CN101821560B - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN101821560B CN101821560B CN200880110783.1A CN200880110783A CN101821560B CN 101821560 B CN101821560 B CN 101821560B CN 200880110783 A CN200880110783 A CN 200880110783A CN 101821560 B CN101821560 B CN 101821560B
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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
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- 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
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- 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
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- 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
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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
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser temperature
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
An air conditioner exhibiting a preferred COP even under a different use condition. In a cooling medium circuit (10), a compressor (21), an outdoor heat exchanger (23), an indoor expansion valve (41, 51), and indoor heat exchanger (42, 52) are interconnected so as to circulate the cooling medium. An outdoor fan (28) sends a fluid to the outdoor heat exchanger (23). A heat exchange temperature sensor (33) detects the condensation temperature of the cooling medium. An outdoor temperature sensor (36) detects the temperature of the outdoor air subjected to heat exchange with the cooling medium in the outdoor heat exchanger (23). A control unit (8) divides the degree of supercooling of the cooling medium present near the outlet of the outdoor heat exchanger (23) by the difference between the detected condensation temperature of the cooling medium and the detected temperature of the outdoor air and controls at least one of the compressor (21), the indoor expansion valve (41, 51), and the outdoor fan (28) according to the quotient of the division used as a target value.
Description
Technical field
The optimization running that the present invention relates to the coefficient of performance of conditioner controls.
Background technology
All the time, in the refrigerating plant of the refrigerant loop formed having connection compressor, condenser, expansion valve and evaporimeter, implement to control to improve the coefficient of performance (COP).
On the other hand, such as, in the conditioner shown in following patent document 1, control each component part in refrigerant loop, to make degree of subcooling reach certain in desired value, improve COP thus.
Patent document 1: Japanese Unexamined Patent Publication 2001-263831 publication
Summary of the invention
But, in the control of the conditioner described in above-mentioned patent document 1, different due to for blowdown firing and warming operation, or due to output when each operates, degree of subcooling as target there are differences, and cannot make COP optimization under various service condition.
The present invention proposes in view of above-mentioned this point, the object of the present invention is to provide a kind ofly also can make the optimized conditioner of COP when service condition is different.
First invention conditioner comprises refrigerant loop, fluid delivery mechanism, condensation temperature knows mechanism, fluid temperature (F.T.) knows mechanism and control part.Refrigerant loop is formed by connecting compressor, condenser, expansion mechanism and evaporimeter, and cold-producing medium can be circulated.Fluid delivery mechanism carries fluid to condenser.Condensation temperature knows that the physical quantity of the condensation temperature for asking for cold-producing medium detects in mechanism.Fluid temperature (F.T.) knows that the physical quantity for asking for the temperature of carrying out the fluid of heat exchange with the cold-producing medium in condenser detects in mechanism.At least one using the degree of subcooling of the cold-producing medium near condensator outlet divided by knowing condensation temperature that the detected value of mechanism is known according to condensation temperature and knowing that the value of the poor gained of the fluid temperature (F.T.) that the detected value of mechanism is known is as desired value according to fluid temperature (F.T.), in control compressor, expansion mechanism and fluid delivery mechanism of control part.
Wherein, as the mechanism of detecting physical quantities herein, such as, can be not only by the mechanism of temperature sensor direct-detection temperature, also comprise the mechanism etc. the pressure detected by pressure sensor etc. being carried out to temperature conversion.
Herein, even if when the service condition of conditioner changes, also COP can be improved by simple control.
The conditioner of the second invention, has first fluid temperature and knows that mechanism and second fluid temperature know mechanism in the conditioner of the first invention.First fluid temperature knows that the physical quantity for asking for the temperature of carrying out the fluid before heat exchange with the cold-producing medium in condenser detects in mechanism.Second fluid temperature knows that the physical quantity for asking for the temperature of carrying out the fluid after heat exchange with the cold-producing medium in condenser detects in mechanism.According to first fluid temperature, control part calculates knows that the detected value of mechanism and second fluid temperature know the temperature that the mean value of the detected value of mechanism is known, as condensation temperature.
Herein, due to the condensation temperature being suitable for calculating COP can be obtained, therefore, it is possible to improve COP further.
The conditioner of the 3rd invention, in the conditioner of the first invention or the second invention, desired value is more than 0.15, lower than 0.75.
Herein, even if when ambient environmental conditions in the running changes, also reliably COP can be improved further.
The conditioner of the 4th invention, in the conditioner of the first invention or the second invention, desired value is more than 0.4, lower than 0.6.
Herein, even if when ambient environmental conditions in the running changes, also reliably COP can be improved further.
The conditioner of the 5th invention, in the first invention ~ the 3rd invention any one conditioner in, fluid temperature (F.T.) detects the temperature of extraneous gas under knowing the state that mechanism is cooling operation cycle at refrigerant loop.
Herein, when supplying blowdown firing, outdoor heat converter works as the condenser of cold-producing medium, and fluid temperature knows that outdoor temperature detects in mechanism, can detect the temperature of the air of the indoor heat converter worked as condenser by this thus.
The conditioner of the 6th invention, in the first invention ~ the 5th invention any one conditioner in, fluid temperature (F.T.) know mechanism refrigerant loop be warming operation circulation state under, detect indoor temperature.
Herein, when warming operation, indoor heat converter works as the condenser of cold-producing medium, and fluid temperature (F.T.) knows that indoor temperature detects in mechanism, can detect the temperature of the air of the indoor heat converter worked as condenser by this thus.
In the conditioner of the first invention, even if when the service condition of conditioner changes, also COP can be improved by simple control.
In the conditioner of the second invention, the condensation temperature being suitable for calculating COP can be obtained, therefore, it is possible to improve COP further.
In the conditioner of the 3rd invention, even if when ambient environmental conditions in the running changes, also reliably COP can be improved further.
