EP2211123B1 - Klimaanlage - Google Patents

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Publication number
EP2211123B1
EP2211123B1 EP08837535.7A EP08837535A EP2211123B1 EP 2211123 B1 EP2211123 B1 EP 2211123B1 EP 08837535 A EP08837535 A EP 08837535A EP 2211123 B1 EP2211123 B1 EP 2211123B1
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EP
European Patent Office
Prior art keywords
temperature
refrigerant
indoor
fluid
air conditioner
Prior art date
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Active
Application number
EP08837535.7A
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English (en)
French (fr)
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EP2211123A1 (de
EP2211123A4 (de
Inventor
Tatsuya Makino
Takeshi Arai
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication of EP2211123A4 publication Critical patent/EP2211123A4/de
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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
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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

Definitions

  • the present invention relates to the control of an air conditioner's operation such that the air conditioner's coefficient of performance is optimized.
  • a conventional refrigeration apparatus which comprises a refrigerant circuit that comprises and connects a compressor, a condenser, an expansion valve, and an evaporator, control is performed to improve the coefficient of performance (COP).
  • COP coefficient of performance
  • Patent Document 1
  • JP 08-189735 A describes an operation control device for an air conditioning device.
  • An outdoor heat-exchange sensor Thc which detects a refrigerant temperature Tcs is provided at the refrigerant outlet side of an outdoor heat-exchanger 23.
  • a theoretical value Tct of a saturation temperature which is equivalent to the temperature under the pressure of a high-pressure refrigerant in a refrigerant circulation circuit 11 is calculated.
  • a compensation value ⁇ of a supercooled temperature SC which is proportional to a differential temperature between the theoretical value Tct of the saturation temperature being equivalent to the temperature under high pressure and the refrigerant temperature Tcs detected by the outdoor heat-exchange sensor Thc, is introduced.
  • an actual saturated temperature Tcx is introduced by adding the compensation value ⁇ to the outdoor heat-exchange temperature Tcs detected by the outdoor heat-exchange sensor Thc.
  • the present invention was conceived considering the points discussed above, and it is an object of the present invention to provide an air conditioner that can optimize the COP under any of various conditions.
  • An air conditioner comprises a refrigerant circuit, a fluid feeding mechanism, a condensing temperature ascertaining means, a fluid temperature ascertaining means, and a control unit.
  • the refrigerant circuit comprises and connects a compressor, a condenser, an expansion mechanism, and an evaporator such that a refrigerant circulates therein.
  • the fluid feeding mechanism feeds a fluid toward the condenser.
  • the condensing temperature ascertaining means senses a physical quantity in order to derive a condensing temperature of the refrigerant.
  • the fluid temperature ascertaining means senses a physical quantity in order to derive the temperature of the fluid, which exchanges heat with the refrigerant inside the condenser.
  • the control unit controls at least one member selected from the group consisting of the compressor, the expansion
  • the fluid feeding mechanism uses as a target value a value calculated by dividing a degree of supercooling of the refrigerant in the vicinity of the condenser outlet by the difference between the condensing temperature ascertained by a detection value of the condensing temperature ascertaining means and a fluid temperature ascertained by a detection value of the fluid temperature sensing means.
  • the means of sensing the physical quantity includes, for example, not only sensing the temperature directly with a temperature sensor, but also converting the pressure sensed by a pressure sensor and the like to a temperature.
  • An air conditioner according to a second aspect of the invention is the air conditioner according to the first aspect of the invention that comprises a first fluid temperature ascertaining means and a second fluid temperature ascertaining means.
  • the first fluid temperature ascertaining means senses a physical quantity in order to derive the temperature of the fluid prior to exchanging heat with the refrigerant inside the condenser.
  • the second fluid temperature ascertaining means senses a physical quantity in order to derive the temperature of the fluid after exchanging heat with the refrigerant inside the condenser.
  • the control unit sets the condensing temperature to the temperature ascertained by calculating the average of the detection value of the first fluid temperature ascertaining means and the detection value of the second fluid temperature ascertaining means.
