WO2012114454A1 - Appareil à cycle de réfrigération - Google Patents

Appareil à cycle de réfrigération Download PDF

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Publication number
WO2012114454A1
WO2012114454A1 PCT/JP2011/053839 JP2011053839W WO2012114454A1 WO 2012114454 A1 WO2012114454 A1 WO 2012114454A1 JP 2011053839 W JP2011053839 W JP 2011053839W WO 2012114454 A1 WO2012114454 A1 WO 2012114454A1
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WO
WIPO (PCT)
Prior art keywords
temperature
compressor
refrigeration cycle
solenoid valve
heat exchanger
Prior art date
Application number
PCT/JP2011/053839
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English (en)
Japanese (ja)
Inventor
小山　昌喜
小谷　正直
遼太 飯島
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Priority to PCT/JP2011/053839 priority Critical patent/WO2012114454A1/fr
Priority to JP2013500750A priority patent/JP5965895B2/ja
Priority to EP20110859245 priority patent/EP2679930A4/fr
Priority to CN201180067090.0A priority patent/CN103380334B/zh
Publication of WO2012114454A1 publication Critical patent/WO2012114454A1/fr

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Classifications

    • 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • 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
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2521—On-off valves controlled by pulse signals
    • 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
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a capacity control compressor capable of capacity control.
  • the present invention is suitable for a refrigeration cycle apparatus such as an air-conditioning hot-water supply system for a new generation house having a high eco (environmental-friendly) effect, and can be operated in a wide range, and can efficiently operate even in an ultra-small capacity operation mode. It is particularly suitable for a refrigeration cycle apparatus having a scroll compressor that can be controlled.
  • a scroll compressor used in a refrigeration cycle apparatus such as an air conditioner or a water heater is required to be capable of capacity control over a wide range with a single unit. That is, in the cooling operation of the air conditioner, the room temperature is generally high at the start of operation, and thus it is necessary to operate rapidly. In such a case, high speed operation (high speed rotation) is performed at the time of start-up, but when the room is cooled to a certain degree and the state is shifted to a steady operation state, low speed operation (low speed rotation) is performed with a small capacity.
  • Patent Document 1 a high pressure chamber, a discharge chamber, and a low pressure suction pipe formed between an outer shell coupling fitting provided on one end side of a compressor and a piston connected to a non-orbiting scroll member are respectively interposed with solenoid valves.
  • PWM pulse width adjustment
  • the solenoid valve is turned off (closed) during normal capacity control, and the solenoid valve is turned on (opened) during small capacity control to suck the refrigerant gas on the low pressure side.
  • the amount of refrigerant gas discharged is adjusted by returning it to the tube, enabling a wide range of volume control from 0 to 100%.
  • the lower limit setting value of the motor rotation speed that cannot be actually implemented due to the problems of oil film breakage and torque fluctuation in the above-described slide bearing (the drive signal to the motor has a frequency of about 5 Hz.
  • Compression operation with a small capacity control (ultra-small capacity operation mode) corresponding to the following ultra-low speed operation is possible, and the compressed refrigerant gas is discharged into the discharge pipe.
  • the refrigerant gas can be circulated gently by being guided to the refrigeration cycle via the.
  • a scroll compressor provided with a bypass port, a flow path that opens the bypass port to an intake pressure atmosphere, a control valve that opens and closes the flow path, and a control valve are set according to the operating load of the air conditioner And a control means that opens and closes by a plurality of control patterns based on the short-period time distribution.
  • the air conditioner equipped with the scroll compressor according to Patent Document 2 it is possible to control the capacity by 60% by discharging the refrigerant gas being compressed into the suction chamber and reducing the confined volume when the suction is completed.
  • 60-100% capacity control operation is realized in stages by opening and closing a control valve for discharging refrigerant gas in the middle of compression to the suction chamber according to a plurality of patterns with a short-period time distribution. .
  • JP-A-8-334094 Japanese Patent Laid-Open No. 11-324951
  • the discharge pressure and the suction pressure vary due to the opening and closing of a control valve such as a solenoid valve for capacity control.
  • a control valve such as a solenoid valve for capacity control.
  • PWM control pulse width adjustment control
  • the suction pressure fluctuates greatly, and this capacity control method is used for the air conditioner.
  • the blowing temperature fluctuates and the comfort cannot be maintained.
  • a loss occurs when the control valve is opened and closed. Therefore, if the duty cycle is shortened, the fluctuation is reduced, but the loss is increased and the efficiency is lowered.
  • Patent Document 1 capacity adjustment is performed by PWM control of a solenoid valve to turn it on and off, and a wide range of capacity control is possible.
  • Patent Document 1 only describes that the solenoid valve is subjected to PWM control and the capacity control is performed by changing the on-off time ratio (duty ratio) in order to adjust the target capacity.
  • the on-off time ratio duty ratio
  • Patent Document 2 a load state of a refrigeration cycle is detected based on signals from a temperature sensor and a pressure sensor provided in a condenser and an evaporator, and a capacity control operation and a full load operation are switched. In the capacity control operation, the bypass operation is performed with a predetermined time distribution.
  • this Patent Document 2 as in Patent Document 1, no consideration is given to improving comfort while suppressing a decrease in efficiency.
  • An object of the present invention is to obtain a refrigeration cycle apparatus capable of efficient operation control even in an ultra-small capacity operation mode and improving comfort.
  • the present invention provides a refrigeration cycle apparatus comprising a compressor, an outdoor heat exchanger, an opening controllable expansion valve, and an indoor heat exchanger, wherein refrigerant in the compressor is being compressed.
