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WO2011037012A1 - Climatiseur - Google Patents

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Publication number
WO2011037012A1
WO2011037012A1 PCT/JP2010/065442 JP2010065442W WO2011037012A1 WO 2011037012 A1 WO2011037012 A1 WO 2011037012A1 JP 2010065442 W JP2010065442 W JP 2010065442W WO 2011037012 A1 WO2011037012 A1 WO 2011037012A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
cylinders
air conditioner
refrigerant
temperature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2010/065442
Other languages
English (en)
Japanese (ja)
Inventor
勇輔 関
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Japan Corp
Original Assignee
Toshiba Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Priority to JP2011532956A priority Critical patent/JP5450637B2/ja
Priority to CN201080040862.7A priority patent/CN102667354B/zh
Publication of WO2011037012A1 publication Critical patent/WO2011037012A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • 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 conditioner equipped with a compressor.
  • an air conditioner having an operating capability that matches the volume of the installation location is installed.
  • An air conditioner in recent years is equipped with an inverter, and the operating capacity of the air conditioner is controlled by changing the rotation speed of the compressor by the inverter. For this reason, it can adapt to an installation place or can perform the optimal driving
  • the indoor throttle mechanism is set to the minimum flow rate. Transition. This is a change to the dehumidifying operation mode described above by changing the indoor throttle mechanism.
  • the compressor is operated at a low capacity, but the dehumidifying operation is performed not by the compressor control but by the heat exchanger control in the indoor unit. It has been broken.
  • the amount of refrigerant discharged from the compressor cannot be changed greatly. For this reason, since the amount of circulating refrigerant in the refrigeration cycle does not change greatly, the heat exchange capacity in the indoor heat exchanger cannot be significantly reduced. This is the same during the dehumidifying operation.
  • the indoor throttle mechanism is set to the minimum flow rate under the air conditioning load condition that is lower than the minimum capacity of the compressor, the evaporation temperature becomes low and the air temperature blown into the room is low. .
  • an object of the present invention to provide an air conditioner that can be comfortably air-conditioned by preventing overcooling by operating control that does not overcool the air temperature during cooling.
  • the present embodiment includes an indoor heat exchanger, an indoor unit provided with an indoor fan, a compressor connected to the indoor unit and having a plurality of cylinders, the number of operating cylinders being variable, and outdoor heat exchange. And an outdoor unit provided with a throttle mechanism, and a control unit that variably controls the operating rotational speed of the compressor, and the control unit operates the compressor based on the outside air temperature during cooling operation.
  • An air conditioner capable of operating the air conditioner in an operation mode in which the number of cylinders is set to a minimum number of cylinders and the operation speed of the compressor is set to a minimum number of rotations capable of refrigeration cycle operation. provide.
  • the capacity of the entire refrigeration cycle is reduced by performing an operation in which the refrigerant discharge amount is reduced during the minimum capacity operation during the cooling operation. It can be lowered to prevent the air blown from the indoor unit from being too cold, and comfortable air conditioning becomes possible.
  • the air conditioner 1 includes an indoor unit 2 installed indoors, an outdoor unit 3 connected to the indoor unit 2, and a remote controller 4.
  • the user basically performs various operations such as operation mode selection, temperature setting, and air volume setting of the air conditioner 1 using the remote controller 4.
  • the indoor unit 2 includes a moving panel 2b that can be separated from the front panel 2a.
  • a space is generated between the front panel 2a and the movable panel 2b, and indoor air is sucked through the space (air inlet).
  • An air inlet 2 c is also provided on the upper surface of the indoor unit 2.
  • An air outlet 2d is provided at the lower part of the front panel 2a. The outlet 2d is also provided with a vertical air flow louver 2e for adjusting the blowing air up and down and a horizontal air flow louver 2f for adjusting the blowing air left and right. It has been.
  • the indoor unit 2 accommodates an indoor heat exchanger and an indoor fan (not shown) in a suction port of the front panel 2a and a ventilation path from the suction port 2c to the air outlet 2d.
  • the movable panel 2b is movable in a direction away from the front panel 2a, and the inner suction port is opened by the movement. Further, the movable panel 2b closes the inner suction port by moving (returning) in a direction in contact with the front panel 2a.