  • the COP can be improved even more because a condensing temperature suited to the calculation of the COP is obtained.
  • An air conditioner according a third aspect of the invention is the air conditioner according to the first or second aspects of the invention, wherein the target value is greater than or equal to 0.15 and less than 0.75.
  • the COP can be even more reliably improved even if ambient environmental conditions fluctuate during operation.
  • An air conditioner according a fourth aspect of the invention is an air conditioner according to the first or second aspects of the invention, wherein the target value is greater than or equal to 0.4 and less than 0.6.
  • the COP can be even more reliably improved even if ambient environmental conditions fluctuate during operation.
  • An air conditioner according to a fifth aspect of the invention is the air conditioner according to any of the first through third aspects of the invention, wherein the fluid temperature ascertaining means senses an outside air temperature in the state wherein the refrigerant circuit is undergoing a cooling operation cycle.
  • the outdoor heat exchanger functions as a condenser of the refrigerant during the cooling operation; however, by making the fluid temperature ascertaining means sense the outdoor temperature, the temperature of the air that passes through the outdoor heat exchanger, which functions as the condenser, can be sensed.
  • An air conditioner according to a sixth aspect of the invention is the air conditioner according to any of the first through fifth aspects of the invention, wherein the fluid temperature ascertaining means senses an indoor temperature in the state wherein the refrigerant circuit is undergoing a heating operation cycle.
  • the indoor heat exchanger functions as a condenser of the refrigerant during the heating operation; however, by making the fluid temperature ascertaining means sense the indoor temperature, the temperature of the air that passes through the indoor heat exchanger, which functions as the condenser, can be sensed.
  • the COP can be improved using a simple method of control even if usage conditions of the air conditioner fluctuate.
  • the COP can be improved even more because a condensing temperature suited to the calculation of the COP is obtained.
  • the COP can be more reliably improved even if ambient environmental conditions fluctuate during operation.
  • the COP can be more reliably improved even if ambient environmental conditions fluctuate during operation.
  • the temperature of the air that passes through an outdoor heat exchanger which functions as a condenser, can be sensed.
  • the temperature of the air that passes through an indoor heat exchanger which functions as a condenser, can be sensed.
  • FIG. 1 is a schematic drawing of an air conditioner 1 according to one embodiment of the present invention.
  • the air conditioner 1 is used to cool and heat an indoor space of, for example, a building by performing a vapor compression type refrigeration cycle operation.
  • the air conditioner 1 principally comprises: a single outdoor unit 2, which serves as a heat source unit; a plurality of indoor units 4, 5 (in the present embodiment, two), which are connected in parallel with the outdoor unit 2 and serve as utilization units; and a liquid refrigerant connection piping 6 and a gas refrigerant connection piping 7, which connect the outdoor unit 2 and the indoor units 4, 5 and serve as refrigerant connection pipings.
  • a vapor compression type refrigerant circuit 10 of the air conditioner 1 of the present embodiment is configured by the connection of the outdoor unit 2, the indoor units 4, 5, the liquid refrigerant connection piping 6, and the gas refrigerant connection piping 7.
  • the indoor units 4, 5 are, for example, embedded in or suspended from the indoor ceiling of a building or attached to an indoor wall surface.
  • the indoor units 4, 5 are connected to the outdoor unit 2 via the liquid refrigerant connection piping 6 and the gas refrigerant connection piping 7 and constitute part of the refrigerant circuit 10.
  • the indoor unit 4 principally comprises an indoor side refrigerant circuit 10a (in the indoor unit 5, an indoor side refrigerant circuit 10b ), which constitutes part of the refrigerant circuit 10.
  • the indoor side refrigerant circuit 10a principally comprises an indoor expansion valve 41, which serves as an expansion mechanism, and an indoor heat exchanger 42, which serves as a utilization side heat exchanger.
  • the indoor expansion valve 41 is a motor operated expansion valve that is connected to a liquid side of the indoor heat exchanger 42 and serves to, for example, regulate the flow volume of the refrigerant that flows inside the indoor side refrigerant circuit 10a; furthermore, the opening and closing of the indoor expansion valve 41 is controlled in accordance with a pulse signal.