In the conditioner of the 4th invention, even if when ambient environmental conditions in the running changes, also reliably COP can be improved further.
In the conditioner of the 5th invention, the temperature of the air by the indoor heat converter worked as condenser can be detected.
In the conditioner of the 6th invention, the temperature of the air by the indoor heat converter worked as condenser can be detected.
Accompanying drawing explanation
Fig. 1 is the summary construction diagram of the conditioner in one embodiment of the present invention.
Fig. 2 is the control block diagram of conditioner.
Fig. 3 is control flow chart when carrying out best COP control running.
Fig. 4 represents the coefficient of performance and the degree of subcooling figure divided by the relation of the value of the difference gained of condensation temperature and air themperature.
Fig. 5 represents to meet the degree of subcooling of relation of regulation and the figure of the relation of condensation temperature.
Fig. 6 is the summary construction diagram of the conditioner in variation (C).
Fig. 7 is the control block diagram of the conditioner in variation (C).
Fig. 8 represents in the conditioner in variation (G), APF than with the figure of degree of subcooling divided by the relation of the value of the difference gained of condensation temperature and air themperature.
Fig. 9 is the figure of the relation representing existing degree of subcooling and the coefficient of performance.
Symbol description
1 conditioner
8 control parts
10 refrigerant loops
21 compressors
23 outdoor heat converters (condenser)
28 outdoor fans (fluid delivery mechanism)
33 heat exchange temperature sensors (condensation temperature knows mechanism)
36 outdoor temperature sensor (fluid)
361 by front outdoor temperature sensor (first fluid temperature knows mechanism)
362 by rear outdoor temperature sensor (second fluid temperature knows mechanism)
41,51 indoor expansion valve (expansion mechanism)
42,52 indoor heat converters (evaporimeter)
Detailed description of the invention
Below, with reference to the accompanying drawings the embodiment of conditioner of the present invention is described.
(structure of conditioner 1)
Fig. 1 is the summary construction diagram of the conditioner 1 in one embodiment of the present invention.
Conditioner 1 is the freeze cycle running by carrying out steam compression type, the device used in the indoor cooling heating of building etc.Conditioner 1 mainly comprises: as an outdoor unit 2 of heat source unit; Multiple stage (being 2 the in the present embodiment) indoor unit 4,5 as the machine of use be connected in parallel with it; As the liquid refrigerant connecting pipings 6 of cold-producing medium connecting pipings and the gas refrigerant connecting pipings 7 that connect outdoor unit 2 and indoor unit 4,5.That is, the steam compression type of the conditioner 1 of present embodiment refrigerant loop 10 by connect outdoor unit 2, indoor unit 4,5, liquid refrigerant connecting pipings 6 and gas refrigerant connecting pipings 7 and form.
(indoor unit 4,5)
Indoor unit 4,5 is set up in the mode of the wall surface of indoor with the mode such as indoor top or wall hanging that embed or be suspended on building etc.Indoor unit 4,5 is connected with outdoor unit 2 with gas refrigerant connecting pipings 7 via liquid refrigerant connecting pipings 6, forms a part for refrigerant loop 10.
Below, the structure of indoor unit 4,5 is described.In addition, indoor unit 4 is identical structure with indoor unit 5, therefore, the structure of indoor unit 4 is only described herein, for the structure of indoor unit 5, the symbol of represent the various piece of indoor unit 4 forties is replaced to the symbol of fifties, omit the explanation of various piece.
Indoor unit 4 mainly has the indoor refrigerant loop 10a (being indoor refrigerant loop 10b in indoor unit 5) of the part forming refrigerant loop 10.This indoor refrigerant loop 10a mainly has as the indoor expansion valve 41 of expansion mechanism with as the indoor heat converter 42 using side heat exchanger.
In the present embodiment, indoor expansion valve 41 is that the electric expansion valve be connected with the hydraulic fluid side of indoor heat converter 42, carries out folding control according to pulse signal in order to regulate etc. the flow of the cold-producing medium flowed through in the refrigerant loop 10a of indoor.This indoor expansion valve 41,51 controls in running at best COP described later, in order to make the COP optimization of freeze cycle, utilizes control part 8 to carry out the control of aperture adjustment, the control etc. of fixing aperture.
In the present embodiment, indoor heat converter 42 is the fin tube type heat exchangers of the intersection fin type be made up of heat-transfer pipe and multiple fin, evaporimeter when supplying blowdown firing as cold-producing medium works, cooling room air, condenser when warming operation as cold-producing medium works, heating indoor air.
In the present embodiment, indoor unit 4 has and sucks in unit by room air, after making it carry out heat exchange with cold-producing medium in indoor heat converter 42, and the indoor fan 43 as blowing fan supply in air supply chamber.Indoor fan 43 can change the air quantity of the air of supply chamber inside heat exchanger 42, in the present embodiment, by centrifugal fan, multiblade fan etc. that the motor 43a be made up of DC fan motor drives.
In addition, in indoor unit 4, various sensor is provided with.The hydraulic fluid side temperature sensor 44 of the temperature (that is, corresponding with evaporating temperature when condensation temperature during warming operation or confession blowdown firing refrigerant temperature) detecting cold-producing medium is provided with in the hydraulic fluid side of indoor heat converter 42.The gas side temperature sensor 45 of the temperature detecting cold-producing medium is provided with at the gas side of indoor heat converter 42.The indoor temperature transmitter 46 of the temperature (that is, indoor temperature) detecting the room air flowed in unit is provided with in the suction inlet side of the room air of indoor unit 4.In the present embodiment, hydraulic fluid side temperature sensor 44, gas side temperature sensor 45 and indoor temperature transmitter 46 are made up of thermistor.In addition, indoor unit 4 has the indoor control part 47 of the action controlling the various piece forming indoor unit 4.And, the microcomputer that indoor control part 47 has the control in order to carry out indoor unit 4 and arranges, memory etc., the exchange of control signal etc. can be carried out between the remote controller (not shown) being used for operating separately indoor unit 4, between outdoor unit 2, carry out the exchange of control signal etc. via conveyer line 8a.
