling degree and the appropriate subcooling degree efficiency based on the value (Grr/For) acquired by dividing the refrigerant circulation ratio Grr by the outdoor fan rotation speed ratio For (Grr/For) and the determination threshold on the basis of the values quantitatively.
  • Ft represents a current compressor rotation speed [rps].
  • Ftmax is a compressor rotation speed upper limit [rps].
  • Ps represents a current inlet pressure of the compressor 14 or an inlet pressure [MPaA] of the entire of the outdoor unit 10.
  • Psc is Ps at the evaporation temperature as a reference (for example, -10°C).
  • Fig. 10 is shown in which the axis of ordinates in Fig. 7 is changed to the subcooling degree efficiency.
  • Fig. 10 is a characteristic chart representing a relation between the refrigerant circulation quantity when the outdoor rotation speed is variably changed and the subcooling degree efficiency at the outlet of the subcooling device 16.
  • the subcooling degree efficiency at the outlet of the subcooling device 16 is, as described above, a value acquired by dividing the subcooling degree Sc1 at the outlet of the subcooling device 16 by the difference between the condensation temperature and the outdoor temperature.
  • Fig. 10 shows a case where the subcooling degree efficiency Scef under a condition of various outdoor fan rotation speed is represented on the axis of ordinates, and the refrigerant circulation quantity Gr on the axis of abscissa. Further, in Fig. 10 , points indicated with “ ⁇ ” represent that the refrigerant leakage rate is 0%. Further, points indicated with “ ⁇ ” represent the refrigerant leakage of 10%. Further, points indicated with " ⁇ ” represent the refrigerant leakage of 15%.
  • a line 631 is a regression line of " ⁇ "
  • a line 632 is a regression line of " ⁇ ”
  • a line 633 is a regression line of " ⁇ ”.
  • the line 631 is also a line representing the appropriate subcooling degree.
  • the determination threshold can be calculated such that the subcooling degree Sc1s in Eq. (2) is regarded as the appropriate subcooling degree efficient (the line 631).
  • the airconditioning device 1 calculates the appropriate subcooling degree efficiency on the basis of the refrigerant circulation quantity and makes determination of the refrigerant leakage on the basis of the appropriate subcooling degree efficiency, so that an effect is provided which is the same as that provided by determination of the refrigerant leakage determination made on the basis of the appropriate subcooling degree which is calculated on the basis of the refrigerant circulation quantity.
  • a measured subcooling degree efficiency obtained by dividing the measured subcooling degree by a difference between the condensation temperature and the outdoor temperature is calculated.
  • Fig. 11 shows an example of configuration of the airconditioning device according to the second embodiment.
  • An outdoor unit 10a of the air conditioning device 1a in Fig. 11 is further provided with an economizer 41, a economizer valve (economizer decompressor) 42 for allowing a low temperature and low pressure refrigerant to flow through the economizer 41, and a temperature sensor 10th for measuring a refrigerant (liquid refrigerant) temperature at an outlet of the economizer 41, which is difference from the airconditioning device 1 in Fig. 1 .
  • economizer valve economizer decompressor
  • a subcooling liquid (subcooled refrigerant) flowing out from the subcooling device 16 on an upstream side of the economizer 41 is divided into a first passage in which the subcooled liquid flows into the liquid injection valve 17, a third passage (main passage) in which the subcooled liquid flows into the economizer 41, and a fourth passage (bypass passage) in which the subcooled liquid flows into the economizer valve 42.
  • the second passage in the first embodiment is divided into the third passage and the fourth passage.
  • the subcooling liquid in the fourth passage flows into the economizer valve 42 and decompressed by the economizer valve 42 with temperature decrease, and then flows into the economizer 41.
  • the subcooling liquid in the third passage (main passage) is further subcooled by thermal exchange with the subcooling liquid in the fourth passage which is decompressed by the economizer valve 42 with a low temperature.
  • the refrigerant in the third passage subcooled by the economizer 41 is supplied to the indoor heat exchanger 21 as a evaporator in the indoor unit 20 through the pipe 30.
  • the subcooling liquid in the fourth passage is evaporated by the economizer 41, and then flows out from the economizer 41 and joins with the refrigerant in the first passage flowing from the liquid injection valve 17.
  • the joined refrigerant flows into an intermediate pressure section of the compressor 14 which compresses the refrigerant up to the discharge pressure Pd.
  • Fig. 12 is a Mollier chart (P-h diagram) of the airconditioning device according to the second embodiment. Occasionally Fig. 11 is referred.
  • the elements in Fig. 12 which is same or like elements in Fig. 3 are designated with the same or like references and the detailed description is omitted.
  • the subcooling degree at the outlet of the economizer 41 is used in place of the subcooling degree at the outlet of the subcooling device 16.