  • a bypass flow path for bypassing to the suction side a solenoid valve for opening and closing the bypass flow path, a time ( ⁇ 1) for opening (ON) state and a time ( ⁇ 2) for closing (OFF) the solenoid valve
  • the solenoid valve is controlled to be closed when the suction pressure (Ps0) before opening the noid valve is greater than an allowable deviation ( ⁇ P), and the
  • the refrigerant being compressed in the compressor is supplied to the suction side of the compressor A bypass flow path to be bypassed, a solenoid valve for opening and closing the bypass flow path, a time ( ⁇ 1) for opening (ON) state and a time ( ⁇ 2) for closing (OFF) the solenoid valve And a controller that controls the capacity by adjusting the flow rate of the refrigerant discharged from the compressor to the refrigeration cycle, and the controller controls the duty cycle (the sum of the opening time and the closing time of the solenoid valve).
  • the schematic block diagram which shows Example 1 of the refrigerating-cycle apparatus of this invention The diagram explaining the fluctuation
  • the schematic block diagram of the refrigerating-cycle apparatus which shows Example 3 of this invention.
  • the flowchart explaining the compressor rotation speed control routine in Example 3 of this invention The longitudinal section showing an example of the capacity control compressor used for the present invention.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus showing Embodiment 1 of the present invention, in which the present invention is used for a room air conditioner (air conditioner).
  • the refrigeration cycle apparatus shown in FIG. 1 will be described together with the operation during cooling operation.
  • the refrigerant compressed by the compressor 1 flows into the four-way valve 5 from the high-pressure side connection pipe 7, passes through the four-way valve 5, and flows out to the outdoor connection pipe 8. Thereafter, the refrigerant is condensed and liquefied by exchanging heat with the outdoor air in the outdoor heat exchanger 2 and dissipating heat, and is decompressed by the expansion valve 3.
  • the refrigerant that has been decompressed to low temperature and low pressure enters the indoor heat exchanger 4, cools the indoor air and evaporates / gases itself, and flows again into the four-way valve 5 from the indoor connection pipe 9. Circulates through the low-pressure side connection port, returns to the suction side of the compressor 1 and is compressed again.
  • the refrigerant pipe connection destination of the four-way valve 5 is switched.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 101 passes through the four-way valve 5 from the high-pressure side connection pipe 7, flows out into the indoor connection pipe 9, flows into the indoor heat exchanger 4, and dissipates heat to the indoor air. By doing this, it heats up and condenses itself.
  • the condensed refrigerant is decompressed by the expansion valve 3, exchanges heat with outdoor air in the outdoor heat exchanger 2, evaporates and gasifies, flows into the four-way valve 5 from the outdoor connection pipe 8, and then flows to the low-pressure side connection pipe 10. The circulation of returning to the suction side of the compressor 1 and being compressed again is repeated.
  • bypass pipe 11 is a bypass pipe (bypass flow path) that guides the refrigerant gas at the discharge pressure to the suction side of the compressor 1, and one end of the bypass pipe 11 is connected to the low-pressure side connection pipe 10 on the compressor suction side.
  • the bypass pipe 11 is provided with a solenoid valve 12 that is controlled to be opened (ON) and closed (OFF) by a pulse width adjustment (PWM) control signal.
  • PWM pulse width adjustment
  • the solenoid valve 12 is repeatedly operated in an open state and a closed state, and ON / OFF of the discharge-side refrigerant flowing into the suction side is repeated.
  • a capacity adjustment mechanism that performs small capacity control of refrigerant discharged from the compressor to the refrigeration cycle is realized.
  • Reference numeral 13 shown in FIG. 1 denotes a discharge temperature sensor attached to the discharge side pipe (high-pressure side connection pipe 7) of the compressor 1, and detects the refrigerant discharge temperature (refrigerant inlet temperature to the condenser) from the compressor.
  • Reference numeral 14 denotes an indoor heat exchanger temperature sensor attached at a substantially intermediate position of the indoor heat exchanger 4, and this temperature sensor 14 is used for the refrigerant during the cooling operation in which the indoor heat exchanger 4 functions as an evaporator. Used to detect the evaporation temperature.
  • reference numeral 15 denotes an outdoor heat exchanger temperature sensor attached at a substantially intermediate position of the outdoor heat exchanger 2, and this temperature sensor 15 is used for the refrigerant during the heating operation in which the outdoor heat exchanger 2 functions as an evaporator. Used to detect the evaporation temperature.
  • 16 is an indoor temperature sensor that detects the temperature of the room in which the indoor heat exchanger 4 is provided
  • 17 is an outdoor temperature sensor that detects the outside air temperature near the installation of the outdoor heat exchanger 2.
  • an inverter (motor drive circuit) 18 is connected to the compressor 1, and the inverter 18 is connected to a commercial AC power source 19.
  • the inverter 18 rectifies the voltage of the commercial AC power supply 19, converts it to a voltage having a frequency according to the command, and outputs the voltage to a motor provided in the compressor 1.
  • the inverter 18 is connected to the control unit 20 and drives the motor based on a command from the control unit 20.
  • the control unit 20 includes the four-way valve 5, the expansion valve 3, the outdoor fan 21, the indoor fan 22, the indoor heat exchanger temperature sensor 14, the outdoor heat exchanger temperature sensor 15, and the indoor temperature sensor 16.
  • the outdoor temperature sensor 17, the discharge temperature sensor 13, the suction pressure sensor 23, the inverter 18, and a remote control type operation device (not shown; hereinafter referred to as a remote controller) are connected to each other.
  • the unit 20 is configured to control the entire refrigeration cycle apparatus (room air conditioner).
  • the control unit 20 puts the four-way valve 5 in the state of the cooling operation, and operates the compressor 1, the outdoor fan 21 and the indoor fan 22 at a predetermined rotation speed set in advance as an initial value. .
  • the refrigerant discharged from the compressor 1 repeats circulation such as returning to the compressor 1 through the four-way valve 5, the outdoor heat exchanger 2, the expansion valve 3, the indoor heat exchanger 4, and the four-way valve 5 again.
