JP6440930B2 - Air conditioner and control method of air conditioner - Google Patents

Air conditioner and control method of air conditioner Download PDF

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JP6440930B2
JP6440930B2 JP2013129895A JP2013129895A JP6440930B2 JP 6440930 B2 JP6440930 B2 JP 6440930B2 JP 2013129895 A JP2013129895 A JP 2013129895A JP 2013129895 A JP2013129895 A JP 2013129895A JP 6440930 B2 JP6440930 B2 JP 6440930B2
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compressor
refrigerant
air conditioner
crankcase heater
energization
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JP2015004473A (en
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隆博 加藤
隆博 加藤
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Priority to CN201480016525.2A priority patent/CN105190196B/en
Priority to PCT/JP2014/065764 priority patent/WO2014203828A1/en
Priority to EP14813089.1A priority patent/EP2960598A4/en
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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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • 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
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/34—Heater, e.g. gas burner, electric air heater
    • 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
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02334—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during heating
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/01—Heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • 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
    • F25B2600/01—Timing
    • 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
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Description

本発明は、空気調和機及び空気調和機の制御方法に関するものである。   The present invention relates to an air conditioner and an air conditioner control method.

空気調和機を長時間停止しておくと、冷媒が液状態となって圧縮機内に溜り込み、その状態で圧縮機を起動すると、液圧縮により圧縮機を損傷する虞がある。このため、特に寒冷地向けの空気調和機では、圧縮機にクランクケースヒータを付設し、空気調和機を運転する前にクランクケースヒータに通電して圧縮機を加熱することにより、液冷媒の溜り込みによる液圧縮を防止している。   If the air conditioner is stopped for a long time, the refrigerant becomes liquid and accumulates in the compressor. If the compressor is started in this state, the compressor may be damaged by liquid compression. For this reason, particularly in an air conditioner for cold regions, a crankcase heater is attached to the compressor, and before the air conditioner is operated, the crankcase heater is energized to heat the compressor, thereby collecting liquid refrigerant. This prevents liquid compression due to intrusion.

しかしながら、圧縮機の運転停止中にクランクケースヒータに継続的な通電がされると、クランクケースヒータの消費電力が増し、空気調和機の待機電力が増加する。   However, if the crankcase heater is energized continuously while the compressor is stopped, the power consumption of the crankcase heater increases and the standby power of the air conditioner increases.

この課題を解決するために、特許文献１には、圧縮機が停止状態にあるときにはクランクケースヒータを作動させた後、冷凍機油温度が所定温度以上となった時点でクランクケースヒータの作動を停止させて、圧縮機の再起動に備える空気調和機が記載されている。   In order to solve this problem, Patent Document 1 discloses that after the crankcase heater is operated when the compressor is in a stopped state, the operation of the crankcase heater is stopped when the refrigeration oil temperature exceeds a predetermined temperature. An air conditioner prepared for restarting the compressor is described.

特許第３７９９９４０号公報Japanese Patent No. 3799940

しかしながら、特許文献１に記載の空気調和機は、圧縮機の停止状態において、冷凍機油温度が所定温度未満になる毎にクランクケースヒータを繰り返し通電させる必要があり、待機電力の低減が限定的であった。   However, in the air conditioner described in Patent Document 1, it is necessary to repeatedly energize the crankcase heater every time the refrigeration oil temperature becomes lower than a predetermined temperature when the compressor is stopped, and the reduction in standby power is limited. there were.

本発明は、このような事情に鑑みてなされたものであって、圧縮機が停止されている期間において、クランクケースヒータに通電することにより生じる待機電力をより低減できる、空気調和機及び空気調和機の制御方法を提供することを目的とする。   The present invention has been made in view of such circumstances, and an air conditioner and an air conditioner that can further reduce standby power generated by energizing a crankcase heater during a period in which the compressor is stopped. It aims at providing the control method of a machine.

上記課題を解決するために、本発明の空気調和機及び空気調和機の制御方法は以下の手段を採用する。   In order to solve the above problems, the air conditioner and the air conditioner control method of the present invention employ the following means.

本発明の第一態様は、圧縮機にクランクケースヒータが付設され、前記クランクケースヒータに通電することにより前記圧縮機が加熱可能とされ、前記圧縮機の起動が予め定められたスケジュールに従って行われる空気調和機において、前記圧縮機が停止されている期間であって前記圧縮機が起動される前に、冷媒の過熱度及び外気温度に基づいて、前記クランクケースヒータの通電時間を算出し、算出した前記クランクケースヒータの通電時間と前記スケジュールとから、前記クランクケースヒータの通電を開始するタイミングを決定する制御手段を備え、前記制御手段は、前記タイミングに達するまで、前記通電時間の算出を繰り返し行い、新たな前記タイミングの決定を繰り返す空気調和機を提供する。 In the first aspect of the present invention, a crankcase heater is attached to the compressor, the compressor can be heated by energizing the crankcase heater, and the compressor is started according to a predetermined schedule. In the air conditioner, the energization time of the crankcase heater is calculated based on the superheat degree of the refrigerant and the outside air temperature before the compressor is started in the period when the compressor is stopped. Control means for determining a timing for starting energization of the crankcase heater from the energization time of the crankcase heater and the schedule, and the control means repeatedly calculates the energization time until the timing is reached. An air conditioner is provided that repeats the determination of the new timing.

本構成によれば、空気調和機は、圧縮機にクランクケースヒータが付設され、クランクケースヒータに通電することにより圧縮機が加熱可能とされている。空気調和機は、停止されている圧縮機を起動する前に、クランクケースヒータに通電して圧縮機を加熱する。これにより、液冷媒は、加熱されて気化するので、液冷媒の溜り込みによる液圧縮が防止される。   According to this configuration, in the air conditioner, the crankcase heater is attached to the compressor, and the compressor can be heated by energizing the crankcase heater. The air conditioner heats the compressor by energizing the crankcase heater before starting the stopped compressor. Thereby, since the liquid refrigerant is heated and vaporized, liquid compression due to the accumulation of the liquid refrigerant is prevented.