  • the mark of " ⁇ " indicates the subcooling degree at the outlet of the economizer 41.
  • Points shown in Fig. 4 have values when the outdoor temperature and the evaporation temperature Te, etc. change variously under the above-described condition.
  • an opening degree of the economizer valve 42 is controlled by the discharging temperature Td of the compressor 14. More specifically, under a high pressure rate condition in which the discharging temperature Td becomes high, controlling such as increasing the opening degree of the economizer valve 42, etc. is made. This changes the flow rate of the bypass passage to the economizer 41 in accordance with the discharging temperature Td.
  • the subcooling degree for the refrigerant circulation quantity at the outlet on the main side of the economizer 41 disperses as shown in Fig. 4 . Accordingly, the determination of the refrigerant leakage cannot be made by only the refrigerant circulation quantity. In other words, there is a region where " ⁇ " and " ⁇ " are overlapping. Accordingly, it is difficult that the subcooling degree at the outlet on the main passage of the economizer 41 is used as a simple determination index using the refrigerant circulation quantity as described in the first embodiment.
  • the controller 100 can determine whether the refrigerant quantity is appropriate or not using the determination threshold for the subcooling degree at the outlet of the subcooling device 16 calculated from Eqs. (1) to (3) similar to the first embodiment. According to this, the controller 100 can make refrigerant leakage determination stable even under various operation conditions.
  • economizer outlet subcooling degree the subcooling degree at the liquid stop valve 18b subcooled by the economizer 41.
  • Fig. 13 is a characteristic chart indicating a relation between the refrigerant circulation quantity and an economizer outlet subcooling degree.
  • an economizer outlet subcooling degree SCeco is represented on the axis of ordinates
  • the refrigerant circulation quantity Gr is represented on the axis of abscissa.
  • points indicated with " ⁇ ” represent the refrigerant leakage of 0%. Further, points indicated with “ ⁇ ” represent the refrigerant leakage of 10%. Points indicated with “ ⁇ ” represent the refrigerant leakage of 15%.
  • a line 641 is a regression line of " ⁇ "
  • a line 642 is a regression line of " ⁇ ”
  • a line 643 is a regression line of " ⁇ ”.
  • the line 641 is also a line representing the appropriate subcooling degree.
  • the line 641 is also a line representing an appropriate economizer outlet subcooling degree. Further, the line representing the determination threshold is not limited to the line 641.
  • A10 and A11 are, for example, coefficients determined by the line 641 having a refrigerant leakage rate of 0%.
  • A10 and A11 are variable in accordance with specifications of the outdoor heat exchanger 11, the outdoor fan 12, the indoor heat exchanger 21, the indoor fan 22, etc.
  • determination using the subcooling degree of the subcooling device 16 in the first embodiment is made as a main determination and the subcooling degree of the economizer 41 according to the second embodiment is used as an auxiliary determination.
  • a process for using the subcooling degree of the economizer 41 is used as auxiliary determination is described below. The determination process is carried out in the step S113 in Fig. 6 .
  • the refrigerant quantity determining section 115 determines whether the quantity of the refrigerant is insufficient (leakage) or not using the subcooling degree of the subcooling device16 ( Fig. 4 ) or the subcooling degree efficiency ( Fig. 9 ) (first embodiment).
  • the refrigerant quantity determining section 115 determines whether the refrigerant is insufficient (leakage) with the economizer outlet subcooling degree SCeco (second embodiment).
  • the refrigerant quantity determining section 115 determines "Yes" in the step S113.
  • the refrigerant quantity determining section 115 determines "No" in the step S113.
  • Performing Processes 1 to 3 prevents an erroneous determination due to influence of sensor error and variation in operation state.
  • the air conditioning device 1a can acquire the determination threshold for increasing accuracy in refrigerant leakage determination using the economizer outlet subcooling degree.
  • a third embodiment of the present invention is described below referring to Fig. 14 .
  • the controllers 100 according to the first and second embodiments determine whether the refrigerant leaks or not. However, this can be used for determining whether the refrigerant quantity is appropriate or not when the refrigerant is charged. In the third embodiment, a method of determining whether the refrigerant quantity is appropriate or not is described below. Further, the third embodiment is applicable to both the airconditioning device 1 according to the first embodiment and the air conditioning device 1a according to the second embodiment.
  • Fig. 14 is a flowchart showing process of refrigerant leakage determination process according to the third embodiment.
  • the processes which are same as those in Fig. 6 are designated with the same step reference, and the detailed description is omitted.
  • A3 in Eq. (2) is set to be larger than 0.6 used in the first embodiment.
  • A3 0.8 is an example, and the value of A3 is not limited to 0.8 as long as the value for A3 is suitable for determining an appropriate quantity of the refrigerant.