  • the indoor unit 2 as shown in FIG. 1 is used, but other types of indoor units (for example, ceiling-mounted-built-in type indoor units) are used. May be.
  • the outdoor unit 3 is installed outside and supplies refrigerant to the indoor unit 2 connected by the refrigeration cycle A (see FIG. 2). Although the outdoor unit 3 is shown in a simplified manner in FIG. 1, as will be described later, the outdoor unit 3 includes a compressor 31 and the like inside.
  • the remote controller 4 is used to transmit an instruction such as an operation mode selected by the user to the indoor unit 2.
  • the remote controller 4 in the present embodiment is provided with a display unit 4a representing various displays and an operation mode button 4b for setting an operation mode of “cooling” or “heating”.
  • buttons such as a temperature setting button are also provided.
  • the shape, design, etc. of the remote controller 4 are merely examples, and the shape, design, etc. are not limited.
  • transmission / reception of signals between the remote controller 4 and the indoor unit 2 can be performed by various communication formats in addition to the wireless communication format as shown in FIG. 1 or FIG. 3.
  • the air conditioner 1 includes the indoor unit 2 and the outdoor unit 3 connected to the indoor unit 2.
  • the indoor unit 2 includes an indoor heat exchanger 21 that performs heat exchange between the refrigerant and room air, and an indoor fan 22 that blows the heat-exchanged air into the room. Is provided.
  • each device normally provided in an indoor unit of an air conditioner is naturally provided.
  • An indoor heat exchanger 21, an indoor fan 22, and a control unit 23 for controlling each device (not shown) are further provided.
  • transmission / reception of signals of the control unit 23 is shown in a simplified manner.
  • a compressor 31, a four-way valve 32, an outdoor heat exchanger 33, a throttling mechanism 34, an accumulator 35, and a switching valve 36 that switches a refrigerant supplied to the compressor 31 are connected via a pipe. It is connected.
  • the indoor unit 2 and the outdoor unit 3 are connected by a refrigerant circulation pipe, and a refrigeration cycle A is configured. That is, the piping is connected between the throttle mechanism 34 of the outdoor unit 3 and the four-way valve 32 so that the indoor heat exchanger 21 of the indoor unit 2 is located.
  • the refrigerant flows in the order of the throttle mechanism 34, the indoor heat exchanger 21, and the four-way valve 32 (during cooling), or in the order of the four-way valve 32, the indoor heat exchanger 21, and the throttle mechanism 34 (during heating).
  • a pulse motor valve (PMV) is used as the throttle mechanism 34, and a four-way valve is used as the switching valve 36.
  • the control unit 37 which controls each apparatus which comprises the outdoor units 3, such as the compressor 31 mentioned above, the outdoor heat exchanger 33, and the switching valve 36, is further provided.
  • transmission / reception of signals of the control unit 33 is shown in a simplified manner.
  • the compressor 31 is a so-called dual compressor provided with a plurality of (two in this embodiment) cylinders as will be described later.
  • the refrigerant is supplied to the compressor 31 via the accumulator 35. Further, the high-pressure refrigerant compressed in the compression chambers 31b and 31f, which will be described later, is discharged to the three-way valve 32 and the like through the internal space of the compressor 31 (the inside of the compressor 31 becomes discharge pressure).
  • a supply path for each of the two cylinders of the compressor 31 is provided on the discharge side of the accumulator 35 (see also FIGS. 4 and 5).
  • the first supply path M that is one system directly supplies the refrigerant to the compressor 31.
  • the refrigerant supplied via the first supply path M is a low-pressure refrigerant that has passed through the accumulator 35.
  • the second supply path N that is the other system supplies the refrigerant to the compressor 31 via the switching valve 36.
  • the refrigerant supplied via the second supply path N is the low-pressure refrigerant (FIG. 4: N1 + N2: O and Q) that has passed through the accumulator 35, or the high-pressure refrigerant supplied from the compressor 31 (FIG. 5: N2). : Any one of P and R).
  • the operation of the air conditioner 1 will be described by taking the cooling operation as an example.
  • the refrigerant flows in the direction indicated by the solid line arrow in FIG.
  • the refrigerant is compressed by the compressor 31 in the outdoor unit 3 and discharged as a high-temperature high-pressure gas.
  • the high-temperature and high-pressure gaseous refrigerant is guided to the outdoor heat exchanger 33 through the four-way valve 32.
  • the refrigerant is cooled by receiving wind from the outdoor fan 38 in the outdoor heat exchanger 33, and a part or all of the refrigerant is condensed.
