US20110132011A1 - Air conditioning apparatus - Google Patents

Air conditioning apparatus Download PDF

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Publication number
US20110132011A1
US20110132011A1 US13/054,823 US200913054823A US2011132011A1 US 20110132011 A1 US20110132011 A1 US 20110132011A1 US 200913054823 A US200913054823 A US 200913054823A US 2011132011 A1 US2011132011 A1 US 2011132011A1
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United States
Prior art keywords
expansion valve
high pressure
outdoor
refrigerant
flow rate
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Abandoned
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US13/054,823
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English (en)
Inventor
Akiharu Kojima
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Daikin Industries Ltd
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Daikin Industries Ltd
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOJIMA, AKIHARU
Publication of US20110132011A1 publication Critical patent/US20110132011A1/en
Abandoned legal-status Critical Current

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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
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • 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
    • F24F2140/10—Pressure
    • F24F2140/12—Heat-exchange fluid pressure
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2600/21—Refrigerant outlet evaporator 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to an air conditioning apparatus and particularly to an air conditioning apparatus that is equipped with a blower fan that supplies air as a heat source to a condenser that configures a refrigerant circuit and which air conditioning apparatus can control the air flow rate of the blower fan such that high pressure in a refrigeration cycle operation becomes a target high pressure.
  • An air conditioning apparatus pertaining to a first aspect of the invention comprises: a refrigerant circuit that is configured as a result of a compressor, a condenser, a first expansion valve, a second expansion valve, and an evaporator being sequentially connected; and a blower fan that supplies air as a heat source to the condenser, wherein the air flow rate of the blower fan and the opening degree of the first expansion valve are controlled such that high pressure in a refrigeration cycle operation of the refrigerant circuit becomes a target high pressure.
  • “high pressure in a refrigeration cycle operation” means the pressure of the refrigerant flowing from the discharge side of the compressor, through the condenser, and into the first expansion valve.
  • target high pressure is not something that means just a single pressure value but is something that also means, for example, a pressure range between a lower limit value of the high pressure and an upper limit value of the high pressure.
  • the quantity of the refrigerant accumulating in the condenser is adjusted by controlling the opening degree of the first expansion valve, and therefore control of the high pressure can be performed, so even in an operating condition where the temperature difference between the saturation temperature of the refrigerant in the condenser and the temperature of the air is small and where it is easy for the heat exchange efficiency in the condenser to drop, like, for example, when the outside air temperature is high, the high pressure can be raised and a situation where the heat exchange efficiency in the condenser drops can be suppressed.
  • the high pressure can be maintained by accumulating the refrigerant in the condenser, and in a situation where the high pressure rises too much in a step where the air flow rate is small, the high pressure can be maintained by decreasing the refrigerant accumulating in the condenser.
  • An air conditioning apparatus pertaining to a second aspect of the invention is the air conditioning apparatus pertaining to the first aspect of the invention, wherein the opening degree of the first expansion valve is controlled such that the high pressure becomes the target high pressure in a state where air flow rate control of the blower fan has been performed such that the air flow rate of the blower fan becomes a prescribed air flow rate, and when the high pressure does not become the target high pressure by opening degree control of the first expansion valve, the prescribed air flow rate is changed by air flow rate control of the blower fan.
  • control is performed such that the high pressure becomes the target high pressure by opening degree control of the first expansion valve, and basically opening degree control of the first expansion valve becomes performed preferentially over air flow rate control of the blower fan because the prescribed air flow rate of the blower fan is changed when the high pressure does not become the target high pressure by just opening degree control of the first expansion valve, so the high pressure can be controlled even more finely.
  • An air conditioning apparatus pertaining to a third aspect of the invention is the air conditioning apparatus pertaining to the second aspect of the invention, wherein a receiver that can accumulate refrigerant is connected between the first expansion valve and the second expansion valve.
  • the quantity of the refrigerant accumulating in the condenser fluctuates because of opening degree control of the first expansion valve, but because this fluctuation in the quantity of the refrigerant is absorbed as a result of the quantity of the refrigerant accumulating in the receiver fluctuating and the state of the refrigerant sent to the evaporator is stable, a situation where the quantity of the refrigerant in the evaporator fluctuates or where the state of the refrigerant sucked into the compressor fluctuates, for example, can be suppressed.
  • An air conditioning apparatus pertaining to a fourth aspect of the invention is the air conditioning apparatus pertaining to the third aspect of the invention, wherein the opening degree of the second expansion valve is controlled such that a degree of superheat of refrigerant in an outlet of the evaporator or a state quantity equivalent to the degree of superheat becomes a target degree of superheat or a target state quantity equivalent to the target degree of superheat.