  • the coefficient A3 in Eq. (2) is set to 1.2, etc. which is equal to or higher than 1 and the determination threshold Sclth to have a value exceeding the ideal appropriate subcooling degree Sc1s (appropriate subcooling degree).
  • the refrigerant quantity determining section 115 determines that the receiver 13 is in a full state (refrigerant excess). This operation provides detection of the full state (excessive refrigerant) of the receiver 13.
  • the refrigerant quantity determining section 115 determines whether the refrigerant quantity is appropriate or not by determining whether the measured subcooling degree Sc1 at the outlet of the subcooling device 16, calculated in the step S112 is equal to or greater than the determination threshold Sc1th.
  • step S113a when the measured subcooling degree Sc1 at the outlet of the subcooling device 16 is equal to or greater than the determination threshold Sclth (YES in S113), the refrigerant quantity determining section 115 determines that the refrigerant quantity is appropriate, and the processing section 111 returns the processing to the step S101.
  • the refrigerant quantity determining section 115 determines whether a predetermined period has elapsed or not (S114).
  • step S114 when the predetermined period has not elapsed (NO in the step +S114), the processing section 111 returns the processing to the step S112.
  • the processing section 111 returns the processing to a step S111.
  • the refrigerant quantity determining section 115 determines that the refrigerant quantity is abnormal (S121a).
  • the outputting section 116 sends a refrigerant abnormality flag to the display device 200, an alarm (not shown), and a concentrated monitoring device (not shown).
  • the display device 200 makes an alarming indication of "There may be abnormality in refrigerant quantity", etc.
  • the refrigerant having a predetermined quantity according to the capacity of the receiver 13 or a quantity calculated as an additional charging quantity is added (calculation of charging quantity and addition:S122a). Further, the calculation of the additional quantity and addition of the refrigerant may be done when determination is made that the refrigerant leakage occurs in Fig. 6 .
  • a process in a step S122a may be omitted.
  • the airconditioning device 1 in the third embodiment can determine whether the refrigerant quantity is appropriate or not in addition to the determination that the refrigerant quantity is insufficient (leakage).
  • inflammable refrigerants having a GWP (Global Warming Potential) not smaller than 1000 such as R404A, R407C, R407F, R407E, R410A, R134a, R507A, R448A, R449A, R450A, R452A, and R513A are used.
  • GWP Global Warming Potential
  • the performance coefficient COP Coefficient Of Performance
  • the performance coefficient COP Coefficient Of Performance
  • the GWP is not smaller than 1000, which relatively large, it is important to earlier detection of the refrigerant leakage from point view of prevention of global warming. Therefore, the refrigerant leakage determination according to the embodiments of the invention has a high usefulness.
  • a refrigerant having a low GWP for example, GWP is not larger 750
  • a refrigerant having a low flammability is used, though the influence on global warming can be made small, but it is desirable to make earlier determination of the refrigerant leakage because of the low flammability. Accordingly, when the latter, i.e., the refrigerant having a low flammability, is used, the technology according to the present embodiments providing the refrigerant leakage determination has a high usefulness.
  • the refrigerant used in the airconditioning device 1 may be a refrigerant having the GWP not larger than 750 such as R32, R1123, R1234yf, R1234ze(E), R454A, R454B, R444B.
  • the above-described explanations are made such that the airconditioning devices 1, 1a perform cooling.
  • the receiver 13 and the subcooling device 16 are installed on the side of the condenser (the indoor heat exchanger 21) operated for heating and an expansion valve is installed at the inlet of the outdoor heat exchanger 11.
  • the receiver 13 may be installed on a side of the indoor unit 20.
  • the receiver 13 may not be installed on the sides of the outdoor unit 10 and the indoor unit 20.
  • the airconditioning devices 1, 1a can be applied to a package air conditioner, a room air conditioner, etc.
  • the airconditioning devices 1, 1a When the airconditioning devices 1, 1a according to the embodiments are used as a refrigerator, if the section corresponding to the indoor unit 20 is a unit cooler, the airconditioning devices 1, 1a can be used for cooling a freezing storage room, if the airconditioning devices 1, 1a are used as a show case, the airconditioning devices 1, 1a are used for cooling displayed foods or drinks.
  • the cooling target is not limited to these.
  • the controller 100 may be installed in the outdoor unit 10 or the indoor unit 20 and may be as a separated device from the outdoor unit 10 and the indoor unit 20.
  • control line and a data line are shown which are considered to be necessary, and not all control lines and data lines are shown.

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CN108027188A (zh) 2018-05-11
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JP2017053566A (ja) 2017-03-16
CN108027188B (zh) 2020-08-14

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