しかしながら、クランクケースヒータの通電を適切なタイミングで開始しないと、クランクケースヒータの通電を必要以上に行うこととなり、待機電力が増加する。
そこで、圧縮機が停止されている期間であって圧縮機が起動される前に、冷媒の過熱度及び外気温度に基づいて、クランクケースヒータの通電を開始するタイミングを決定する。すなわち、圧縮機が起動を開始する時間に上記パラメータが予め定められた目標値に達するように、クランクケースヒータの通電を開始するタイミングが決定される。
具体的には、冷媒の温度が、圧縮機の運転開始時に溜まり込みを解消できる温度に達するように、冷媒の過熱度が低いほど、クランクケースヒータの通電を開始するタイミングが早くされる。一方、冷媒の過熱度が高いほど、クランクケースヒータの通電を開始するタイミングが遅くされる。これにより、クランクケースヒータの通電時間が必要以上に長くなることが抑制される。 However, unless energization of the crankcase heater is started at an appropriate timing, energization of the crankcase heater is performed more than necessary, and standby power increases.
Therefore, the timing for starting energization of the crankcase heater is determined based on the superheat degree of the refrigerant and the outside air temperature before the compressor is started in the period in which the compressor is stopped. That is, the timing for starting energization of the crankcase heater is determined so that the parameter reaches a predetermined target value at the time when the compressor starts to start.
Specifically, the lower the degree of superheat of the refrigerant, the earlier the timing of starting energization of the crankcase heater so that the temperature of the refrigerant reaches a temperature at which accumulation can be eliminated at the start of operation of the compressor. On the other hand, the higher the degree of superheat of the refrigerant, the later the timing for starting energization of the crankcase heater. Thereby, it is suppressed that the energization time of a crankcase heater becomes longer than necessary.

液冷媒の溜まり込みは、過熱度が十分に高い場合には少ない。また、圧縮機の下部温度が十分に高いと液冷媒の溜まり込みは少ない。しかし、圧縮機の下部温度では、外気温度の影響も受けやすく、必ずしも冷媒の状態を正しく計測しているとは限らない。一方、冷媒の過熱度は、冷媒の温度のみならず、冷媒の圧力とも相関のあるパラメータである。このため、冷媒の過熱度の計測は、圧縮機の下部温度の計測に比べて、冷媒の状態をより正しく計測していることとなる。従って、過熱度を用いることで、クランクケースヒータの通電を開始するタイミングをより正確に決定できる。  The accumulation of liquid refrigerant is small when the degree of superheat is sufficiently high. Also, if the lower temperature of the compressor is sufficiently high, the liquid refrigerant will not accumulate. However, the lower temperature of the compressor is easily affected by the outside air temperature, and the state of the refrigerant is not necessarily measured correctly. On the other hand, the degree of superheat of the refrigerant is a parameter correlated with not only the temperature of the refrigerant but also the pressure of the refrigerant. For this reason, the measurement of the superheat degree of the refrigerant measures the state of the refrigerant more correctly than the measurement of the lower temperature of the compressor. Therefore, the timing for starting energization of the crankcase heater can be determined more accurately by using the degree of superheat.
また、クランクケースヒータを通電しても、外気温度の違いによって、圧縮機の温度、すなわち冷媒の温度の上昇の度合いは異なってくる。そこで、本構成は、過熱度だけでなく外気温度も用いて、クランクケースヒータの通電時間を算出し、通電を開始するタイミングを決定する。すなわち、上記パラメータの値が同じでも、外気温度が低いほど、クランクケースヒータの通電を開始するタイミングが早くされ、外気温度が高いほど、クランクケースヒータの通電を開始するタイミングが遅くされる。これにより、クランクケースヒータに通電するタイミングをより正確に決定できる。従って、本構成によれば、圧縮機が停止されている期間において、クランクケースヒータに通電することにより生じる待機電力をより低減できる。  Even if the crankcase heater is energized, the degree of increase in the compressor temperature, that is, the refrigerant temperature, varies depending on the difference in the outside air temperature. Therefore, in this configuration, the energization time of the crankcase heater is calculated using not only the degree of superheat but also the outside air temperature, and the timing for starting energization is determined. That is, even when the parameter values are the same, the lower the outside air temperature, the earlier the timing for starting energization of the crankcase heater, and the higher the outside air temperature, the later the timing for starting energization of the crankcase heater. Thereby, the timing which supplies with electricity to a crankcase heater can be determined more correctly. Therefore, according to this configuration, standby power generated by energizing the crankcase heater can be further reduced while the compressor is stopped.

上記第一態様では、表示灯が制御基板に備えられ、前記表示灯が、リモコンへの操作がない状態が所定時間以上継続した場合、または、室外機の能力が所定時間以上変化しない場合、または、前記圧縮機の起動及び停止の変更が所定時間以上ない場合に消灯することが好ましい。 In the first aspect, the table示灯is provided on the control board, the indicator light, when the state free operation of the remote control has continued for a predetermined time or more, or, if the capacity of the outdoor unit does not change more than a predetermined time, or It is preferable to turn off the light when there is no change in starting and stopping of the compressor for a predetermined time or more .

本構成は、空気調和機の消費電力をより低減できる。   This configuration can further reduce the power consumption of the air conditioner.

本発明の第二態様は、圧縮機にクランクケースヒータが付設され、前記クランクケースヒータに通電することにより前記圧縮機が加熱可能とされ、前記圧縮機の起動が予め定められたスケジュールに従って行われる空気調和機の制御方法であって、前記圧縮機が停止されている期間であって前記圧縮機が起動される前に、冷媒の温度と相関関係のあるパラメータに基づいて、前記クランクケースヒータの通電時間を算出し、算出した前記クランクケースヒータの通電時間と前記スケジュールとから、前記クランクケースヒータの通電を開始するタイミングを決定し、前記タイミングに達するまで、前記通電時間の算出を繰り返し行い、新たな前記タイミングの決定を繰り返す空気調和機の制御方法を提供する。 The second condition like the present invention, the crank case heater is attached to the compressor, wherein the compressor is configured to be heated by energizing the crankcase heater, the line according to the schedule start of the compressor is predetermined a crack Ru control method of an air conditioner, the before said compressor is a period that is stopped compressor is started, based on parameters that correlate to the temperature of the refrigerant, the crankcase Calculate the energization time of the heater, determine the timing for starting energization of the crankcase heater from the calculated energization time of the crankcase heater and the schedule, and repeat the calculation of the energization time until the timing is reached An air conditioner control method is provided that repeats the determination of the new timing .

本発明によれば、圧縮機が停止されている期間において、クランクケースヒータに通電することにより生じる待機電力をより低減できる、という優れた効果を有する。   According to the present invention, there is an excellent effect that standby power generated by energizing the crankcase heater can be further reduced during a period in which the compressor is stopped.

