WO2010103734A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2010103734A1 WO2010103734A1 PCT/JP2010/000971 JP2010000971W WO2010103734A1 WO 2010103734 A1 WO2010103734 A1 WO 2010103734A1 JP 2010000971 W JP2010000971 W JP 2010000971W WO 2010103734 A1 WO2010103734 A1 WO 2010103734A1
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- Prior art keywords
- compressor
- refrigerant
- shell
- temperature
- air conditioner
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/005—Arrangement or mounting of control or safety devices of safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/121—Casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/04—Carter parameters
- F04B2201/0403—Carter housing temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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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
- 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
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/01—Heaters
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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
- F25B2500/00—Problems to be solved
- F25B2500/27—Problems to be solved characterised by the stop of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
Definitions
- the present invention relates to an air conditioner that configures a refrigerant circuit to perform cooling or heating, and in particular, refrigerant present in the refrigerant circuit accumulates in the compressor when the apparatus is stopped, resulting in a decrease in insulation resistance and a deterioration in lubrication performance.
- the present invention relates to a means for avoiding causing such problems.
- an air conditioner that constitutes a refrigerant circuit
- it is generally configured by units of an indoor unit and an outdoor unit and piping that connects the units.
- the indoor unit has an indoor heat exchanger
- the outdoor unit has an outdoor heat exchanger, a compressor, and a decompression device, and each is connected by piping inside the unit.
- the unit composed of these is connected by piping at the installation site and functions as an air conditioner.
- the refrigerant circuit configured by the above connection is filled with a refrigerant, and further, refrigeration oil for driving the compressor is also present in the refrigerant circuit.
- refrigerant when the outside air temperature is low and the temperature inside the compressor is lower than the outside air temperature and there is a temperature difference between the outside air temperature and the temperature inside the compressor, there is a phenomenon that refrigerant accumulates in the compressor of the outdoor unit that is at a low temperature. Arise.
- the refrigeration oil is diluted with the refrigerant or liquefied refrigerant exists in the compression chamber.
- a compressor of an air conditioner generally has a device (heater) for heating a shell, or a motor in the compressor is energized to heat the compressor, thereby the air conditioner.
- Means for suppressing refrigerant accumulation at the time of stopping is used.
- the timing for executing this means is determined by a predetermined outside air temperature as a trigger, and provides a control technique for heating the compressor when the outside air temperature is lower than the predetermined temperature or at night when the outside air temperature is lower than the predetermined temperature. (See Patent Document 1).
- Japanese Patent Laid-Open No. 10-030563 pages 4 to 5, FIGS. 1 and 3) Japanese Patent Laid-Open No. 2008-170052 (pages 4 to 5, FIG. 1)
- the above prior art determines whether or not the compressor heating device can be operated in a time zone or at a predetermined temperature. For example, the compressor heating device may be operating even in a situation where no refrigerant has accumulated in the compressor. high. This leads to an increase in standby power when the air conditioner is stopped, which is inefficient. Also, when comparing each temperature with the shell temperature, there are many control factors and there are some useless temperature detection locations, so the effect is small against complicated control and the operation of the compressor heating device There is a risk of inefficiency due to frequent switching.
- the present invention has been made to solve the above-mentioned problems of the prior art, and the main purpose is to pipe the compressor, the indoor unit side heat exchanger, the outdoor unit side heat exchanger, the pressure reducing device, and the four-way valve.
- simple and efficient refrigerant accumulation in the compressor is detected by detecting the occurrence of refrigerant accumulation in the compressor based on the detection conditions of the compressor shell temperature and the outside air temperature, and determining whether or not the compressor heating device can be operated.
- An object is to obtain an air conditioner capable of preventing the above.
- An air conditioner includes a compressor shell temperature detecting device that detects a shell temperature of a compressor that constitutes a refrigerant circuit, an outside air temperature detecting device that detects an outside air temperature, and an output of the compressor shell temperature detecting device. And a control device that determines whether or not refrigerant has accumulated in the compressor based on an output of the outside air temperature detection device and a preset threshold value.
- the control device when the control device detects a temperature at which the compressor shell temperature is lower than the outside air temperature, the control device determines that the refrigerant has accumulated in the compressor shell, and thus operates the compressor heating device.
