EP2960598A1 - Climatiseur, et procédé de commande de climatiseur - Google Patents

Climatiseur, et procédé de commande de climatiseur Download PDF

Info

Publication number
EP2960598A1
EP2960598A1 EP14813089.1A EP14813089A EP2960598A1 EP 2960598 A1 EP2960598 A1 EP 2960598A1 EP 14813089 A EP14813089 A EP 14813089A EP 2960598 A1 EP2960598 A1 EP 2960598A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
air conditioner
crankcase heater
temperature
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.)
Withdrawn
Application number
EP14813089.1A
Other languages
German (de)
English (en)
Other versions
EP2960598A4 (fr
Inventor
Takahiro Kato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2960598A1 publication Critical patent/EP2960598A1/fr
Publication of EP2960598A4 publication Critical patent/EP2960598A4/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/34—Heater, e.g. gas burner, electric air heater
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02334—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/01—Heaters
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2500/16—Lubrication
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B2500/31—Low ambient temperatures
    • 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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures

Definitions

  • the present invention relates to an air conditioner and a method for controlling an air conditioner.
  • the compressor When an air conditioner is stopped for a long period, the refrigerant is liquefied and is accumulated inside the compressor. When the compressor is started in this state, there is a risk that the compressor will be damaged as a result of liquid compression.
  • the compressor in air conditioners for use in cold regions, the compressor is provided with a crankcase heater, which is energized before operating the air conditioner to heat the compressor and thereby prevents the liquid compression caused by the accumulation of liquid refrigerant.
  • crankcase heater is energized continuously while the compressor is stopped, power consumed by the crankcase heater will increase, thus increasing the standby power consumption of the air conditioner.
  • Patent Document 1 discloses an air conditioner in which, while a compressor is stopped, a crankcase heater is caused to operate and, upon a refrigerating machine oil temperature reaching a predetermined temperature, the operation of the crankcase heater is stopped to prepare for the restart of the compressor.
  • Patent Document 1 Japanese Patent No. 3799940B
  • Patent Document 1 needs to energize the crankcase heater every time the refrigerating machine oil temperature decreases lower than the predetermined temperature, thus limiting the reduction in standby power consumption.
  • the present invention has been conceived in view of such circumstances, and an object of the present invention is to provide an air conditioner and a method for controlling an air conditioner capable of further reducing the standby power consumption that occurs as a result of the crankcase heater being energized while the compressor is stopped.
  • the air conditioner and the method for controlling an air conditioner of the present invention employ the following means.
  • a compressor is provided with a crankcase heater, and energizing the crankcase heater allows the compressor to be heated.
  • Such an air conditioner includes control means that determine, on the basis of a parameter having a correlation with a temperature of a refrigerant, a timing for starting to energize the crankcase heater while the compressor is stopped and before the compressor is started.
  • the air conditioner is configured so that the compressor is provided with the crankcase heater, and energizing the crankcase heater allows the compressor to be heated.
  • the crankcase heater is energized to heat the compressor before the stopped compressor is started. Accordingly, the liquid refrigerant is heated and vaporized, preventing liquid compression due to an accumulation of the liquid refrigerant.
  • crankcase heater will be energized more than necessary and standby power consumption will increase.
  • the timing for starting to energize the crankcase heater is determined on the basis of the parameter having the correlation with the temperature of the refrigerant while the compressor is stopped and before the compressor is started. Specifically, the timing for starting to energize the crankcase heater is determined so that the above-described parameter reaches a preset target value when the compressor is started.
  • the timing for starting to energize the crankcase heater is set to be earlier as the value of the parameter having the correlation with the temperature of the refrigerant decreases so that the refrigerant reaches a temperature at which the accumulation thereof can be eliminated by the start time of the compressor.
  • the timing for starting to energize the crankcase heater is delayed. Accordingly, the period of energizing the crankcase heater is suppressed from being longer than necessary.
  • the standby power consumption that occurs due to the energization of the crankcase heater while the compressor is stopped can be reduced.
  • the parameter be a degree of superheating of the refrigerant.
