EP2211123A1 - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- EP2211123A1 EP2211123A1 EP08837535A EP08837535A EP2211123A1 EP 2211123 A1 EP2211123 A1 EP 2211123A1 EP 08837535 A EP08837535 A EP 08837535A EP 08837535 A EP08837535 A EP 08837535A EP 2211123 A1 EP2211123 A1 EP 2211123A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- temperature
- refrigerant
- outdoor
- indoor
- fluid
- 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.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 172
- 238000004781 supercooling Methods 0.000 claims abstract description 47
- 239000012530 fluid Substances 0.000 claims abstract description 44
- 238000010438 heat treatment Methods 0.000 claims description 37
- 238000001816 cooling Methods 0.000 claims description 35
- 230000007246 mechanism Effects 0.000 claims description 14
- 238000001514 detection method Methods 0.000 claims description 11
- 239000007788 liquid Substances 0.000 description 43
- 230000006870 function Effects 0.000 description 13
- 238000005057 refrigeration Methods 0.000 description 13
- 230000001276 controlling effect Effects 0.000 description 7
- 230000001105 regulatory effect Effects 0.000 description 7
- 230000007613 environmental effect Effects 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 239000000470 constituent Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000001447 compensatory effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
Images
Classifications
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- 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
- 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 mechanism, and the fluid feeding mechanism using 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. 9 is a conventional graph showing the coefficient of performance versus the degree of supercooling.
- 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 liquid side temperature sensor 44, the gas side temperature sensor 45, and the indoor temperature sensor 46 each has a thermistor.
- the indoor unit 4 comprises an indoor side control unit 47, which controls the operation of all parts that constitute the indoor unit 4.
- the indoor side control unit 47 comprises a microcomputer, memory, and the like, which are provided so that the indoor side control unit 47 can control the indoor unit 4; furthermore, the indoor side control unit 47 can exchange both control signals with a remote control (not shown), which is for the purpose of separately operating the indoor unit 4, and control signals and the like with the outdoor unit 2 via a transmission line 8a .
- the outdoor unit 2 is installed on the outside of a building, is connected to the indoor units 4, 5 via the liquid refrigerant connection piping 6 and the gas refrigerant connection piping 7, and constitutes the refrigerant circuit 10 between the indoor units 4, 5.
- 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 refrigerant circuit 61 comprises: a branching circuit 61a, which is connected such that some of the refrigerant that is fed from the outdoor expansion valve 38 to the indoor expansion valves 41, 51 branches from a position between the outdoor heat exchanger 23 and the supercooler 25; and a merging circuit 61b, which is connected to the inlet side of the compressor 21 such that the refrigerant returns from an outlet on the bypass refrigerant circuit side of the supercooler 25 to the inlet side of the compressor 21. Furthermore, a bypass expansion valve 62, which serves to regulate the flow volume of the refrigerant that flows through the bypass refrigerant circuit 61, is provided to the branching circuit 61a.
- 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.
- various sensors are provided to the outdoor unit 2. Specifically, an inlet pressure sensor 29, which detects an inlet pressure of the compressor 21, a discharge pressure sensor 30, which detects a discharge pressure of the compressor 21, an inlet temperature sensor 31, which detects an inlet temperature Ts of the compressor 21, and a discharge temperature sensor 32, which detects a discharge temperature Td of the compressor 21, are provided to the outdoor unit 2.
- the inlet temperature sensor 31 is provided at a position between the accumulator 24 and the compressor 21.
- a heat exchanging temperature sensor 33 which detects the temperature of the refrigerant that flows inside the outdoor heat exchanger 23 (i.e., the refrigerant temperature that corresponds to the condensing temperature during the cooling operation or the evaporating temperature during the heating operation) is provided to the outdoor heat exchanger 23.
- a liquid side temperature sensor 34 which detects the temperature of the refrigerant, is provided to the liquid side of the outdoor heat exchanger 23.
- a liquid pipe temperature sensor 35 which detects the temperature of the refrigerant (i.e., a liquid pipe temperature), is provided to an outlet on the main refrigerant circuit side of the supercooler 25.
- 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.
- the outdoor unit 2 comprises an outdoor side control unit 37, which controls the operation of all parts that constitute the outdoor unit 2.
- the outdoor side control unit 37 comprises, for example, a microcomputer and memory, which are provided to control the outdoor unit 2, and an inverter circuit, which controls the motor 21a, and is capable of exchanging control signals and the like with the indoor side unit 47 in the indoor unit 4 and the indoor side unit 57 in the indoor unit 5 via the transmission line 8a.
- the control unit 8, which controls the operation of the entire air conditioner 1 comprises the indoor side control units 47, 57, the outdoor side control unit 37, and the transmission line 8a, which connects the control units 37, 47, 57.
- the 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.
- the control unit 8 which comprises the indoor side control units 47, 57 and the outdoor side control unit 37, both switches between the cooling operation and the heating operation via the four-way switching valve 22 and controls each piece of equipment of the outdoor unit 2 and the indoor units 4, 5 in accordance with the operating load of each of the indoor units 4, 5.
- 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.
- 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.
- control unit 8 In optimal COP control during 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 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.
- each value is detected as described below.
- 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 (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, an external remote control (not shown) to perform the heating 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 broken lines in FIG. 1 , namely, the state wherein the discharge 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 and, further, the inlet side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23.