- heating the compressor shell has an effect of avoiding refrigerant accumulation in the compressor.
- FIG. 5 is a control hysteresis diagram (part 1) that shows an example of ON / OFF conditions of a compressor heating control method according to the present invention.
- FIG. 11 is a control hysteresis diagram (part 2) illustrating an example of ON / OFF conditions of the compressor heating control method according to the present invention.
- It is the refrigerant circuit which added the discharge side check valve for the purpose of the load reduction of the compressor heating control method of this invention.
- FIG. 1 is a configuration diagram illustrating a refrigerant circuit of an air-conditioning apparatus according to Embodiment 1 of the present invention.
- the air conditioner includes an outdoor unit 10, an indoor unit 20, and a pipe connecting them.
- the outdoor unit 10 includes a compressor 1, a four-way valve 2, a pressure reducing device 4, an outdoor unit side heat exchanger 5, and an accumulator 6.
- the indoor unit 20 has a built-in indoor heat exchanger 3.
- the four-way valve 2 built in the outdoor unit 10 has a role of changing the course direction of the refrigerant circuit.
- an air conditioner having both cooling and heating functions performs a cooling operation when high-temperature and high-pressure refrigerant discharged from a compressor is sent to the outdoor heat exchanger 5, and the indoor heat exchanger 3 When it is sent to the room, heating operation is performed.
- the four-way valve 2 has a role of switching the operation cycle, and the operation cycle can be freely switched by switching the slide valve in the four-way valve 2.
- the decompression device 4 built in the outdoor unit 10 has a role of decompressing the low-temperature and high-pressure liquid refrigerant condensed by the heat exchanger to a pressure at which it is easily evaporated.
- the refrigerant after being discharged from the compressor 1, the refrigerant remains at a high pressure until it passes through a predetermined path of the refrigerant circuit corresponding to the cooling or heating operation cycle and reaches the decompression device 4.
- the refrigerant circuit that passes from the time when the device 4 passes to the time when it reaches the suction port of the compressor 1 has a low pressure.
- Refrigerator oil exists as lubricating oil for driving a compressor.
- the refrigerating machine oil does not always remain in the compressor, and a small amount of the refrigerating machine oil is always taken out of the compressor along with the operation of the air conditioner and travels with the refrigerant in the refrigerant circuit. If a large amount of refrigerating machine oil is discharged from the inside of the compressor, if the refrigerating machine oil is insufficient in the compressor drive unit, the drive shaft of the compressor may be seized and may break down.
- the refrigeration oil may be diluted by mixing refrigerant, and when the viscosity of the refrigeration oil decreases due to refrigerant dilution, the compressor drive shaft is burned out due to the refrigeration oil shortage in the compressor as described above, There is a risk of failure.
- Refrigerator oil shortage is generally caused by refrigerant accumulation in the compressor.
- a refrigerating machine oil having high compatibility with a refrigerant is used, and the refrigerant flows in from an external refrigerant circuit as the temperature of the compressor cools when the air conditioner is stopped.
- the refrigerant dissolves in the refrigeration oil (this is called “sleeping” of the refrigerant into the refrigeration oil), and the refrigerant is diluted with the refrigerant or at the next operation. This will lead to an increase in the amount of refrigeration oil taken out.
- the refrigerant liquefies inside the compressor.
- liquid refrigerant also exists in the compression portion, leading to an increase in the compression load during operation of the compressor, and causing deterioration and failure of the equipment.
- the cause of the refrigerant accumulation in the compressor is the low temperature of the compressor.
- the high and low pressure difference generated in the refrigerant circuit gradually shifts to equal pressure.
- the refrigerant moves to a lower temperature / low pressure portion.
- the compressor is in a lower temperature / low pressure state than the ambient temperature, the refrigerant gradually accumulates inside the compressor, and the refrigerant accumulation state that causes the compressor failure described above Become.
- the compressor heating device 24 includes a heater attached outside the shell and a motor inside the compressor. By energizing the motor, the compressor can be heated from the motor heat generation effect. Since the attachment of the heater leads to high cost of the air conditioner, a motor energization method is desirable as this embodiment.
- a device for detecting the compressor shell temperature and the outside air temperature for example, a thermistor is installed in the air conditioner.