  • the accumulation of liquid refrigerant is small when the degree of superheating is sufficiently high. Moreover, when a temperature of a lower portion of the compressor is sufficiently high, the accumulation of liquid refrigerant is small. However, the temperature of the lower portion of the compressor is easily affected by outside air temperature; thus, the state of the refrigerant may not always be measured correctly.
  • the degree of superheating of the refrigerant is a parameter that has a correlation not only with the temperature of the refrigerant, but also with the pressure of the refrigerant. Hence, measuring the degree of superheating of the refrigerant allows the state of the refrigerant to be more correctly measured than measuring the temperature of the lower portion of the compressor.
  • the timing for energizing the crankcase heater can be more accurately determined.
  • control means determine, on the basis of the parameter and outside air temperature, the timing for starting to energize the crankcase heater while the compressor is stopped and before the compressor is started.
  • the temperature of the compressor specifically the degree of an increase in temperature of the refrigerant, will differ depending on differences in the outside air temperature.
  • the timing for starting to energize the crankcase heater is determined on the basis of the parameter having the correlation with the temperature of the refrigerant and the outside air temperature. Specifically, even if the parameter values are the same, the timing for starting to energize the crankcase heater becomes earlier as the outside air temperature decreases. Similarly, the timing for starting to energize the crankcase heater becomes later as the outside temperature increases.
  • the timing for energizing the crankcase heater can be more accurately determined.
  • the compressor be started according to a preset schedule.
  • the timing for energizing the crankcase heater can be more accurately determined.
  • a control board be provided with an indicator light that indicates a control status and that the indicator light turn off when control is stable for at least a predetermined period.
  • the power consumption of the air conditioner can be further reduced.
  • a compressor is provided with a crankcase heater, and energizing the crankcase heater allows the compressor to be heated.
  • Such a method includes the step of determining, on the basis of a parameter having a correlation with a temperature of a refrigerant, a timing for starting to energize the crankcase heater while the compressor is stopped and before the compressor is started.
  • the present invention exhibits the advantageous effect of allowing a further reduction in the standby power consumption that occurs as a result of the crankcase heater being energized while the compressor is stopped.
  • FIG. 1 is a schematic configuration diagram of a multiple air conditioner according to a first embodiment of the present invention
  • FIG. 2 is a configuration diagram of the surroundings of a compressor including a crankcase heater of the multiple air conditioner.
  • a plurality of inside units 3A and 3B are connected to a single outside unit 2 in parallel via branching devices 6 between gas-side piping 4 and liquid-side piping 5 leading from the outside unit 2.
  • the outside unit 2 includes an inverter-driven compressor 10 that compresses a refrigerant, an oil separator 11 that separates lubricating oil from the refrigerant gas, a four-way selector valve 12 that switches circulating directions of the refrigerant, an outside heat exchanger 13 that allows the refrigerant to exchange heat with the outside air, a supercooling coil 14 that is integrally constituted with the outside heat exchanger 13, an outside expansion valve (EEVH) 15, a receiver 16 that stores liquid refrigerant, a supercooling heat exchanger 17 that supercools the liquid refrigerant, a supercooling expansion valve (EEVSC) 18 that controls the amount of refrigerant to be branched to the supercooling heat exchanger 17, an accumulator 19 that separates a liquid component from the refrigerant gas to be sucked into the compressor 10 so as to allow only a gas component to be sucked into the compressor 10, a gas-side control valve 20, and a liquid-side control valve 21.
  • the above-described devices on the outside unit 2 side are connected in a well-known manner via refrigerant piping 22, thereby configuring an outside refrigerant circuit 23.
  • the outside unit 2 is provided with an outside fan 24 that makes outside air flow to the outside heat exchanger 13, and an oil return circuit 25 between the oil separator 11 and intake piping of the compressor 10.
  • the oil return circuit 25 returns, by a predetermined amount, the lubricating oil separated from the discharged refrigerant gas in the oil separator 11 to the compressor 10.
  • the gas-side piping 4 and the liquid-side piping 5 are cooling piping connected to the gas-side control valve 20 and the liquid-side control valve 21 of the outside unit 2.
  • the length of this piping is set according the distance between the outside unit 2 and the plurality of inside units 3A and 3B connected to the outside unit 2.
  • An appropriate number of branching devices 6 is provided part way along the gas-side piping 4 and the liquid-side piping 5, and an appropriate number of the inside units 3A and 3B is connected via the branching devices 6.