- 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.
- control unit 8 controls the degree of opening of each of the indoor expansion valves 41, 51 such that 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 control unit 8 may derive a target coordinate value (S) that is closest to a coordinate value (P) of an actual measured value in the current state and may perform various types of control, such as controlling the indoor expansion valves 41, 51, the bypass expansion valve 62, and the like, controlling the rotational speed of the motor 43a of the indoor fan 43, controlling the rotational speed of the motor 21a of the compressor 21, controlling both the adjustment and fixing of the degree of opening of the outdoor expansion valve 38, controlling the rotational speed of the motor 28a of the outdoor fan 28, and so on, such that the degree of supercooling and the condensing temperature at the target coordinate value (S) are achieved.
- various types of control such as controlling the indoor expansion valves 41, 51, the bypass expansion valve 62, and the like, controlling the rotational speed of the motor 43a of the indoor fan 43, controlling the rotational speed of the motor 21a of the compressor 21, controlling both the adjustment and fixing of the degree of opening of the outdoor expansion valve 38, controlling the rotational speed of the motor 28a of the outdoor fan 28, and so on
- control unit 8 detects the degree of supercooling SCr by calculating the degree of supercooling SCr through 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 the refrigerant's saturation temperature value.
- the present invention is not limited thereto; for example, temperature sensors that detect the temperature of the refrigerant flowing inside each of the indoor heat exchangers 42, 52 may be provided in advance, and the control unit 8 may detect the degree of supercooling SCr of the refrigerant at the outlets of the indoor heat exchangers 42, 52 by calculating the degree of supercooling SCr of optimal COP control during the heating operation through subtracting the refrigerant temperature value that corresponds to the condensing temperature detected by the temperature sensors from the refrigerant temperature value detected by the liquid side temperature sensors 44, 54.
- optimal COP control operation may be performed using the average of values obtained by two temperature sensors per heat exchanger as the air temperature Ta.
- a pre-passage outdoor temperature sensor 361 which senses the indoor temperature before air passes through the outdoor heat exchanger 23, and a post-passage outdoor temperature sensor 362, which senses the temperature of the air after the air has passed through the outdoor heat exchanger 23 and exchanged heat, may be provided, and the average of the detection values sensed by these sensors may be used as the value of the air temperature Ta.
- the present invention is not limited thereto; for example, optimal COP control may be performed as it is in the abovementioned embodiment, but on a refrigeration cycle that comprises, for example, only the main refrigerant circuit and not the bypass refrigerant circuit 61 discussed above. In this case as well, it is possible to achieve the energy saving effect of the present invention.
- the air conditioner may be a water cooled type wherein water is used as the fluid that passes through the heat exchanger.
- control unit 8 controls the degree of opening of each of the indoor expansion valves 41, 51 such that 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 may control the degree of opening of each of the indoor expansion valves 41, 51 such that 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 falls within a range of greater than or equal to 0.4 and less than 0.6. Even in this case, it is possible to achieve the same effects as those achieved in the abovementioned embodiments.
- a COP related target value that can yield a satisfactory COP ratio is specified by comparing the value (i.e., the COP 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 with the COP ratio (i.e., the COP ratio at each degree of supercooling ( SC ) for the case wherein the COP is 100% at a certain degree of supercooling ( SC )), and then controlling the degree of opening of each of the indoor expansion valves 41, 51 such that the COP related target value falls within the specified range.
- the value i.e., the COP 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
- the COP ratio i.e., the COP ratio at each degree of supercooling ( SC ) for the case wherein the COP is 100% at a certain degree of supercooling ( SC )
- 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.
- performing an evaluation that is closer to actual usage-by performing optimal APF control that targets a satisfactory APF value-than can be achieved using the COP-which evaluates the performance for a case (i.e., the rated condition) wherein operation is performed under a certain constant temperature condition-makes it possible to obtain a greater energy saving effect.
- control unit 8 controls the degree of opening of each of the indoor expansion valves 41 , 51 such that the value calculated by dividing by the difference between the condensing temperature Tc of the refrigerant and the air temperature Ta is 0.5.
- 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.
- operation may be performed wherein two different COP related target values and two different APF related target values-one for the circuit connection state wherein the cooling operation is performed and one for the circuit connection state wherein the heating operation is performed-are prescribed.
- the present invention is particularly useful for operating an air conditioner such that it saves energy under various conditions, thereby optimizing the COP even when usage conditions vary.
Abstract
Description
- The present invention relates to the control of an air conditioner's operation such that the air conditioner's coefficient of performance is optimized.
- In 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).
- Accordingly, in an air conditioner described in
Patent Document 1 below, for example, controlling each component in the refrigerant circuit such that a degree of supercooling remains constant at a target value improves the COP. -
Patent Document 1
Japanese Unexamined Patent Application Publication No.2001-263831 - However, because the target degree of supercooling differs both between a cooling operation and a heating operation and in accordance with the output during these operations, the air conditioner control recited in the
abovementioned Patent Document 1 cannot optimize the COP under various conditions. - 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 according to a first aspect of the invention 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 mechanism, and the fluid feeding mechanism using 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.
- Furthermore, herein, 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.
- Here, it is possible to improve the COP using a simple method of control even if the usage conditions of the air conditioner fluctuate.
- 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. Furthermore, 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.