  • the expansion valve 3 is constituted by an electronic expansion valve, for example, and rotates a pulse motor built in the electronic expansion valve so as to open at an initial predetermined opening.
  • the indoor heat exchanger (use side heat exchanger) 4 functions as an evaporator.
  • the room temperature is detected by the room temperature sensor 16 provided in the vicinity of the ventilation passage entrance of the indoor heat exchanger 4, and according to the difference from the set temperature set by the remote controller.
  • the controller 20 controls the inverter 18 to vary the compressor speed. Thereby, the operation of the compressor 1 according to the air conditioning load is performed.
  • the detected temperature (discharged refrigerant temperature) of the discharge temperature sensor 13 is detected every predetermined control time, and the detected temperature, the detected temperature (evaporation temperature) of the indoor heat exchanger temperature sensor 14, and the indoor temperature sensor 16 are detected.
  • the opening degree of the expansion valve 3 is controlled at each control time according to the difference between the detected temperature (indoor temperature) and the target discharge temperature determined from the rotational speed command values of the compressor 1 and the outdoor fan 21.
  • the operating frequency of the compressor 1 is reduced and the discharge refrigerant temperature is set to a set value until the detected temperature falls to a predetermined set value.
  • the opening of the expansion valve 3 is controlled so that By this discharge temperature control, the compressor 1 is prevented from being abnormally heated, and the compressor 1 is prevented from being damaged due to seizure or the like.
  • the control unit 20 switches the four-way valve 5 to the heating operation side, and operates the compressor 1, the outdoor fan 21, and the indoor fan 22 at a predetermined rotation speed set in advance as an initial value.
  • the refrigerant discharged from the compressor 1 sequentially flows through the four-way valve 5, the indoor heat exchanger 4, the expansion valve 3, and the outdoor heat exchanger 2, passes through the four-way valve 5 again, and returns to the compressor 1.
  • the indoor heat exchanger (use side heat exchanger) 4 functions as a condenser.
  • the controller 20 detects the difference between the set temperature by the remote controller and the room temperature detected by the room temperature sensor 16 as an air conditioning load, and the compressor operating frequency (the output frequency of the inverter 18) according to the air conditioning load. ) To control. Thereby, the operation of the compressor 1 according to the heating load is performed.
  • the discharge refrigerant temperature is detected by the discharge temperature sensor 13 every predetermined control time, and the detected discharge refrigerant temperature, the detected temperature (evaporation temperature) of the outdoor heat exchanger temperature sensor 15, and the outdoor temperature sensor 17 are detected.
  • the opening degree of the expansion valve 3 is controlled for each control time according to the difference between the detected temperature (outside air temperature) and the target discharge temperature determined from the rotational speed command values of the compressor 1 and the outdoor fan 21.
  • the operating frequency of the compressor 1 is reduced and the discharge refrigerant temperature is set to a set value until the detected temperature falls to a predetermined set value.
  • the opening of the expansion valve 3 is controlled so that By this discharge temperature control, the compressor 1 is prevented from being abnormally heated, and the compressor 1 is prevented from being damaged due to seizure or the like.
  • an ultra low load operation mode (ultra low capacity operation mode)
  • the solenoid valve 12 provided in the bypass pipe 11 is opened (ON) and closed (PWM) by pulse width adjustment (PWM) control.
  • PWM pulse width adjustment
  • the capacity can be adjusted by repeatedly operating the solenoid valve 12 between the open state and the closed state and repeatedly opening and closing the bypass pipe 11.
  • the fluctuation range of the evaporation pressure during the capacity adjustment operation using the bypass pipe 11 is ⁇ P1. Further, during this capacity adjustment operation, the evaporation pressure generally increases, and the average pressure of the fluctuating evaporation pressure increases by ⁇ P2 with respect to the evaporation pressure before the capacity adjustment operation. If ⁇ P1 during the capacity adjustment operation is large, the evaporation temperature fluctuates accordingly, and the amount of heat exchange in the evaporator fluctuates, so that the capacity of the refrigeration cycle apparatus fluctuates and the blowing temperature fluctuates. For this reason, in order to maintain comfortable air conditioning, it is desirable to reduce ⁇ P1. Further, if ⁇ P2 is large, the endothermic amount is reduced, so the heat exchange amount is also reduced.
  • an appropriate duty cycle is determined according to the flowcharts shown in FIGS. 3 and 4, and capacity adjustment operation control is performed. Yes.
  • the compressor rotation speed control routine will be described with reference to the flowchart shown in FIG.
  • the rotation speed of the compressor is set from the remote controller by reading the indoor temperature Tea in detected by the indoor temperature sensor 16 provided near the inlet of the ventilation passage of the indoor heat exchanger 4 (step 31). setting temperature determining a difference DerutaTea in between (room temperature target value) T * ea in (step 32), in response to the difference, thereby changing the rotational speed of the compressor 1 by an inverter 18 (step 33, 34).
  • the compressor rotational speed fz is controlled to become smaller.
  • step 35 the compressor rotational speed f z is the smaller than the rotational speed f z opt for the capacitive control operation starts, the compressor rotational speed is fixed to f z opt, from the difference between the indoor temperature and the indoor temperature target value
  • the timer of the control unit is also turned on at the same time as the PWM control signal is turned on, and measurement of the elapsed time ⁇ 1 is started.
  • the suction pressure sensor 23 starts measuring the suction pressure, and the PWM control signal is compared until the measured suction pressure Ps exceeds a preset allowable deviation ⁇ P as compared to the suction pressure Ps0 before the PWM control signal is turned on. Remains ON and the pressure measurement is repeated (steps 38 to 41).