  • a single sealed system of refrigeration cycle (refrigeration circuit) 7 is formed.
  • the inside units 3A and 3B include respective inside heat exchangers 30 that are used for inside air conditioning to cause the inside air to exchange heat with the refrigerant, an inside expansion valve (EEVC) 31, and an inside fan 32 that causes the inside air to circulate in the inside heat exchanger 30.
  • the inside units 3A and 3B are connected to the branching devices 6 via the inside branching gas-side piping 4A and 4B and the branching liquid-side piping 5A and 5B.
  • the pressure of the refrigerant discharged from the compressor 10 is measured by a pressure sensor 33.
  • cooling operation is performed as follows.
  • the refrigerant gas compressed by the compressor 10 and discharged at high temperature and high pressure has the lubricating oil contained therein separated by the oil separator 11. Thereafter, the refrigerant gas is circulated to the outside heat exchanger 13 via the four-way selector valve 12 and is condensed and liquefied in the outside heat exchanger 13 as a result of heat exchange with the outside air that is blown through by the outside fan 24. This liquid refrigerant is further cooled by the supercooling coil 14, then passed through an outside expansion valve 15 and stored in the receiver 16.
  • the liquid refrigerant that has its circulation flow adjusted by the receiver 16 is split away from the liquid refrigerant piping while being circulated through a liquid refrigerant side piping via the supercooling heat exchanger 17, and undergoes supercooling through heat exchange with a portion of the refrigerant that has undergone adiabatic expansion in the supercooling expansion valve (EEVSC) 18.
  • This liquid refrigerant is introduced from the outside unit 2 to the liquid-side piping 5 via the liquid-side control valve 21. Further, the liquid refrigerant introduced to the liquid-side piping 5 is split by the branching devices 6 and flows to branching liquid-side piping 5A and 5B of the inside units 3A and 3B.
  • the liquid refrigerant flowing in the respective branching liquid-side piping 5A and 5B is introduced to the inside units 3A and 3B, undergoes adiabatic expansion in the inside expansion valve (EEVC) 31, and is introduced to the inside heat exchanger 30 as a gas-liquid two-phase flow.
  • EEVC inside expansion valve
  • the inside air being circulated by the inside fan 32 exchanges heat with the refrigerant so that the inside air is cooled, thereby cooling the room.
  • the refrigerant is vaporized and sent to the branching devices 6 through the branching gas-side piping 4A and 4B, and is merged in the gas-side piping 4 with the refrigerant gas form another inside unit.
  • the refrigerant gas merged in the gas-side piping 4 is again returned to the outside unit 2, passed through the gas-side control valve 20 and the four-way selector valve 12 to merge with the refrigerant gas from the supercooling heat exchanger 17, and then introduced to the accumulator 19.
  • the liquid component contained in the refrigerant gas is separated out, and the gas component alone is introduced to the compressor 10. This refrigerant is compressed again by the compressor 10.
  • the cooling operation is performed through repetition of the above-described cycle.
  • Heating operation is performed as follows.
  • Refrigerant gas after being compressed by the compressor 10 and discharged at high temperature and high pressure, has the lubricating oil contained therein separated by the oil separator 11, and is then circulated to the gas-side control valve 20 via the four-way selector valve 12.
  • the refrigerant circulated to the gas-side control valve 20 is introduced from the outside unit 2 through the gas-side piping 4, and then introduced to a plurality of the inside units 3A and 3B via the branching devices 6 and the inside branching gas-side piping 4A and 4B.
  • the high pressure and high temperature refrigerant gas introduced to the inside units 3A and 3B exchanges heat with the inside air being circulated in the inside heat exchanger 30 via the inside fan 32, thus heating the inside air and providing heating in the room.
  • the liquid refrigerant condensed by the inside heat exchanger 30 is passed through the inside expansion valve (EEVC) 31 and the branching liquid-side piping 5A and 5B to the branching devices 6, and is merged with refrigerant from another inside unit before being returned through the liquid-side piping 5 to the outside unit 2.
  • EEVC inside expansion valve
  • an opening degree of the inside expansion valve (EEVC) 31 in the inside units 3A and 3B is controlled so that the refrigerant outlet temperature or the degree of supercooling of the refrigerant in the inside heat exchanger 30, which functions as a condenser, reach a target value.
  • EEVC inside expansion valve
  • the refrigerant that has returned to the outside unit 2 is passed through the liquid-side control valve 21 to the supercooling heat exchanger 17 and undergoes supercooling in the same way as in the case of cooling, before being introduced to the receiver 16 and temporarily stored therein to adjust circulation flow.
  • the liquid refrigerant After being supplied to the outside expansion valve (EEVH) 15 and undergoing adiabatic expansion, the liquid refrigerant is passed through the supercooling coil 14 and introduced to the outside heat exchanger 13.