  • the refrigerant in the liquid phase state or the gas-liquid two-phase state is expanded by the throttle mechanism 34 and becomes a low pressure.
  • the gas-liquid two-phase refrigerant that has exited the throttle mechanism 34 flows into the indoor heat exchanger 21 and exchanges heat with the indoor air. That is, the refrigerant evaporates by heat exchange, and the air sucked into the indoor heat exchanger 21 is cooled. The cooled air is supplied into the room by the indoor fan 22 and the room is cooled. The refrigerant after the heat exchange passes through the four-way valve 32 and returns to the compressor 31 via the accumulator 35. Thereafter, the above-described refrigeration cycle is repeated. On the other hand, in the heating operation, the refrigerant flows in the direction indicated by the broken-line arrow in FIG. 2, and the refrigerant is condensed in the indoor heat exchanger 21 to heat the room.
  • FIG. 3 is a block diagram showing the internal configuration of the control unit 23 of the indoor unit 2 and the control unit 37 of the outdoor unit 3.
  • the control unit 23 of the indoor unit 2 (hereinafter referred to as “indoor control unit 23”) includes a reception unit 23a that receives a signal from the remote controller 4, an MCU (Micro Controller Unit) 23b, and a transmission unit 23c. .
  • MCU Micro Controller Unit
  • the user uses the remote controller 4 to determine various operating conditions such as the operation mode of the air conditioner 1 and transmits it to the indoor unit 2 (indoor control unit 23).
  • the receiving unit 23a transmits the received operating condition to the MCU 23b.
  • the MCU 23b controls the driving of the indoor fan 22 via the driving circuit 23d, or controls the driving of each component device such as the louvers 2e and 2f and the damper via the driving circuit (not shown). Carry out driving based on driving commands from users. Further, the MCU 23b transmits a signal to the outdoor unit 3 through the transmission unit 23c, and the outdoor unit 3 that has received the signal controls driving of the compressor 31 and the like.
  • the indoor unit 2 and the outdoor unit 3 are electrically connected, and a signal transmitted from the indoor control unit 23 is a receiving unit of the control unit 37 of the outdoor unit 3 (hereinafter referred to as “outdoor control unit 37”). Received by 37a.
  • the received signal is transmitted to the drive circuits 37c to 37g that drive each device constituting the outdoor unit 3 via the MCU 37b.
  • the drive circuit 37 c drives the compressor 31.
  • the drive circuit 37d drives the four-way valve 32, and the drive circuit 37e drives the throttle mechanism 34.
  • the drive circuit 37f drives the switching valve 36, and the drive circuit 37g drives the outdoor fan 38.
  • the compressor 31 is provided with two upper and lower compression chambers 31b and 31f with an intermediate partition plate 31a interposed therebetween.
  • Low pressure refrigerant is supplied to the upper compression chamber 31b through the first supply path M, and the upper rolling piston 31c rotates to compress the refrigerant.
  • An upper vane 31d is pressed against the upper rolling piston 31c by an elastic body (spring) 31e. Therefore, the upper vane 31d reciprocates following the rotation of the upper rolling piston 31c.
  • the lower compression chamber 31f is supplied with a low-pressure or high-pressure refrigerant through the second supply path N as will be described later.
  • the low-pressure refrigerant supplied (FIG. 4)
  • the lower rolling piston 31g rotates to compress the refrigerant into a high-pressure refrigerant and send it to the outdoor heat exchanger 33.
  • a lower vane 31h is pressed against the lower rolling piston 31g by an elastic body (spring: not shown). Therefore, the lower vane 31h reciprocates following the rotation of the lower rolling piston 31g.
  • high-pressure refrigerant supplied (FIG. 5)
  • the lower vane 31h is held away from the lower rolling piston 31g by the magnetic body 31i, and the lower rolling piston 31g rotates without reciprocation of the lower vane 31h.
  • FIG. 4 shows a case where two cylinders of the compressor 31 are driven.
  • the term “cylinder” collectively represents mechanisms such as rolling pistons 31c and 31g and vanes 31d and 31h provided in the compression chambers 31b and 31f.
  • the low-pressure refrigerant flows into the accumulator 35 from the indoor heat exchanger 21 via the four-way valve 32.
  • the accumulator 35 and the compressor 31 are connected by two systems (first supply path M and second supply path N).
  • the first supply path M directly connects the accumulator 35 and the compressor 31 and supplies low-pressure refrigerant to the upper compression chamber 31b.
  • the refrigerant is compressed by the rotation of the upper rolling piston 31c, becomes a high pressure, and is sent to the outdoor heat exchanger 33.
  • the refrigerant is supplied to the lower compression chamber 31f through the second supply path N.
  • a switching valve 36 is provided on the second supply path N.
  • the path from the accumulator 35 to the switching valve 36 is referred to as a second supply path N1