- a thermistor is a device that is generally installed as a means for detecting and controlling temperature in controlling an air conditioner, and is widely used as a low-cost detector that has sufficient accuracy to perform appropriate control. ing.
- the control plate 23 is required as a control device that determines the above two temperature detection conditions and determines the energization of the compressor motor.
- the control plate 23 compares the compressor shell temperature with the outside air temperature, and permits the heating of the compressor motor, that is, the motor energization when the conditional expression (1) is satisfied.
- the control plate 23 operates the compressor heating device 24 to heat the compressor 1, thereby avoiding refrigerant accumulation in the compressor.
- Conditional expression (2) is a condition deviating from conditional expression (1), that is, an event that avoids refrigerant accumulation in the compressor. When it is determined that the compressor temperature is clearly higher than the outside air temperature, it is considered that there is a large amount of refrigerant in the outdoor heat exchanger or accumulator, not in the compressor, and the amount of refrigerant present in the compressor is It is an amount that is judged as no problem.
- the constant ⁇ is a control constant for constructing the energization temperature condition to the compressor motor with hysteresis as shown in FIG.
- the constant ⁇ is a control constant for constructing the energization temperature condition to the compressor motor with hysteresis as shown in FIG.
- the present embodiment changes every moment depending on various factors such as the thickness of the compressor shell and the heat insulation around the shell, which is inconvenient because adjustment is required for each device in order to set the prohibited time. For this reason, the method of determining regardless of the state of the apparatus by setting the control temperature condition for determining whether or not the compressor motor can be energized as hysteresis is more convenient.
- FIGS. 6 and 7 are flowcharts showing the operation of the control plate 23 according to the first embodiment of the present invention.
- FIG. 6 shows activation for activating a function related to the main control of the control plate (hereinafter referred to as a control function).
- FIG. 7 is a main flowchart showing an operation flow relating to the control function of the control plate.
- the control plate 23 When the power is turned on, the control plate 23 operates in accordance with the start-up flowchart of FIG. 6, and repeatedly executes step S601 until the compressor stops and waits. When the compressor 1 stops (Yes in step S601). ), The control function is activated (step S602).
- the control plate 23 takes in the outside air temperature detected by the outside air temperature thermistor 22 and the compressor shell temperature detected by the compressor shell thermistor 21 based on the flow of FIG. Steps S701 to S702). Next, the control plate 23 compares the compressor shell temperature TCS with the temperature TO1 obtained by subtracting the threshold value ⁇ from the outside air temperature TO (step S703). If the compressor shell temperature TCS is lower than the temperature TO1, the control plate 23 It is determined that the refrigerant has accumulated in the heater, the heating device is operated to heat the compressor 1 (step S704), and the process returns to step S701.
- step S703 if the compressor shell temperature TCS is not lower than the temperature TO1, it is determined that a large amount of refrigerant has not accumulated in the compressor 1, and then the compressor shell temperature TCS is set to the outside air temperature TO. It compares with temperature TO2 which added threshold value (alpha) (step S705). If the shell temperature TCS of the compressor is higher than the temperature TO2, the refrigerant is not accumulated in the compressor 1, so that the operation of the compressor heating device is stopped to stop unnecessary heating of the compressor (step S706). ) Thereafter, the process returns to step S701. In the comparison in step S705, if the compressor shell temperature TCS is not higher than the temperature TO2, nothing is done and the process returns to step S701.
- the constant ⁇ is 3 ° C.
- the hunting phenomenon of the frequent energization operation described above is avoided by expanding the temperature range, which is a condition for energizing the compressor motor, to 6 ° C. (2 ⁇ ).
- the thermistor is used for the temperature detection means as an example for realizing the above form, an error may occur in the detected temperature. Therefore, when the value of ⁇ is small, it is possible to prevent frequent switching of energization due to a thermistor detection error, and to extend the cycle time of repeated energization switching even under a condition with little error.
- the second reason is the temperature difference between the compressor shell temperature and the compressor internal temperature.
- the amount of heat passing generated inside and outside the container is expressed by the following formula (3).
- Q A ⁇ K ⁇ ⁇ T (3)
- Q heat passage amount (W)
- A heat transfer area (m2)
- K heat passage rate (W / m2K)
- ⁇ T inside / outside temperature difference (K).