  • the outside heat exchanger 13 the outside air blown in via the outside fan 24 exchanges heat with the refrigerant, thereby causing the refrigerant to absorb heat from the outside air and then to be vaporized.
  • the refrigerant gas is passed from the outside heat exchanger 13 via the four-way selector valve 12 to merge with the refrigerant gas from the supercooling heat exchanger 17, and then introduced to the accumulator 19.
  • the liquid component contained in the refrigerant gas is separated out, and the gas component alone is introduced to the compressor 10 and compressed again in the compressor 10.
  • the heating operation is performed through repetition of the above-described cycle.
  • the compressor 10 is provided with a crankcase heater (referred to hereinafter as "CH") 40 on the periphery of a sealed housing 10A.
  • the CH 40 is provided to prevent damage to the compressor 10, which occurs when the refrigerant is liquefied and accumulated in the compressor 10 while the compressor 10 is stopped and is then sucked in when the compressor 10 is started, causing the compressor 10 to attempt liquid compression.
  • the CH 40 by being energized to heat the compressor 10 before the air conditioner 1 is operated, removes the liquid refrigerant from the compressor 10; thus, the CH 40 plays a role of preventing liquid compression.
  • the CH 40 is turned ON/OFF via a control unit 41.
  • the control unit 41 includes a normal operation mode control unit 42 that performs normal energization control of the CH 40 on the basis of a preset specification while the compressor 10 is stopped and a reduced operation mode control unit 43 that calculates an ON timing for the CH 40 and turns CH 40 ON/OFF.
  • the control unit 41 includes switching means 44 that allow the control mode to be selectively switched to either a normal operation mode or a reduced operation mode.
  • the switching means 44 are, for example, configured so that switching operation can be performed from a remote control 45.
  • control unit 41 is configured of, for example, a central processing unit (CPU), a random access memory (RAM), and a computer-readable storage medium, and the like.
  • CPU central processing unit
  • RAM random access memory
  • a sequence of processing to realize various functions is, for example, recorded in a recording medium or the like in program form.
  • the CPU then reads this program into RAM or the like and executes processing and calculation on the information to realize the various functions.
  • control unit 41 includes, on a control board, an indicator light 50 that indicates a control status of the air conditioner 1.
  • the indicator light 50 is used to indicate when the air conditioner 1 requires maintenance or the like.
  • the indicator light 50 is, for example, a 7-segment display, but is not limited to this, and may be a single or plurality of LED lamps.
  • control unit 41 receives measurement values from an under-dome temperature sensor 52 that measures a temperature of a lower portion of the compressor 10 (hereinafter referred to as "under-dome temperature”), measurement values from an outside air temperature sensor 46 that measures an outside air temperature, and measurement values from a pressure sensor 33.
  • the normal operation mode control unit 42 constantly energizes the CH 40 while the compressor 10 is stopped, thus keeping the CH 40 ON and heating the compressor 10. In this case, when the compressor 10 is started up, the CH 40 is kept OFF while the compressor 10 is running. When the compressor 10 is stopped, the CH 40 is kept ON while the compressor 10 is stopped.
  • the CH 40 is energized to heat the compressor 10 before the stopped compressor 10 is started.
  • the refrigerant is heated and vaporized; thus, liquid compression due to the accumulation of refrigerant is prevented.
  • the CH 40 will be energized more than necessary and standby power consumption will increase.
  • the reduced operation mode control unit 43 determines, on the basis of a parameter having a correlation with the temperature of the refrigerant, the timing for starting to energize the CH 40 while the compressor 10 is stopped and before the compressor 10 is started. Specifically, the timing for starting to energize the CH40 is determined so that the above-described parameter reaches a preset target value when the compressor 10 is started.
  • the degree of superheating of the refrigerant is calculated by subtracting a saturation temperature, which is calculated on the basis of measurement values of the pressure sensor 33, from the under-dome temperature measured by the under-dome temperature sensor 52.
  • the reduced operation mode control unit 43 calculates the period for energizing the CH 40 from the relationship between the degree of superheating shown in the graph in FIG. 3 and an ON period of the CH 40 (hereinafter referred to as the "heater-ON period").
  • the timing for starting to energize the CH 40 is set to be earlier as the degree of superheating decreases, so that the refrigerant reaches the degree of superheating at which the accumulation thereof can be eliminated by the start time of the compressor 10. Conversely, the timing for starting to energize the CH 40 is set later as the degree of superheating increases. Furthermore, if the degree of superheating is sufficiently high, the energization of the CH 40 is not performed while the compressor 10 is stopped.