  • the path from the switching valve 36 to the compressor 31 is referred to as a second supply path N2.
  • a buffer tank 39 is provided on the second supply path N2 to alleviate sudden pressure changes.
  • the switching valve 36 is closed and the second supply path N1 and the second supply path N2 are connected. Accordingly, the low-pressure refrigerant is supplied to the compressor 31 (upper compression chamber 31b) via the first supply path M, and the low-pressure refrigerant is supplied to the compressor 31 (lower compression chamber 31f) via the second supply path N. Is done. In this way, the low-pressure refrigerant is supplied to the upper compression chamber 31b and the lower compression chamber 31f, and the refrigerant is compressed by the rotation of the upper rolling piston 31c and the lower rolling piston 31g. The compressed high-pressure refrigerant is supplied to the outdoor heat exchanger 33 via the four-way valve 32.
  • This operation is a so-called two-cylinder operation. For example, the two-cylinder operation is performed when the air conditioner 1 is started or during a medium to high capacity operation.
  • a bypass path 40 connected to the switching valve 36 is provided in the middle of the pipe connecting the compressor 31 and the four-way valve 32. However, since the switching valve 36 is closed in the above-described case, the high-pressure refrigerant that satisfies the bypass passage 40 is not supplied to the second supply passage N2.
  • FIG. 5 shows the operating state of the compressor 31 in the cool breeze operation mode.
  • “Cool wind operation” refers to an operation of blowing cool air into the installation space of the air conditioner 1 (indoor unit 2).
  • the indoor unit 2 sucks indoor air, exchanges heat with the indoor heat exchanger 21, and blows out the heat-exchanged air into the room.
  • “cool wind operation” air that is about 5 ⁇ 1 ° C. lower than the air temperature taken in by the indoor unit 2 is blown into the room.
  • the cool air operation mode is located between the “blower operation mode” in which there is no difference between the suction temperature and the blowout temperature and the “cooling operation mode” in which cool air having a large difference between the suction temperature and the blowout temperature is supplied.
  • the operation frequency of the compressor is minimized and the indoor heat exchanger is controlled.
  • cold air is supplied even during operation at the minimum operation frequency. It is as described above. Therefore, in this embodiment, in addition to the operation at the minimum operation frequency, the number of drive cylinders of the compressor 31 is further minimized, thereby reducing the amount of refrigerant flowing in the refrigeration cycle and preventing overcooling. Provide a comfortable space for the elderly.
  • a high-pressure refrigerant is supplied to the lower compression chamber 31f. That is, a part of the high-pressure refrigerant supplied from the compressor 31 to the outdoor heat exchanger 33 is supplied to the lower compression chamber 31f via the bypass passage 40, the switching valve 36, and the second supply passage N2. Since the switching valve 36 is opened, the high-pressure refrigerant flows through such a path. In this case, the low-pressure refrigerant from the accumulator 35 enters the second supply path N1, but is not supplied to the lower compression chamber 31f because it terminates at the switching valve 36.
  • a pressure (discharge pressure: high pressure) inside the compressor 31 acts as a back pressure on the lower vane 31h of the lower compression chamber 31f, and is pressed against the lower rolling piston 31g by the back pressure and the elastic force of the spring. It was.
  • the low-pressure refrigerant is supplied to the lower compression chamber 31f, the above-described back pressure acts effectively, so the lower vane 31h is pressed against the lower rolling piston 31g (FIG. 4).
  • the high-pressure refrigerant is supplied to the lower compression chamber 31f, so the back pressure described above does not work effectively. For this reason, the lower vane 31h is separated from the lower rolling piston 31g and held by the magnetic force of the magnetic body 31i. As a result, the lower rolling piston 31g idles in the lower compression chamber 31f.
  • the lower rolling piston 31g does not work to compress the refrigerant, the one-cylinder operation is performed only in the upper compression chamber 31b. In this state, the amount of refrigerant to be compressed decreases, so the amount of refrigerant discharged to the outdoor heat exchanger 33 decreases.
  • FIG. 6 is a flowchart of the control in the cool breeze operation mode.
  • the user operates the remote controller 4 to select the cool wind operation mode. For example, this operation is performed by long-pressing the “cooling” button of the remote controller 4.
  • FIG. 1 shows the state changed to the cool wind operation mode, and “cool wind” is displayed on the display unit 4a.
  • a cool wind operation mode start command (signal) is transmitted to the receiving unit 23a of the indoor unit 2 (ST1).