本発明の第１実施形態に係るマルチ空気調和機の概略構成図である。It is a schematic block diagram of the multi air conditioner which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係るマルチ空気調和機のクランクケースヒータを備えた圧縮機周りの構成図である。It is a block diagram around the compressor provided with the crankcase heater of the multi air conditioner which concerns on 1st Embodiment of this invention. 本発明の第１実施形態に係る過熱度とヒータＯＮ時間との関係を示すグラフである。It is a graph which shows the relationship between the superheat degree which concerns on 1st Embodiment of this invention, and heater ON time. 本発明の第１実施形態に係るＣＨ通電処理の流れを示すフローチャートである。It is a flowchart which shows the flow of CH energization processing concerning a 1st embodiment of the present invention. 本発明の第２実施形態に係る過熱度とヒータＯＮ時間との関係を示すグラフである。It is a graph which shows the relationship between the superheat degree which concerns on 2nd Embodiment of this invention, and heater ON time.

以下に、本発明に係る空気調和機及び空気調和機の制御方法の一実施形態について、図面を参照して説明する。   DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment of an air conditioner and an air conditioner control method according to the present invention will be described with reference to the drawings.

〔第１実施形態〕
以下、本発明の第１実施形態について説明する。
図１には、本発明の第１実施形態に係るマルチ空気調和機の概略構成図が示され、図２には、そのクランクケースヒータを備えた圧縮機周りの構成図が示されている。
マルチタイプの空気調和機１は、１台の室外機２に対して、複数台の室内機３Ａ，３Ｂが室外機２から導出されるガス側配管４及び液側配管５の間に分岐器６を介して互いに並列に接続される。 [First Embodiment]
The first embodiment of the present invention will be described below.
FIG. 1 shows a schematic configuration diagram of a multi-air conditioner according to the first embodiment of the present invention, and FIG. 2 shows a configuration diagram around a compressor provided with the crankcase heater.
The multi-type air conditioner 1 has a branching unit 6 between a gas side pipe 4 and a liquid side pipe 5 from which a plurality of indoor units 3A and 3B are led out from the outdoor unit 2 with respect to one outdoor unit 2. Are connected to each other in parallel.

室外機２は、冷媒を圧縮するインバータ駆動の圧縮機１０と、冷媒ガス中から潤滑油を分離する油分離器１１と、冷媒の循環方向を切換える四方切換弁１２と、冷媒と外気とを熱交換させる室外熱交換器１３と、室外熱交換器１３と一体的に構成されている過冷却コイル１４と、室外側膨張弁（ＥＥＶＨ）１５と、液冷媒を貯留するレシーバ１６と、液冷媒に過冷却を与える過冷却熱交換器１７と、過冷却熱交換器１７に分流される冷媒量を制御する過冷却用膨張弁（ＥＥＶＳＣ）１８と、圧縮機１０に吸入される冷媒ガスから液分を分離し、ガス分のみを圧縮機１０側に吸入させるアキュームレータ１９と、ガス側操作弁２０と、液側操作弁２１とを備える。   The outdoor unit 2 heats an inverter-driven compressor 10 that compresses refrigerant, an oil separator 11 that separates lubricating oil from refrigerant gas, a four-way switching valve 12 that switches the circulation direction of refrigerant, and refrigerant and outside air. The outdoor heat exchanger 13 to be exchanged, the supercooling coil 14 configured integrally with the outdoor heat exchanger 13, the outdoor expansion valve (EEVH) 15, the receiver 16 storing the liquid refrigerant, and the liquid refrigerant A subcooling heat exchanger 17 that provides supercooling, a supercooling expansion valve (EEVSC) 18 that controls the amount of refrigerant that is diverted to the subcooling heat exchanger 17, and a liquid component from the refrigerant gas that is drawn into the compressor 10. And an accumulator 19 that sucks only the gas component to the compressor 10 side, a gas side operation valve 20, and a liquid side operation valve 21.

室外機２側の上記各機器は、冷媒配管２２を介して公知の如く接続され、室外側冷媒回路２３を構成している。また、室外機２には、室外熱交換器１３に対して外気を通風する室外ファン２４が設けられているとともに、油分離器１１と圧縮機１０の吸入配管との間に、油分離器１１内で吐出冷媒ガスから分離された潤滑油を所定量ずつ圧縮機１０側に戻すための油戻し回路２５が設けられる。   Each said apparatus by the side of the outdoor unit 2 is connected as is well-known via the refrigerant | coolant piping 22, and comprises the outdoor side refrigerant circuit 23. FIG. The outdoor unit 2 is provided with an outdoor fan 24 that ventilates the outdoor air to the outdoor heat exchanger 13, and the oil separator 11 is interposed between the oil separator 11 and the suction pipe of the compressor 10. An oil return circuit 25 is provided for returning the lubricating oil separated from the discharged refrigerant gas to the compressor 10 by a predetermined amount.

ガス側配管４及び液側配管５は、室外機２のガス側操作弁２０及び液側操作弁２１に接続される冷媒配管であり、現場での据え付け施工時に、室外機２とそれに接続される複数台の室内機３Ａ，３Ｂとの間の距離に応じて、その配管長が設定される。ガス側配管４及び液側配管５の途中には、適宜数の分岐器６が設けられ、該分岐器６を介して適宜台数の室内機３Ａ，３Ｂが接続される。これによって、密閉された１系統の冷凍サイクル（冷媒回路）７が構成される。   The gas side pipe 4 and the liquid side pipe 5 are refrigerant pipes connected to the gas side operation valve 20 and the liquid side operation valve 21 of the outdoor unit 2, and are connected to the outdoor unit 2 and to it during installation on site. The pipe length is set according to the distance between the plurality of indoor units 3A and 3B. An appropriate number of branching devices 6 are provided in the middle of the gas side piping 4 and the liquid side piping 5, and an appropriate number of indoor units 3 </ b> A and 3 </ b> B are connected via the branching devices 6. As a result, a sealed refrigeration cycle (refrigerant circuit) 7 is configured.

室内機３Ａ，３Ｂは、室内空気を冷媒と熱交換させて室内の空調に供する室内熱交換器３０と、室内側膨張弁（ＥＥＶＣ）３１と、室内空気を室内熱交換器３０に循環させる室内ファン３２とを備えており、室内側の分岐ガス側配管４Ａ，４Ｂ及び分岐液側配管５Ａ，５Ｂを介して分岐器６に接続される。   The indoor units 3A and 3B include an indoor heat exchanger 30 that exchanges heat between indoor air and refrigerant for indoor air conditioning, an indoor expansion valve (EEVC) 31, and an indoor air that circulates indoor air to the indoor heat exchanger 30. The fan 32 is provided, and is connected to the branching device 6 via the indoor branch gas side pipes 4A and 4B and the branch liquid side pipes 5A and 5B.