- Here, 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.
- Here, 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.
- Here, 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.
- Here, 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.
- Here, 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.
- In an air conditioner according to the first aspect of the invention, the COP can be improved using a simple method of control even if usage conditions of the air conditioner fluctuate.
- In an air conditioner according to the second aspect of the invention, the COP can be improved even more because a condensing temperature suited to the calculation of the COP is obtained.
- In an air conditioner according to the third aspect of the invention, the COP can be more reliably improved even if ambient environmental conditions fluctuate during operation.
- In an air conditioner according to the fourth aspect of the invention, the COP can be more reliably improved even if ambient environmental conditions fluctuate during operation.
- In an air conditioner according to the fifth aspect of the invention, the temperature of the air that passes through an outdoor heat exchanger, which functions as a condenser, can be sensed.
- In an air conditioner according to the sixth aspect of the invention, 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 view of an air conditioner according to one embodiment of the present invention. -
FIG. 2 is a control block diagram of the air conditioner. -
FIG. 3 is a control flow chart showing a flow when an optimal COP control operation is performed. -
FIG. 4 is a graph showing a coefficient of performance versus a value that is calculated by dividing a degree of supercooling by the difference between a condensing temperature and an air temperature. -
FIG. 5 is a graph showing a relationship between the condensing temperature and the degree of supercooling that satisfies a prescribed relationship. -
FIG. 6 is a schematic drawing of the air conditioner according to a modified example (C). -
FIG. 7 is a control block diagram of the air conditioner according to the modified example (C). -
FIG. 8 is a graph showing for an air conditioner according to a modified example (G), an APF ratio versus the value that is calculated by dividing the degree of supercooling by the difference between the condensing temperature and the air temperature. -
FIG. 9 is a conventional graph showing the coefficient of performance versus the degree of supercooling. -
- 1
- Air conditioner
- 8
- Control unit
- 10
- Refrigerant circuit
- 21
- Compressor
- 23
- Outdoor heat exchanger (condenser)
- 28
- Outdoor fan (fluid feeding mechanism)
- 33
- Heat exchanging temperature sensor (condensing temperature ascertaining means)
- 36
- Outdoor temperature sensor (fluid)
- 361
- Pre-passage outdoor temperature sensor (first fluid temperature ascertaining means)
- 362
- Post-passage outdoor temperature sensor (second fluid temperature ascertaining means)
- 41, 51
- Indoor expansion valves (expansion mechanisms)
- 42, 52
- Indoor heat exchangers (evaporators)
- The following text explains the embodiments of an air conditioner according to the present invention, referencing the drawings.
-
FIG. 1 is a schematic drawing of anair 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. Theair conditioner 1 principally comprises: a singleoutdoor unit 2, which serves as a heat source unit; a plurality ofindoor units 4, 5 (in the present embodiment, two), which are connected in parallel with theoutdoor unit 2 and serve as utilization units; and a liquid refrigerant connection piping 6 and a gas refrigerant connection piping 7, which connect theoutdoor unit 2 and theindoor units type refrigerant circuit 10 of theair conditioner 1 of the present embodiment is configured by the connection of theoutdoor unit 2, theindoor units refrigerant connection piping 7. - The
indoor units indoor units outdoor unit 2 via the liquid refrigerant connection piping 6 and the gas refrigerant connection piping 7 and constitute part of therefrigerant circuit 10. - The following text explains the configuration of the
indoor units indoor unit 4 and theindoor unit 5 are configured similarly, only the configuration of theindoor unit 4 will be explained herein; in addition, the constituent parts of theindoor unit 5 are assigned reference numerals in the 50s instead of the 40s, which are used for the constituent components of theindoor unit 4, and the explanation of each constituent part of theindoor unit 5 is omitted. - The
indoor unit 4 principally comprises an indoor siderefrigerant circuit 10a (in theindoor unit 5, an indoor siderefrigerant circuit 10b), which constitutes part of therefrigerant circuit 10. The indoor siderefrigerant circuit 10a principally comprises anindoor expansion valve 41, which serves as an expansion mechanism, and an indoor heat exchanger 42, which serves as a utilization side heat exchanger. - In the present embodiment, 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 siderefrigerant circuit 10a; furthermore, the opening and closing of theindoor expansion valve 41 is controlled in accordance with a pulse signal. During the optimal COP control operation discussed below, acontrol unit 8 controls theindoor expansion valves - In the present embodiment, 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.