  • a control unit 8 controls the indoor expansion valves 41, 51 by, for example, adjusting or fixing their degrees of opening, so as to optimize the COP of the refrigeration cycle.
  • the indoor heat exchanger 42 is a cross fin type fin and tube heat exchanger that comprises a heat transfer pipe and numerous fins and functions during the cooling operation as an evaporator of the refrigerant, thereby cooling the indoor air, and during the heating operation as a condenser of the refrigerant, thereby heating the indoor air.
  • the indoor unit 4 comprises an indoor fan 43, which serves as a ventilation fan that sucks the indoor air into the unit, exchanges heat between that air and the refrigerant via the indoor heat exchanger 42, and then supplies that air to the indoor space as supplied air.
  • the indoor fan 43 is capable of varying the volume of the air supplied to the indoor heat exchanger 42 and, in the present embodiment, is a centrifugal fan, a multiblade fan, or the like that is driven by a motor 43a, which has a DC fan motor.
  • the indoor unit 4 is provided with various sensors.
  • a liquid side temperature sensor 44 which detects the temperature of the refrigerant (i.e., the condensing temperature during the heating operation or the refrigerant temperature that corresponds to the evaporating temperature during the cooling operation), is provided to the liquid side of the indoor heat exchanger 42.
  • a gas side temperature sensor 45 which detects the temperature of the refrigerant, is provided to a gas side of the indoor heat exchanger 42.
  • An indoor temperature sensor 46 which detects the temperature of the indoor air (i.e., the indoor temperature) that flows into the unit, is provided to the indoor air inlet side of the indoor unit 4.
  • the outdoor unit 2 principally comprises an outdoor side coolant circuit 10c, which constitutes part of the refrigerant circuit 10.
  • the outdoor side coolant circuit 10c principally comprises: a compressor 21; a four-way switching valve 22; an outdoor heat exchanger 23, which serves as a heat source side heat exchanger; an outdoor expansion valve 38, which serves as an expansion mechanism; an accumulator 24; a supercooler 25, which serves as a temperature regulating mechanism; a liquid side shutoff valve 26; and a gas side shutoff valve 27.
  • the compressor 21 is capable of varying its operating capacity and, in the present embodiment, is a positive-displacement compressor that is driven by a motor 21a whose rotational speed is controlled by an inverter.
  • the four-way switching valve 22 switches the refrigerant's flow direction; furthermore, during the cooling operation, the four-way switching valve 22 can both connect a discharge side of the compressor 21 and a gas side of the outdoor heat exchanger 23 as well as an inlet side of the compressor 21 (specifically, the accumulator 24 ) and the gas refrigerant connection piping 7 side of the four-way switching valve 22 (refer to the solid lines of the four-way switching valve 22 in FIG.
  • the four-way switching valve 22 can both connect the discharge side of the compressor 21 and the gas refrigerant connection piping 7 side of the four-way switching valve 22 as well as the inlet side of the compressor 21 and the gas side of the outdoor heat exchanger 23 (refer to the broken lines of the four-way switching valve 22 in FIG.
  • both the indoor heat exchangers 42, 52 in order to cause both the indoor heat exchangers 42, 52 to function as condensers of the refrigerant compressed by the compressor 21 and the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42, 52.
  • the outdoor heat exchanger 23 is a cross fin type fin and tube heat exchanger that comprises a heat transfer pipe and numerous fins, functions as a condenser of the refrigerant during the cooling operation, and functions as an evaporator of the refrigerant during the heating operation.
  • the gas side of the outdoor heat exchanger 23 is connected to the four-way switching valve 22, and the liquid side of the outdoor heat exchanger 23 is connected to the liquid refrigerant connection piping 6.
  • the outdoor expansion valve 38 is a motor operated expansion valve that is connected to the liquid side of the outdoor heat exchanger 23 and serves to regulate the pressure, flow volume, and the like of the refrigerant that flows inside the outdoor side refrigerant circuit 10c.