(outdoor unit 2)
Outdoor unit 2 is arranged on the outdoor of building etc., is connected with gas refrigerant connecting pipings 7 by liquid refrigerant connecting pipings 6 with indoor unit 4,5, between indoor unit 4,5, form refrigerant loop 10.
Below, the structure of outdoor unit 2 is described.Outdoor unit 2 mainly has the outside refrigerant loop 10c of the part forming refrigerant loop 10.This outside refrigerant loop 10c mainly has compressor 21, No. four transfer valve 22, the outdoor heat converter 23 as heat source side heat exchanger, the outdoor expansion valve 38 as expansion mechanism, reservoir 24, subcooler 25, hydraulic fluid side stop valve 26 and gas side stop valve 27 as thermoregulation mechanism.
Compressor 21 is the compressors that can change running capacity, in the present embodiment, by the positive displacement compressor that the motor 21a by inverter control revolution drives.In the present embodiment, only have a compressor 21, but not limited thereto, also according to the connection number of units etc. of indoor unit, the compressor of more than 2 can be connected in parallel.
No. four transfer valves 22 are valves of the flow direction for switching cold-producing medium, in order to when for blowdown firing, outdoor heat converter 23 is worked as the condenser of the cold-producing medium compressed by compressor 21, and make indoor heat converter 42, 52 work as the evaporimeter of the cold-producing medium be condensed in outdoor heat converter 23, connect the discharge side of compressor 21 and the gas side of outdoor heat converter 23, and connect the suction side of compressor 21 (specifically, reservoir 24) and gas refrigerant connecting pipings 7 side (solid line with reference to Tu1 No. tetra-transfer valve 22), in order to when warming operation, indoor heat converter 42,52 is worked as the condenser of the cold-producing medium compressed by compressor 21, and outdoor heat converter 23 is worked as the evaporimeter of the cold-producing medium be condensed in indoor heat converter 42,52, connect discharge side and gas refrigerant connecting pipings 7 side of compressor 21, and connect the suction side of compressor 21 and the gas side (dotted line with reference to Tu1 No. tetra-transfer valve 22) of outdoor heat converter 23.
In the present embodiment, outdoor heat converter 23 is the fin tube type heat exchangers of the intersection fin type be made up of heat-transfer pipe and multiple fin, can work by the condenser when supplying blowdown firing as cold-producing medium, the evaporimeter when warming operation as cold-producing medium works.The gas side of outdoor heat converter 23 is connected with No. four transfer valves 22, and its hydraulic fluid side is connected with liquid refrigerant connecting pipings 6.
In the present embodiment, outdoor expansion valve 38 is to regulate the pressure, flow etc. of the cold-producing medium flow through in the refrigerant loop 10c of outside, and the electric expansion valve be connected with the hydraulic fluid side of outdoor heat converter 23.
In the present embodiment, outdoor unit 2 has and sucks in unit by outdoor air, makes itself and cold-producing medium carry out heat exchange, the outdoor fan 28 as blowing fan afterwards outside discharge chamber in outdoor heat converter 23.This outdoor fan 28 is fans of the air quantity Wo of the air that can change supply chamber outer heat-exchanger 23, in the present embodiment, by the propeller fan etc. that the motor 28a be made up of DC fan motor drives.
Reservoir 24 is connected between No. four transfer valves 22 and compressor 21, according to the variation etc. of the operating load of indoor unit 4,5, can be stored in the container of the residual refrigerant produced in refrigerant loop 10.
In the present embodiment, subcooler 25 is heat exchangers of Double-pipe type, and in order to after being condensed in outdoor heat converter 23, the cold-producing medium being sent to indoor expansion valve 41,51 carries out cooling and arranging.In the present embodiment, subcooler 25 is connected between outdoor expansion valve 38 and hydraulic fluid side stop valve 26.
In the present embodiment, the bypass refrigerant loop 61 of the cooling source of subcooler 25 is provided as.In addition, in the following description, conveniently, the part removed outside bypass refrigerant loop 61 in refrigerant loop 10 is called main refrigerant circuit.
Bypass refrigerant loop 61 is connected with main refrigerant circuit, makes heat exchanger 23 outdoor be sent to a part for the cold-producing medium of indoor expansion valve 41,51 from main refrigerant circuit branch, and returns to the suction side of compressor 21.Specifically, bypass refrigerant loop 61 has: the shunting circuit 61a be connected in the mode making expansion valve 38 outdoor be sent to the position branch of a part outdoor between heat exchanger 23 with subcooler 25 of the cold-producing medium of indoor expansion valve 41,51; With the loop 61b that confluxes that the mode returning to the suction side of compressor 21 with the outlet of the side, bypass refrigerant loop from subcooler 25 is connected with the suction side of compressor 21.And, the bypass expansion valve 62 of the flow for regulating the cold-producing medium flowing through bypass refrigerant loop 61 is provided with at duplexure 61a.Herein, bypass expansion valve 62 is made up of electric expansion valve.Thus, heat exchanger 23 is sent to the cold-producing medium of indoor expansion valve 41,51 outdoor, in subcooler 25, by by the post-decompression cold-producing medium flowing through bypass refrigerant loop 61 of bypass expansion valve 62 by but.That is, subcooler 25 is regulated by the aperture of bypass expansion valve 62 and carries out capability control.In addition, about this bypass expansion valve 62, controlling in running at best COP described later, in order to make the COP optimization of freeze cycle, also carrying out the control of aperture adjustment, the control etc. of fixing aperture by control part 8.