また、圧縮機１０から吐出される冷媒の圧力は、圧力センサ３３によって測定される。   Further, the pressure of the refrigerant discharged from the compressor 10 is measured by the pressure sensor 33.

上記の空気調和機１において、冷房運転は以下のように行われる。
圧縮機１０で圧縮され、吐出された高温高圧の冷媒ガスは、油分離器１１で冷媒中に含まれている潤滑油が分離される。その後、冷媒ガスは、四方切換弁１２により室外熱交換器１３側に循環され、室外熱交換器１３で室外ファン２４により送風される外気と熱交換して凝縮液化される。この液冷媒は、過冷却コイル１４で更に冷却された後、室外側膨張弁１５を通過し、レシーバ１６内にいったん貯留される。 In the air conditioner 1 described above, the cooling operation is performed as follows.
The high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is separated from the lubricating oil contained in the refrigerant by the oil separator 11. Thereafter, the refrigerant gas is circulated to the outdoor heat exchanger 13 side by the four-way switching valve 12, and heat is exchanged with the outdoor air blown by the outdoor fan 24 in the outdoor heat exchanger 13 to be condensed and liquefied. The liquid refrigerant is further cooled by the supercooling coil 14, passes through the outdoor expansion valve 15, and is temporarily stored in the receiver 16.

レシーバ１６で循環量が調整された液冷媒は、過冷却熱交換器１７を経て液冷媒配管側を流通される過程で、液冷媒配管から分流され、過冷却用膨張弁（ＥＥＶＳＣ）１８で断熱膨張された一部の冷媒と熱交換されて過冷却度が付与される。この液冷媒は、液側操作弁２１を経て室外機２から液側配管５へと導出される。更に液側配管５に導出された液冷媒は、分岐器６を介して各室内機３Ａ，３Ｂの分岐液側配管５Ａ，５Ｂへと分流される。   The liquid refrigerant whose circulation amount is adjusted by the receiver 16 is diverted from the liquid refrigerant pipe in the process of flowing through the liquid refrigerant pipe side through the supercooling heat exchanger 17 and is insulated by the supercooling expansion valve (EEVSC) 18. Heat exchange is performed with a part of the expanded refrigerant to provide a degree of supercooling. The liquid refrigerant is led out from the outdoor unit 2 to the liquid side pipe 5 through the liquid side operation valve 21. Furthermore, the liquid refrigerant led out to the liquid side pipe 5 is diverted to the branch liquid side pipes 5A and 5B of the indoor units 3A and 3B via the branching unit 6.

分岐液側配管５Ａ，５Ｂに分流された液冷媒は、各室内機３Ａ，３Ｂに流入し、室内側膨張弁（ＥＥＶＣ）３１で断熱膨張され、気液二相流となって室内熱交換器３０に流入される。室内熱交換器３０では、室内ファン３２により循環される室内空気と冷媒とが熱交換され、室内空気は冷却されて室内の冷房に供される。一方、冷媒はガス化され、分岐ガス側配管４Ａ，４Ｂを経て分岐器６に至り、他の室内機からの冷媒ガスとガス側配管４で合流される。   The liquid refrigerant divided into the branch liquid side pipes 5A and 5B flows into the indoor units 3A and 3B, is adiabatically expanded by the indoor side expansion valve (EEVC) 31, and becomes a gas-liquid two-phase flow. 30. In the indoor heat exchanger 30, the indoor air circulated by the indoor fan 32 and the refrigerant are heat-exchanged, and the indoor air is cooled and supplied to the indoor cooling. On the other hand, the refrigerant is gasified, reaches the branching device 6 through the branch gas side pipes 4A and 4B, and is merged with the refrigerant gas from the other indoor units in the gas side pipe 4.

ガス側配管４で合流された冷媒ガスは、再び室外機２に戻り、ガス側操作弁２０、四方切換弁１２を経て、過冷却熱交換器１７からの冷媒ガスと合流された後、アキュームレータ１９に導入される。アキュームレータ１９では、冷媒ガス中に含まれている液分が分離され、ガス分のみが圧縮機１０に吸入される。この冷媒は、圧縮機１０において再び圧縮され、以上のサイクルを繰り返すことによって冷房運転が行われる。   The refrigerant gas merged in the gas side pipe 4 returns to the outdoor unit 2 again, merges with the refrigerant gas from the supercooling heat exchanger 17 through the gas side operation valve 20 and the four-way switching valve 12, and then accumulator 19. To be introduced. In the accumulator 19, the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10. This refrigerant is compressed again in the compressor 10, and the cooling operation is performed by repeating the above cycle.

一方、暖房運転は、以下のように行われる。
圧縮機１０により圧縮され、吐出された高温高圧の冷媒ガスは、油分離器１１で冷媒中に含まれている潤滑油が分離された後、四方切換弁１２を介してガス側操作弁２０側に循環される。ガス側操作弁２０側に循環された冷媒は、ガス側配管４を経て室外機２から導出され、分岐器６、室内側の分岐ガス側配管４Ａ，４Ｂを経て複数台の室内機３Ａ，３Ｂに導入される。 On the other hand, the heating operation is performed as follows.
The high-temperature and high-pressure refrigerant gas compressed and discharged by the compressor 10 is separated from the lubricating oil contained in the refrigerant by the oil separator 11 and then the gas-side operation valve 20 side through the four-way switching valve 12. It is circulated in. The refrigerant circulated to the gas-side operation valve 20 side is led out from the outdoor unit 2 through the gas-side pipe 4, and passes through the branching unit 6 and the indoor-side branching gas-side pipes 4A and 4B to be a plurality of indoor units 3A and 3B. To be introduced.

室内機３Ａ，３Ｂに導入された高温高圧の冷媒ガスは、室内熱交換器３０で室内ファン３２を介して循環される室内空気と熱交換され、室内空気は加熱されて室内の暖房に供される。室内熱交換器３０で凝縮された液冷媒は、室内側膨張弁（ＥＥＶＣ）３１、分岐液側配管５Ａ，５Ｂを経て分岐器６に至り、他の室内機からの冷媒と合流された後、液側配管５を経て室外機２側に戻される。なお、暖房時、室内機３Ａ，３Ｂでは、凝縮器として機能する室内熱交換器３０の冷媒出口温度又は冷媒過冷却度が目標値となるように、室内側膨張弁（ＥＥＶＣ）３１の開度が制御されるようになっている。   The high-temperature and high-pressure refrigerant gas introduced into the indoor units 3A and 3B is heat-exchanged with the indoor air circulated through the indoor fan 32 in the indoor heat exchanger 30, and the indoor air is heated and used for indoor heating. The The liquid refrigerant condensed in the indoor heat exchanger 30 reaches the branching device 6 through the indoor expansion valve (EEVC) 31 and the branch liquid side pipes 5A and 5B, and is merged with the refrigerant from other indoor units. It returns to the outdoor unit 2 side through the liquid side pipe 5. During heating, in the indoor units 3A and 3B, the opening degree of the indoor expansion valve (EEVC) 31 is set so that the refrigerant outlet temperature or the refrigerant subcooling degree of the indoor heat exchanger 30 functioning as a condenser becomes a target value. Is to be controlled.