  • state quantity equivalent to the degree of superheat and “target state quantity equivalent to the target degree of superheat” mean not only the degree of superheat of the refrigerant in the outlet of the evaporator but include also a state quantity equivalent to the degree of superheat of the refrigerant in the outlet of the evaporator, such as the degree of superheat of the refrigerant in the discharge of the compressor.
  • FIG. 1 is a general configuration diagram of an air conditioning apparatus pertaining to an embodiment of the present invention.
  • FIG. 2 is a control block diagram of the air conditioning apparatus.
  • FIG. 3 is a flowchart mainly showing control of an outdoor expansion valve of the air conditioning apparatus pertaining to the embodiment of the present invention.
  • FIG. 4 is a flowchart mainly showing control of an outdoor fan of the air conditioning apparatus pertaining to the embodiment of the present invention.
  • FIG. 5 is a diagram showing the distribution (excluding the insides of pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus pertaining to the embodiment of the present invention is stable at a standard pressure.
  • FIG. 6 is a diagram showing the distribution (excluding the insides of pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus pertaining to the embodiment of the present invention is stable at a high pressure.
  • FIG. 7 is a diagram showing the distribution (excluding the insides of pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus pertaining to the embodiment of the present invention is stable at a low pressure.
  • FIG. 1 is a general configuration diagram of an air conditioning apparatus 1 pertaining to the embodiment of the present invention.
  • the air conditioning apparatus 1 is an apparatus used to cool the inside of a room in a building or the like by performing a vapor compression refrigeration cycle operation.
  • the air conditioning apparatus 1 is mainly equipped with an outdoor unit 2 , an indoor unit 4 , and a liquid refrigerant connection pipe 5 and a gas refrigerant connection pipe 6 that interconnect the outdoor unit 2 and the indoor unit 4 . That is, a vapor compression refrigerant circuit 10 of the air conditioning apparatus 1 of the present embodiment is configured as a result of the outdoor unit 2 , the indoor unit 4 , and the liquid refrigerant connection pipe 5 and the gas refrigerant connection pipe 6 being connected.
  • the indoor unit 4 is installed by being embedded in or hung from a ceiling inside a room in a building or the like or by being mounted on a wall surface inside a room or the like.
  • the indoor unit 4 is connected to the outdoor unit 2 via the liquid refrigerant connection pipe 5 and the gas refrigerant connection pipe 6 and configures part of the refrigerant circuit 10 .
  • the indoor unit 4 mainly has an indoor-side refrigerant circuit 10 a that configures part of the refrigerant circuit 10 .
  • This indoor-side refrigerant circuit 10 a mainly has an indoor expansion valve EV 2 serving as a second expansion valve and an indoor heat exchanger 41 .
  • the indoor expansion valve EV 2 is an electrically driven expansion valve that is connected to the liquid side of the indoor heat exchanger 41 in order to adjust, for example, the flow rate of the refrigerant flowing through the inside of the indoor-side refrigerant circuit 10 a.
  • the indoor heat exchanger 41 is a cross-fin type fin-and-tube heat exchanger configured by heat transfer tubes and numerous fins and is a heat exchanger that functions as an evaporator of the refrigerant to cool the room air.
  • the indoor unit 4 has an indoor fan 42 for sucking the room air into the inside of the unit, allowing heat to be exchanged with the refrigerant in the indoor heat exchanger 41 , and thereafter supplying the air to the inside of the room as supply air.
  • the indoor fan 42 is, in the present embodiment, a centrifugal fan or a multiblade fan or the like driven by an indoor fan motor 42 a.
  • the indoor unit 4 has an indoor-side controller 43 that controls the operation of each part configuring the indoor unit 4 .
  • the indoor-side controller 43 has a microcomputer and a memory and the like disposed in order to control the indoor unit 4 and is configured such that it can exchange control signals and the like with a remote controller (not shown) for individually operating the indoor unit 4 and such that it can exchange control signals and the like with the outdoor unit 2 via a transmission line 7 a.
  • the outdoor unit 2 is installed outdoors of a building or the like, is connected to the indoor unit 4 via the liquid refrigerant connection pipe 5 and the gas refrigerant connection pipe 6 , and configures the refrigerant circuit 10 together with the indoor unit 4 .
  • the outdoor unit 2 mainly has an outdoor-side refrigerant circuit 10 b that configures part of the refrigerant circuit 10 .