  • the PWM control signal is turned OFF, the solenoid valve 12 is closed, the timer is turned OFF, the elapsed time measurement is finished, and ⁇ 1 is opened. The time is determined (step 42).
  • the closing time ⁇ 2 is determined from the opening time ⁇ 1 and the current duty ratio d, and the PWM capacity control operation is performed based on this duty cycle (step 43).
  • the fluctuation of the suction pressure due to the opening and closing of the solenoid valve is determined within the range of ⁇ P. Therefore, by setting the ⁇ P in a range that does not impair the air conditioning comfort, it is possible to operate with an optimal duty cycle. .
  • FIG. 4 is a flowchart for explaining an expansion valve opening control routine in the refrigeration cycle apparatus of the present embodiment.
  • step 45 the state quantity of the refrigeration cycle is read. That is, the indoor temperature, outdoor temperature, indoor heat exchanger temperature, outdoor heat exchanger temperature, and the like detected by each sensor are read, and the rotation speed of the compressor 1, the rotation speeds of the indoor and outdoor fans 21, 22 and expansion The opening degree of the valve 3 is read.
  • step 46 when the PWM control signal is OFF, the expansion valve 3 has a detected temperature (discharge refrigerant temperature) Td of the discharge temperature sensor 13 that is detected by the outdoor heat exchanger temperature sensor 15 (condensation temperature) Tao.
  • the detected temperature of the outdoor temperature sensor 17 (ambient temperature) Tai, is controlling the opening so as to approach the target discharge temperature Td * determined from the rotational speed command value fp of the rotational speed f z and the outdoor fan 21 of the compressor 1 ( Steps 47-51).
  • step 46 when the PWM control signal is ON, a corrected compressor rotational speed f z ′ obtained by dividing the compressor rotational speed f z opt at the start of the capacity control operation by the duty ratio d at that time is determined (step 52).
  • the corrected compressor rotational speed f z ′, the detected temperature (condensation temperature) Tao of the outdoor heat exchanger temperature sensor 15, the detected temperature (outside air temperature) Tai of the outdoor temperature sensor 17, and the rotational speed command value fp of the outdoor fan 21 The routine is switched to a routine for controlling the expansion valve 3 so that the detected temperature (discharge refrigerant temperature) Td of the discharge temperature sensor 13 approaches the target discharge temperature Td * determined from (steps 52 to 57).
  • the expansion valve opening degree is changed to an appropriate opening amount even with respect to the reduced refrigerant circulation amount during the PWM capacity control operation. And increase in ⁇ P2 can be prevented.
  • the fluctuation of the suction pressure (evaporation pressure) due to the opening and closing of the solenoid valve 12 is determined in a range based on the allowable deviation ⁇ P, so that the fluctuation of the evaporation pressure is suppressed within a certain range.
  • This makes it possible to improve comfort such as air conditioning and to prevent an increase in loss due to a too short duty cycle, thus enabling highly efficient capacity control operation.
  • FIG. 5 is a schematic configuration diagram of a refrigeration cycle apparatus showing a second embodiment of the present invention, which is used for a room air conditioner as in the first embodiment.
  • the same reference numerals as those in FIG. 1 indicate the same or corresponding parts.
  • the difference from the first embodiment is that the suction pressure sensor is removed, and a blowout temperature sensor 24 is provided in the vicinity of the ventilation passage outlet of the indoor heat exchanger 4. This is the point that the blowing temperature is detected.
  • the temperature of the evaporator-side heat exchanger (the indoor heat exchanger 4 during the cooling operation, the outdoor heat exchanger 2 during the heating operation), and the blowout temperature of the indoor heat exchanger 4 measured by the blowout temperature sensor 24.
  • the fluctuation of the evaporation pressure can be estimated.
  • a compressor rotation speed control routine in the refrigeration cycle apparatus of the second embodiment will be described with reference to FIG.
  • Rotational speed of the compressor 1 as described above, read the indoor temperature Tea in detected by the indoor temperature sensor 16 provided near the ventilation passage inlet of the indoor heat exchanger 4 (step 31), is set from the remote controller
  • a difference ⁇ Tea in from the set temperature (target indoor temperature) T * ea in is obtained (step 32), and the rotation speed of the compressor 1 is varied by the inverter 18 in accordance with this difference (steps 33 and 34).
  • the compressor rotational speed fz is controlled to become smaller.
  • step 35 the compressor rotational speed f z is the smaller than the rotational speed f z opt for the capacitive control operation starts, the compressor rotational speed is fixed to f z opt, from the difference between the indoor temperature and the indoor temperature target value
  • the determined initial duty ratio d is determined (steps 36 and 37), and the PWM capacity control operation for turning the solenoid valve 12 on and off is performed.
  • the timer of the control unit is also turned on at the same time as the PWM control signal is turned on, and measurement of the elapsed time ⁇ 1 is started.
  • step 61 the measurement of the evaporator side heat exchanger temperature Tev0 by the temperature sensor (14 or 15) of the heat exchanger on the evaporator side is started (step 61), and further the evaporator side heat exchanger temperature at the start of the measurement. and Tev0, from said air temperature Tea out of the air temperature sensor 24 indoor heat exchanger 4 detected by, according to the table to hold a predetermined control constant to calculate a tolerance DerutaTev (step 62).
  • the PWM control signal Compared to the evaporator side heat exchanger temperature Tev0 before the PWM control signal is turned ON, the PWM control signal remains ON until the measured evaporator side heat exchanger temperature Tev exceeds the allowable deviation ⁇ Tev, and the evaporator The measurement of the side heat exchanger temperature Tev is repeated (steps 63 to 65).
  • the PWM control signal is turned OFF, the solenoid valve 12 is closed, and the timer is turned OFF. Then, the elapsed time measurement is finished, and ⁇ 1 is determined as the opening time.