室外機２側に戻った冷媒は、液側操作弁２１を経て過冷却熱交換器１７に至り、冷房時の場合と同様に過冷却が付与された後、レシーバ１６に流入され、いったん貯留されることにより循環量が調整される。この液冷媒は、室外側膨張弁（ＥＥＶＨ）１５に供給されて断熱膨張された後、過冷却コイル１４を経て室外熱交換器１３に流入される。   The refrigerant that has returned to the outdoor unit 2 side reaches the supercooling heat exchanger 17 via the liquid side operation valve 21, and is given supercooling as in the case of cooling, and then flows into the receiver 16 and temporarily stored. Thus, the circulation amount is adjusted. The liquid refrigerant is supplied to the outdoor expansion valve (EEVH) 15 and subjected to adiabatic expansion, and then flows into the outdoor heat exchanger 13 through the supercooling coil 14.

室外熱交換器１３においては、室外ファン２４を介して送風される外気と冷媒とが熱交換され、冷媒は外気から吸熱して蒸発ガス化される。該冷媒は、室外熱交換器１３から四方切換弁１２を経て、過冷却熱交換器１７からの冷媒ガスと合流された後、アキュームレータ１９に導入される。アキュームレータ１９では、冷媒ガス中に含まれている液分が分離されてガス分のみが圧縮機１０に吸入され、圧縮機１０において再び圧縮される。以上のサイクルを繰り返すことによって暖房運転が行われる。   In the outdoor heat exchanger 13, heat is exchanged between the outside air blown through the outdoor fan 24 and the refrigerant, and the refrigerant absorbs heat from the outside air and is evaporated and gasified. The refrigerant is introduced from the outdoor heat exchanger 13 through the four-way switching valve 12 to the refrigerant gas from the supercooling heat exchanger 17 and then introduced into the accumulator 19. In the accumulator 19, the liquid component contained in the refrigerant gas is separated, and only the gas component is sucked into the compressor 10 and compressed again in the compressor 10. The heating operation is performed by repeating the above cycle.

さらに、上記空気調和機１において、圧縮機１０には、図２に示されるように、密閉ハウジング１０Ａの外周にクランクケースヒータ（以下「ＣＨ」という。）４０が付設されている。このＣＨ４０は、圧縮機１０が停止期間中に、圧縮機１０内に冷媒が液状態となって溜り込み、その液冷媒を圧縮機１０が起動時に吸込んで液圧縮を起こし、圧縮機１０が損傷するのを防ぐために設けられるものであり、空気調和機１を運転する前にＣＨ４０に通電して圧縮機１０を加熱することにより、液冷媒を圧縮機１０から追出し、液圧縮を防止する役割を担うものである。   Further, in the air conditioner 1, the compressor 10 is provided with a crankcase heater (hereinafter referred to as “CH”) 40 on the outer periphery of the hermetic housing 10A as shown in FIG. In the CH 40, during the period when the compressor 10 is stopped, the refrigerant accumulates in the compressor 10 in a liquid state, and the compressor 10 sucks the liquid refrigerant when the compressor 10 starts up, causing liquid compression, and the compressor 10 is damaged. This is provided to prevent the liquid refrigerant from being discharged from the compressor 10 by energizing the CH 40 and heating the compressor 10 before the air conditioner 1 is operated. It is what you bear.

ＣＨ４０は、制御部４１を介して通電のＯＮ／ＯＦＦ制御がされる。制御部４１は、圧縮機１０が停止期間中、ＣＨ４０に対して予め定められたスペックに基づいて常時通電制御する通常運転モード制御部４２と、ＣＨ４０のＯＮタイミングを算出して該ＣＨ４０をＯＮ／ＯＦＦ制御する運転低減モード制御部４３とを備える。制御部４１は、制御モードを通常運転モード又は運転低減モードのいずれかのモードに選択的に切替えできる切替え手段４４を備えており、切替え手段４４は、例えば、リモコン４５側から切替え操作できるように構成される。   The CH 40 is ON / OFF controlled for energization via the control unit 41. The control unit 41 calculates a normal operation mode control unit 42 that constantly controls energization based on a predetermined specification for the CH 40 while the compressor 10 is stopped, calculates the ON timing of the CH 40, and turns the CH 40 ON / OFF. An operation reduction mode control unit 43 that performs OFF control is provided. The control unit 41 includes a switching unit 44 that can selectively switch the control mode to either the normal operation mode or the operation reduction mode. The switching unit 44 can be switched from the remote controller 45 side, for example. Composed.

なお、制御部４１は、例えば、ＣＰＵ（Central Processing Unit）、ＲＡＭ（Random Access Memory）、及びコンピュータ読み取り可能な記録媒体等から構成される。そして、各種機能を実現するための一連の処理は、一例として、プログラムの形式で記録媒体等に記録されており、このプログラムをＣＰＵがＲＡＭ等に読み出して、情報の加工・演算処理を実行することにより、各種機能が実現される。   The control unit 41 includes, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), and a computer-readable recording medium. A series of processes for realizing various functions is recorded on a recording medium or the like in the form of a program as an example, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized.

また、制御部４１は、その制御基板上に空気調和機１の制御状態を示す表示灯５０を備える。表示灯５０は、空気調和機１のメンテナンス等に要するものである。表示灯５０は、例えば７セグメントディスプレイであるが、これに限らず、１つ又は複数のＬＥＤ灯であってもよい。
さらに、制御部４１には、圧縮機１０下部の温度（以下「ドーム下温度」という。）を測定するドーム下温度センサ５２による測定値、外気温を測定する外気温センサ４６による測定値、及び圧力センサ３３による測定値が入力される。 Moreover, the control part 41 is provided with the indicator lamp 50 which shows the control state of the air conditioner 1 on the control board. The indicator lamp 50 is required for maintenance of the air conditioner 1 or the like. The indicator lamp 50 is, for example, a 7-segment display, but is not limited thereto, and may be one or a plurality of LED lamps.
Further, the control unit 41 has a measured value by the under-dome temperature sensor 52 that measures the temperature of the lower portion of the compressor 10 (hereinafter referred to as “under-dome temperature”), a measured value by the outside air temperature sensor 46 that measures the outside air temperature, and A measurement value by the pressure sensor 33 is input.