  • This outdoor-side refrigerant circuit 10 b mainly has a compressor 21 , an outdoor heat exchanger 22 , an outdoor expansion valve EV 1 serving as a first expansion valve, a receiver 23 , a liquid-side stop valve 24 , and a gas-side stop valve 25 .
  • the compressor 21 is, in the present embodiment, a positive displacement compressor driven by a compressor motor 21 a.
  • the compressor motor 21 a is configured such that it is driven as a result of being supplied with electrical power via an inverter device (not shown) and such that it can vary its operating capacity by varying its frequency (that is, its speed).
  • the outdoor heat exchanger 22 is a cross-fin type fin-and-tube heat exchanger configured by heat transfer tubes and numerous fins and is a heat exchanger that functions as a condenser of the refrigerant.
  • the gas side of the outdoor heat exchanger 22 is connected to the compressor 21 , and the liquid side of the outdoor heat exchanger 22 is connected to the outdoor expansion valve EV 1 .
  • the outdoor unit 2 has an outdoor fan 26 serving as a blower fan for sucking outdoor air into the inside of the unit, allowing heat to be exchanged with the refrigerant in the outdoor heat exchanger 22 , and thereafter expelling the air to the outdoors.
  • This outdoor fan 26 is a fan that can vary the air flow rate of the outdoor air as a heat source supplied to the outdoor heat exchanger 22 and, in the present embodiment, is a propeller fan or the like driven by an outdoor fan motor 26 a comprising a DC fan motor.
  • the outdoor fan motor 26 a is configured such that it is driven as a result of being supplied with electrical power via an inverter device (not shown) and such that it can vary the air flow rate of the outdoor fan 26 by stepwise varying its frequency (that is, its speed).
  • the receiver 23 is a container that can accumulate refrigerant and is connected between the outdoor expansion valve EV 1 and the liquid-side stop valve 24 ; the receiver 23 can absorb fluctuations in the distribution of the quantity of the refrigerant in the refrigerant circuit 10 .
  • the liquid-side stop valve 24 and the gas-side stop valve 25 are valves disposed in openings to which external devices and pipes (specifically, the liquid refrigerant connection pipe 5 and the gas refrigerant connection pipe 6 ) connect.
  • the liquid-side stop valve 24 is connected to the receiver 23 .
  • the gas-side stop valve 25 is connected to the compressor 21 .
  • various sensors are disposed in the outdoor unit 2 .
  • a suction pressure sensor 27 that detects the suction pressure of the compressor 21
  • a discharge pressure sensor 28 that detects the discharge pressure of the compressor 21
  • a suction temperature sensor 29 that detects the suction temperature of the compressor 21
  • a discharge temperature sensor 30 that detects the discharge temperature of the compressor 21
  • the suction temperature sensor 29 and the discharge temperature sensor 30 comprise thermistors.
  • the outdoor unit 2 has an outdoor-side controller 31 that controls the operation of each part configuring the outdoor unit 2 .
  • the outdoor-side controller 31 has a microcomputer and a memory disposed in order to control the outdoor unit 2 and an inverter circuit and the like that controls the compressor motor 21 a, and the outdoor-side controller 31 is configured such that it can exchange control signals and the like with the indoor-side controller 43 of the indoor unit 4 via the transmission line 7 a. That is, a controller 7 that performs operation control of the entire air conditioning apparatus 1 is configured by the indoor-side controller 43 , the outdoor-side controller 31 , and the transmission line 7 a that interconnects the indoor-side controller 43 and the outdoor-side controller 31 .
  • the controller 7 is, as shown in FIG. 2 , connected such that it can receive detection signals of the various sensors 27 to 30 and is connected such that it can control the various devices and valves 21 a, 26 a, 42 a, EV 1 , and EV 2 on the basis of these detection signals and the like.
  • FIG. 2 is a control block diagram of the air conditioning apparatus 1 .
  • the refrigerant connection pipes 5 and 6 are refrigerant pipes constructed on site when installing the air conditioning apparatus 1 in an installation location such as a building, and pipes having various lengths and pipe diameters are used depending on installation conditions such as the installation location and the combination of the outdoor unit and the indoor unit.
  • the refrigerant circuit 10 of the air conditioning apparatus 1 is configured as a result of the indoor-side refrigerant circuit 10 a, the outdoor-side refrigerant circuit 10 b, and the refrigerant connection pipes 5 and 6 being connected, that is, as a result of the compressor 21 , the outdoor heat exchanger 22 serving as the condenser, the outdoor expansion valve EV 1 serving as the first expansion valve, the receiver 23 , the refrigerant pipes 5 and 6 , the indoor expansion valve EV 2 serving as the second expansion valve, and the indoor heat exchanger 41 serving as the evaporator being sequentially connected.