- In the present embodiment, 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 amotor 43a, which has a DC fan motor. - In addition, 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 gasside temperature sensor 45, which detects the temperature of the refrigerant, is provided to a gas side of the indoor heat exchanger 42. Anindoor 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 theindoor unit 4. In the present embodiment, the liquid side temperature sensor 44, the gasside temperature sensor 45, and theindoor temperature sensor 46 each has a thermistor. In addition, theindoor unit 4 comprises an indoorside control unit 47, which controls the operation of all parts that constitute theindoor unit 4. Furthermore, the indoorside control unit 47 comprises a microcomputer, memory, and the like, which are provided so that the indoorside control unit 47 can control theindoor unit 4; furthermore, the indoorside control unit 47 can exchange both control signals with a remote control (not shown), which is for the purpose of separately operating theindoor unit 4, and control signals and the like with theoutdoor unit 2 via atransmission line 8a. - The
outdoor unit 2 is installed on the outside of a building, is connected to theindoor units refrigerant circuit 10 between theindoor units - The following text explains the configuration of the
outdoor unit 2. Theoutdoor unit 2 principally comprises an outdoorside coolant circuit 10c, which constitutes part of therefrigerant circuit 10. The outdoorside coolant circuit 10c principally comprises: acompressor 21; a four-way switching valve 22; anoutdoor heat exchanger 23, which serves as a heat source side heat exchanger; anoutdoor expansion valve 38, which serves as an expansion mechanism; anaccumulator 24; asupercooler 25, which serves as a temperature regulating mechanism; a liquidside shutoff valve 26; and a gasside 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 amotor 21a whose rotational speed is controlled by an inverter. In the present embodiment, there is only onecompressor 21, but the present invention is not limited thereto; two or more compressors may be connected in parallel in accordance with, for example, the number of indoor units connected. - 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. 1 ) in order to cause both the outdoor heat exchanger 23 to function as a condenser of the refrigerant compressed by the compressor 21 and the indoor heat exchangers 42, 52 to function as evaporators of the refrigerant condensed in the outdoor heat exchanger 23; in addition, during the heating operation, 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 inFIG. 1 ) 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. - In the present embodiment, 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 theoutdoor heat exchanger 23 is connected to the four-way switching valve 22, and the liquid side of theoutdoor heat exchanger 23 is connected to the liquidrefrigerant connection piping 6. - In the present embodiment, the
outdoor expansion valve 38 is a motor operated expansion valve that is connected to the liquid side of theoutdoor heat exchanger 23 and serves to regulate the pressure, flow volume, and the like of the refrigerant that flows inside the outdoor siderefrigerant circuit 10c. - In the present embodiment, the
outdoor unit 2 comprises anoutdoor 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 theoutdoor heat exchanger 23, and then discharging that air to the outdoor space. Theoutdoor fan 28 is capable of varying the air volume Wo of the air supplied to theoutdoor heat exchanger 23 and, in the present embodiment, is a propeller fan or the like that is driven by amotor 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 thecompressor 21 and is capable of accumulating surplus refrigerant generated inside therefrigerant circuit 10 in accordance with, for example, fluctuations in the operating loads of theindoor units - In the present embodiment, the
supercooler 25 is a double pipe type heat exchanger that is provided in order to cool the refrigerant fed to theindoor expansion valves outdoor heat exchanger 23. In the present embodiment, thesupercooler 25 is connected to and disposed between theoutdoor expansion valve 38 and the liquidside shutoff valve 26. - The present embodiment provides a
bypass refrigerant circuit 61, which serves as a cooling source of thesupercooler 25. Furthermore, in the explanation below, the portion of therefrigerant circuit 10 that excludes thebypass 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 theoutdoor heat exchanger 23 to theindoor expansion valves compressor 21. Specifically, thebypass refrigerant circuit 61 comprises: a branchingcircuit 61a, which is connected such that some of the refrigerant that is fed from theoutdoor expansion valve 38 to theindoor expansion valves outdoor heat exchanger 23 and thesupercooler 25; and a mergingcircuit 61b, which is connected to the inlet side of thecompressor 21 such that the refrigerant returns from an outlet on the bypass refrigerant circuit side of thesupercooler 25 to the inlet side of thecompressor 21. Furthermore, abypass expansion valve 62, which serves to regulate the flow volume of the refrigerant that flows through thebypass refrigerant circuit 61, is provided to the branchingcircuit 61a. Here, thebypass expansion valve 62 has a motor operated expansion valve. Thereby, the refrigerant that is fed from theoutdoor heat exchanger 23 to theindoor expansion valves bypass expansion valve 62 and then is cooled by the refrigerant that flows through thebypass refrigerant circuit 61 in thesupercooler 25. Namely, the performance of thesupercooler 25 is controlled by regulating the degree of opening of thebypass expansion valve 62. Furthermore, thecontrol unit 8 also controls thebypass 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 gasside 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 liquidside shutoff valve 26 is connected to theoutdoor heat exchanger 23. The gasside shutoff valve 27 is connected to the four-way switching valve 22. - In addition, various sensors are provided to the
outdoor unit 2. Specifically, aninlet pressure sensor 29, which detects an inlet pressure of thecompressor 21, adischarge pressure sensor 30, which detects a discharge pressure of thecompressor 21, aninlet temperature sensor 31, which detects an inlet temperature Ts of thecompressor 21, and adischarge temperature sensor 32, which detects a discharge temperature Td of thecompressor 21, are provided to theoutdoor unit 2. Theinlet temperature sensor 31 is provided at a position between theaccumulator 24 and thecompressor 21. A heat exchangingtemperature sensor 33, which detects the temperature of the refrigerant that flows inside the outdoor heat exchanger 23 (i.e., the refrigerant temperature that corresponds to the condensing temperature during the cooling operation or the evaporating temperature during the heating operation) is provided to theoutdoor heat exchanger 23. A liquidside temperature sensor 34, which detects the temperature of the refrigerant, is provided to the liquid side of theoutdoor heat exchanger 23. A liquidpipe temperature sensor 35, which detects the temperature of the refrigerant (i.e., a liquid pipe temperature), is provided to an outlet on the main refrigerant circuit side of thesupercooler 25. Abypass temperature sensor 63, which serves to detect the temperature of the refrigerant that flows through the outlet on the bypass refrigerant circuit side of thesupercooler 25, is provided to the mergingcircuit 61b of thebypass refrigerant circuit 61. Anoutdoor 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 theoutdoor unit 2. - In the present embodiment, the