  • the outdoor unit 2 comprises an outdoor fan 28, which serves as a ventilation fan for the purpose of sucking outdoor air into the unit, exchanging heat between that air and the refrigerant via the outdoor heat exchanger 23, and then discharging that air to the outdoor space.
  • the outdoor fan 28 is capable of varying the air volume Wo of the air supplied to the outdoor heat exchanger 23 and, in the present embodiment, is a propeller fan or the like that is driven by a motor 28a, which has a DC fan motor.
  • the accumulator 24 is a vessel that is connected to and disposed between the four-way switching valve 22 and the compressor 21 and is capable of accumulating surplus refrigerant generated inside the refrigerant circuit 10 in accordance with, for example, fluctuations in the operating loads of the indoor units 4, 5.
  • the supercooler 25 is a double pipe type heat exchanger that is provided in order to cool the refrigerant fed to the indoor expansion valves 41, 51 after the refrigerant has been condensed in the outdoor heat exchanger 23.
  • the supercooler 25 is connected to and disposed between the outdoor expansion valve 38 and the liquid side shutoff valve 26.
  • the present embodiment provides a bypass refrigerant circuit 61, which serves as a cooling source of the supercooler 25. Furthermore, in the explanation below, the portion of the refrigerant circuit 10 that excludes the bypass refrigerant circuit 61 is called a main refrigerant circuit for the sake of convenience.
  • the bypass refrigerant circuit 61 is connected to the main refrigerant circuit such that some of the refrigerant that is fed from the outdoor heat exchanger 23 to the indoor expansion valves 41, 51 branches off from the main refrigerant circuit and returns to the inlet side of the compressor 21.
  • the bypass expansion valve 62 has a motor operated expansion valve.
  • the refrigerant that is fed from the outdoor heat exchanger 23 to the indoor expansion valves 41, 51 is decompressed by the bypass expansion valve 62 and then is cooled by the refrigerant that flows through the bypass refrigerant circuit 61 in the supercooler 25.
  • the performance of the supercooler 25 is controlled by regulating the degree of opening of the bypass expansion valve 62.
  • the control unit 8 also controls the bypass expansion valve 62 by, for example, adjusting or fixing the degree of opening in order to optimize the COP of the refrigeration cycle during optimal COP control operation discussed below.
  • the liquid side shutoff valve 26 and the gas side shutoff valve 27 are provided to a connection port that connects to external equipment and piping (specifically, the liquid refrigerant connection piping 6 and the gas refrigerant connection piping 7 ).
  • the liquid side shutoff valve 26 is connected to the outdoor heat exchanger 23.
  • the gas side shutoff valve 27 is connected to the four-way switching valve 22.
  • a bypass temperature sensor 63 which serves to detect the temperature of the refrigerant that flows through the outlet on the bypass refrigerant circuit side of the supercooler 25, is provided to the merging circuit 61b of the bypass refrigerant circuit 61.
  • An outdoor temperature sensor 36 which detects the temperature of the outdoor air that flows inside the unit (i.e., the outdoor temperature), is provided to the outdoor air inlet side of the outdoor unit 2.
  • the inlet temperature sensor 31, the discharge temperature sensor 32, the heat exchanging temperature sensor 33, the liquid side temperature sensor 34, the liquid pipe temperature sensor 35, the outdoor temperature sensor 36, and the bypass temperature sensor 63 each has a thermistor.
  • control unit 8 is connected such that it can both receive the detection signals of the various sensors 29 to 36, 44 to 46, 54 to 56, 63 and can control the various equipment and valves 21, 22, 24,28a, 38, 41, 43a, 51, 62 based on these detection signals.
  • the refrigerant connection pipings 6, 7 are refrigerant pipings that are laid onsite when the air conditioner 1 is installed at an installation location, such as a building, and comprise pipes of various lengths and pipe diameters in accordance with the installation location and the installation conditions, such as the particular combination of outdoor units and indoor units to be configured.