  • the air conditioning apparatus 1 of the present embodiment is configured such that it can use the controller 7 configured from the indoor-side controller 43 and the outdoor-side controller 31 to perform control of each device of the outdoor unit 2 and the indoor unit 4 .
  • the high-pressure liquid refrigerant that has condensed in the outdoor heat exchanger 22 is sent to the indoor unit 4 via the outdoor expansion valve EV 1 (here, in a completely open state) serving as the first expansion valve, the receiver 23 , the liquid-side stop valve 24 , and the liquid refrigerant connection pipe 5 .
  • the outdoor expansion valve EV 1 here, in a completely open state
  • This high-pressure liquid refrigerant that has been sent to the indoor unit 4 has its pressure reduced by the indoor expansion valve EV 2 serving as the second expansion valve, becomes low-pressure refrigerant in a gas-liquid two-phase state, is sent to the indoor heat exchanger 41 , evaporates in the indoor heat exchanger 41 as a result of undergoing heat exchange with the room air supplied by the indoor fan 42 and being heated, and becomes low-pressure gas refrigerant.
  • This low-pressure gas refrigerant that has evaporated in the indoor heat exchanger 41 is sent to the outdoor unit 2 via the gas refrigerant connection pipe 6 and the gas-side stop valve 25 and is again sucked into the compressor 21 . In this manner, in the refrigerant circuit 10 of the air conditioning apparatus 1 of the present embodiment, a refrigeration cycle operation that cools the inside of the room is performed.
  • the heat exchange efficiency in the outdoor heat exchanger 22 comes to fluctuate because the temperature difference between the saturation temperature of the refrigerant in the outdoor heat exchanger 22 and the air temperature fluctuates depending on fluctuations in the outside air temperature.
  • control is performed with respect to the air flow rate of the outdoor fan 26 such that high pressure in the refrigeration cycle operation (in the present embodiment, the pressure of the refrigerant flowing from the discharge side of the compressor 21 , through the outdoor heat exchanger 22 , and into the outdoor expansion valve EV 1 ) becomes a target high pressure, but with just air flow rate control of the outdoor fan 26 , the heat exchange efficiency in the outdoor heat exchanger 22 drops and therefore there is the fear that the operating efficiency of the air conditioning apparatus 1 overall cannot be optimized because sometimes the air flow rate can only be changed stepwise, it is difficult to control the high pressure finely, and the temperature difference between the saturation temperature of the refrigerant in the outdoor heat exchanger 22 and the temperature of the air becomes smaller particularly when the outside air temperature is high.
  • the air conditioning apparatus 1 is configured such that the high pressure can be controlled finely mainly not just by air flow rate control of the outdoor fan 26 but by jointly using opening degree control of the outdoor expansion valve EV 1 .
  • FIG. 3 is a flowchart mainly showing control of the outdoor expansion valve EV 1 of the air conditioning apparatus 1 pertaining to the present embodiment
  • FIG. 4 is a flowchart mainly showing control of the outdoor fan 26 of the air conditioning apparatus 1 pertaining to the present embodiment
  • FIG. 5 is a diagram showing the distribution (excluding the insides of the pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus 1 pertaining to the present embodiment is stable at a standard pressure
  • FIG. 3 is a flowchart mainly showing control of the outdoor expansion valve EV 1 of the air conditioning apparatus 1 pertaining to the present embodiment
  • FIG. 4 is a flowchart mainly showing control of the outdoor fan 26 of the air conditioning apparatus 1 pertaining to the present embodiment
  • FIG. 5 is a diagram showing the distribution (excluding the insides of the pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus 1 pertaining to the present embodiment is stable at a standard pressure
  • FIG. 3 is a flowchart mainly showing control of the outdoor expansion valve EV
  • FIG. 6 is a diagram showing the distribution (excluding the insides of the pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus 1 pertaining to the present embodiment is stable at a high pressure
  • FIG. 7 is a diagram showing the distribution (excluding the insides of the pipes) of liquid refrigerant when the high pressure in the air conditioning apparatus 1 pertaining to the present embodiment is stable at a low pressure.
  • step S 1 the outdoor expansion valve EV 1 is placed in a completely open state, and in step S 2 , it is determined whether or not the outdoor fan 26 serving as the blower fan has reached a prescribed air flow rate.