inlet temperature sensor 31, thedischarge temperature sensor 32, the heat exchangingtemperature sensor 33, the liquidside temperature sensor 34, the liquidpipe temperature sensor 35, theoutdoor temperature sensor 36, and thebypass temperature sensor 63 each has a thermistor. - In addition, the
outdoor unit 2 comprises an outdoorside control unit 37, which controls the operation of all parts that constitute theoutdoor unit 2. Furthermore, the outdoorside control unit 37 comprises, for example, a microcomputer and memory, which are provided to control theoutdoor unit 2, and an inverter circuit, which controls themotor 21a, and is capable of exchanging control signals and the like with theindoor side unit 47 in theindoor unit 4 and theindoor side unit 57 in theindoor unit 5 via thetransmission line 8a. Namely, thecontrol unit 8, which controls the operation of theentire air conditioner 1, comprises the indoorside control units side control unit 37, and thetransmission line 8a, which connects thecontrol units - As shown in
FIG. 2 , which is a control block diagram of theair conditioner 1, thecontrol unit 8 is connected such that it can both receive the detection signals of thevarious sensors 29 to 36, 44 to 46, 54 to 56, 63 and can control the various equipment andvalves - The
refrigerant connection pipings 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. - As described above, in the
air conditioner 1 of the present embodiment, thecontrol unit 8, which comprises the indoorside control units side control unit 37, both switches between the cooling operation and the heating operation via the four-way switching valve 22 and controls each piece of equipment of theoutdoor unit 2 and theindoor units indoor units - First, the optimal COP control operation, which is performed during the cooling operation, will be explained, referencing
FIG. 1 andFIG. 2 . - If the control unit 8 (more specifically, the indoor
side control units side control unit 37, and thetransmission line 8a that connects thecontrol units 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 inFIG. 1 , namely, the state wherein the discharge side of thecompressor 21 is connected to the gas side of theoutdoor heat exchanger 23 and, further, the inlet side of thecompressor 21 is connected to the gas side of theindoor heat exchangers 42, 52 via the gasside shutoff valve 27 and the gasrefrigerant connection piping 7. - At this time, the
outdoor expansion valve 38 is set to the fully open state. The liquidside shutoff valve 26 and the gasside shutoff valve 27 are set to an open state. - In optimal COP control during 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 inFIG. 3 (i.e., step S10). - Furthermore, the method 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.
- Furthermore, 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 theindoor expansion valves 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. - Here, in the present embodiment, each value is detected as described below.
- First, the
control unit 8 calculates the degree of supercooling SCr of the refrigerant at the outlet of theoutdoor heat exchanger 23 by subtracting the value sensed by the heat exchangingtemperature sensor 33, which detects the temperature of the refrigerant flowing through theoutdoor heat exchanger 23, from the value sensed by the liquidpipe temperature sensor 35, which detects the temperature of the refrigerant at the outlet of thesupercooler 25 on the main refrigerant circuit side. In addition, thecontrol unit 8 uses the value sensed by the heat exchangingtemperature sensor 33 of theoutdoor heat exchanger 23 to ascertain the condensing temperature Tc of the refrigerant. Furthermore, thecontrol unit 8 uses the value sensed by theoutdoor temperature sensor 36 of theoutdoor unit 2 to ascertain a temperature Ta of the outdoor air. - When the
refrigerant circuit 10 is in this state, thecontrol unit 8 activates thecompressor 21, theoutdoor fan 28, and the indoor fans 43, 53. In so doing, low pressure gas refrigerant is sucked into and compressed by thecompressor 21, thereby turning into high pressure gas refrigerant. Subsequently, the high pressure gas refrigerant is fed to theoutdoor heat exchanger 23 via the four-way switching valve 22, is condensed by the exchange of its heat with the outdoor air supplied by theoutdoor fan 28, and turns into high pressure liquid refrigerant. - Furthermore, this high pressure liquid refrigerant passes through the
outdoor expansion valve 38, flows into thesupercooler 25, exchanges heat with the refrigerant that flows through thebypass refrigerant circuit 61, and thereby is further cooled such that it transitions to the supercooled state. At this time, some of the high pressure liquid refrigerant condensed in theoutdoor heat exchanger 23 branches to thebypass refrigerant circuit 61 and, after its pressure is reduced by thebypass expansion valve 62, returns to the inlet side of thecompressor 21. Here, that portion of the refrigerant that passes through thebypass expansion valve 62 evaporates as a result of its pressure being reduced to a level close to that of the inlet pressure of thecompressor 21. Furthermore, the refrigerant that flows from the outlet of thebypass expansion valve 62 of thebypass refrigerant circuit 61 toward the inlet side of thecompressor 21 passes through thesupercooler 25 and exchanges heat with the high pressure liquid refrigerant that is fed from theoutdoor heat exchanger 23 on the main refrigerant circuit side to theindoor units - Furthermore, 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 theindoor units indoor expansion valves indoor units 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 theindoor heat exchangers 42, 52, exchanges heat with the indoor air via theindoor 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 gasside shutoff valve 27 and the four-way switching valve 22, and flows into theaccumulator 24. Furthermore, the low pressure gas refrigerant that flows into theaccumulator 24 is once again sucked into thecompressor 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 theindoor expansion valves bypass expansion valve 62 and thereby can optimize the coefficient of performance (COP) during the cooling operation. - The following text explains the optimal COP control operation during the heating operation.