  • the closing time ⁇ 2 is determined from this ⁇ 1 and the current duty ratio d, and the PWM capacity control operation is performed based on this duty cycle (steps 66 and 67).
  • the opening degree control of the expansion valve 3 is controlled according to the same routine as the expansion valve opening degree control routine in the first embodiment shown in FIG.
  • the evaporation can be performed by setting the allowable range ⁇ Tev to an appropriate range. Even without a pressure sensor (suction pressure sensor) for measuring pressure, it is possible to suppress fluctuations in the evaporation pressure within a certain range, and it can be manufactured at a lower cost, and the capacity control operation with high air conditioning comfort and high efficiency. Can be realized.
  • FIG. 7 is a schematic configuration diagram of a refrigeration cycle apparatus showing a third embodiment of the present invention, which is used for a room air conditioner as in the first and second embodiments.
  • the same reference numerals as those in FIGS. 1 and 5 denote the same or corresponding parts.
  • the difference from the first and second embodiments is that the suction pressure sensor 23 in the first embodiment and the blowout temperature provided in the vicinity of the ventilation passage outlet of the indoor heat exchanger 4 in the second embodiment. This is the point where the sensor 24 is removed.
  • the evaporator-side heat exchanger is operated under discharge superheat control so that the suction superheat degree is zero at the outlet, that is, the dryness is 1. Since the dryness is usually about 0.1 to 0.3 at the inlet of the evaporator-side heat exchanger, the heat exchanger has a distribution in which the dryness gradually increases from the inlet toward the outlet.
  • the amount of refrigerant circulating decreases, and the amount of refrigerant flowing out of the evaporator-side heat exchanger decreases relative to the amount of refrigerant flowing into the evaporator-side heat exchanger.
  • the evaporator side heat exchanger When the heat exchanger temperature sensor (14 or 15) is arranged near the center of the heat exchanger, the evaporator side heat exchanger temperature (evaporator temperature) Tev measured by this sensor is as shown in FIG. .
  • the evaporator temperature Tev gradually rises and gradually dries from the outlet side of the heat exchanger, so that the heat exchanger temperature sensor (14 or 15) is installed.
  • the measured temperature rises rapidly when the area around it is dry. For this reason, it becomes possible to grasp
  • the installation position of the heat exchanger temperature sensor 14 or 15 is set near the center of the heat exchanger in the present embodiment, the installation position may be appropriately selected so that the variation of the air conditioning capability can be appropriately allowed. .
  • a compressor rotation speed control routine in the refrigeration cycle apparatus of the third embodiment will be described with reference to FIG.
  • Rotational speed of the compressor 1 as described above, read the indoor temperature Tea in detected by the indoor temperature sensor 16 provided near the ventilation passage inlet of the indoor heat exchanger 4 (step 31), is set from the remote controller
  • a difference ⁇ Tea in from the set temperature (target indoor temperature) T * ea in is obtained (step 32), and the rotation speed of the compressor 1 is varied by the inverter 18 in accordance with this difference (steps 33 and 34).
  • the compressor rotational speed fz is controlled to become smaller.
  • step 35 the compressor rotational speed f z is the smaller than the rotational speed f z opt for the capacitive control operation starts, the compressor rotational speed is fixed to f z opt, from the difference between the indoor temperature and the indoor temperature target value
  • the determined initial duty ratio d is determined (steps 36 and 37), and the PWM capacity control operation for turning the solenoid valve 12 on and off is performed.
  • the timer of the control unit is turned ON and measurement of the elapsed time ⁇ 1 is started.
  • the measurement of the evaporator side heat exchanger temperature (evaporator temperature) Tev0 by the temperature sensor (14 or 15) of the heat exchanger on the evaporation side is started (step 61), and further the evaporator temperature at the start of the measurement. It is preset from Tev0 and the air temperature Tai or Tao measured by the indoor temperature sensor 16 or the outdoor temperature sensor 17 provided in the vicinity of the ventilation passage entrance of the indoor heat exchanger 4 or the outdoor heat exchanger 2 serving as an evaporator. The allowable deviation ⁇ Tev is calculated according to the table held as the control constant.
  • This allowable deviation ⁇ Tev is a temperature measurement position where the heat exchanger temperature sensor 14 or 15 is installed, after the heat exchanger dries (the degree of dryness of the refrigerant increases), resulting in a rapid temperature rise. (Step 68). Compared to the heat exchanger temperature Tev0 before the PWM control signal is turned ON, the PWM control signal remains ON until the measured heat exchanger temperature Tev exceeds the allowable deviation ⁇ Tev, and the evaporator side heat exchanger temperature Tev The measurement is repeated (steps 63 to 65).
  • the PWM control signal is turned OFF, the solenoid valve 12 is closed, and the timer is turned OFF. Then, the elapsed time measurement is finished, and ⁇ 1 is determined as the opening time.
  • the closing time ⁇ 2 is determined from this ⁇ 1 and the current duty ratio d, and the PWM capacity control operation is performed by this duty cycle (steps 66 and 67).
  • the opening degree control of the expansion valve 3 is controlled according to the same routine as the expansion valve opening degree control routine in the first embodiment shown in FIG.
  • the evaporation can be performed by setting the allowable range ⁇ Tev to an appropriate range. Even if there is no suction pressure sensor 23 (see FIG. 1) for measuring the pressure or a blowout temperature sensor 24 (see FIG. 5) for measuring the air blowing temperature into the room, the fluctuation of the evaporation pressure is kept within a certain range.
  • FIG. 10 is a longitudinal sectional view showing a scroll compressor as an example of a capacity control compressor used in the present invention
  • FIG. 11 is a diagram showing a normal operation of the scroll compressor shown in FIG. 10 (the solenoid valve 12 of the capacity adjusting mechanism is closed).