  • the step of changing the air flow rate of the outdoor fan 26 is divided into plural stages, and “prescribed air flow rate” means any of these plural steps of changing the air flow rate.
  • the prescribed air flow rate of the outdoor fan 26 is set to a predetermined initial air flow rate.
  • step S 3 changing of the air flow rate of the outdoor fan 26 in step S 3 is performed, and then the flow moves to the processing of step S 4 .
  • step S 4 it is determined whether or not the opening degree of the outdoor expansion valve EV 1 is smaller than a minimum opening degree+ ⁇ .
  • a means a fluctuation in the opening degree of the outdoor expansion valve EV 1 that is needed until the inside of the refrigerant circuit 10 becomes stable by changing the prescribed air flow rate of the outdoor fan 26 .
  • the outdoor expansion valve EV 1 is in the completely open state and its opening degree is not smaller than the minimum opening degree+ ⁇ , so the flow moves to the processing of step S 5 .
  • step S 5 it is determined whether or not the high pressure in the refrigeration cycle operation is larger than a lower limit value of a target high pressure.
  • the discharge pressure detected by the discharge pressure sensor 28 is used for the high pressure.
  • the target high pressure is defined as a pressure range between a lower limit value and an upper limit value, and these are set on the basis of conditions such as the operating capacity of the compressor 21 and the outside air temperature in step S 13 described later.
  • step S 7 it is determined whether or not the high pressure in the refrigeration cycle operation is larger than the upper limit value of the target high pressure. Then, when it has been determined in step S 7 that the high pressure in the refrigeration cycle operation is not larger than the upper limit value of the target high pressure, the flow moves to the processing of step S 8 where the opening degree of the outdoor expansion valve EV 1 is maintained at the current opening degree. Further, when it has been determined in step S 7 that the high pressure in the refrigeration cycle operation is larger than the upper limit value of the target high pressure, the flow moves to the processing of step S 9 where an opening operation that increases the opening degree of the outdoor expansion valve EV 1 is performed, and then the flow moves to the processing of step S 10 .
  • step S 10 it is determined whether or not the opening degree of the outdoor expansion valve EV 1 is greater than completely open ⁇ .
  • ⁇ means a fluctuation in the opening degree of the outdoor expansion valve EV 1 that is needed until the inside of the refrigerant circuit 10 becomes stable by changing the prescribed air flow rate of the outdoor fan 26 .
  • step S 10 when it has been determined in step S 10 that the opening degree of the outdoor expansion valve EV 1 is not larger than completely open ⁇ , the flow returns to the processing of step S 4 and goes through the processing of steps S 4 and S 5 , and the opening operation of the outdoor expansion valve EV 1 in step S 9 is repeated until it is determined in step S 7 that the high pressure in the refrigeration cycle operation is larger than the upper limit value of the target high pressure or until it is determined in step S 10 that the opening degree of the outdoor expansion valve EV 1 is larger than completely open ⁇ .
  • control of the opening degree of the outdoor expansion valve EV 1 is performed such that the high pressure in the refrigeration cycle operation falls inside the pressure range between the lower limit value and the upper limit value of the target high pressure in a state where the outdoor fan 26 has been set to a certain prescribed air flow rate.
  • step S 5 when it has not been determined in step S 5 that the high pressure in the refrigeration cycle operation is larger than the lower limit value of the target high pressure and it has been determined in step S 4 that the opening degree of the outdoor expansion valve EV 1 is smaller than the minimum opening degree+ ⁇ , or when it has not been determined in step S 7 that the high pressure in the refrigeration cycle operation is not larger than the upper limit value of the target high pressure and it has been determined in step S 10 that the opening degree of the outdoor expansion valve EV 1 is larger than completely open ⁇ , the high pressure in the refrigeration cycle operation cannot fall inside the pressure range between the lower limit value and the upper limit value of the target high pressure by just opening degree control of the outdoor expansion valve EV 1 , and so the flow moves to the processing of step S 11 where the prescribed air flow rate is changed by air flow rate control of the outdoor fan 26 , thereafter the flow returns to the processing of steps S 2 and S 3 , and then opening degree control of the outdoor expansion valve EV 1 comprising steps S 4 to S 10 is again performed.
  • step S 12 the operating capacity of the compressor 21 is decided on the basis of conditions such as the evaporation temperature, and the operating capacity of the compressor 21 is set by frequency control of the compressor motor 21 a.
  • a value obtained by converting the suction pressure detected by the suction pressure sensor 27 into the saturation temperature is used for the evaporation temperature.