- W heat passage amount
- m2K heat passage rate
- K inside / outside temperature difference
- K inside / outside temperature difference
- the compressor shell is generally made of an iron material, the heat passage rate is lower than other materials used in refrigerant circuits such as aluminum and copper.
- the compressor shell is made thick because it needs to have high pressure resistance. Therefore, there is a temperature difference between the temperature detected by the thermistor attached to the outer shell of the compressor shell and the refrigerant temperature inside the shell.
- ⁇ 3 ° C. is set as a threshold value for judging the accumulation of the refrigerant by the difference between
- control plate 23 is expressed as It is possible to change (1) and (2) to equations (4) and (5), respectively.
- control method is a means for directly judging refrigerant accumulation in the compressor and avoiding the accumulation phenomenon with the minimum necessary power supply time, the air conditioner is stopped. It is possible to avoid as much as possible the standby electric energy when the device is in use, and this is a useful method for energy saving of the entire device.
- the refrigerant accumulation in the compressor is judged with only the minimum necessary apparatus and a simple control type, and whether or not the compressor motor is energized is easily introduced into a general air conditioner.
- it is useful in the sense that it can be widely used in general refrigerant circuits that construct a refrigerant circuit with a compressor.
- Embodiment 2 when the refrigerant circuit having the structure as shown in FIG. 1 described in ⁇ Embodiment 1> has a check valve 31 on the compressor discharge side as shown in FIG. It is expected that the load will be reduced by the compressor heating control method shown in the first embodiment. This embodiment will be described in this embodiment.
- Refrigerant accumulation in the compressor is a phenomenon that occurs as a result of refrigerant flowing into the compressor when the compressor is in a low pressure / low temperature state when the air conditioner is stopped as described above. This causes not only the low pressure suction side but also the back flow from the high pressure discharge side. Therefore, by adding a check valve to the discharge side, the refrigerant discharged from the discharge side to the heat exchanger connected to the compressor discharge pipe is prevented from flowing back into the compressor and flowing into the compressor, It is possible to reduce the amount of refrigerant accumulated in the compressor.
- the greatest advantage of this structure is that the energization time to the compressor heating device can be reduced.
- the compressor heating control can maintain the state of the refrigerant in a gaseous state by applying heat to the refrigerant, and can avoid the cause of compressor failure due to dilution of the refrigeration oil or liquid refrigerant. If the refrigerant in the compressor becomes a gas state due to the compressor heating, more refrigerant than necessary flows to the discharge side.
- the present embodiment by having a check valve structure on the discharge side as described above, not only the amount of refrigerant flowing backward from the discharge side is suppressed, but also cooling of excess refrigerant discharged by compressor heating is performed. It becomes possible to prevent the return. For this reason, it is possible to consume a small amount of energy by heating the compressor even during long-term standby.
- Embodiment 3 FIG.
- the refrigerant circuit having the structure as shown in FIG. 1 described in ⁇ Embodiment 1> by performing a pump-down operation when the operation of the compressor heating device is stopped, ⁇ Embodiment 1> The load reduction by the compressor heating control method shown is expected. This embodiment will be described in this embodiment.
- the pump-down operation is an operation method for collecting the refrigerant diffused in the refrigerant circuit on the outdoor unit side, and is an operation method mainly used when the air conditioner is removed.
- the decompression device is throttled as much as possible, and the refrigerant accumulated on the low pressure side is moved to the discharge side, specifically, to the indoor heat exchanger during heating operation.
- Refrigerant separated from oil by the operation of the compressor heating device is expelled to the discharge side by pump-down operation, and the amount of refrigerant remaining in the compressor is reduced, so that energy consumption due to compressor heating is small even during long-term standby. It is possible to do it.
- Embodiment 4 In the refrigerant circuit as shown in FIG. 1 or FIG. 5, by performing the pump-down operation when the operation of the air conditioner is stopped, the refrigerant that has diffused and remained in the refrigerant circuit low pressure side in advance is discharged to the discharge side of the compressor. It is possible to collect the refrigerant, and the amount of refrigerant existing in the compressor at the time of operation stop is small. That is, it is possible to consume a small amount of energy by heating the compressor even during long-term standby.