  • control unit 8 (more specifically, the indoor side control units 47, 57, the outdoor side control unit 37, and the transmission line 8a that connects the control units 37, 47, 57 ) receives an instruction from, for example, the external remote control (not shown) to perform the cooling operation, then, during the refrigeration cycle, the control unit 8 controls the connection state of the four-way switching valve 22 such that the four-way switching valve 22 is in the state indicated by the solid lines in FIG. 1 , namely, the state wherein the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23 and, further, the inlet side of the compressor 21 is connected to the gas side of the indoor heat exchangers 42, 52 via the gas side shutoff valve 27 and the gas refrigerant connection piping 7.
  • the outdoor expansion valve 38 is set to the fully open state.
  • the liquid side shutoff valve 26 and the gas side shutoff valve 27 are set to an open state.
  • step S10 determines whether the value calculated in step S10 is 0.5 (i.e., step S20 ). Here, if the value calculated in step S10 is 0.5, then control continues as is.
  • step S10 the control unit 8 performs compensatory control by regulating the degree of opening of each of the indoor expansion valves 41, 51 and the degree of opening of the bypass expansion valve 62 such that the refrigeration cycle can be carried out in the state wherein the value calculated by dividing the degree of supercooling SCr by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta is 0.5 (i.e., step S30 ). Furthermore, the step S20 is repeated.
  • the control unit 8 calculates the degree of supercooling SCr of the refrigerant at the outlet of the outdoor heat exchanger 23 by subtracting the value sensed by the heat exchanging temperature sensor 33, which detects the temperature of the refrigerant flowing through the outdoor heat exchanger 23, from the value sensed by the liquid pipe temperature sensor 35, which detects the temperature of the refrigerant at the outlet of the supercooler 25 on the main refrigerant circuit side.
  • the control unit 8 uses the value sensed by the heat exchanging temperature sensor 33 of the outdoor heat exchanger 23 to ascertain the condensing temperature Tc of the refrigerant.
  • the control unit 8 uses the value sensed by the outdoor temperature sensor 36 of the outdoor unit 2 to ascertain a temperature Ta of the outdoor air.
  • the control unit 8 activates the compressor 21, the outdoor fan 28, and the indoor fans 43, 53. In so doing, low pressure gas refrigerant is sucked into and compressed by the compressor 21, thereby turning into high pressure gas refrigerant. Subsequently, the high pressure gas refrigerant is fed to the outdoor heat exchanger 23 via the four-way switching valve 22, is condensed by the exchange of its heat with the outdoor air supplied by the outdoor fan 28, and turns into high pressure liquid refrigerant.
  • this high pressure liquid refrigerant passes through the outdoor expansion valve 38, flows into the supercooler 25, exchanges heat with the refrigerant that flows through the bypass refrigerant circuit 61, and thereby is further cooled such that it transitions to the supercooled state.
  • some of the high pressure liquid refrigerant condensed in the outdoor heat exchanger 23 branches to the bypass refrigerant circuit 61 and, after its pressure is reduced by the bypass expansion valve 62, returns to the inlet side of the compressor 21.
  • that portion of the refrigerant that passes through the bypass expansion valve 62 evaporates as a result of its pressure being reduced to a level close to that of the inlet pressure of the compressor 21.
  • the refrigerant that flows from the outlet of the bypass expansion valve 62 of the bypass refrigerant circuit 61 toward the inlet side of the compressor 21 passes through the supercooler 25 and exchanges heat with the high pressure liquid refrigerant that is fed from the outdoor heat exchanger 23 on the main refrigerant circuit side to the indoor units 4, 5.
  • the high pressure liquid refrigerant which is now in a supercooled state, transits the liquid side shutoff valve 26 and the liquid refrigerant connection piping 6 and is fed to the indoor units 4, 5.
  • the indoor expansion valves 41, 51 reduce the pressure of the high pressure liquid refrigerant fed to the indoor units 4, 5 such that this pressure almost reaches the inlet pressure of the compressor 21, and thereby the high pressure liquid refrigerant turns into low pressure refrigerant in the vapor-liquid two-phase state, is subsequently fed to the indoor heat exchangers 42, 52, exchanges heat with the indoor air via the indoor heat exchangers 42, 52, evaporates, and turns into low pressure gas refrigerant.