  • step S 13 a target high pressure (here, a lower limit value and an upper limit value) is set on the basis of conditions such as the operating capacity of the compressor 21 decided that was in step S 12 and the outside air temperature.
  • step S 14 like in step S 7 described above, it is determined whether or not the high pressure in the refrigeration cycle operation is larger than the upper limit value of the target high pressure. Then, when it has been determined in step S 14 that the high pressure in the refrigeration cycle operation is larger than the upper limit value of the target high pressure, the flow moves to the processing of step S 15 where, like in step S 10 described above, it is determined whether or not the opening degree of the outdoor expansion valve EV 1 is larger than completely open ⁇ .
  • step S 15 when it has been determined in step S 15 that the opening degree of the outdoor expansion valve EV 1 is not larger than completely open ⁇ , the flow moves to step S 16 where it waits for the opening degree control of the outdoor expansion valve EV 1 described above to be reflected, and then the flow returns to the processing of step S 12 .
  • step S 17 when it has been determined in step S 15 that the opening degree of the outdoor expansion valve EV 1 is larger than completely open ⁇ , the flow moves to step S 17 , which corresponds to step S 11 described above, where the prescribed air flow rate of the outdoor fan 26 is changed in a direction in which it is increased, and then the flow returns to the processing of step S 12 .
  • step S 18 when it has been determined in step S 14 that the high pressure in the refrigeration cycle operation is not larger than the upper limit value of the target high pressure, the flow moves to the processing of step S 18 .
  • step S 18 which corresponds to step S 5 described above, it is determined whether or not the high pressure in the refrigeration cycle operation is smaller than the lower limit value of the target high pressure. Then, when it has been determined in step S 18 that the high pressure in the refrigeration cycle operation is smaller than the lower limit value of the target high pressure, the flow moves to the processing of step S 19 where, like in step S 10 described above, it is determined whether or not the opening degree of the outdoor expansion valve EV 1 is smaller than the minimum opening degree+ ⁇ .
  • step S 19 when it has been determined in step S 19 that the opening degree of the outdoor expansion valve EV 1 is not smaller than the minimum opening degree+ ⁇ , the flow moves to step S 20 where it waits for the opening degree control of the outdoor expansion valve EV 1 described above to be reflected, and then the flow returns to the processing of step S 12 . Further, when it has been determined in step S 19 that the opening degree of the outdoor expansion valve EV 1 is smaller than the minimum opening degree+ ⁇ , the flow moves to step S 21 , which corresponds to step S 11 described above, where the prescribed air flow rate of the outdoor fan 26 is changed in a direction in which it is decreased, and then the flow returns to step S 12 . Further, also when it has been determined in step S 18 that the high pressure in the refrigeration cycle operation is not smaller than the lower limit value of the target high pressure, the flow returns to the processing of step S 12 .
  • control of the opening degree of the outdoor expansion valve EV 1 is performed such that the high pressure becomes the target high pressure in a state where air flow rate control of the outdoor fan 26 has been performed such that the air flow rate of the outdoor fan 26 becomes the prescribed air flow rate, and when the high pressure does not become the target high pressure by opening degree control of the outdoor expansion valve EV 1 , control by which the prescribed air flow rate is changed by air flow rate control of the outdoor fan 26 is performed.
  • the opening degree of the indoor expansion valve EV 2 is controlled such that the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 serving as the evaporator becomes a target degree of superheat.
  • the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 is obtained by converting the suction pressure detected by the suction pressure sensor 27 into the saturation temperature and subtracting this saturation temperature from the suction temperature detected by the suction temperature sensor 29 .
  • the distribution (excluding the insides of the pipes) of the liquid refrigerant in the refrigerant circuit 10 becomes the state shown in FIG. 5 (the hatchings shown in the outdoor heat exchanger 22 , the receiver 23 , and the indoor heat exchanger 41 represent the liquid refrigerant).
  • the receiver 23 is connected between the outdoor expansion valve EV 1 and the indoor expansion valve EV 2 , so as shown in FIG. 6 , the increase in the quantity of the liquid refrigerant accumulating in the outdoor heat exchanger 22 that arises because of the closing operation of the outdoor expansion valve EV 1 is absorbed as a result of the quantity of the liquid refrigerant accumulating in the receiver 23 decreasing.
  • opening degree control of the indoor expansion valve EV 2 is performed such that the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 becomes the target degree of superheat, so as shown in FIG.