  • FIG. 12 is an enlarged cross-sectional view of the main part for explaining the flow of the refrigerant gas in the operation mode in the state
  • FIG. 12 is an operation in which the solenoid valve 12 of the capacity adjustment mechanism is in the open state during the bypass operation of the capacity control compressor shown in FIG. It is a principal part expanded sectional view explaining the flow of the refrigerant gas at the time of mode.
  • the scroll compressor 1 includes a fixed scroll 102 having a spiral wrap in a sealed case (chamber) 115 provided with a suction pipe 113 for sucking refrigerant gas and a discharge pipe 114 for discharging compressed refrigerant gas. And a compression mechanism portion composed of the orbiting scroll 101 having a spiral wrap meshing with the fixed scroll 102 is provided.
  • a motor 100 including a rotor 100a and a stator 100b is provided below the compression mechanism, and a crankshaft 106 serving as a rotation main shaft is integrally connected to the rotor 100a.
  • the crankshaft 106 is rotatably supported by a main bearing 105 a provided on the frame 105 and an auxiliary bearing 112 provided on the lower frame 111 below the sealed case 115.
  • An orbiting bearing 130 is provided on the back of the orbiting scroll 101, and an eccentric portion 106 a provided on the upper end side of the crankshaft 106 is inserted into the orbiting bearing 130.
  • Reference numeral 107 denotes an Oldham ring (rotation prevention member).
  • the spiral wraps provided on the respective end plates of the orbiting scroll 101 and the fixed scroll 102 are configured as asymmetric wraps having different winding angles, whereby the orbiting scroll 101 and the fixed scroll 102 are engaged with each other.
  • the two sealed chambers formed on the inner line side and the outer line side of the orbiting scroll wrap have asymmetric scroll shapes with different maximum sealed volumes.
  • compression chambers are formed on the outer line side and the inner line side of the wrap on the winding end side of the orbiting scroll 101, respectively.
  • the compression chamber formed on the outer line side and the compression chamber formed on the inner line side have different sizes and are formed with a phase shift of about 180 degrees with respect to the shaft rotation of the crankshaft 106. .
  • the discharge port 108 is opened near the center of the fixed scroll 102, and the winding end of the spiral wrap is about 180 degrees to the vicinity of the winding end of the spiral wrap of the orbiting scroll 101. It is extended. For this reason, when the spiral wraps of the orbiting scroll 101 and the fixed school 102 are combined to form a compression chamber, they are confined by the outer line side of the spiral scroll of the orbiting scroll 101 and the inner line side of the spiral wrap of the fixed scroll 102.
  • the size of the first compression chamber formed is different from the size of the second compression chamber formed by being confined by the inner side of the spiral wrap of the orbiting scroll 101 and the outer side of the spiral wrap of the fixed scroll 102.
  • the phase of the crankshaft 106 is shifted by about 180 degrees.
  • a release port 125 communicating with the compression chamber is formed on the outer peripheral side of the discharge port 108 in the fixed scroll 102, and a release valve 124, which is an overcompression prevention valve, is formed in the release port 125.
  • a discharge head cover 118 attached to the top plate (upper surface of the end plate) of the fixed scroll 102 forms a discharge head space 123 so as to cover the discharge port 108 and the release valve 124, and a through hole 119 provided at a predetermined location.
  • a discharge valve 121 ⁇ ⁇ ⁇ having a check valve action for opening or closing the valve is provided.
  • bypass pipe 11 guides the refrigerant gas in the discharge head space 123 to the outside of the sealed case 115, one end side is coupled to the discharge head cover 118, passes through the sealed case 115, and the other end side is outside the sealed case 115. Has been pulled out.
  • the other end of the bypass pipe 11 communicates with the suction pipe 113 for sucking refrigerant gas, and a solenoid valve 12 is provided in the middle of the bypass pipe 11.
  • the solenoid valve 12 is configured to be driven and controlled to an open state and a closed state by a pulse width adjustment (PWM) control signal described in each of the above-described embodiments.
  • PWM pulse width adjustment
  • the discharge head cover 118, the bypass pipe 11, and the solenoid valve 12 provide a bypass flow path for guiding the refrigerant gas in the discharge head space 123 from the bypass pipe 11 to the suction pipe 113 when the solenoid valve 12 is opened. Forming. Further, in the ultra-small capacity operation mode, the solenoid valve 12 is repeatedly operated between an open state and a closed state, and the presence or absence of use of the bypass flow path is repeated to act as a capacity adjustment mechanism for performing small capacity control.
  • the suction pipe 113 is for taking in the refrigerant gas of the refrigeration cycle, and is connected to the fixed scroll 102.
  • the lower end side of the crankshaft 106 in the sealed case 115 is an oil reservoir 116 that stores oil.
  • a flywheel 117 for stabilizing rotation is provided between the rotor 100 a and the auxiliary bearing 112 in the crankshaft 106.
  • the back pressure chamber (intermediate chamber) 109 formed by the fixed scroll 102, the orbiting scroll 101 ⁇ ⁇ , and the frame 105 oil supplied from the oil reservoir 116 is provided around the eccentric portion 106 a of the crankshaft 106. Guided through slewing bearing 130.
  • the back pressure chamber 109 is configured such that when the refrigerant gas in the oil is foamed and the pressure rises, the increased pressure is released to the suction side by a control valve (not shown) to maintain a predetermined pressure level. .
  • This suction side passes through a fixed outer peripheral groove provided on the outer periphery of the spiral body of the fixed scroll 102. Since this fixed outer peripheral groove reaches the refrigerant gas inlet, the fixed outer peripheral groove is always inhaled.
  • the discharge pressure acts on the central portion, and the intermediate pressure acts on the outer peripheral portion. For this reason, the orbiting scroll 101 is pressed against the fixed scroll 102 with an appropriate pressure, and the seal in the axial direction between the scroll wraps is maintained.