Hydraulic fluid side stop valve 26 and gas side stop valve 27 are the valves arranged at the connector with outer setting, pipe arrangement (specifically, being liquid refrigerant connecting pipings 6 and gas refrigerant connecting pipings 7).Hydraulic fluid side stop valve 26 is connected with outdoor heat converter 23.Gas side stop valve 27 is connected with No. four transfer valves 22.
In addition, outdoor unit 2 is provided with various sensor.Specifically, the discharge temperature sensor 32 of the discharge temperature Td of the suction pressure sensor 29 being provided with the suction pressure detecting compressor 21 at outdoor unit 2, the discharge pressure sensor 30 detecting the discharge pressure of compressor 21, the inlet temperature sensor 31 detecting the inlet temperature Ts of compressor 21 and detection compressor 21.Inlet temperature sensor 31 is arranged on the position between reservoir 24 and compressor 21.The heat exchange temperature sensor 33 of the temperature (that is, corresponding with evaporating temperature when condensation temperature during confession blowdown firing or warming operation refrigerant temperature) detecting the cold-producing medium flow through in outdoor heat converter 23 is provided with at outdoor heat converter 23.The hydraulic fluid side temperature sensor 34 of the temperature detecting cold-producing medium is provided with in the hydraulic fluid side of outdoor heat converter 23.The liquid pipe temperature sensor 35 of the temperature (that is, liquid pipe temperature) detecting cold-producing medium is provided with in the outlet of the main refrigerant circuit side of subcooler 25.The bypass temperature sensor 63 of the temperature of the cold-producing medium of the outlet for detecting the side, bypass refrigerant loop flowing through cooler 25 is provided with at the loop 61b that confluxes in bypass refrigerant loop 61.The outdoor temperature sensor 36 of the temperature (that is, outdoor temperature) detecting the outdoor air flowed in unit is provided with in the suction inlet side of the outdoor air of outdoor unit 2.
In the present embodiment, inlet temperature sensor 31, discharge temperature sensor 32, heat exchange temperature sensor 33, hydraulic fluid side temperature sensor 34, liquid pipe temperature sensor 35, outdoor temperature sensor 36 and bypass temperature sensor 63 are made up of thermistor.
In addition, outdoor unit 2 has the outside control part 37 of the action controlling the various piece forming outdoor unit 2.And, the inverter circuit etc. of the microcomputer that outside control part 37 has the control in order to carry out outdoor unit 2 and arranges, memory, control motor 21a, can carry out the exchange of control signal etc. between the indoor control part 47,57 of indoor unit 4,5 via conveyer line 8a.That is, by indoor control part 47,57, conveyer line 8a between outside control part 37 and connection control portion 37,47,57, form and the control part 8 controlled that operates carried out to conditioner 1 entirety.
As shown in Fig. 2 of the control block diagram as conditioner 1, control part 8 is connected in the mode of the detection signal that can receive various sensor 29 ~ 36,44 ~ 46,54 ~ 56,63, and with can control according to these detection signals etc. various equipment and valve 21,22,24,28a, 38,41,43a, 51,53a, 62 mode be connected.
(cold-producing medium connecting pipings 6,7)
When the setting place such as building arrange conditioner 1, cold-producing medium connecting pipings 6,7 is the refrigerant pipings carrying out at the scene constructing, according to setting model such as the combinations of setting place, outdoor unit and indoor unit, use the pipe arrangement with various length and caliber.
As mentioned above, the conditioner 1 of present embodiment, utilize the control part 8 be made up of indoor control part 47,57 and outside control part 37, switched for blowdown firing and warming operation by No. four transfer valves 22 and operate, and according to the operating load of each indoor unit 4,5, carry out the control of each equipment of outdoor unit 2 and indoor unit 4,5.
(best COP controls running)
(controlling for best COP during blowdown firing)
First, using Fig. 1 and Fig. 2, being described controlling running for best COP during blowdown firing.
Control part 8 (more particularly, indoor control part 47, 57, outside control part 37 and connection control portion 37, 47, conveyer line 8a between 57), when receiving the instruction carried out for blowdown firing from the remote controller (not shown) etc. of outside, for freeze cycle, control the connection status of No. four transfer valves 22, No. four transfer valves 22 are made to become the state shown in solid line of Fig. 1, namely, the discharge side of compressor 21 is connected with the gas side of outdoor heat converter 23, and the suction side of compressor 21 is via gas side stop valve 27 and gas refrigerant connecting pipings 7 and indoor heat converter 42, the state that the gas side of 52 connects.
Now, outdoor expansion valve 38 becomes full-gear.Hydraulic fluid side stop valve 26 and gas side stop valve 27 become open state.
In controlling for best COP during blowdown firing, first as depicted in the flow chart of fig.3, calculated cooling degree SCr is divided by the value (step S10) of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta for control part 8.
Then, whether the value that judgement calculates in step slo is 0.5 (step S20).Herein, if the value calculated in step slo is 0.5, then continues former state and implement this control.
Then, when the value that step S10 calculates is not 0.5, as Correction and Control, control part 8 regulates the control of the aperture of indoor expansion valve 41,51 and the aperture of bypass expansion valve 62 respectively, makes it possible to realize the freeze cycle that degree of subcooling SCr is the state of 0.5 divided by the value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta.And then return step S20.
Herein, in the present embodiment, each value detects in the following manner.
First, control part 8 carry out from by be detected cooler 25 main refrigerant circuit side outlet refrigerant temperature liquid pipe temperature sensor 35 detected by value deduct by the computing of the value detected detected by the heat exchange temperature sensor 33 flowing through refrigerant temperature in outdoor heat converter 23, calculate the degree of subcooling SCr of the cold-producing medium of the outlet of outdoor heat converter 23 thus.In addition, control part 8 knows the condensation temperature Tc of cold-producing medium according to the value detected by the heat exchange temperature sensor 33 in outdoor interchanger 23.And control part 8 knows the temperature Ta of outdoor air according to the value detected by the outdoor temperature sensor 36 of outdoor unit 2.