  • the quantity of the liquid refrigerant accumulating in the outdoor heat exchanger 22 decreases as shown in FIG. 7 because the opening degree of the outdoor expansion valve EV 1 becomes larger because of the opening operation of the outdoor expansion valve EV 1 in step S 8 , and so the interior capacity of the outdoor heat exchanger 22 increases.
  • the receiver 23 is connected between the outdoor expansion valve EV 1 and the indoor expansion valve EV 2 , so as shown in FIG. 7 , the decrease in the quantity of the liquid refrigerant accumulating in the outdoor heat exchanger 22 that arises because of the opening operation of the outdoor expansion valve EV 1 is absorbed as a result of the quantity of the liquid refrigerant accumulating in the receiver 23 increasing.
  • opening degree control of the indoor expansion valve EV 2 is performed such that the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 becomes the target degree of superheat, so as shown in FIG.
  • the air conditioning apparatus 1 of the present embodiment has the following characteristics.
  • the quantity of the refrigerant accumulating in the outdoor heat exchanger 22 serving as the condenser is adjusted by controlling the opening degree of the outdoor expansion valve EV 1 serving as the first expansion valve, and therefore control of the high pressure can be performed, so even in an operating condition where the temperature difference between the saturation temperature of the refrigerant in the outdoor heat exchanger 22 and the temperature of the air is small and where it is easy for the heat exchange efficiency in the outdoor heat exchanger 22 to drop, like, for example, when the outside air temperature is high, the high pressure can be raised and a situation where the heat exchange efficiency in the outdoor heat exchanger 22 drops can be suppressed.
  • the high pressure can be maintained by accumulating the refrigerant in the outdoor heat exchanger 22 , and in a situation where the high pressure rises too much in a step where the air flow rate is small, the high pressure can be maintained by decreasing the refrigerant accumulating in the outdoor heat exchanger 22 .
  • control is performed such that the high pressure becomes the target high pressure by opening degree control of the outdoor expansion valve EV 1 , and basically opening degree control of the outdoor expansion valve EV 1 becomes performed preferentially over air flow rate control of the outdoor fan 26 because the prescribed air flow rate of the outdoor fan 26 is changed when the high pressure does not become the target high pressure by just opening degree control of the outdoor expansion valve EV 1 , so the high pressure can be controlled even more finely.
  • the quantity of the refrigerant accumulating in the outdoor heat exchanger 22 fluctuates because of opening degree control of the outdoor expansion valve EV 1 , but because this fluctuation in the quantity of the refrigerant is absorbed as a result of the quantity of the refrigerant accumulating in the receiver 23 fluctuating and the state of the refrigerant sent to the indoor heat exchanger 41 serving as the evaporator is stable, a situation where the quantity of the refrigerant in the indoor heat exchanger 41 fluctuates or where the state of the refrigerant sucked into the compressor 21 fluctuates, for example, can be suppressed.
  • the air conditioning apparatus 1 of the present embodiment even though control is performed such that the high pressure becomes the target high pressure by jointly using opening degree control of the outdoor expansion valve EV 1 together with air flow rate control of the outdoor fan 26 , it becomes difficult for the quantity of the refrigerant in the portion of the refrigerant circuit 10 from the indoor expansion valve EV 2 via the indoor heat exchanger 41 to the compressor 21 to fluctuate because the receiver 23 that can accumulate the refrigerant is connected between the outdoor expansion valve EV 1 and the indoor expansion valve EV 2 serving as the second expansion valve, and therefore it can be made difficult for the control to affect the operating state of the indoor heat exchanger 41 or the compressor 21 .
  • the air conditioning apparatus 1 of the present embodiment it can be made difficult for the quantity of the refrigerant in the portion of the refrigerant circuit 10 from the indoor expansion valve EV 2 via the indoor heat exchanger 41 to the compressor 21 to fluctuate because of the receiver 23 , and the quantity of the refrigerant in the indoor heat exchanger 41 and the state of the refrigerant in the outlet of the indoor heat exchanger 41 can be stabilized by opening degree control of the indoor expansion valve EV 2 , so the operating efficiency of the air conditioning apparatus 1 overall can be optimized and the reliability of the compressor 21 can be improved (e.g., out-of-gas operation and wet compression can be prevented).
  • the present invention was applied to the separate type air conditioning apparatus 1 where the compressor 21 and the outdoor heat exchanger 22 are disposed in the outdoor unit 2 , but the present invention is not limited to this and may also be applied to air conditioning apparatus of other unit configurations, such as a remote condenser type air conditioning apparatus where the compressor 21 is disposed in the indoor unit 4 .