通常運転モード制御部４２は、予め定められているスペック記載のＣＨ４０のＯＮ条件を満たす場合、圧縮機１０が停止期間中はＣＨ４０に対して常に通電し、ＣＨ４０をＯＮとして圧縮機１０を加熱する。この場合、ＣＨ４０は、圧縮機１０が起動されると、起動中はＯＦＦとされ、圧縮機１０が停止されると、停止期間中は常にＯＮされるようになる。   The normal operation mode control unit 42 always energizes the CH 40 while the compressor 10 is in the stop period and heats the compressor 10 by turning on the CH 40 when the CH 40 ON condition described in the spec is set. . In this case, when the compressor 10 is started, the CH 40 is turned off during the start-up, and when the compressor 10 is stopped, the CH 40 is always turned on during the stop period.

このように、空気調和機１は、停止されている圧縮機１０を起動する前に、ＣＨ４０に通電して圧縮機１０を加熱する。これにより、液冷媒は、加熱されて気化するので、液冷媒の溜り込みによる液圧縮が防止される。
しかしながら、ＣＨ４０の通電を適切なタイミングで開始しないと、ＣＨ４０の通電を必要以上に行うこととなり、待機電力が増加する。 As described above, the air conditioner 1 heats the compressor 10 by energizing the CH 40 before starting the stopped compressor 10. Thereby, since the liquid refrigerant is heated and vaporized, liquid compression due to the accumulation of the liquid refrigerant is prevented.
However, unless energization of CH40 is started at an appropriate timing, energization of CH40 is performed more than necessary, and standby power increases.

そこで、本第１実施形態に係る運転低減モード制御部４３は、圧縮機１０が停止されている期間であって圧縮機１０が起動される前に、冷媒の温度と相関関係のあるパラメータに基づいて、ＣＨ４０の通電を開始するタイミングを決定する。すなわち、圧縮機１０が起動を開始する時間に上記パラメータが予め定められた目標値に達するように、ＣＨ４０の通電を開始するタイミングが決定される。   Therefore, the operation reduction mode control unit 43 according to the first embodiment is based on parameters correlated with the refrigerant temperature before the compressor 10 is started in the period in which the compressor 10 is stopped. Thus, the timing for starting energization of CH40 is determined. That is, the timing for starting energization of the CH 40 is determined so that the parameter reaches a predetermined target value at the time when the compressor 10 starts to start.

なお、本第１実施形態に係る上記パラメータは、冷媒の過熱度である。液冷媒の溜まり込みは、過熱度が十分に高い場合には少ないためである。過熱度は、ドーム下温度センサ５２によって測定されたドーム下温度から圧力センサ３３の測定値に基づいて算出される飽和温度を減算することで算出される。   Note that the parameter according to the first embodiment is the degree of superheat of the refrigerant. This is because the accumulation of liquid refrigerant is small when the degree of superheat is sufficiently high. The degree of superheat is calculated by subtracting the saturation temperature calculated based on the measured value of the pressure sensor 33 from the under-dome temperature measured by the under-dome temperature sensor 52.

そして、運転低減モード制御部４３は、図３のグラフに示されるような過熱度とＣＨ４０のＯＮ時間（以下「ヒータＯＮ時間」という。）との関係から、ＣＨ４０を通電する時間を算出する。
具体的には、冷媒は、圧縮機１０の運転開始時に溜まり込みを解消できる過熱度に達するように、過熱度が低いほど、ＣＨ４０の通電を開始するタイミングが早くされる。一方、過熱度が高いほど、ＣＨ４０の通電を開始するタイミングが遅くされる。さらに、過熱度が十分に高い場合は、圧縮機１０の停止中にＣＨ４０の通電は行われない。
これにより、ＣＨ４０の通電時間が必要以上に長くなることが抑制される。 Then, the operation reduction mode control unit 43 calculates the time for energizing the CH 40 from the relationship between the degree of superheat as shown in the graph of FIG. 3 and the ON time of the CH 40 (hereinafter referred to as “heater ON time”).
Specifically, the timing at which energization of the CH 40 is started earlier as the degree of superheat is lower so that the refrigerant reaches the degree of superheat at which accumulation can be eliminated at the start of operation of the compressor 10. On the other hand, the higher the degree of superheat, the later the timing for starting energization of CH40. Furthermore, when the degree of superheat is sufficiently high, the CH 40 is not energized while the compressor 10 is stopped.
Thereby, it is suppressed that the energization time of CH40 becomes longer than necessary.

過熱度とヒータＯＮ時間との関係は、（１）式のように関数ｆで表わされるが、その関係は図３に示されるような線形でなくてもよい。
ヒータＯＮ時間＝ｆ（過熱度） ・・・（１）
関数ｆは、圧縮機１０の熱容量、ＣＨ４０の出力、及び圧縮機１０からの放熱量等に基づいて予め決定される。なお、圧縮機１０を起動可能とする過熱度の目標値は、例えば１０〜１５℃である。 Although the relationship between the degree of superheat and the heater ON time is expressed by the function f as shown in equation (1), the relationship may not be linear as shown in FIG.
Heater ON time = f (degree of superheat) (1)
The function f is determined in advance based on the heat capacity of the compressor 10, the output of the CH 40, the heat radiation from the compressor 10, and the like. In addition, the target value of the superheat degree which can start the compressor 10 is 10-15 degreeC, for example.

また、本第１実施形態に係る制御部４１は、空気調和機１の起動及び停止、すなわち圧縮機１０等の各種構成機器の起動及び停止等を、予め定められたスケジュールに従って行う、所謂スケジュールタイマの機能を備える。制御部４１は、スケジュールタイマが設定されている場合、スケジュールタイマに従って、空気調和機１の停止期間中は、各構成機器に対する不要な電力をカットし、空気調和機１をスリープ状態とする。   The control unit 41 according to the first embodiment is a so-called schedule timer for starting and stopping the air conditioner 1, that is, starting and stopping various components such as the compressor 10 according to a predetermined schedule. It has the function of. When the schedule timer is set, the control unit 41 cuts unnecessary power for each component device according to the schedule timer and puts the air conditioner 1 into the sleep state during the stop period of the air conditioner 1.