  • This low pressure gas refrigerant transits the gas refrigerant connection piping 7, is fed to the outdoor unit 2, transits the gas side shutoff valve 27 and the four-way switching valve 22, and flows into the accumulator 24. Furthermore, the low pressure gas refrigerant that flows into the accumulator 24 is once again sucked into the compressor 21.
  • the control unit 8 performs the abovementioned optimal COP control operation during the cooling operation by regulating the degree of opening of each of the indoor expansion valves 41, 51 and of the bypass expansion valve 62 and thereby can optimize the coefficient of performance (COP) during the cooling operation.
  • control unit 8 sets the liquid side shutoff valve 26 and the gas side shutoff valve 27 to the open state and closes the bypass expansion valve 62.
  • control unit 8 regulates the degree of opening of the outdoor expansion valve 38.
  • control unit 8 In optimal COP control during the heating operation, too, as in the cooling operation, the control unit 8 first calculates a value by dividing a degree of supercooling SCr by the difference between a condensing temperature Tc of the refrigerant and an air temperature Ta, as shown in the flow chart in FIG. 3 (i.e., step S10 ).
  • step S10 determines whether the value calculated in step S10 is 0.5 (i.e., step S20 ). Here, if the value calculated in step S10 is 0.5, then control continues as is.
  • step S10 if the value calculated in step S10 is not 0.5, then the control unit 8 performs compensatory control by regulating the degree of opening of each of the indoor expansion valves 41, 51 such that the refrigeration cycle can be carried out in the state wherein the value calculated by dividing the degree of supercooling SCr by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta is 0.5. Furthermore, the step S20 is repeated.
  • each value is detected as described below.
  • the control unit 8 detects the degree of supercooling SCr of the refrigerant at the outlet of each of the indoor heat exchangers 42, 52 by converting the discharge pressure of the compressor 21 detected by the discharge pressure sensor 30 to the saturation temperature value that corresponds to the condensing temperature and then subtracting the refrigerant temperature value detected by the liquid side temperature sensors 44, 54 from this refrigerant saturation temperature value.
  • the control unit 8 uses the value sensed by the liquid side temperature sensors 44, 54 of the indoor heat exchangers 42, 52 to ascertain the condensing temperature Tc of the refrigerant.
  • the control unit 8 uses the value sensed by the indoor temperature sensors 46, 56 of the indoor units 4, 5 to ascertain the temperature Ta of the indoor air.
  • control unit 8 activates the compressor 21, the outdoor fan 28, and the indoor units 43, 53 when the refrigerant circuit 10 is in this state, the low pressure gas refrigerant is sucked into and compressed by the compressor 21, turns into a high pressure gas refrigerant, and is then fed to the indoor units 4, 5 via the four-way switching valve 22, the gas side shutoff valve 27, and the gas refrigerant connecting pipe 7.
  • the high pressure gas refrigerant fed to the indoor units 4, 5 exchanges heat with the indoor air in the indoor heat exchangers 42, 52 and is thereby condensed and transitions to high pressure liquid refrigerant, after which it passes through the indoor expansion valves 41, 51, at which time its pressure is reduced in accordance with the degree of opening of each of the indoor expansion valves 41, 51.
  • the refrigerant that passes through the indoor expansion valves 41, 51 is fed to the outdoor unit 2 via the liquid refrigerant connection piping 6, the refrigerant's pressure is further reduced via the liquid side shutoff valve 26, the supercooler 25, and the outdoor expansion valve 38, and the refrigerant then flows into the outdoor heat exchanger 23. Furthermore, the vapor-liquid two-phase low pressure refrigerant that flows into the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied by the outdoor fan 28, evaporates, turns into low pressure gas refrigerant, transits the four-way switching valve 22, and flows into the accumulator 24. Furthermore, the low pressure gas refrigerant that flows into the accumulator 24 is once again sucked into the compressor 21.
  • the control unit 8 performs the abovementioned optimal COP control operation during the heating operation by regulating the degree of opening of each of the indoor expansion valves 41, 51 and thereby can optimize the coefficient of performance (COP) during the heating operation.