  • the receiving unit 23a transmits the cool wind operation start command received from the remote controller 4 to the outdoor control unit 37a via the MCU 23b and the transmitting unit 23c.
  • the receiving unit 37a transmits the received cool wind operation start command to the MCU 37b.
  • the MCU 37b compares the preset temperature with the outdoor temperature (ST2).
  • the preset temperature is a temperature (for example, 35 ° C.) for determining whether or not to start the cool wind operation, and is stored in the MCU 37b.
  • the preset temperature can be arbitrarily set in consideration of the installation location of the air conditioner 1 and the like.
  • the outdoor temperature is measured by the outside air temperature sensor 50 and transmitted to the MCU 37b.
  • the MCU 37b compares the outdoor temperature with the preset temperature and determines that the outdoor temperature is lower than the preset temperature (NO in ST2), the MCU 37b does not shift to the cool wind operation mode even if the cool wind operation start command is received. To wait. Therefore, in this case, the operation mode immediately before the cool wind operation mode is selected is continued.
  • the MCU 37b determines that the outdoor temperature is equal to or higher than the preset temperature (YES in ST2), it switches the number of drive cylinders of the compressor 31 from 2 cylinders to 1 cylinder and operates at the minimum operating frequency. Start. That is, cool air operation is started (ST3).
  • the two-cylinder operation is executed for about 10 minutes at a frequency (for example, around 20 Hz) about twice the minimum operation frequency to protect the compressor 31. Thereafter, a two-cylinder operation at the minimum frequency (for example, around 10 Hz) is executed until 19 minutes after the start, and after a lapse of 19 minutes, the operation shifts to a one-cylinder operation at the minimum frequency (stable operation).
  • a frequency for example, around 20 Hz
  • a two-cylinder operation at the minimum frequency for example, around 10 Hz
  • the MCU 37b switches the switching valve 36 from the closed state (FIG. 4) to the open state (FIG. 5) via the drive circuit 37d, and the high-pressure refrigerant is supplied to the lower compression chamber 31f.
  • the high-pressure refrigerant is supplied to the lower compression chamber 31f, as described above, the lower vane 31h is held by the magnetic body 31i, and the lower rolling piston 31g idles to perform one cylinder operation.
  • the compressor 31 By operating the compressor 31 in this manner, the amount of refrigerant flowing through the refrigeration cycle A is reduced, and the amount of refrigerant that is heat-exchanged by the indoor heat exchanger 21 is reduced. As a result, not “cold wind” but “cool wind” is supplied to the room.
  • the MCU 37b continues the cool breeze operation unless it receives a cool breeze operation end command from the indoor control unit 23 (NO in ST4).
  • the cool wind operation end command is transmitted, for example, when the user presses and holds down the “cooling” button again to cancel the cool wind operation mode and select the cooling operation mode.
  • the command is transmitted to the outdoor control unit 37 as a cool wind operation end command.
  • the cool wind operation is ended. That is, the operation with the frequency according to the load is performed while the one cylinder operation is performed, or the operation with the frequency according to the load is performed by shifting from the one cylinder operation to the two cylinder operation (ST5).
  • the transition to 2-cylinder operation is actually performed as follows. First, the switching valve 36 is switched from the open state (FIG. 5) to the closed state (FIG. 4) via the drive circuit 37d. As a result, the supply of the high-pressure refrigerant to the lower compression chamber 31f is completed, the second supply path N1 and the second supply path N2 are connected, and the low-pressure refrigerant is supplied to the lower compression chamber 31f via the accumulator 35. Due to the supply of the low-pressure refrigerant, the lower vane 31h moves away from the magnetic body 31i, contacts the lower rolling piston 31g, and follows the rotation of the lower rolling piston 31g. In this way, the compressor 31 shifts to the 2-cylinder operation.
  • the measurement results of various data after the start of operation in the cool air operation mode of the air conditioner are shown in FIG. 7 (graph) and Table 1 below.
  • the said measurement is a result at the time of installing the indoor unit 2 in a 12.5 tatami room, and performing the cool wind operation.
  • the indoor unit can supply cool air having a blowing temperature that is not excessively cooled from the indoor temperature (suction temperature) into the room, coupled with the minimum frequency operation. it can. For this reason, while supplying the air which feels cool to a user, the bad influence by too cold is not given. Such operation also saves energy in the operation of the compressor.
  • a component can be deform