  • the refrigerant gas in the compression chamber is discharged through the release port 125 and the release valve 124 into the discharge head space. 123 is discharged.
  • the release valve 124 is closed, discharged from the discharge port 108 into the discharge head space 123, and further, the discharge valve 121 is pushed away from the through hole 119 to discharge chamber. 103 is discharged.
  • the refrigerant gas discharged into the discharge chamber 103 passes through the passage formed between the fixed scroll 102 and the frame 105 and the sealed case 115 and flows into the discharge space 104 where the motor 100 is provided.
  • the sealed case 115 has a high-pressure chamber structure in which a discharge pressure space is provided.
  • an inverter 18 that is a motor drive circuit for driving the motor 100 and a pulse width adjustment control signal for driving and controlling the open state and the closed state of the solenoid valve 12 are generated.
  • a control unit 20 as operation instruction control means for controlling operations of the inverter 18 and the solenoid drive circuit 12a according to operation instructions.
  • FIG. 11 shows the flow of the refrigerant gas in the first operation mode in which the solenoid valve 12 of the capacity adjustment mechanism provided in the scroll compressor is in the closed state.
  • the solenoid drive circuit 12a closes the solenoid valve 12 at the period ⁇ 2 of the falling edge of the rectangular wave of the pulse width adjustment control signal, and the inverter 18 drives the motor 100 to drive the rotor 100a. And the crankshaft 106 is rotated. Along with this, the orbiting scroll 101 starts the orbiting motion.
  • the first compression chamber and the second compression chamber formed by the engagement of the spiral bodies of the orbiting scroll 101 and the fixed scroll 102 move toward the center while reducing their volumes.
  • the refrigerant gas flowing in from the suction pipe 113 is compressed in the first compression chamber and the second compression chamber, and the high-pressure refrigerant gas is discharged from the discharge port 108 formed in the fixed scroll 102.
  • the ink is discharged into the head space 123.
  • the pressure in the compression chamber becomes higher than the pressure in the discharge head space 123 during the compression process, the refrigerant gas whose pressure has been increased through the release port 125 and the release valve 124 as described above enters the discharge head space 123. Discharged.
  • the release valve 124 indicates a valve plate portion attached to the tip of a coil spring 127 attached to the tip side of the holding portion 126, but a release valve mechanism including the holding portion 126 and the coil spring 127. The entire part is sometimes called a release valve.
  • the discharge valve 121 covering the through hole 119 of the discharge head cover 118 is pushed open, and the refrigerant gas is discharged into the discharge chamber 103. Discharged.
  • the solenoid valve 12 In the first operation mode, the solenoid valve 12 is closed and the refrigerant gas is allowed to flow to the refrigeration cycle side without using the bypass pipe 11, so it may be called a load operation.
  • FIG. 12 shows the flow of the refrigerant gas in the second operation mode in which the solenoid valve 12 of the capacity adjustment mechanism provided in the scroll compressor is in the open state.
  • the solenoid drive circuit 12a opens the solenoid valve 12 at the period ⁇ 1 of the rising edge of the rectangular wave of the pulse width adjustment control signal, and the inverter 18 drives the motor 100 to drive the rotor 100a and the crank.
  • the shaft 106 is rotated.
  • the orbiting scroll 101 starts the orbiting motion.
  • the first compression chamber and the second compression chamber formed by the engagement of the spiral bodies of the orbiting scroll 101 and the fixed scroll 102 are reduced in volume while being reduced in the center direction. Move to.
  • the pressure in the discharge head space 123 is lower than the pressure in the discharge chamber 103 and the discharge valve 121 covering the through hole 119 of the discharge head cover 118 is closed, so that the refrigerant gas is not discharged into the discharge chamber 103.
  • the pressure in the discharge head space 123 is higher than the pressure in the discharge head space 123. Therefore, the refrigerant gas is discharged into the discharge head space 123 through the release port 125 and the release valve 124.
  • the refrigerant gas in the compression chamber that has moved further to the center side than the release port 125 is discharged from the discharge port 108 into the discharge head space 123.
  • the refrigerant gas discharged into the discharge head space 123 flows to the suction pipe 113 through the bypass pipe 11 and the opened solenoid valve 12.
  • the solenoid valve 12 is opened, the refrigerant gas is returned from the bypass pipe 11 to the suction pipe 113 side, and the refrigerant gas is not discharged to the refrigeration cycle side. .
  • release port 125 and the release valve 124 are provided at a position where they are communicated with the compression chambers in all rotation angle regions. The reason is that the internal compression at the scroll wrap can be avoided and the compression operation at the unload operation becomes small.
  • the motor 100 is driven by the inverter 18 and the solenoid valve 12 is closed at the period ⁇ 2 of the rectangular wave falling section of the pulse width adjustment control signal from the solenoid drive circuit 12a.
  • the capacity control can be performed by switching between the load operation (first operation mode) and the unload operation (second operation mode) in which the solenoid valve 12 is opened at the period ⁇ 1 of the rectangular wave rising section. it can.
  • the capacity can be controlled by opening and closing the solenoid valve 12.
  • the high-speed rotation is slightly higher than the lower limit set value of the rotation speed driven by the motor.
  • the rotation speed control of the motor 100 is performed by the inverter 18, and when it is necessary to further reduce the capacity in the low speed rotation range below the predetermined set value, the small capacity control is performed. It is preferable to operate by changing the ratio of the load operation and the unload operation as an ultra-small capacity operation mode by operating the capacity adjusting mechanism (control of opening and closing of the bypass passage by a solenoid valve).