Under the state of this refrigerant loop 10, control part 8 starts compressor 21, outdoor fan 28 and indoor fan 43,53.Thus, the gas refrigerant of low pressure is inhaled into compressor 21 and is compressed, and becomes the gas refrigerant of high pressure.Then, the gas refrigerant of high pressure is sent to outdoor heat converter 23 via No. four transfer valves 22, carries out heat exchange and condensation, become the liquid refrigerant of high pressure with the outdoor air supplied by outdoor fan 28.
Then, the liquid refrigerant of this high pressure, by outdoor expansion valve 38, flows into subcooler 25, carries out heat exchange, become the supercooling state be further cooled with the cold-producing medium flowing through bypass refrigerant loop 61.Now, a part for the liquid refrigerant of the high pressure of condensation in outdoor heat converter 23, branch, in bypass refrigerant loop 61, after being reduced pressure, returns to the suction side of compressor 21 by bypass expansion valve 62., be depressurized to the suction pressure close to compressor 21 by the cold-producing medium of bypass expansion valve 62 herein, so its part evaporation.Then, the cold-producing medium flowed to the suction side of compressor 21 from the outlet of the bypass expansion valve 62 in bypass refrigerant loop 61 is by subcooler 25, and the liquid refrigerant being sent to the high pressure of indoor unit 4,5 with the outdoor heat converter 23 from main refrigerant circuit side carries out heat exchange.
Then, the liquid refrigerant becoming the high pressure of supercooling state, via hydraulic fluid side stop valve 26 and liquid refrigerant connecting pipings 6, is sent to indoor unit 4,5.This is sent to the liquid refrigerant of the high pressure of indoor unit 4,5, the suction pressure close to compressor 21 is reduced pressure into by indoor expansion valve 41,51, become the cold-producing medium of the gas-liquid two-phase state of low pressure, be sent to indoor heat converter 42,52, in indoor heat converter 42,52, carry out heat exchange with room air and evaporate, becoming the gas refrigerant of low pressure.
The gas refrigerant of this low pressure is sent to outdoor unit 2 via gas refrigerant connecting pipings 7, flows into reservoir 24 via gas side stop valve 27 and No. four transfer valves 22.Then, the gas refrigerant flowing into the low pressure of reservoir 24 is inhaled into compressor 21 again.
Control part 8, by regulating the aperture of indoor expansion valve 41,51 and bypass expansion valve 62, realizes above-described for best COP control running during blowdown firing, can make thus for the coefficient of performance (COP) optimization during blowdown firing.
(best COP during warming operation controls running)
Below, control running to best COP during warming operation to be described.
Control part 8 (more particularly, indoor control part 47, 57, outside control part 37 and connection control portion 37, 47, conveyer line 8a between 57), when receiving from the remote controller (not shown) etc. of outside the instruction carrying out warming operation, for freeze cycle, control the connection status of No. four transfer valves 22, No. four transfer valves 22 are made to become the state shown in dotted line of Fig. 1, namely, the discharge side of compressor 21 is via gas side stop valve 27 and gas refrigerant connecting pipings 7 and indoor heat converter 42, the gas side of 52 connects, and the state that the suction side of compressor 21 is connected with the gas side of outdoor heat converter 23.
In addition, control part 8 makes hydraulic fluid side stop valve 26 and gas side stop valve 27 be open state, closes bypass expansion valve 62.
Further, in order to outdoor expansion valve 38 being decompressed to the pressure (that is, evaporating pressure) that the cold-producing medium of inflow outdoor heat exchanger 23 can be made to evaporate in outdoor heat converter 23, control part 8 carries out the regulable control of aperture.
During best COP when warming operation controls, same with refrigeration, first as depicted in the flow chart of fig.3, calculated cooling degree SCr is divided by the value (step S10) of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta for control part 8.
Then, whether the value that judgement calculates in step slo is 0.5 (step S20).Herein, if the value calculated in step slo is 0.5, then continues former state and implement this control.
Then, when the value that step S10 calculates is not 0.5, as Correction and Control, control part 8 carries out the control of aperture regulating indoor expansion valve 41,51, makes it possible to realize the freeze cycle that degree of subcooling SCr is the state of 0.5 divided by the value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta.And then return step S20.
Herein, in the present embodiment, each numerical value detects in the following manner.First, control part 8 carries out the discharge pressure of the compressor 21 detected by discharge pressure sensor 30 to be converted into the saturation temperature value corresponding with condensation temperature, and the computing of the refrigerant temperature value detected by hydraulic fluid side temperature sensor 44,54 is deducted from the saturation temperature value of this cold-producing medium, detect the degree of subcooling SCr of the cold-producing medium of the outlet of indoor heat converter 42,52 thus.In addition, control part 8 knows the condensation temperature Tc of cold-producing medium according to the value detected by the hydraulic fluid side temperature sensor 44,54 in indoor heat converter 42,52.And control part 8 knows the temperature Ta of room air according to the value detected by the indoor temperature transmitter 46,56 of indoor unit 4,5.
Under the state of this refrigerant loop 10, control part 8 starts compressor 21, outdoor fan 28 and indoor fan 43,53, then the gas refrigerant of low pressure is inhaled into compressor 21 and is compressed, become the gas refrigerant of high pressure, via No. four transfer valves 22, gas side stop valve 27 and gas refrigerant connecting pipings 7, be sent to indoor unit 4,5.
Then, the gas refrigerant being sent to the high pressure of indoor unit 4,5 carries out heat exchange and condensation with room air in outdoor heat converter 42,52, becomes the liquid refrigerant of high pressure, then, when passing through indoor expansion valve 41,51, the valve opening according to indoor expansion valve 41,51 is depressurized.