- If the control unit 8 (more specifically, the indoor
side control units side control unit 37, and thetransmission line 8a that connects thecontrol units 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 broken lines inFIG. 1 , namely, the state wherein the discharge side of thecompressor 21 is connected to the gas side of theindoor heat exchangers 42, 52 via the gasside shutoff valve 27 and the gas refrigerant connection piping 7 and, further, the inlet side of thecompressor 21 is connected to the gas side of theoutdoor heat exchanger 23. - In addition, the
control unit 8 sets the liquidside shutoff valve 26 and the gasside shutoff valve 27 to the open state and closes thebypass expansion valve 62. - Furthermore, to reduce the pressure of the refrigerant that flows into the
outdoor heat exchanger 23 to an extent such that the refrigerant can evaporate (i.e., the evaporating pressure) in theoutdoor heat exchanger 23, thecontrol unit 8 regulates the degree of opening of theoutdoor expansion valve 38. - 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 inFIG. 3 (i.e., step S10). - Furthermore, the method 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.
- Furthermore, 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 theindoor expansion valves - Here, in the present embodiment, each value is detected as described below. First, the
control unit 8 detects the degree of supercooling SCr of the refrigerant at the outlet of each of theindoor heat exchangers 42, 52 by converting the discharge pressure of thecompressor 21 detected by thedischarge 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. In addition, thecontrol unit 8 uses the value sensed by the liquid side temperature sensors 44, 54 of theindoor heat exchangers 42, 52 to ascertain the condensing temperature Tc of the refrigerant. Furthermore, thecontrol unit 8 uses the value sensed by theindoor temperature sensors indoor units - If the
control unit 8 activates thecompressor 21, theoutdoor fan 28, and the indoor units 43, 53 when therefrigerant circuit 10 is in this state, the low pressure gas refrigerant is sucked into and compressed by thecompressor 21, turns into a high pressure gas refrigerant, and is then fed to theindoor units way switching valve 22, the gasside shutoff valve 27, and the gasrefrigerant connecting pipe 7. - Furthermore, the high pressure gas refrigerant fed to the
indoor units indoor heat exchangers 42, 52 and is thereby condensed and transitions to high pressure liquid refrigerant, after which it passes through theindoor expansion valves indoor expansion valves - The refrigerant that passes through the
indoor expansion valves outdoor unit 2 via the liquid refrigerant connection piping 6, the refrigerant's pressure is further reduced via the liquidside shutoff valve 26, thesupercooler 25, and theoutdoor expansion valve 38, and the refrigerant then flows into theoutdoor heat exchanger 23. Furthermore, the vapor-liquid two-phase low pressure refrigerant that flows into theoutdoor heat exchanger 23 exchanges heat with the outdoor air supplied by theoutdoor fan 28, evaporates, turns into low pressure gas refrigerant, transits the four-way switching valve 22, and flows into theaccumulator 24. Furthermore, the low pressure gas refrigerant that flows into theaccumulator 24 is once again sucked into thecompressor 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 theindoor expansion valves - The
air conditioner 1 of the present embodiment has the following features. - In a conventional air conditioner, 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.
- However, with this approach, as shown in, for example,
FIG. 9 , 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. Furthermore, if a target degree of supercooling that corresponds to the abovementioned state is used and the refrigeration cycle is controlled such that the target degree of supercooling is maintained at a constant level, then not only would it be necessary to retain numerous target values, but control would become complicated and optimizing the COP may not be possible. Furthermore, here, it is assumed that, for example, 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. - In contrast, in the
air conditioner 1 of the present embodiment, thecontrol unit 8 performs control wherein the degree of opening of, for example, each of theindoor expansion valves FIG. 4 , then it is evident that under every condition, regardless of whether it is during the cooling rated operation, the cooling season operation, the heating rated operation, or the heating season operation, the optimal value of the COP as calculated by dividing the degree of supercooling by the difference between the condensing temperature and the air temperature will fall within the range of 0.4 through 0.6. - Consequently, as discussed above, the
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. - The above text explained an embodiment of the present invention based on the drawings, but the specific configuration of the present invention is not limited to these embodiments, and it is understood that variations and modifications may be effected without departing from the spirit and scope of the invention.
- The abovementioned embodiment explained an exemplary case wherein the
control unit 8 controls the degree of opening of each of theindoor expansion valves - However, the present invention is not limited thereto; for example,
FIG. 5 shows a graph derived by transforming a relational expression between Tc and SC that satisfies SCr/(Tc - Ta) = 0.5. Specifically, the relational expression is Tc = 2SC + Ta. - Furthermore, from among the coordinate values that satisfy this relational expression, for example, the
control unit 8 may derive a target coordinate value (S) that is closest to a coordinate value (P) of an actual measured value in the current state and may perform various types of control, such as controlling theindoor expansion valves bypass expansion valve 62, and the like, controlling the rotational speed of themotor 43a of the indoor fan 43, controlling the rotational speed of themotor 21a of thecompressor 21, controlling both the adjustment and fixing of the degree of opening of theoutdoor expansion valve 38, controlling the rotational speed of themotor 28a of theoutdoor fan 28, and so on, such that the degree of supercooling and the condensing temperature at the target coordinate value (S) are achieved. - Even in this case, effects equal to those in the abovementioned embodiments can be achieved.