  • the air conditioner 1 of the present embodiment has the following features.
  • a degree of supercooling index that enables COP optimization is defined, and control is performed such that the degree of supercooling remains constant at the value of this index.
  • the relationship between the COP and a degree of supercooling SC corresponds to the state in which the air conditioner is driven, which is not particularly exceptional. Namely, the optimal degree of supercooling during the cooling rated operation is 7 degree, during the cooling season operation is 3 degree, during the heating rated operation is 9 degree, and during the heating season operation is 4 degree. Furthermore, if the refrigeration cycle is controlled using a specific value as the target degree of supercooling, then the optimal degree of supercooling will vary with the conditions, thereby making it impossible to optimize the COP.
  • the outside air temperature is in the range of 18°C through 20°C during the cooling season and in the range of 13°C through 18°C during the heating season.
  • control unit 8 performs control wherein the degree of opening of, for example, each of the indoor expansion valves 41, 51 is regulated such that the refrigeration cycle can be performed in the state wherein the value calculated by dividing the degree of supercooling SCr by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta is 0.5.
  • the value calculated by dividing the degree of supercooling SCr by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta is 0.5.
  • control unit 8 performs optimal COP control such that the value calculated by dividing the degree of supercooling by the difference between the condensing temperature and the air temperature is 0.5, which makes it possible both to optimize the COP using a simple method of control-that is, merely by setting a single value to a target of 0.5 without maintaining a target value for every condition-and to save energy, whether during the cooling rated operation, the cooling season operation, the heating operation, or the heating season operation.
  • an optimal AFP control may be performed.
  • the optimal AFP control for example, controlls the degree of opening of each of the indoor expansion valves 41, 51 such that a AFP related target value falls within a specified range.
  • the range of the AFP related target value which can yield a satisfactory AFP may be specified by comparing the AFP with a value (i.e., the AFP related target value) obtained by dividing the degree of supercooling SCr by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta.
  • a range may be derived such that an APF ratio indicated by the ordinate in FIG. 8 is 100% or greater.
  • This APF ratio is called the APF ratio at each degree of supercooling (SC) when the APF is 100% at a certain degree of supercooling (SC).
  • This APF is a value that indicates the cooling and heating capacity per 1 KW of power consumption when an air conditioner is operated for one year under certain fixed conditions.
  • APF can be calculated more finely by, for example, complying with the conditions specified in JRA 4048:2006 (i.e., the standard for implementing JIS B8616:2006) created by the Japan Refrigeration and Air Conditioning Industry Association Standards.
  • each calculated weighting factor is multiplied by the corresponding COP ratio-that is, the COP ratio during the cooling rated operation, the COP ratio during the cooling season operation, the COP ratio during the heating rated operation, the COP ratio during the heating season operation, and the COP ratio during the heating low temperature operation-these values are totaled, and thereby the APF ratio is obtained as a value that can fully evaluate the aggregate of cooling and heating.
  • the present invention is not limited thereto; for example, so that values suited to, for example, the season and operating environmental conditions for the COP related target value, the APF related target value, discussed in the modified example (G) section can be used, control may be performed such that, for example, the COP related target value and the APF related target value are modified according to the season, the operating environmental conditions, and the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Claims (6)

  1. Klimaanlage (1), umfassend:
    einen Kältemittelkreislauf (10), der einen Kompressor (21), einen Kondensator (23), einen Expansionsmechanismus (41, 51) und einen Verdampfer (42, 52) umfasst und verbindet, sodass ein Kältemittel darin zirkuliert;
    einen Fluidzuführmechanismus (28), der dem Kondensator (23) ein Fluid zuführt;
    ein Mittel zur Ermittlung einer Kondensationstemperatur (33), das eine physikalische Menge misst, um eine Kondensationstemperatur des Kältemittels abzuleiten;
    ein Mittel zur Ermittlung einer Fluidtemperatur (36), das eine physikalische Menge misst, um die Temperatur des Fluids abzuleiten, wobei das Fluid mit dem Kältemittel innerhalb des Kondensators (23) Wärme tauscht; gekennzeichnet durch
    eine Steuereinheit (8), die mindestens ein Element steuert, ausgewählt aus der Gruppe bestehend aus dem Kompressor (21), dem Expansionsmechanismus (41, 51) und dem Fluidzuführmechanismus (28), unter Verwendung als ein Zielwert eines Werts, der durch Dividieren eines Grads von Unterkühlung des Kältemittels in der Nähe eines Auslasses des Kondensators durch die Differenz zwischen der Kondensationstemperatur, die durch einen Erfassungswert des Mittels zur Ermittlung einer Kondensationstemperatur (33) ermittelt wird, und einer Fluidtemperatur, die durch einen Erfassungswert des Mittels zum Messen einer Fluidtemperatur (36) ermittelt wird, berechnet wird.