By the cold-producing medium of this indoor expansion valve 41,51, be sent to outdoor unit 2 via liquid refrigerant connecting pipings 6, after being further depressurized via hydraulic fluid side stop valve 26, subcooler 25 and outdoor expansion valve 38, inflow outdoor heat exchanger 23.Then, the cold-producing medium of the gas-liquid two-phase state of the low pressure of inflow outdoor heat exchanger 23 carries out heat exchange with the outdoor air supplied by outdoor fan 28 and evaporates, and becomes the gas refrigerant of low pressure, flows into reservoir 24 via No. four transfer valves 22.Then, the gas refrigerant flowing into the low pressure of reservoir 24 is inhaled into compressor 21 again.
Control part 8 is by regulating the aperture of indoor expansion valve 41,51, and best COP when implementing above-mentioned warming operation controls running, can make the coefficient of performance (COP) optimization during warming operation thus.
(feature of the conditioner 1 of present embodiment)
The conditioner 1 of present embodiment has following characteristics.
In existing conditioner, determine the index that can make the optimized degree of subcooling of COP, then carry out control according to this desired value and make degree of subcooling certain.
Such as, but like this, shown in Fig. 9, COP and degree of subcooling SC do not have the relation corresponding with the situation making conditioner operate especially.That is, 7 degree during the specified running of cooling, cooling when to operate intergrade 3 degree, heat specified running time 9 degree, when to operate intergrade 4 degree of heating are the degree of subcooling of the best respectively.So, when using be specifically worth control freeze cycle as target degree of subcooling, according to the difference of each condition, difference can be produced with best degree of subcooling, COP optimization cannot be made.Further, respectively according to situation determination target degree of subcooling, with when this target degree of subcooling keeps certain mode to control freeze cycle, not only need to keep multiple desired value, and control to become loaded down with trivial details, COP optimization may not be made.Herein, suppose that such as external air temperature is the situation of the condition of 18 ~ 20 DEG C as cooling intergrade; As heating intergrade, such as external air temperature is the situation of 13 ~ 18 DEG C.
On the other hand, in the conditioner 1 of present embodiment, control part 8 carries out the control of the aperture regulating indoor expansion valve 41,51 etc., makes to realize the freeze cycle that degree of subcooling SCr is the state of 0.5 divided by the value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta.Herein, as shown in Figure 4, if research COP and degree of subcooling are divided by the relation of the value of the difference gained of condensation temperature and air themperature, then when the specified running of cooling, cooling when to operate intergrade, heat specified running time and heating any one situation when to operate intergrade under, all, degree of subcooling is in the scope of 0.4 ~ 0.6 divided by the value of the difference gained of condensation temperature and air themperature to the optimum value of the COP under each condition.
Therefore, as mentioned above, control part 8 carries out best COP control, degree of subcooling is made to become 0.5 divided by the value of the difference gained of condensation temperature and air themperature, even if do not have the desired value under each condition thus, also can make COP optimization by means of only using 0.5 this numerical value as the simple control of target, in any one situation of the specified running of cooling, cooling running intergrade, warming operation and heating running intergrade, all can realize energy-conservation.
(other embodiment)
Below with reference to the accompanying drawings embodiments of the present invention are illustrated, but concrete structure is not limited to these embodiments, can changes within a range not departing from the gist of the invention.
(A)
In the above-described embodiment, enumerate the aperture that control part 8 controls indoor expansion valve 41,51, the situation making degree of subcooling SCr become 0.5 divided by the numerical value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta is that example is illustrated.
But the present invention is not limited thereto, such as, as shown in Figure 5, obtained the relational expression of Tc and the SC of the relation meeting SCr/ (Tc-Ta)=0.5 by the distortion of formula, and represent by coordinate diagram.Specifically, relational expression is Tc=2SC+Ta.
Then, such as, control part 8 obtains the coordinates of targets value (S) closest to the coordinate value (P) of the measured value of present status in the coordinate value meeting this relational expression, in order to realize degree of subcooling and the condensation temperature of this coordinates of targets value (S), be not only indoor expansion valve 41, 51, the control of bypass expansion valve 62 grade, revolution for the motor 43a of indoor fan 43 controls, revolution for the motor 21a of compressor 21 controls, for the control that the aperture of outdoor expansion valve 38 adjusts, the control of fixing aperture, each control for the revolution control etc. of the motor 28a of outdoor fan 28 also can be realized by control part 8.
In the case, also the effect same with above-mentioned embodiment can be obtained.
(B)
In the above-described embodiment, be illustrated for following situation, during best COP when warming operation controls, the discharge pressure of the compressor 21 detected by discharge pressure sensor 30 is converted into the saturation temperature value corresponding with condensation temperature by control part 8, deduct the refrigerant temperature value detected by hydraulic fluid side temperature sensor 44,54 from the saturation temperature value of this cold-producing medium, detect degree of subcooling SCr thus.
But, the present invention is not limited thereto, such as, also the temperature sensor of the temperature detecting the cold-producing medium flow through in each indoor heat converter 42,52 can be pre-set, about the calculating of the degree of subcooling SCr that best COP during warming operation controls, control part 8, by carrying out the computing deducting the refrigerant temperature value corresponding with the condensation temperature detected by this temperature sensor from the refrigerant temperature value detected by hydraulic fluid side temperature sensor 44,54, carries out the degree of subcooling SCr of the cold-producing medium of the outlet of indoor heat converter 42,52.
(C)
In the above-described embodiment, about air themperature, enumerate for a heat exchanger by the value detected by a sensor (outdoor temperature sensor 36, indoor temperature transmitter 46,56) be used as air themperature Ta and carry out best COP control running situation be that example is illustrated.