- The abovementioned embodiment explained an exemplary case wherein, when optimal COP control is performed during the heating operation, the
control unit 8 detects the degree of supercooling SCr by calculating the degree of supercooling SCr through converting the discharge pressure of thecompressor 21 detected by thedischarge 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 the refrigerant's saturation temperature value. - However, the present invention is not limited thereto; for example, temperature sensors that detect the temperature of the refrigerant flowing inside each of the
indoor heat exchangers 42, 52 may be provided in advance, and thecontrol unit 8 may detect the degree of supercooling SCr of the refrigerant at the outlets of theindoor heat exchangers 42, 52 by calculating the degree of supercooling SCr of optimal COP control during the heating operation through subtracting the refrigerant temperature value that corresponds to the condensing temperature detected by the temperature sensors from the refrigerant temperature value detected by the liquid side temperature sensors 44, 54. - The abovementioned embodiment explained an exemplary case wherein optimal COP control operation is performed using the value sensed by a single sensor that senses a single heat exchanger (i.e., the
outdoor temperature sensor 36, and theindoor temperature sensors 46, 56) as the air temperature Ta. - However, the present invention is not limited thereto; for example, optimal COP control operation may be performed using the average of values obtained by two temperature sensors per heat exchanger as the air temperature Ta.
- Specifically, for example, as shown in
FIG 6 andFIG. 7 , a pre-passageoutdoor temperature sensor 361, which senses the indoor temperature before air passes through theoutdoor heat exchanger 23, and a post-passageoutdoor temperature sensor 362, which senses the temperature of the air after the air has passed through theoutdoor heat exchanger 23 and exchanged heat, may be provided, and the average of the detection values sensed by these sensors may be used as the value of the air temperature Ta. - In such a case, it would be possible to more accurately ascertain the temperature of the air subjected to the exchange of heat, to further optimize the COP, and to save energy.
- The abovementioned embodiment explained an exemplary case wherein optimal COP control is performed in the
refrigerant circuit 10, which is provided with thebypass refrigerant circuit 61. - However, the present invention is not limited thereto; for example, optimal COP control may be performed as it is in the abovementioned embodiment, but on a refrigeration cycle that comprises, for example, only the main refrigerant circuit and not the
bypass refrigerant circuit 61 discussed above. In this case as well, it is possible to achieve the energy saving effect of the present invention. - The abovementioned embodiment explained an exemplary case of an air cooled air conditioner.
- However, the present invention is not limited thereto; for example, the air conditioner may be a water cooled type wherein water is used as the fluid that passes through the heat exchanger.
- The abovementioned embodiment explained an exemplary case wherein the
control unit 8 controls the degree of opening of each of theindoor expansion valves - However, the present invention is not limited thereto; for example, the
control unit 8 may control the degree of opening of each of theindoor expansion valves - The abovementioned embodiment explained an exemplary case wherein a COP related target value that can yield a satisfactory COP ratio is specified by comparing the value (i.e., the COP 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 with the COP ratio (i.e., the COP ratio at each degree of supercooling (SC) for the case wherein the COP is 100% at a certain degree of supercooling (SC)), and then controlling the degree of opening of each of the
indoor expansion valves - However, the present invention is not limited thereto. For example, as shown in
FIG. 8 , an optimal AFP control may be performed. The optimal AFP control, for example, controlls the degree of opening of each of theindoor expansion valves 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. Here, APF can be calculated by the expression APF = (the aggregate of performance exhibited during the cooling season + the aggregate of performance exhibited during the heating season)/(the aggregate of the amount of power consumed during the cooling season + the aggregate of the amount of power consumed during the heating season).
- Furthermore, 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.
- When creating the graph in
FIG. 8 , first, based on measurement conditions specified in the standard, the weighting factor for each 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-is back calculated. Furthermore, 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. - Furthermore, performing an evaluation that is closer to actual usage-by performing optimal APF control that targets a satisfactory APF value-than can be achieved using the COP-which evaluates the performance for a case (i.e., the rated condition) wherein operation is performed under a certain constant temperature condition-makes it possible to obtain a greater energy saving effect.
- The abovementioned embodiment explained an exemplary case wherein the
control unit 8 controls the degree of opening of each of theindoor expansion valves - However, 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.
- For example, operation may be performed wherein two different COP related target values and two different APF related target values-one for the circuit connection state wherein the cooling operation is performed and one for the circuit connection state wherein the heating operation is performed-are prescribed.
- The present invention is particularly useful for operating an air conditioner such that it saves energy under various conditions, thereby optimizing the COP even when usage conditions vary.