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Abstract
Description
図1は、本発明の実施の形態1における空気調和装置の冷媒回路を示す構成図である。図1に示すように空気調和装置は室外機10と室内機20及びこれらを接続する配管とから構成される。室外機10は、圧縮機1、四方弁2、減圧装置4、室外機側熱交換器5、及びアキュームレータ6を内蔵している。また、室内機20は、室内側熱交換器3を内蔵している。
図1の冷媒回路の中で、室外機10に内蔵されている四方弁2は、冷媒回路の進路方向を変更する役割を持つ。通常、冷房及び暖房の両方の機能を有する空気調和装置は、圧縮機から吐出された高温・高圧の冷媒を室外側熱交換器5に送り込んだ場合に冷房運転を行い、室内側熱交換器3に送り込んだ場合に暖房運転を行う。四方弁2はこの運転サイクルを切り替える役割を有し、四方弁2内にあるスライド弁を切り替えることで運転サイクルを自由に切り替えることが出来る。
一方、室外機10に内蔵された減圧装置4は、熱交換器によって凝縮された低温・高圧の液冷媒を、蒸発しやすい圧力まで減圧させる役割を持つ。つまり、圧縮機1から吐出された後、冷房、または暖房の運転サイクルに応じた冷媒回路の所定の経路を通過し、減圧装置4に到達するまでは、冷媒は高圧を維持しており、減圧装置4通過以降より圧縮機1の吸入口に到達するまでに通過する冷媒回路では、低圧となる。
また、冷凍機油は冷媒の混入によって希釈される場合があり、冷媒希釈による冷凍機油の粘度低下が生じた場合、上記と同様に圧縮機内の冷凍機油不足状態となり圧縮機駆動軸が焼きつけを起こし、故障する恐れがある。
本実施形態を実現するためには、少なくとも圧縮機シェル温度21及び外気温度22を検知することが必要である為、図2のようにサーミスタを取付ける必要がある。また、上記2つの温度の検知条件を判断し、圧縮機モーターへの通電を判断する制御装置としての制御板23が必要である。
制御板23は圧縮機シェル温度と外気温度を比較し、条件式(1)が成り立った場合は圧縮機モーターの加熱、すなわちモーター通電を許可する。
[圧縮機シェル温度]≦[外気温度]-α (α = 例えば3℃) …(1)
圧縮機シェル温度と外気温度がほとんど同じであると判断された場合、圧縮機内部に冷媒が溜まりこんでいる可能性が高い。従って、制御板23は圧縮機加熱装置24を動作させて圧縮機1を加熱することにより圧縮機内部の冷媒溜まりこみを回避する。上記条件において、外気温度が高い場合には冷媒溜まりこみの可能性は低くなるものの、少なくとも外気温度と同等以下の温度である場合には、室外機側に存在している冷媒が圧縮機に集まる可能性が生じる。その為、外気温度による条件設定は行わないことが望ましい。
[圧縮機シェル温度]>[外気温度]+α …(2)
上記条件式(2)は条件式(1)を逸脱した条件であり、即ち圧縮機内の冷媒溜まりこみを回避している事象と考えられる。外気温度よりも明らかに圧縮機温度が高いと判断される場合、冷媒は圧縮機ではなく室外熱交換器、あるいはアキュームレータに多く存在すると考えられ、圧縮機内部に存在する冷媒量は駆動しても問題ないと判断される量である。従って本条件中における圧縮機の過度な加熱は待機電力量として無駄であり、非効率な状況と判断される為、通電しないのが望ましい。
また、上記式(1)、(2)とも条件は常時有効であり、空気調和装置に電源が供給されている期間は常に有効とする。
次に、制御板23の動作を図2及び図6を用いて説明する。
制御板23は、電源が投入されると、図6の起動用フローチャートに従って動作し、圧縮機が停止するまではステップS601を繰り返し実行して待機し、圧縮機1が停止すると(ステップS601のYes)、制御機能を起動する(ステップS602)。