But the present invention is not limited thereto, such as, also can be by the mean value of the value obtained by two temperature sensors, air themperature Ta is used as a heat exchanger, and carries out best COP control running.
Specifically, such as, also can be, as shown in Figure 6, Figure 7, arrange and detect by temperature sensor 361 before the heat exchange of the indoor temperature before outdoor heat converter 23 and detect temperature sensor 362 by outdoor heat converter 23 and after carrying out the heat exchange of the temperature of the air after heat exchange, use the value of mean value as air themperature Ta of the detected value of each sensor.
In the case, the temperature of the air carrying out heat exchange can be known more exactly, COP can be made to optimize further, reach energy-conservation object.
(D)
In the above-described embodiment, enumerating the situation of carrying out best COP control in the refrigerant loop 10 being provided with bypass refrigerant loop 61 is that example is illustrated.
Such as, but the present invention is not limited thereto, for not there is above-mentioned bypass refrigerant loop 61, the freeze cycle be only made up of main refrigerant circuit, also can carry out the best COP same with above-mentioned embodiment and control.In the case, also energy-saving effect of the present invention can be obtained.
(E)
In the above-described embodiment, the conditioner enumerating air-cooled type is that example is illustrated.
But the present invention is not limited thereto, such as, also can be adopt water as the water-cooled conditioner of the fluid by heat exchanger.
(F)
In the above-described embodiment, enumerate the aperture that control part 8 controls indoor expansion valve 41,51, the situation making degree of subcooling SCr become 0.5 divided by the value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta is that example is illustrated.
But, the present invention is not limited thereto, such as, control part 8 also can control the aperture etc. of indoor expansion valve 41,51, makes degree of subcooling SCr be in more than 0.4, lower than in the scope of 0.6 divided by the value of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta.In the case, the effect substantially identical with above-mentioned embodiment can also be obtained.
(G)
In the above-described embodiment, enumerating following situation is that example is illustrated, by comparing degree of subcooling SCr divided by the value (COP associated objects value) of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta and COP ratio (ratio of the COP under each degree of subcooling (SC) when making the COP under certain degree of subcooling (SC) be 100%), determine the COP associated objects value can improving COP ratio, control the aperture of indoor expansion valve 41,51, make COP associated objects value be in specific scope.
But the present invention is not limited thereto.Such as, as shown in Figure 8, also can be, by comparing degree of subcooling SCr divided by the value (APF associated objects value) of the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta and annual energy consumption efficiency (APF:Annual PerformanceFactor), determine the APF associated objects value can improving APF, carry out the control of the aperture etc. controlling indoor expansion valve 41,51, make APF associated objects value be in specific scope, and implement best APF and control.Herein, when determining the scope of APF associated objects value, such as, APF in fig. 8 shown in ordinate can also be asked for than the scope being more than 100%.This APF ratio refers to, the ratio of the APF under each degree of subcooling (SC) when making the APF under certain degree of subcooling (SC) be 100%.
This APF is the value for system/heating capacity when representing in a year every 1kW power consumption when operating conditioner under certain certain condition.Herein, according to formula APF=(summation of the ability played between the summation+heating period of the ability played in during cooling)/(summation of the power consumption between the summation+heating period of the power consumption in during cooling), APF can be calculated.
In addition, such as, the condition of the standard JRA4048:2006 (in order to implement the standard of JIS B8616:2006) that can be able to formulate according to Japanese refrigerating and air conditioning industry, calculates APF in more detail.
When the coordinate diagram of construction drawing 8, first, according to the condition determination of this standard, the COP ratio in the middle of COP ratio when calculating the specified running of cooling by inverse operation, cooling during running, heat specified running time COP ratio, COP ratio in the middle of heating during running and the running of heating low temperature time COP than respective weight coefficient.Then, COP ratio in the middle of COP ratio when each weight coefficient calculated being multiplied by respectively the specified running of corresponding cooling, cooling during running, heat specified running time COP ratio, COP ratio in the middle of heating during running and the running of heating low temperature time COP ratio, by adding up to each value, as the value can evaluated for the sum total of cold-peace heating, obtain APF ratio.
And, by controlling with the best APF that to improve this APF value be target, compared with evaluating the COP of the performance of (rated condition) when operating under the temperature conditions that certain is certain, can carry out, close to the actual evaluation used, more energy-conservation effect may being obtained.
(H)
In the above-described embodiment, enumerate the aperture that control part 8 controls indoor expansion valve 41,51, make the value divided by the condensation temperature Tc of cold-producing medium and the difference gained of air themperature Ta be 0.5 situation be that example is illustrated.
But, the present invention is not limited thereto, such as, also can carry out according to season, operating conditions condition etc. the control changing COP associated objects value, APF associated objects value, the COP associated objects value making to record in variation (G) hurdle, APF associated objects value can use the preferred value corresponding with season, operating conditions condition etc.
Such as, as this COP associated objects value, APF associated objects value, the COP associated objects value that value when also can determine to carry out the loop connection status for blowdown firing is different with the value these two when carrying out the loop connection status of warming operation and APF associated objects value, and operate.
Utilizability in industry
By utilizing the present invention, also can make COP optimization when service condition is different, therefore, the situation of conditioner energy-saving operation also can be made under different conditions particularly useful for hope.