そして、運転低減モード制御部４３は、算出したヒータＯＮ時間及びスケジュールに従って、ＣＨ４０を通電する時刻（以下「ＣＨ通電開始時刻」という。）を算出する。例えば、スケジュールタイマによって空気調和機１の起動が午前８時となっている場合、ヒータＯＮ時間が３時間と算出されると、ＣＨ通電開始時刻は午前５時とされる。   Then, the operation reduction mode control unit 43 calculates a time for energizing the CH 40 (hereinafter referred to as “CH energization start time”) according to the calculated heater ON time and schedule. For example, when the air conditioner 1 is started at 8:00 am by the schedule timer, if the heater ON time is calculated as 3 hours, the CH energization start time is 5:00 am.

なお、ドーム下温度が十分に高いと液冷媒の溜まり込みは少ない。このため、（２）式に示されるように、運転低減モード制御部４３は、ヒータＯＮ時間＝ｆ（ドーム下温度）の関数を用いて、ヒータＯＮ時間を算出してもよい。
しかし、ドーム下温度では、外気温度の影響も受けやすく、必ずしも冷媒の状態を正しく計測しているとは限らない。一方、冷媒の過熱度は、冷媒の温度のみならず、冷媒の圧力とも相関のあるパラメータである。このため、冷媒の過熱度の計測は、圧縮機の下部温度の計測に比べて、冷媒の状態をより正しく計測していることとなる。
従って、冷媒の温度と相関関係のあるパラメータとして過熱度を用いることによって、ＣＨ４０に通電するタイミングをより正確に決定できる。 Note that when the temperature under the dome is sufficiently high, the liquid refrigerant does not accumulate. For this reason, as shown in the equation (2), the operation reduction mode control unit 43 may calculate the heater ON time using a function of heater ON time = f (under-dome temperature).
However, the temperature under the dome is easily affected by the outside air temperature, and the state of the refrigerant is not always measured correctly. On the other hand, the degree of superheat of the refrigerant is a parameter correlated with not only the temperature of the refrigerant but also the pressure of the refrigerant. For this reason, the measurement of the superheat degree of the refrigerant measures the state of the refrigerant more correctly than the measurement of the lower temperature of the compressor.
Therefore, by using the degree of superheat as a parameter having a correlation with the refrigerant temperature, it is possible to more accurately determine the timing of energizing CH40.

図４は、圧縮機１０が停止されている期間であって圧縮機１０が起動される前に、運転低減モード制御部４３で実行されるＣＨ４０への通電処理（以下「ＣＨ通電処理」という。）の流れを示すフローチャートである。なお、ＣＨ通電処理は、圧縮機１０が停止されている期間に実行される。   FIG. 4 is a period in which the compressor 10 is stopped and before the compressor 10 is started, the energization process to the CH 40 (hereinafter referred to as “CH energization process”) executed by the operation reduction mode control unit 43. ). Note that the CH energization process is executed during a period in which the compressor 10 is stopped.

まず、ステップ１００では、過熱度を算出する。   First, in step 100, the degree of superheat is calculated.

次のステップ１０２では、算出した過熱度に基づいて、ヒータＯＮ時間を算出する。   In the next step 102, the heater ON time is calculated based on the calculated degree of superheat.

次のステップ１０４では、算出したヒータＯＮ時間に基づいて、ＣＨ通電開始時刻を算出する。   In the next step 104, the CH energization start time is calculated based on the calculated heater ON time.

次のステップ１０６では、現在時刻がＣＨ通電開始時刻に達したか否かを判定し、肯定判定の場合はステップ１０８へ移行し、否定判定の場合はステップ１００へ戻る。   In the next step 106, it is determined whether or not the current time has reached the CH energization start time. If the determination is affirmative, the process proceeds to step 108. If the determination is negative, the process returns to step 100.

ステップ１０８では、ＣＨ４０の通電を開始する。   In step 108, energization of CH40 is started.

なお、ステップ１０６からステップ１００へ戻った場合は、新たに算出した過熱度、ヒータＯＮ時刻に基づいて、新たなＣＨ通電開始時刻を算出する。   When returning from step 106 to step 100, a new CH energization start time is calculated based on the newly calculated superheat degree and heater ON time.

また、本実施形態に係る制御部４１は、制御が所定時間以上安定している場合に表示灯５０を消灯する。制御が安定している場合とは、例えば、リモコン４５への操作が無い場合、室外機２の能力に変化がない場合、圧縮機１０の起動及び停止の変更が無い場合である。また、表示灯５０は、スケジュールタイマに応じて消灯する。
これにより、空気調和機１の消費電力がより低減される。 Further, the control unit 41 according to the present embodiment turns off the indicator lamp 50 when the control is stable for a predetermined time or more. The case where the control is stable is, for example, a case where there is no operation on the remote controller 45, a case where there is no change in the capacity of the outdoor unit 2, or a case where there is no change in starting and stopping of the compressor 10. The indicator lamp 50 is turned off according to the schedule timer.
Thereby, the power consumption of the air conditioner 1 is further reduced.

以上説明したように、本第１実施形態に係る空気調和機１は、圧縮機１０にＣＨ４０が付設され、ＣＨ４０に通電することにより圧縮機が加熱可能とされている。そして、制御部４１が、圧縮機１０が停止されている期間であって圧縮機１０が起動される前に、冷媒の温度と相関関係のあるパラメータである過熱度に基づいて、ＣＨ４０を開始するタイミングを決定する。
従って、本第１実施形態に係る空気調和機１は、圧縮機１０が停止されている期間において、ＣＨ４０に通電することにより生じる待機電力をより低減できる。 As described above, in the air conditioner 1 according to the first embodiment, the CH 10 is attached to the compressor 10, and the compressor can be heated by energizing the CH 40. Then, the control unit 41 starts CH40 based on the degree of superheat that is a parameter correlated with the temperature of the refrigerant before the compressor 10 is started in the period in which the compressor 10 is stopped. Determine timing.
Therefore, the air conditioner 1 according to the first embodiment can further reduce standby power generated by energizing the CH 40 during the period in which the compressor 10 is stopped.

〔第２実施形態〕
以下、本発明の第２実施形態について説明する。
なお、本第２実施形態に係る空気調和機１の構成は、図１，２に示す第１実施形態に係る空気調和機１の構成と同様であるので説明を省略する。 [Second Embodiment]
Hereinafter, a second embodiment of the present invention will be described.
The configuration of the air conditioner 1 according to the second embodiment is the same as the configuration of the air conditioner 1 according to the first embodiment shown in FIGS.