Claims (6)
- An air conditioner (1), comprising:a refrigerant circuit (10) comprising and connecting a compressor (21), a condenser (23), an expansion mechanism (41, 51), and an evaporator (42, 52) such that a refrigerant circulates therein;a fluid feeding mechanism (28) feeding a fluid toward the condenser (23);a condensing temperature ascertaining means (33) sensing a physical quantity in orderto derive a condensing temperature of the refrigerant;a fluid temperature ascertaining means (36) sensing a physical quantity in order to derive the temperature of the fluid, the fluid exchanging heat with the refrigerant inside the condenser (23); anda control unit (8) controlling at least one member selected from the group consisting of the compressor (21), the expansion mechanism (41, 51), and the fluid feeding mechanism (28) using as a target value a value calculated by dividing a degree of supercooling of the refrigerant in the vicinity of an outlet of the condenser by the difference between the condensing temperature ascertained by a detection value of the condensing temperature ascertaining means (33) and a fluid temperature ascertained by a detection value of the fluid temperature sensing means (36).
- The air conditioner (1) according to claim 1, wherein
the fluid temperature ascertaining means (36) comprises a first fluid temperature ascertaining means (361) sensing a physical quantity in order to derive the temperature of the fluid prior to exchanging heat with the refrigerant inside the condenser (23), and a second fluid temperature ascertaining means (362) sensing a physical quantity in order to derive the temperature of the fluid after exchanging heat with the refrigerant inside the condenser (23); and
the control unit (8) sets the condensing temperature to the temperature ascertained by calculating the average of the detection value of the first fluid temperature ascertaining means (36a) and the detection value of the second fluid temperature ascertaining means (36b). - The air conditioner (1) according to claim 1 or claim 2, wherein
the target value is greater than or equal to 0.15 and less than 0.75. - The air conditioner (1) according to claim 1 or claim 2, wherein
the target value is greater than or equal to 0.4 and less than 0.6. - The air conditioner (1) according to any one of claim 1 through claim 3, wherein the fluid temperature ascertaining means (36) senses an outside air temperature in the state wherein the refrigerant circuit (10) is undergoing a cooling operation cycle.
- The air conditioner (1) according to any one of claim 1 through claim 5, wherein the fluid temperature ascertaining means (36) senses an indoor temperature in the state wherein the refrigerant circuit (10) is undergoing a heating operation cycle.
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JP2007264615 | 2007-10-10 | ||
PCT/JP2008/002865 WO2009047906A1 (en) | 2007-10-10 | 2008-10-10 | Air conditioner |
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EP2211123A4 EP2211123A4 (en) | 2012-07-18 |
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JP (1) | JP5056855B2 (en) |
CN (1) | CN101821560B (en) |
AU (1) | AU2008310483B2 (en) |
ES (1) | ES2716469T3 (en) |
WO (1) | WO2009047906A1 (en) |
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CN103115417A (en) * | 2013-03-19 | 2013-05-22 | 海尔集团公司 | Refrigeration method of low temperature environment air conditioner |
WO2013165535A1 (en) * | 2012-05-03 | 2013-11-07 | Carrier Corporation | Air conditioning system having supercooled phase change material |
CN105627496A (en) * | 2014-10-29 | 2016-06-01 | 青岛海尔空调器有限总公司 | Low-temperature refrigerating control method of air conditioner and air conditioner |
CN112856842A (en) * | 2021-01-25 | 2021-05-28 | 珠海格力电器股份有限公司 | Control method of water chiller and water chiller |
US20220026082A1 (en) * | 2019-05-31 | 2022-01-27 | Rheem Manufacturing Company | Sequential Hot Gas Reheat System In An Air Conditioning Unit |
US11486617B2 (en) * | 2017-10-27 | 2022-11-01 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
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WO2009103472A1 (en) * | 2008-02-20 | 2009-08-27 | Carrier Corporation | Method of controlling a heat-rejection heat exchanging side of a refrigerant circuit |
JP4840522B2 (en) * | 2009-06-12 | 2011-12-21 | ダイキン工業株式会社 | Refrigeration equipment |
JP5116780B2 (en) * | 2010-01-13 | 2013-01-09 | 新日本空調株式会社 | Evaluation method of energy saving performance of ventilation air conditioning system |
JP5171924B2 (en) * | 2010-10-29 | 2013-03-27 | 三菱電機株式会社 | Air conditioner |
JP5979112B2 (en) * | 2013-09-30 | 2016-08-24 | ダイキン工業株式会社 | Refrigeration equipment |
JP5858022B2 (en) * | 2013-10-24 | 2016-02-10 | ダイキン工業株式会社 | Air conditioner |
JP2016053437A (en) * | 2014-09-03 | 2016-04-14 | 三菱電機株式会社 | Refrigeration cycle device and air conditioning device |
JP6400223B2 (en) * | 2015-10-13 | 2018-10-03 | 三菱電機株式会社 | Air conditioner and control method of air conditioner |
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CN107192084B (en) * | 2017-04-13 | 2020-02-04 | 青岛海尔空调器有限总公司 | Method for detecting heating energy efficiency ratio and heating quantity of air conditioner on line |
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Also Published As
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CN101821560A (en) | 2010-09-01 |
CN101821560B (en) | 2015-02-04 |
AU2008310483A1 (en) | 2009-04-16 |
AU2008310483B2 (en) | 2011-09-08 |
JP5056855B2 (en) | 2012-10-24 |
EP2211123A4 (en) | 2012-07-18 |
JPWO2009047906A1 (en) | 2011-02-17 |
WO2009047906A1 (en) | 2009-04-16 |
ES2716469T3 (en) | 2019-06-12 |
EP2211123B1 (en) | 2018-12-05 |
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