  2. Klimaanlage (1) nach Anspruch 1, wobei
    das Mittel zur Ermittlung einer Fluidtemperatur (36) ein erstes Mittel zur Ermittlung einer Fluidtemperatur (361), das eine physikalische Menge misst, um die Temperatur des Fluids vor Wärmetausch mit dem Kältemittel innerhalb des Kondensators (23) abzuleiten, und ein zweites Mittel zur Ermittlung einer Fluidtemperatur (362) umfasst, das eine physikalische Menge misst, um die Temperatur des Fluids nach Wärmetausch mit dem Kältemittel innerhalb des Kondensators (23) abzuleiten; und
    die Steuereinheit (8) die Kondensationstemperatur auf die Temperatur einstellt, die durch Berechnen des Durchschnitts des Erfassungswerts des ersten Mittels zum Feststellen einer Fluidtemperatur (36a) und des Erfassungswerts des zweiten Mittels zum Feststellen einer Fluidtemperatur (36b) festgestellt wird.
  3. Klimaanlage (1) nach Anspruch 1 oder Anspruch 2, wobei
    der Zielwert größer als oder gleich 0,15 und kleiner als 0,75 ist.
  4. Klimaanlage (1) nach Anspruch 1 oder Anspruch 2, wobei
    der Zielwert größer als oder gleich 0,4 und kleiner als 0,6 ist.
  5. Klimaanlage (1) nach einem der Ansprüche 1 bis 3, wobei
    das Mittel zur Ermittlung einer Fluidtemperatur (36) eine Außenlufttemperatur in dem Zustand misst, wobei der Kältemittelkreislauf (10) einen Kühlbetriebszyklus durchläuft.
  6. Klimaanlage (1) nach einem der Ansprüche 1 bis 5, wobei
    das Mittel zur Ermittlung einer Fluidtemperatur (36) eine Innenraumtemperatur in dem Zustand misst, wobei der Kältemittelkreislauf (10) einen Wärmebetriebszyklus durchläuft.
EP08837535.7A 2007-10-10 2008-10-10 Klimaanlage Active EP2211123B1 (de)

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JP2007264615 2007-10-10
PCT/JP2008/002865 WO2009047906A1 (ja) 2007-10-10 2008-10-10 空気調和装置

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JP5171924B2 (ja) * 2010-10-29 2013-03-27 三菱電機株式会社 空気調和装置
EP2844924B1 (de) * 2012-05-03 2019-04-03 Carrier Corporation Klimaanlage mit supergekühltem speicherstoff
CN103115417B (zh) * 2013-03-19 2015-04-01 海尔集团公司 低温环境空调器的制冷方法
JP5979112B2 (ja) * 2013-09-30 2016-08-24 ダイキン工業株式会社 冷凍装置
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ES2716469T3 (es) 2019-06-12
AU2008310483B2 (en) 2011-09-08
CN101821560A (zh) 2010-09-01
WO2009047906A1 (ja) 2009-04-16
JP5056855B2 (ja) 2012-10-24
CN101821560B (zh) 2015-02-04
EP2211123A1 (de) 2010-07-28
AU2008310483A1 (en) 2009-04-16
EP2211123A4 (de) 2012-07-18

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