制御機能が起動されると、制御板23は、図7のフローに基づいて、まず外気温度サーミスタ22が検出した外気温度を取り込むとともに圧縮機シェルサーミスタ21が検出した圧縮機のシェル温度を取り込む(ステップS701~S702)。次に、制御板23は、圧縮機のシェル温度TCSを外気温度TOから閾値αを差し引いた温度TO1と比較し(ステップS703)、圧縮機のシェル温度TCSが温度TO1より低ければ圧縮機1内に冷媒が溜まり込んでいると判断し、加熱装置を動作させて圧縮機1を加熱し(ステップS704)、ステップS701へ戻る。ステップS703の比較において、圧縮機のシェル温度TCSが温度TO1より低くなければ圧縮機1内に冷媒が多量に溜まり込んでいないと判断し、次に、圧縮機のシェル温度TCSを外気温度TOに閾値αを加えた温度TO2と比較する(ステップS705)。そして、圧縮機のシェル温度TCSが温度TO2より高ければ圧縮機1内に冷媒が溜まっていないので、圧縮機加熱装置の動作を停止して圧縮機への無駄な加熱を止めさせた(ステップS706)後、ステップS701へ戻る。また、ステップS705の比較において、圧縮機のシェル温度TCSが温度TO2より高くなければ何もせずステップS701へ戻る。
第1に圧縮機モーターへの通電可否条件となる温度範囲を6℃(2α)と広げることにより上記で示した頻繁な通電動作のハンチング現象を回避する為である。上記形態を実現する一例として温度検知手段にサーミスタを用いているが、検知温度に誤差が生じる恐れがある。従ってαの値が小さい場合、サーミスタ検知誤差によって頻繁に通電切り替えが生じるのを防ぐとともに、誤差があまりない条件であっても繰返し通電切り替えのサイクル時間を延長する効果がある。
Q = A・K・ΔT …(3)
ここでQ:熱通過量(W)、A:伝熱面積(m2)、K:熱通過率(W/m2K)、ΔT:内外温度差(K)とする。圧縮機シェルは一般に鉄製材料で作製されているため、他のアルミや銅といった冷媒回路で用いられる材料よりも熱通過率は低い。さらに圧縮機シェルは高い耐圧性能を備える必要があるため、厚く作られている。このことから、圧縮機シェル外殻に取付けられたサーミスタによる検知温度とシェル内部の冷媒温度には温度差が生じる。この温度差を考慮した上でシェル外殻の温度と外気温度の差で冷媒の溜まりこみを判断するしきい値としてα=3℃を設けている。
[圧縮機シェル温度]≦[外気温度]-α + β (β = 例えば2℃) …(4)
[圧縮機シェル温度]>[外気温度]+α + β …(5)
圧縮機が油枯渇運転に極端に弱い、あるいはサーミスタ検知精度が悪いなど、冷媒溜まりこみ運転と判断するに乏しい事象であっても圧縮機加熱装置を作動させたい場合には、制御板23は図4に示すように上記式(4)、(5)を用いて圧縮機加熱装置の作動可否を制御する。ただし、定数βの数値が大きいと過剰保護となり、待機電力量の増加や圧縮機寿命の低下に繋がる恐れがあるため注意が必要である。
一方、<実施の形態1>にて説明した図1のような構造を持つ冷媒回路において、図5に示すように圧縮機吐出側に逆止弁31を持つ冷媒回路である場合、<実施の形態1>で示した圧縮機加熱制御方法による負荷軽減が期待される。
本実施の形態では、このような形態について説明する。
本構造の最大の利点は、前記圧縮機加熱装置への通電時間を軽減できることにある。即ち、圧縮機加熱制御は冷媒に熱を与えることで冷媒の状態をガス状で維持し、冷凍機油の希釈や液冷媒による圧縮機故障原因を回避することができる。圧縮機加熱により圧縮機内の冷媒がガス状態になれば、必要以上の冷媒は吐出側に流れることになる。
本実施の形態によれば、以上のように吐出側に逆止弁の構造を持つことにより、吐出側から逆流する冷媒量を抑制するだけでなく、圧縮機加熱により吐出した余分な冷媒の冷却戻りを防ぐことが可能になる。その為、圧縮機加熱によるエネルギー消費は長期待機中であっても少量で済ませることが可能になる。
一方、<実施の形態1>にて説明した図1のような構造を持つ冷媒回路において、圧縮機加熱装置の作動を停止する際にポンプダウン運転を行うことで、<実施の形態1>で示した圧縮機加熱制御方法による負荷軽減が期待される。