  • the capacity adjusting mechanism having a simple structure can efficiently perform the small capacity control even in the ultra-small capacity operation mode. That is, the compression operation in the ultra-small capacity control (ultra-small capacity operation mode) corresponding to the ultra-low speed operation below the lower limit set value of the rotation speed by the motor drive (frequency about 5 Hz in the drive signal to the motor 100). Can be executed without degrading the efficiency of motor drive, and an excellent scroll compressor capable of realizing a wide capacity control of 0 to 100% can be obtained. Further, since the capacity adjusting mechanism provided in the scroll compressor of this embodiment has a simple structure, the scroll compressor can be easily reduced in cost, size, weight and mass production.
  • the duty cycle which is the cycle of the switching time between the load operation and the unload operation, is controlled so that the deviation of the evaporation pressure is within a certain value.
  • an increase in loss due to an excessively short duty cycle can also be prevented, so that highly efficient operation can be realized, and excellent capacity control is possible with a wide range of 0 to 100% with high efficiency.
  • a refrigeration cycle apparatus with performance can be realized.
  • high-efficiency and wide-range capacity control can be realized with a simple configuration, so that the cost can be reduced.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Cet appareil à cycle de réfrigération est pourvu d'un compresseur (1), d'un échangeur thermique extérieur (2), d'un détendeur (3) dont le degré d'ouverture est réglable, et un échangeur thermique intérieur (4). L'appareil à cycle de réfrigération est également pourvu : d'un canal d'écoulement de dérivation (11) entraîne la dérivation d'un milieu de refroidissement, comprimé à l'aide du compresseur, vers le côté aspiration du compresseur ; d'une électrovanne (12), qui ouvre/ferme le canal d'écoulement de dérivation ; et d'une unité de réglage (20), qui règle la capacité grâce au réglage du volume d'écoulement du milieu de refroidissement à sortir vers le cycle de réfrigération depuis le compresseur par réglage d'une période où l'électrovanne est à l'état ouvert, et une période où l'électrovanne est à l'état fermé. L'unité de réglage effectue un réglage sur la base d'un rapport d'utilisation, qui est un rapport d'une période ouverte sur un cycle d'utilisation, c'est-à-dire, une somme d'une période où l'électrovanne est ouverte, et d'une période où l'électrovanne est fermée, et lorsque, à l'état où l'électrovanne est à l'état ouvert, la pression d'aspiration du compresseur devient supérieure ou égale à un écart admissible par rapport à la pression d'aspiration avant l'ouverture de l'électrovanne, l'unité de réglage règle l'électrovanne pour qu'elle soit à l'état fermé, et détermine la période fermée sur la base du rapport d'utilisation.
PCT/JP2011/053839 2011-02-22 2011-02-22 Appareil à cycle de réfrigération WO2012114454A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2011/053839 WO2012114454A1 (fr) 2011-02-22 2011-02-22 Appareil à cycle de réfrigération
JP2013500750A JP5965895B2 (ja) 2011-02-22 2011-02-22 冷凍サイクル装置
EP20110859245 EP2679930A4 (fr) 2011-02-22 2011-02-22 Appareil à cycle de réfrigération
CN201180067090.0A CN103380334B (zh) 2011-02-22 2011-02-22 冷冻循环装置

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CN103994616A (zh) * 2013-02-18 2014-08-20 力博特公司 涡旋式压缩机差压控制技术
US9476624B2 (en) 2013-02-18 2016-10-25 Liebert Corporation Scroll compressor differential pressure control during compressor shutdown transitions
JPWO2015004747A1 (ja) * 2013-07-10 2017-02-23 三菱電機株式会社 冷凍サイクル装置
US9829233B2 (en) 2013-02-18 2017-11-28 Liebert Corporation Scroll compressor differential pressure control during compressor startup transitions
WO2023115919A1 (fr) * 2021-12-23 2023-06-29 青岛海尔空调器有限总公司 Procédé et appareil de réglage de fluide frigorigène de climatiseur, et climatiseur et support de stockage

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JP6767841B2 (ja) * 2016-10-14 2020-10-14 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
JP2019020080A (ja) * 2017-07-20 2019-02-07 三菱重工サーマルシステムズ株式会社 空気調和装置及びその運転方法
DE102017123560A1 (de) * 2017-10-10 2019-04-11 Eut Edelstahl Umformtechnik Gmbh Selbstregulierende Einstellvorrichtung für ein Durchflussregelventil, ein Temperierungssystem als auch eine Verteilervorrichtung mit derselben, sowie Verfahren hierzu
KR102052341B1 (ko) * 2017-11-29 2019-12-04 (주)퓨처시스텍 다양한 냉매에 적용되는 차량용 냉동 시스템을 위한 전자 팽창 제어 밸브 장치
WO2019239587A1 (fr) * 2018-06-15 2019-12-19 三菱電機株式会社 Dispositif à cycle frigorifique
JP7332882B2 (ja) * 2019-09-30 2023-08-24 ダイキン工業株式会社 冷凍サイクル装置及び四方弁
CN113670969A (zh) * 2021-09-09 2021-11-19 中国矿业大学(北京) 一种冻融循环模拟装置

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CN103994616A (zh) * 2013-02-18 2014-08-20 力博特公司 涡旋式压缩机差压控制技术
EP2767780A3 (fr) * 2013-02-18 2015-11-18 Liebert Corporation Techniques de régulation de pression différentielle de compresseur à spirales
US9476624B2 (en) 2013-02-18 2016-10-25 Liebert Corporation Scroll compressor differential pressure control during compressor shutdown transitions
US9477235B2 (en) 2013-02-18 2016-10-25 Liebert Corporation Methods of controlling a cooling system based on pressure differences across a scroll compressor
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JP5965895B2 (ja) 2016-08-10
JPWO2012114454A1 (ja) 2014-07-07
CN103380334B (zh) 2016-03-16
EP2679930A1 (fr) 2014-01-01
EP2679930A4 (fr) 2015-04-29
CN103380334A (zh) 2013-10-30

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