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

Abstract

La présente invention concerne un climatiseur équipé: d'une section intérieure qui est munie d'un échangeur thermique intérieur et d'un ventilateur intérieur; d'une section extérieure qui est connectée à la section intérieure et munie d'un compresseur comportant une pluralité de cylindres, le nombre de cylindres étant variable, d'un échangeur thermique extérieur, et d'un mécanisme d'étranglement; et une unité de commande qui effectue la commande variable de la vitesse de fonctionnement du compresseur. L'unité de commande est capable de faire fonctionner, dans une opération de refroidissement, le climatiseur dans un mode de fonctionnement qui établit le nombre de cylindres opérationnels dans le compresseur à un nombre minimum de cylindres en fonction de la température de l'air extérieur et établit la vitesse de fonctionnement du compresseur pour être la vitesse minimum à laquelle le fonctionnement du cycle de refroidissement est possible. Le climatiseur utilise le compresseur capable de commande variable du nombre de cylindres opérationnels et de la vitesse de fonctionnement, de manière à pouvoir fonctionner lorsqu'une quantité de décharge de fluide frigorigène est réduite pendant le fonctionnement à performance minimum lors de l'opération de refroidissement. Cela diminue la performance de l'ensemble du cycle de refroidissement pour empêcher une température de d'éjection provenant de la section intérieure de se refroidir excessivement, permettant un fonctionnement de climatisation confortable.
PCT/JP2010/065442 2009-09-28 2010-09-08 Climatiseur Ceased WO2011037012A1 (fr)

Priority Applications (2)

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JP2011532956A JP5450637B2 (ja) 2009-09-28 2010-09-08 空気調和機
CN201080040862.7A CN102667354B (zh) 2009-09-28 2010-09-08 空调机

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JP2009222255 2009-09-28
JP2009-222255 2009-09-28

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WO2011037012A1 true WO2011037012A1 (fr) 2011-03-31

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JP (1) JP5450637B2 (fr)
CN (1) CN102667354B (fr)
WO (1) WO2011037012A1 (fr)

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JP2015518954A (ja) * 2012-06-08 2015-07-06 ヤック ソシエテ・パ・アクシオンス・シンプリフィエ 空気調和システム
JP2017075729A (ja) * 2015-10-14 2017-04-20 シャープ株式会社 空気調和機

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JP5981376B2 (ja) * 2013-03-27 2016-08-31 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和機、および空気調和機の運転方法
CN106871385B (zh) * 2017-04-13 2020-08-25 青岛海尔空调器有限总公司 一种空调器及控制方法
CN109654686B (zh) * 2018-12-20 2020-12-29 珠海格力电器股份有限公司 空调器控制方法、空调器及计算机可读存储介质

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JP2015098976A (ja) * 2013-11-19 2015-05-28 株式会社東芝 空気調和機
JP2017075729A (ja) * 2015-10-14 2017-04-20 シャープ株式会社 空気調和機

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CN102667354A (zh) 2012-09-12
CN102667354B (zh) 2015-05-06
JPWO2011037012A1 (ja) 2013-02-21
JP5450637B2 (ja) 2014-03-26

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