Claims (5)
1. a conditioner (1), is characterized in that, comprising:
Refrigerant loop (10), it is formed by connecting compressor (21), condenser (23), expansion mechanism (41,51) and evaporimeter (42,52), and cold-producing medium can be circulated;
To the fluid delivery mechanism (28) of described condenser (23) conveying fluid;
The condensation temperature detecting the physical quantity of the condensation temperature for asking for cold-producing medium knows mechanism (33);
Detection is used for asking for the fluid temperature (F.T.) of carrying out the physical quantity of the temperature of the described fluid of heat exchange with the cold-producing medium in described condenser (23) and knows mechanism (36); With
Control part (8), its using the degree of subcooling of the cold-producing medium near described condensator outlet divided by knowing condensation temperature that the detected value of mechanism (33) is known according to described condensation temperature and knowing that the value of the poor gained of the fluid temperature (F.T.) that the detected value of mechanism (36) is known is as desired value according to described fluid temperature (F.T.), control at least one in described compressor (21), described expansion mechanism (41,51) and described fluid delivery mechanism (28)
Described refrigerant loop (10) flow direction had by switching cold-producing medium switches No. four transfer valves (22) for blowdown firing and warming operation,
Described control part carries out described control using more than 0.15 and lower than the identical value of 0.75 as described desired value described confession in blowdown firing and arbitrary running of described warming operation.
2. conditioner (1) as claimed in claim 1, is characterized in that:
Described fluid temperature (F.T.) knows that mechanism (36) has: detection is used for asking for the first fluid temperature of carrying out the physical quantity of the temperature of the described fluid before heat exchange with the cold-producing medium in described condenser (23) and knows mechanism (36a); The second fluid temperature being used for the physical quantity of the temperature asking for the described fluid after carrying out heat exchange with the cold-producing medium in described condenser (23) with detection knows mechanism (36b),
According to described first fluid temperature, described control part (8) calculates knows that the detected value of mechanism (36a) and described second fluid temperature know the temperature that the mean value of the detected value of mechanism (36b) is known, as condensation temperature.
3. conditioner (1) as claimed in claim 1 or 2, is characterized in that:
Described desired value is more than 0.4, lower than 0.6.
4. conditioner (1) as claimed in claim 1 or 2, is characterized in that:
Described fluid temperature (F.T.) knows mechanism (36), under the state of described refrigerant loop (10) for cooling operation cycle, detects the temperature of extraneous gas.
5. conditioner (1) as claimed in claim 1 or 2, is characterized in that:
Described fluid temperature (F.T.) knows mechanism (36), under the state circulated for warming operation, detects indoor temperature at described refrigerant loop (10).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
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| JP2007264615 | 2007-10-10 | ||
| JP2007-264615 | 2007-10-10 | ||
| PCT/JP2008/002865 WO2009047906A1 (en) | 2007-10-10 | 2008-10-10 | Air conditioner |
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| CN101821560A CN101821560A (en) | 2010-09-01 |
| CN101821560B true CN101821560B (en) | 2015-02-04 |
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| CN200880110783.1A Active CN101821560B (en) | 2007-10-10 | 2008-10-10 | Air conditioner |
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| EP (1) | EP2211123B1 (en) |
| JP (1) | JP5056855B2 (en) |
| CN (1) | CN101821560B (en) |
| AU (1) | AU2008310483B2 (en) |
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| EP2242966B1 (en) * | 2008-02-20 | 2012-11-07 | 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 |
| CN104246378B (en) * | 2012-05-03 | 2018-02-16 | 开利公司 | Air-conditioning system with supercooling phase-change material |
| CN103115417B (en) * | 2013-03-19 | 2015-04-01 | 海尔集团公司 | Refrigeration method of low temperature environment 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 |
| 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 |
| WO2017064755A1 (en) * | 2015-10-13 | 2017-04-20 | 三菱電機株式会社 | Air conditioner and air conditioner control method |
| CN106352636B (en) * | 2016-10-31 | 2019-05-03 | 广东美的制冷设备有限公司 | Air-conditioner control method, controller and air conditioner |
| 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 |
| AU2017436890B2 (en) * | 2017-10-27 | 2021-12-09 | Mitsubishi Electric Corporation | Refrigeration cycle device |
| US10655878B2 (en) * | 2018-07-06 | 2020-05-19 | Johnson Controls Technology Company | Variable refrigerant flow system with sub-cooling temperature optimization using extremum-seeking control |
| JP2020122627A (en) * | 2019-01-31 | 2020-08-13 | 株式会社富士通ゼネラル | Air conditioner |
| US11143421B2 (en) * | 2019-05-31 | 2021-10-12 | Rheem Manufacturing Company | Sequential hot gas reheat system in an air conditioning unit |
| EP3816542A1 (en) * | 2019-10-29 | 2021-05-05 | Daikin Industries, Ltd. | Refrigerant system |
| 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 |
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| JPH07107467B2 (en) * | 1988-02-19 | 1995-11-15 | 三洋電機株式会社 | Refrigeration equipment |
| JP3290306B2 (en) * | 1994-07-14 | 2002-06-10 | 東芝キヤリア株式会社 | Air conditioner |
| JP3511708B2 (en) * | 1995-01-10 | 2004-03-29 | ダイキン工業株式会社 | Operation control unit for air conditioner |
| EP0751356B1 (en) * | 1995-06-26 | 2003-02-05 | Denso Corporation | Air conditioning apparatus |
| JP3063574B2 (en) * | 1995-06-26 | 2000-07-12 | 株式会社デンソー | Air conditioner |
| JP2001263831A (en) | 2000-03-24 | 2001-09-26 | Mitsubishi Electric Corp | Refrigerating cycle system |
| JP2001280735A (en) * | 2000-03-30 | 2001-10-10 | Tokyo Gas Co Ltd | Engine-driven heat pump type air-conditioning device having hot water supplying device |
| JP4284262B2 (en) * | 2004-10-08 | 2009-06-24 | 三菱電機株式会社 | Refrigeration air conditioner |
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| AU2008310483B2 (en) | 2011-09-08 |
| ES2716469T3 (en) | 2019-06-12 |
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| AU2008310483A1 (en) | 2009-04-16 |
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| JPWO2009047906A1 (en) | 2011-02-17 |
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| CN101821560A (en) | 2010-09-01 |
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