  • the period of energizing the CH 40 is suppressed from being longer than necessary.
  • the function f is determined in advance on the basis of a heat capacity of the compressor 10, output from the CH 40, the amount of heat radiated from the compressor 10, and the like.
  • the degree of superheating at which the compressor 10 can be started may, for example, be 10 to 15°C.
  • control unit 41 includes a so-called schedule timer function whereby starting and stopping of the air conditioner 1, specifically the starting, stopping, and the like of various sub-assemblies such as the compressor 10, are performed in accordance with a preset schedule. If the schedule timer has been set, the control unit 41 cuts off unnecessary electric power to various sub-assemblies while the air conditioner 1 is stopped, in accordance with the preset schedule, and puts the air conditioner 1 in a sleep state.
  • the reduced operation mode control unit 43 then calculates the time for energizing the CH 40 (hereinafter referred to as the "CH energization start time"). For example, when the heater-ON period is calculated as being 3 hours if the air conditioner 1 is to be started at 8 a.m. according to the schedule timer, the CH energization start time is set to 5 a.m.
  • the degree of superheating of the refrigerant is a parameter that correlates not only with the temperature of the refrigerant, but also with the pressure of the refrigerant. Hence, measuring the degree of superheating of the refrigerant allows the state of the refrigerant to be correctly measured comparing with measuring the temperature of the lower portion of the compressor 10.
  • the timing for energizing the CH 40 can more accurately calculated.
  • FIG. 4 is a flowchart illustrating the flow of processing for energizing the CH 40 (hereinafter referred to as "CH energization processing"), which is executed by the reduced operation mode control unit 43 while the compressor 10 is stopped and before the compressor 10 is started. Note that the CH energization processing is executed while the compressor 10 is stopped.
  • step 100 the degree of superheating is calculated.
  • step 102 the heater-ON period is calculated on the basis of the calculated degree of superheating.
  • step 104 the CH energization start time is calculated on the basis of the calculated heater-ON period.
  • step 106 it is determined whether or not the current time has reached the CH energization start time. When the determination is affirmative, the processing proceeds to step 108. When the determination is negative, the processing returns to step 100.
  • step 108 the energization of the CH 40 is started.
  • a new CH energization start time is calculated on the basis of a newly calculated degree of superheating and heater-ON period.
  • control unit 41 turns off the indicator light 50 when the control is stable for at least a predetermined period.
  • control is stable means that, for example, there has been no operation on the remote control 45, there has been no change in the capabilities of the outside unit 2, and there has been no change in the stopping and starting of the compressor 10.
  • the indicator light 50 turns off in accordance with the schedule timer.
  • the compressor 10 is provided with the CH 40, the energization of the CH 40 allows the compressor 10 to be heated. Then, while the compressor 10 is stopped and before the compressor 10 is started, the control unit 41 determines the timing for starting the CH 40 on the basis of the degree of superheating, which is a parameter having a correlation with the temperature of the refrigerant.
  • the air conditioner 1 according to the first embodiment is capable of further reducing standby power consumption that occurs due to the energization of the CH 40 while the compressor 10 is stopped.
  • the temperature of the compressor 10 specifically the degree of an increase in temperature of the refrigerant, will differ depending on differences in the outside air temperature.
  • the reduced operation mode control unit 43 determines, on the basis of the degree of superheating and the outside air temperature, the timing for starting to energize the CH 40 while the compressor 10 is stopped and before the compressor 10 is started.
  • the heater-ON period may be represented as in Equation (2).
  • Heater ON period f degree of superheating outside air temperature
  • FIG. 5 is graph showing a relationship between the degree of superheating and the heater-ON period according to the second embodiment.
  • the solid line indicates a case in which the outside air temperature is low compared with that indicated by the dashed line.
  • the air conditioner 1 according to the second embodiment can more accurately determine the timing for energizing the crankcase heater.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP14813089.1A 2013-06-20 2014-06-13 Climatiseur, et procédé de commande de climatiseur Withdrawn EP2960598A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013129895A JP6440930B2 (ja) 2013-06-20 2013-06-20 空気調和機及び空気調和機の制御方法
PCT/JP2014/065764 WO2014203828A1 (fr) 2013-06-20 2014-06-13 Climatiseur, et procédé de commande de climatiseur