圧縮機１０が停止されている期間であって圧縮機１０が起動される前に、ＣＨ４０を通電しても、外気温度の違いによって、圧縮機１０の温度、すなわち冷媒の温度の上昇の度合いは異なってくる。   Even if the CH 40 is energized during the period in which the compressor 10 is stopped and before the compressor 10 is started, the temperature of the compressor 10, that is, the degree of increase in the refrigerant temperature, depends on the difference in the outside air temperature. Come different.

そこで、本第２実施形態に係る運転低減モード制御部４３は、圧縮機１０が停止されている期間であって圧縮機１０が起動される前に、過熱度及び外気温度に基づいて、ＣＨ４０の通電を開始するタイミングを決定する。
すなわち、ヒータＯＮ時間は、（２）式のように表わされる。
ヒータＯＮ時間＝ｆ（過熱度、外気温度） ・・・（２） Therefore, the operation reduction mode control unit 43 according to the second embodiment is a period during which the compressor 10 is stopped and before the compressor 10 is started, based on the degree of superheat and the outside air temperature. The timing for starting energization is determined.
That is, the heater ON time is expressed as shown in Equation (2).
Heater ON time = f (degree of superheat, outside air temperature) (2)

図５は、本第２実施形態に係る過熱度とヒータＯＮ時間との関係を示したグラフである。実線は、破線に比べて外気温度が低い場合を示している。このように、過熱度の値が同じでも、外気温度が低いほど、ＣＨ４０の通電を開始するタイミングが早くされる。また、外気温度が高いほど、ＣＨ４０の通電を開始するタイミングが遅くされる。   FIG. 5 is a graph showing the relationship between the degree of superheat and the heater ON time according to the second embodiment. A solid line indicates a case where the outside air temperature is lower than that of the broken line. Thus, even if the value of the degree of superheat is the same, the timing for starting energization of CH40 is advanced as the outside air temperature is lower. In addition, the higher the outside air temperature, the later the timing for starting energization of CH40.

従って、本第２実施形態に係る空気調和機１は、クランクケースヒータに通電するタイミングをより正確に決定できる。   Therefore, the air conditioner 1 according to the second embodiment can more accurately determine the timing of energizing the crankcase heater.

以上、本発明を、上記各実施形態を用いて説明したが、本発明の技術的範囲は上記実施形態に記載の範囲には限定されない。発明の要旨を逸脱しない範囲で上記実施形態に多様な変更又は改良を加えることができ、該変更又は改良を加えた形態も本発明の技術的範囲に含まれる。   As mentioned above, although this invention was demonstrated using said each embodiment, the technical scope of this invention is not limited to the range as described in the said embodiment. Various changes or improvements can be added to the above-described embodiment without departing from the gist of the invention, and embodiments to which the changes or improvements are added are also included in the technical scope of the present invention.

また、上記実施形態で説明したＣＨ通電処理の流れも一例であり、本発明の主旨を逸脱しない範囲内において不要なステップを削除したり、新たなステップを追加したり、処理順序を入れ替えたりしてもよい。   The flow of CH energization processing described in the above embodiment is also an example, and unnecessary steps are deleted, new steps are added, or the processing order is changed within a range not departing from the gist of the present invention. May be.

１ 空気調和機
１０ 圧縮機
４０ クランクケースヒータ
４１ 制御部
５０ 表示灯 DESCRIPTION OF SYMBOLS 1 Air conditioner 10 Compressor 40 Crankcase heater 41 Control part 50 Indicator light

Claims (3)

圧縮機にクランクケースヒータが付設され、前記クランクケースヒータに通電することにより前記圧縮機が加熱可能とされ、前記圧縮機の起動が予め定められたスケジュールに従って行われる空気調和機において、
前記圧縮機が停止されている期間であって前記圧縮機が起動される前に、冷媒の過熱度及び外気温度に基づいて、前記クランクケースヒータの通電時間を算出し、算出した前記クランクケースヒータの通電時間と前記スケジュールとから、前記クランクケースヒータの通電を開始するタイミングを決定する制御手段を備え、
前記制御手段は、前記タイミングに達するまで、前記通電時間の算出を繰り返し行い、新たな前記タイミングの決定を繰り返す空気調和機。 In an air conditioner, a crankcase heater is attached to the compressor, the compressor can be heated by energizing the crankcase heater, and the compressor is started according to a predetermined schedule.
The crankcase heater is calculated by calculating the energization time of the crankcase heater based on the degree of superheat and the outside air temperature of the refrigerant before the compressor is started during the period when the compressor is stopped. From the energization time and the schedule, comprising a control means for determining the timing to start energization of the crankcase heater,
The said control means is an air conditioner which repeats the calculation of the said energization time until it reaches the said timing, and repeats the determination of the said new timing. 表示灯が制御基板に備えられ、
前記表示灯は、リモコンへの操作がない状態が所定時間以上継続した場合、または、室外機の能力が所定時間以上変化しない場合、または、前記圧縮機の起動及び停止の変更が所定時間以上ない場合に、前記表示灯を消灯する請求項１記載の空気調和機。 Table示灯is provided on the control board,
The indicator lamp is in a state where there is no operation on the remote control for a predetermined time or more, or when the capacity of the outdoor unit does not change for a predetermined time or the start and stop of the compressor is not changed for a predetermined time or more. If the air conditioner according to claim 1 Symbol placement extinguishes the indicator. 圧縮機にクランクケースヒータが付設され、前記クランクケースヒータに通電することにより前記圧縮機が加熱可能とされ、前記圧縮機の起動が予め定められたスケジュールに従って行われる空気調和機の制御方法であって、
前記圧縮機が停止されている期間であって前記圧縮機が起動される前に、冷媒の過熱度及び外気温度に基づいて、前記クランクケースヒータの通電時間を算出し、
算出した前記クランクケースヒータの通電時間と前記スケジュールとから、前記クランクケースヒータの通電を開始するタイミングを決定し、
前記タイミングに達するまで、前記通電時間の算出を繰り返し行い、新たな前記タイミングの決定を繰り返す空気調和機の制御方法。 A control method for an air conditioner in which a compressor is provided with a crankcase heater, the compressor can be heated by energizing the crankcase heater, and the compressor is started according to a predetermined schedule. And
Before the compressor is started in the period when the compressor is stopped, the energization time of the crankcase heater is calculated based on the superheat degree of the refrigerant and the outside air temperature ,
From the calculated energization time of the crankcase heater and the schedule, the timing for starting energization of the crankcase heater is determined,
A control method for an air conditioner in which the energization time is repeatedly calculated until the timing is reached, and the new timing is repeatedly determined.
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