  • the present invention was applied to the dedicated cooling type air conditioning apparatus 1 that performs only cooling, but the present invention is not limited to this and may also be applied to air conditioning apparatus of other types, such as a cooling-and-heating switchable type air conditioning apparatus that can switch between cooling and heating and a simultaneous cooling-and-heating type air conditioning apparatus that can simultaneously perform cooling and heating.
  • the discharge pressure detected by the discharge pressure sensor 28 was used as the high pressure, but the present invention is not limited to this, and temperatures or pressures detected by other types of sensors may also be used; for example, when a temperature sensor is disposed in the outdoor heat exchanger 22 , the refrigerant temperature detected by this temperature sensor may be converted to the saturation pressure and used as the high pressure.
  • the target high pressure was defined as a pressure range between the lower limit value of the high pressure and the upper limit value of the high pressure, but the target high pressure is not limited to this and may also, for example, be a single pressure value.
  • the opening degree of the indoor expansion valve EV 2 serving as the second expansion valve is controlled such that the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 serving as the evaporator becomes the target degree of superheat, but the present invention is not limited to this; the opening degree of the indoor expansion valve EV 2 may also be controlled such that a state quantity equivalent to the degree of superheat of the refrigerant in the outlet of the indoor heat exchanger 41 , such as the degree of superheat of the refrigerant in the discharge of the compressor 21 , becomes a target state quantity equivalent to the target degree of superheat.
  • the degree of superheat of the refrigerant in the discharge of the compressor 21 is obtained by subtracting, from the discharge temperature of the compressor 21 (the discharge temperature detected by the discharge temperature sensor 30 ), a value obtained by converting the discharge pressure of the compressor 21 (the discharge pressure detected by the discharge pressure sensor 28 ) into the saturation temperature.
  • opening and closing the outdoor expansion valve EV 1 depending on whether the high pressure is high or low with respect to the target high pressure has been described, but the speed at which the outdoor expansion valve EV 1 is opened and closed may also be varied depending on the difference between the high pressure and the target high pressure, and PI control or the like may also be applied in relation to deciding the speed at which the outdoor expansion valve EV 1 is opened and closed.
  • controlling the outdoor expansion valve EV 1 before or during changing the air flow rate of the outdoor fan 26 has not been described, but changes in the high pressure resulting from changing the air flow rate of the outdoor fan 26 may be predicted beforehand, and feed-forward control that performs control to open and close the outdoor expansion valve EV 1 by a predetermined opening degree beforehand or performs control to open and close the outdoor expansion valve EV 1 at a predetermined speed within a predetermined amount of time beforehand may also be performed.
  • the present invention is widely applicable to air conditioning apparatus that are equipped with a blower fan that supplies air as a heat source to a condenser that configures a refrigerant circuit and which air conditioning apparatus can control the air flow rate of the blower fan such that high pressure in a refrigeration cycle operation becomes a target high pressure.
  • Patent Literature 1 JP-A No. 1-225852

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
US13/054,823 2008-07-29 2009-07-23 Air conditioning apparatus Abandoned US20110132011A1 (en)

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JP2008194955A JP4497234B2 (ja) 2008-07-29 2008-07-29 空気調和装置
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PCT/JP2009/003468 WO2010013416A1 (ja) 2008-07-29 2009-07-23 空気調和装置

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CN112805514A (zh) * 2018-11-15 2021-05-14 李东源 改善了效率的热泵
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CN113915722A (zh) * 2021-10-28 2022-01-11 宁波奥克斯电气股份有限公司 一种低温制冷时的控制方法、装置及多联机系统
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US20140140810A1 (en) * 2011-06-22 2014-05-22 Carrier Corporation Condenser fan speed control for air conditioning system efficiency optimization
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CN112805514A (zh) * 2018-11-15 2021-05-14 李东源 改善了效率的热泵
US11300313B2 (en) * 2019-02-14 2022-04-12 Qingdao Haier Air-Conditioning Electronic Co., Ltd Cooling medium control method for multi-connected air conditioning system
CN110068101A (zh) * 2019-04-29 2019-07-30 宁波奥克斯电气股份有限公司 换热器清洗控制方法、装置及空调器
CN113757958A (zh) * 2020-06-04 2021-12-07 维谛技术有限公司 一种空调系统的控制方法及装置
CN113915722A (zh) * 2021-10-28 2022-01-11 宁波奥克斯电气股份有限公司 一种低温制冷时的控制方法、装置及多联机系统

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CN102105752A (zh) 2011-06-22
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JP4497234B2 (ja) 2010-07-07

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