Publications (2)

Publication Number Publication Date
EP2960598A1 true EP2960598A1 (fr) 2015-12-30
EP2960598A4 EP2960598A4 (fr) 2016-05-25

Family

ID=52104563

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14813089.1A Withdrawn EP2960598A4 (fr) 2013-06-20 2014-06-13 Climatiseur, et procédé de commande de climatiseur

Country Status (4)

Country Link
EP (1) EP2960598A4 (fr)
JP (1) JP6440930B2 (fr)
CN (1) CN105190196B (fr)
WO (1) WO2014203828A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019074738A1 (fr) * 2017-10-10 2019-04-18 Carrier Corporation Système et procédé de hvac
US11060773B2 (en) 2015-07-30 2021-07-13 Daikin Industries, Ltd. Refrigerating device
US11333381B2 (en) 2015-08-03 2022-05-17 Daikin Industries, Ltd. Determination device

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6236734B2 (ja) * 2013-07-24 2017-11-29 三浦工業株式会社 ヒートポンプ
US10684046B2 (en) * 2015-11-20 2020-06-16 Mitsubishi Electric Corporation Refrigeration cycle apparatus in which a lubricating oil circulates together with refrigerant
CN106016606B (zh) * 2016-05-25 2019-05-14 珠海格力电器股份有限公司 空调压缩机电加热带的控制方法及装置
CN106382777A (zh) * 2016-08-29 2017-02-08 珠海格力电器股份有限公司 一种空调系统及过冷器回流冷媒的回流控制方法
CN106765867B (zh) * 2016-11-14 2018-12-07 珠海格力电器股份有限公司 一种空调冷水机组控制方法及系统
JP2019138501A (ja) * 2018-02-07 2019-08-22 三菱重工サーマルシステムズ株式会社 制御装置、冷媒回路システム及び通知方法
JP7063750B2 (ja) * 2018-07-10 2022-05-09 ファナック株式会社 温度推定装置、寿命評価装置、およびロボットシステム
JP7280482B2 (ja) * 2019-03-15 2023-05-24 ダイキン工業株式会社 冷凍サイクル装置
JP7130864B2 (ja) * 2019-05-14 2022-09-05 東芝キヤリア株式会社 熱源システム
JP7399182B2 (ja) * 2019-11-15 2023-12-15 三菱電機株式会社 冷熱源ユニットおよび冷凍サイクル装置

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6024377B2 (ja) * 1978-12-01 1985-06-12 三洋電機株式会社 空気調和機の運転制御装置
US4444017A (en) * 1982-03-29 1984-04-24 Carrier Corporation Method and apparatus for controlling the operation of a compressor crankcase heater
US5572878A (en) * 1994-10-31 1996-11-12 York International Corporation Air conditioning apparatus and method of operation
JPH10325624A (ja) * 1997-05-28 1998-12-08 Matsushita Seiko Co Ltd 冷凍サイクル装置
JP3799940B2 (ja) 2000-03-07 2006-07-19 ダイキン工業株式会社 空気調和機及びその制御方法
US6886354B2 (en) * 2003-04-04 2005-05-03 Carrier Corporation Compressor protection from liquid hazards
JP3888364B2 (ja) * 2004-04-15 2007-02-28 松下電器産業株式会社 冷蔵庫
JP2006349219A (ja) * 2005-06-14 2006-12-28 Corona Corp リモコン装置
JP2009085463A (ja) * 2007-09-28 2009-04-23 Fujitsu General Ltd 空気調和機
JP5404110B2 (ja) * 2009-03-12 2014-01-29 三菱電機株式会社 空気調和装置
JP5550608B2 (ja) * 2011-07-11 2014-07-16 三菱電機株式会社 空気調和装置
JP5240392B2 (ja) * 2011-09-30 2013-07-17 ダイキン工業株式会社 冷凍装置
JP2013108672A (ja) * 2011-11-21 2013-06-06 Mitsubishi Heavy Ind Ltd クランクケースヒータを備えた空気調和機