本実施の形態では、このような形態について説明する。
圧縮機加熱装置の作動により油から分離した冷媒をポンプダウン運転により吐出側に追い出し、圧縮機内部に残存する冷媒量を減らすことにより、圧縮機加熱によるエネルギー消費は長期待機中であっても少量で済ませることが可能となる。
図1あるいは図5のような冷媒回路において、空気調和機の運転停止時に上記ポンプダウン運転を行うことにより、予め冷媒回路低圧側に拡散して残存する冷媒を圧縮機の吐出側に排出して集めることが可能となり、運転停止時の圧縮機内に予め存在する冷媒量は少量となる。すなわち、圧縮機加熱によるエネルギー消費は長期待機中であっても少量で済ませることが可能となる。
Claims (10)
- 冷媒回路を構成する圧縮機のシェル温度を検知する圧縮機シェル温度検知装置と、
外気温度を検知する外気温度検知装置と、
前記圧縮機シェル温度検知装置の出力と前記外気温度検知装置の出力と、予め設定した閾値とに基づいて前記圧縮機内の冷媒溜まりこみの発生の有無を判断する制御装置と、
を備えたことを特徴とする空気調和装置。 - 前記制御装置は、前記圧縮機シェル温度検知装置の出力が前記外気温度検知装置の出力よりも予め設定された閾値以上低い場合に前記圧縮機内の冷媒溜まりこみが発生したと判断することを特徴とする請求項1記載の空気調和装置。
- 前記圧縮機のシェルを加熱する圧縮機加熱装置を備え、
前記制御装置は、前記圧縮機シェル温度検知装置の出力と前記外気温度検知装置の出力と、前記閾値とに基づいて前記圧縮機内の冷媒溜まりこみが発生したと判断した場合、前記圧縮機加熱装置を動作させ、前記圧縮機のシェルを加熱させることを特徴とする請求項1記載の空気調和装置。 - 前記制御装置は、前記圧縮機シェル温度検知装置の出力が前記外気温度検知装置の出力よりも予め設定された値以上高い温度を検知した場合には、前記圧縮機加熱装置の動作を停止することを特徴とする請求項3記載の空気調和装置。
- 前記閾値はヒステリシスを持つことを特徴とする請求項1~4のいずれかに記載の空気調和装置。
- 前記圧縮機の吐出側配管に接続される熱交換器を備え、
前記圧縮機から吐出された冷媒による前記熱交換器から前記圧縮機への逆流を防止する冷媒逆流防止手段を前記圧縮機の吐出側配管に設けたことを特徴とする請求項1~5のいずれかに記載の空気調和装置。 - 前記制御装置は、前記圧縮機シェル温度検知装置の出力が前記外気温度検知装置の出力よりも予め設定された値以上高い温度を検知した場合には、前記圧縮機加熱装置の動作を停止とともにポンプダウン運転を行うことを特徴とする請求項3記載の空気調和装置。
- 前記圧縮機シェル温度検知装置と前記外気温度検知装置はサーミスタで構成されることを特徴とする請求項1~7のいずれかに記載の空気調和装置。
- 前記圧縮機加熱装置は、前記圧縮機のシェル外部に取付けられるヒーターまたは前記圧縮機内部のモーターであることを特徴とする請求項3または請求項4に記載の空気調和装置。
- 圧縮機、四方弁、室内機側熱交換器、減圧装置、室外機側熱交換器、を配管接続した冷媒回路を有した空気調和装置において、
前記圧縮機のシェルを加熱して油から冷媒を分離する圧縮機加熱装置と、
前記圧縮機加熱装置の作動を停止させると同時にポンプダウン運転を行って、前記圧縮機加熱装置によって油から分離された冷媒を吐出側に追い出して前記圧縮機内部に残存する冷媒量を減らす制御装置と、を有することを特徴とする空気調和装置。
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ES2816557T3 (es) | 2021-04-05 |
AU2010222517A1 (en) | 2011-09-01 |
EP2407733A1 (en) | 2012-01-18 |
US9291379B2 (en) | 2016-03-22 |
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