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11060773B2 (en) 2015-07-30 2021-07-13 Daikin Industries, Ltd. Refrigerating device
US11333381B2 (en) 2015-08-03 2022-05-17 Daikin Industries, Ltd. Determination device
US11609011B2 (en) 2015-08-03 2023-03-21 Daikin Industries, Ltd. Determination device for refrigerant quality
WO2019074738A1 (fr) * 2017-10-10 2019-04-18 Carrier Corporation Système et procédé de hvac
US20200348062A1 (en) * 2017-10-10 2020-11-05 Carrier Corporation Hvac heating system and method
US11668505B2 (en) * 2017-10-10 2023-06-06 Carrier Corporation HVAC heating system and method

Also Published As

Publication number Publication date
WO2014203828A1 (fr) 2014-12-24
JP2015004473A (ja) 2015-01-08
CN105190196A (zh) 2015-12-23
CN105190196B (zh) 2017-10-17
JP6440930B2 (ja) 2018-12-19
EP2960598A4 (fr) 2016-05-25

Similar Documents

Publication Publication Date Title
EP2960598A1 (fr) Climatiseur, et procédé de commande de climatiseur
JP5240392B2 (ja) 冷凍装置
KR101917941B1 (ko) 공기조화기 및 그 제어 방법
US20120260678A1 (en) Air conditioner, method for controlling opening of expansion valve, and computer-readable recording medium with expansion valve opening control program recorded thereon
JP5405076B2 (ja) 空調冷凍システム
JP6887979B2 (ja) 冷媒漏洩判定装置、この冷媒漏洩判定装置を備える冷凍装置、及び冷媒漏洩判定方法
JP2013228130A (ja) 冷凍装置
US20150330703A1 (en) Refrigeration device
JP5522288B2 (ja) 冷凍装置
US11732948B2 (en) Method for controlling refrigerator to alternately cool two storage compartments
JP2014126309A (ja) 空気調和機
JP6432641B1 (ja) 雪氷利用空調システム
JP6576566B2 (ja) 空気調和装置
EP3421904A1 (fr) Régulation de cyclage de compresseur pour systèmes d'écoulement variable
JP2009085463A (ja) 空気調和機
JP5138292B2 (ja) 空気調和装置
JP2007225259A (ja) 冷凍装置
JPWO2016135953A1 (ja) 冷媒量異常検知装置及び冷凍装置
JP2013108672A (ja) クランクケースヒータを備えた空気調和機
CN112682929A (zh) 空调器
JP2012026590A (ja) 冷凍装置
JP6590945B2 (ja) 冷凍装置
JP5318059B2 (ja) 空調システムの制御装置及びその制御装置を備えた空調システム
JP2009162431A (ja) 空気調和機
JP2010025545A (ja) 冷凍空調装置への冷媒充填方法、冷凍空調装置への冷媒充填装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150918

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

A4 Supplementary search report drawn up and despatched

Effective date: 20160422

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 40/02 20060101ALI20160418BHEP

Ipc: F24F 11/02 20060101ALI20160418BHEP

Ipc: F25B 1/00 20060101AFI20160418BHEP

Ipc: F25B 31/00 20060101ALI20160418BHEP

Ipc: F25B 13/00 20060101ALI20160418BHEP

Ipc: F25B 43/02 20060101ALI20160418BHEP

Ipc: F24F 11/00 20060101ALI20160418BHEP

Ipc: F25B 49/02 20060101ALI20160418BHEP

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD.

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20191008